WO2004090367A1 - フローティングキャリパ型ディスクブレーキ - Google Patents
フローティングキャリパ型ディスクブレーキ Download PDFInfo
- Publication number
- WO2004090367A1 WO2004090367A1 PCT/JP2004/004771 JP2004004771W WO2004090367A1 WO 2004090367 A1 WO2004090367 A1 WO 2004090367A1 JP 2004004771 W JP2004004771 W JP 2004004771W WO 2004090367 A1 WO2004090367 A1 WO 2004090367A1
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- Prior art keywords
- rotor
- diameter portion
- diameter
- pressed
- guide
- Prior art date
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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
- F16D55/2265—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 the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
- F16D55/227—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 the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
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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
- F16D55/2265—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 the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
- F16D55/22655—Constructional details of guide pins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/0006—Noise or vibration control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
- F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
- F16D65/095—Pivots or supporting members therefor
Definitions
- the floating caliper type disk brake according to the present invention is used for braking an automobile, and the present invention prevents uneven wear of a pad incorporated in such a disk brake and uneven wear in a radial direction of a rotor. It is intended. Background technology>
- FIGS. 21 and 22 show such a floating caliper type distor brake described in Patent Document 1.
- FIG. This floating caliper type disc brake displaces the caliper 2 with respect to the rotor 1 which rotates together with wheels (not shown) during braking.
- the support 3 provided adjacent to one side of the rotor 1 is fixed to a vehicle body (not shown) via the mounting holes 4 and 4.
- the support 3 supports the caliper 2 so as to be displaceable in the axial direction of the rotor 1.
- a pair of guide pins 5, 5 are provided at both ends of the caliper 2 with respect to the rotation direction of the rotor 1, and a pair of guide holes 6, 6 are also provided at both ends of the support 3, respectively. It is provided parallel to the central axis of 1.
- the two guide pins 5 are slidably inserted in the two guide holes 6 in the axial direction.
- Dust-proof boots 7 are provided between the outer peripheral surfaces of the base ends of the guide pins 5 and the openings of the guide holes 6.
- the inner diameters of the two guide holes 6, 6 may be different from each other, and accordingly, the outer diameters of the two guide pins 5, 5 may be different from each other.
- both the positions are separated from each other in the circumferential direction of the rotor 1.
- Both the reciprocating side and the revolving side engaging portions 8 and 9 are provided.
- Each of the engaging portions 8 and 9 is bent in a U-shape so as to straddle the outer peripheral portion of the rotor 1 in the vertical direction in FIG. 21.
- Pads 10 are provided on both of the engaging portions 8 and 9.
- Both ends of the back plates 11, 11 constituting a, 10 b are slidably engaged in the axial direction of the rotor 1.
- the caliper 2 having a cylinder portion 12 and a claw portion 13 connected by a bridge portion straddling the pads 10a and 10b is arranged.
- a piston 10 that presses the pad 10a on the inner side (the lower side in FIG. 21 in the width direction of the vehicle) against the rotor 1 is fluid-tightly attached to the cylinder section 12 of the caliper 2. It is fitted in.
- pressurized oil is fed into the cylinder section 12, and the piston 14 is used to place the lining 15 of the pad 10 a on the inner side on the inner surface of the rotor 1. Press from below to above. Then, as a reaction of this pressing force, the caliper 2 is displaced downward in FIG. 21 based on the sliding between the two guide pins 5, 5 and the two guide holes 6, 6, and the claw portion 13 presses the lining 15 of the pad 10b on the auta side (outside in the width direction of the vehicle and on the upper side in Fig. 21) against the outer surface of the rotor 1. As a result, the rotor 1 is strongly clamped from both outer side surfaces, and braking is performed.
- a shim plate is provided between the above-mentioned surfaces (or between some surfaces) to reduce noise called noise generated during braking and judder. It is possible that the torque transmitted from the rotor 2 to the pads 10a and 10b due to braking and transmitted to the carrier 3 may be reduced.
- Patent Documents 11 to 12 As prior art documents related to the present invention, there are Patent Documents 11 to 12 in addition to Patent Documents 1 to 10.
- Patent Document 1 JP-A-55-1 23029
- the force F 2 , F in the same direction as the drag force is applied to the inner surface of the claw portion 13 of the caliper 2 (lower surface of FIG. 23) and the tip surface of the piston 14 (upper surface of FIG. 23).
- 3 ⁇ Add from the back plates 11 and 11 of each pad 10a and 10b.
- the caliper 2 tends to rotate clockwise in the figure around the engaging portion o between the guide hole 6 and the guide pin 5 on the reciprocating side (left side in FIG. 23) of the rotor 1. There is. Then, on the basis of the forces F 2 and F 3 , moments Ml and M 2 around the engagement portion o may act on the claw 13 and the piston 14, respectively.
- the length L i between the inner surface of the claw portion 13 and the contact portion of the back plate 11 of the pad 10 b on the auter side and the engaging portion o is equal to the tip surface of the piston 14. greater than the length L 2 between the Pi In'na side of the pad 1 0 back plate 1 1 of the contact portion a and the engaging portion o (1 ⁇ > L 2) . Therefore, the moment I ⁇ , the moment Mi acting on the claw portion 1 3 of the M 2 is greater than the moment M 2 acting on the piston 1 4 (I ⁇ > M 2 ).
- the inner surface of the claw portion 13 and the tip surface of the biston 14 are connected to the back plates 11 a and 10 b of the pads 10 a and 10 b. Is in direct contact with 1 1. For this reason, the frictional force acting between each of the back plates 11 and 11 and the inner surface of the claw portion 13 and the distal end surface of the piston 14 increases. Therefore, the moment Myuarufa, Micromax 2 is increased, the caliper 2 is (and body tilt) larger inclination to the plane direction of the rotor 1 easily. When the caliper 2 is tilted in this manner, the amount of wear of the linings 15 and 15 of the pads 10a and 10b becomes uneven with respect to the rotation direction of the rotor 1.
- the wear on the outgoing side of rotor 1 advances compared to the wear on the inflow side of rotor 1 (the amount of wear increases).
- the wear on the inflow side of the rotor 1 progresses more than the wear on the outflow side of the rotor 1.
- uneven wear occurs in the linings 11 and 11 of the pads 10a and 10b.
- the back surface of the back plate 11 of the inner pad 10a and the tip surface of the piston 14 are different from each other.
- the shim plate is sandwiched only between the back side of the back plate 11 of the pad 10b on the outer side and the inner surface of the claw portion 13. Therefore, by reducing the frictional force acting between some of these surfaces, the force F 2 (or F 3 ) applied to the claw portion 13 or the piston 14 is reduced, and the moment is reduced. It is possible that one of the moments M 2 and M 2 can be reduced.
- the distance between the back surface of the back plate 11 of the inner pad 10a and the tip surface of the biston 14 Also, no shim plate is sandwiched between both the back surface of the back plate 11 of the pad 10b on the end side and the inner surface of the claw portion 13. For this reason, the other of the moments M i and M 2 remains large, and the effect of suppressing the inclination of the caliper 2 during braking is low.
- the outer shim plates are locked to the back plates 11 and 11 so as to cover the adjacent inner shim plates, and the rotors of the outer shim plates with respect to the inner shim plates are fixed. Relative displacement within a predetermined range in the rotation direction 1 is enabled. For this reason, if the frictional force acting between each inner shim plate and each outer shim plate is reduced, it is possible that the inclination of the caliper 2 during braking can be suppressed.
- the range in which the outer shim plates can be displaced with respect to the inner shim plates is limited, and the effect of preventing the inclination of the caliper 2 during braking cannot be effectively obtained.
- the rotor 1 When this temperature rises, the rotor 1 is affected by the offset in the axial direction between the mounting portion for the wheel provided on the inner diameter side and the sliding portion between the pads 10a and 10b provided on the outer diameter side. As a result, at the time of high-temperature braking and immediately after the braking, the sliding portion provided on the outer peripheral portion of the rotor 1 is deformed in the axial direction (specifically, the outer side), for example, as shown by a chain line in FIG.
- Experiments show that the part of the rotor 1 sandwiched between the pair of pads 10a and 10b during braking inclines with respect to a virtual plane existing at right angles to the center of rotation. Has been confirmed.
- the two linings 15 and 15 are brought into contact with both sides of the rotor 1, and the rotor 1 is unevenly worn during high-temperature braking or high-temperature idling.
- the outer wear in the radial direction is more advanced than the inner wear (the amount of wear increases)
- the inner wear is more advanced than the outer wear, regardless of the direction of uneven wear, the rotor 1 is not deformed and both sides of the rotor 1 and the two rings
- the durability of both pads 10 a and 10 b including the rotor 1 and the linings 15 and 15 is reduced. Not good.
- the floating caliper type disk brake of the present invention has been invented to solve such a disadvantage.
- the floating caliper disc brake of the present invention includes a support, a pair of pads, a caliper, a claw portion, and a piston, similarly to the above-mentioned conventionally known floating caliper disc brake.
- the support is fixed to the vehicle body adjacent to the rotor that rotates with the wheels.
- the pair of pads are supported on both sides of the rotor so as to be slidable in the axial direction.
- the above-mentioned carrier has a plurality of guide holes provided in the support and each of these guide holes
- the rotor is displaceably supported in the axial direction of the rotor by a plurality of guide pins that fit into the holes.
- the claw portion of the claw portion and the piston is provided on one of the bridge portions of the carrier that straddles the rotor, and the biston is fitted on the other.
- the pair of pads is pressed against both side surfaces of the rotor to perform braking.
- the back plates of the pair of pads are respectively covered on the surface (rear surface) on the side opposite to the rotor.
- the pressing shim plate is locked to the claw portion and the pressing side of the piston, respectively, and the pressed shim plate and each pressing shim plate slide. They are freely matched.
- the pressed shim plate is fixed or locked on the opposite side (rear side) of the back plate of the pair of pads on the rotor side.
- a pressing shim plate is fixed or locked to the claw portion and the pressing side of the biston, respectively (for example, fixed to the claw portion and the pressing side of the piston by bonding, respectively).
- the pressing side shim plate is slidably butted against.
- FIG. 1 is a view showing a first example of a reference example of the present invention with a part thereof cut away, as viewed from an outer diameter side of a floating caliper type disc brake.
- FIG. 2 is a half side view showing three examples of the shape of the guide pin.
- FIG. 3 is a schematic diagram showing a state in which the carrier is oscillatingly displaced as the rotor is deformed, as viewed in the direction of AA in FIG.
- FIG. 4 is a view similar to FIG. 1, showing a second example of the reference example of the present invention.
- FIG. 5 is a view showing Example 1 of the present invention and corresponding to a section taken along line AA of FIG.
- FIG. 6 is an exploded view of part B of FIG.
- FIG. 7 is an exploded view of the portion C.
- FIG. 8 shows the first embodiment, in which the guide pin and the guide hole can be freely displaced only in the axial direction.
- FIG. 7 is a cross-sectional view for describing an effect obtained by engaging with the first embodiment.
- FIG. 9 is an enlarged cross-sectional view corresponding to a portion D in FIG. 8 for explaining another effect obtained by the first embodiment.
- FIG. 10 is a graph showing the results of an experiment conducted to confirm the effects obtained by the present invention, as a relationship between the hydraulic pressure (braking fluid pressure) of the pressure oil fed into the cylinder during braking and the inclination angle of the carrier. It is.
- FIG. 11 is an exploded perspective view showing a piston, an inner pad, and an inner-side pressing side and a pressed-side shim plate constituting Embodiment 2 of the present invention.
- FIG. 12 is an exploded perspective view showing the claw portion, the auta pad, and the shim plates on the pressing side and the pressed side on the auta side.
- FIG. 13 is a diagram illustrating an engagement state between the claw portion and the pressing shim plate on the autter side according to the second embodiment.
- FIG. 14 is a view similar to FIG. 12, showing a third embodiment of the present invention.
- FIG. 15 is a view similar to FIG. 12 showing the fourth embodiment.
- FIG. 16 is a view similar to FIG. 13, showing another shape of the locking projection formed on the pressing-side shim plate.
- FIG. 17 is a view similar to FIG. 11, illustrating Example 5 of the present invention.
- FIG. 18 is a view similar to FIG. 11, illustrating the sixth embodiment.
- FIG. 19 is a schematic sectional view showing a seventh embodiment of the present invention with a part thereof omitted.
- FIG. 20 is an enlarged cross-sectional view corresponding to a portion E in FIG. 19, showing a state in which the claw portion is displaced with respect to the pressed shim plate and the autter pad on the autter side in the seventh embodiment.
- FIG. 21 is a partially cutaway view showing an example of the conventional structure when viewed from the same direction as FIG.
- FIG. 22 is a sectional view taken along line FF of FIG.
- FIG. 23 is a cross-sectional view for explaining the moment acting on the claw portion and the piston of the caliber during braking.
- FIG. 24 is a partial cross-sectional view showing a state in which the rotor is deformed due to a temperature rise accompanying braking.
- symbol in a figure 1 is a rotor, 2, 2a is a caliper, 3, 3a is a support, 4 is a mounting hole, 5, 5a, 5b, 5c, 5d, 5e, 5a 'is a guide pin, 6, 6a, 6a' is a guide hole, 7, 7a, 7a, is Boots, 8 and 8a are retraction-side engagement parts, 9 and 9a are retraction-side engagement parts, 10a and 10b are pads, 11 is a back plate, 12 is a cylinder, 13 , 13 a is a claw, 14 is a piston, 15 is a lining, 16 is an arm, 17 is a through hole, 18 is a ponolet, 19 is a screw hole, 20 is a screw hole, 20 a, 20 b, 20 c, 20 d, 20 a ′ is a large diameter portion, 21 is an inclined surface portion, 22 is a cylindrical surface portion, 23 a, 23 b, 23 a support,
- a first diameter portion having a predetermined gap or more between a guide hole in which the guide pin is fitted at both ends in the axial direction of the rotor, and at least one guide pin is A second diameter portion having a larger diameter than the first diameter portion is provided at the axial middle portion.
- a plurality of guide pins for supporting the caliper with respect to the support have a predetermined gap or more between the guide holes at both ends in the axial direction and at least one of the guide pins. It swings around an engaging portion between the outer peripheral surface of the second diameter portion formed on the pin and the inner peripheral surface of the guide hole into which the guide pin is inserted. For this reason, even when the rotor is deformed in the axial direction due to a temperature rise due to braking, the inner surface of the claw portion and the tip surface of the piston can be parallel to both side surfaces of the rotor.
- the linings of the pair of pads are pressed almost uniformly from the inner peripheral edge to the outer peripheral edge against both side surfaces of the rotor, and the rotor is unevenly worn due to displacement of the rotor in the inclination direction. That is, it is possible to prevent the wear amount of the rotor from being biased in the radial direction.
- the moment acting on the caliper as a whole based on the force applied to the caliper from the rotor at the time of braking can be made smaller, and the inclination of the caliper with respect to the plane direction of the rotor can be reduced. It can be suppressed more effectively. As a result, the occurrence of uneven wear on each pad can be more effectively suppressed, and the generation of noise and judder called squeal during braking can be more effectively suppressed.
- the floating caliper type disc brake of this reference example has a support 3a, a pair of pads 10a and 10b, a caliper 2a, a claw portion 13a, and a piston 14 (see FIGS. 21 to 2). 2).
- the support 3a is fixed to the vehicle body adjacent to the rotor 1 which rotates with the wheels.
- the pads 10a and 10b are arranged on both sides of the rotor 1 while being supported by the support 3a.
- the support 3a is supported on the vehicle body, the support 3a supports the pads 10a and 10b, and the claw 13a and the piston 14 are used for the support 3a.
- the caliper 2a is supported by the support 3a so as to be capable of displacing the rotor 1 in the axial direction (vertical direction in FIG. 1). For this reason, only the inner side of the support 3a is opened inside the inflow side engagement portion 8a and the outflow side engagement portion 9a provided at both ends of the rotor 1 in the circumferential direction of the rotor 1.
- the holes 6a, 6a are formed in the axial direction of the rotor 1, respectively.
- guide pins 5a and 5a are provided at the tips of a pair of arms 16 and 16 formed in a part (inner end) of the carrier 2a so as to protrude in the circumferential direction of the rotor 1.
- the base end of a is supported and fixed.
- the bolts 18, 18 penetrating from the inner side through the through holes 17, 17 formed at the distal end portions of the both arm portions 16, 16 are connected to the two guide pins 5 a, 5 a ′.
- the screw holes 19, 19 opened in the base end face and tightening further the base ends of the guide pins 5a, 5a are attached to the distal ends of the arms 16, 16 above.
- the support is fixed.
- such a guide pin 5 a N 5 a ′ is inserted into the both guide holes 6 a, 6 a, through the opening on the inner side so that the caliper 2 a supports the support 3 a. Further, the rotor 1 is supported so as to be displaceable in the axial direction (vertical direction in FIG. 1).
- the two guide pins 5a, 5a are solid bodies made of metal, and the two guide pins 5a, 5a have a large diameter whose outer diameter is larger than the outer diameter of both ends at one axially intermediate portion.
- the large diameter portions 20 a, 20 a, in these two guide holes 6 a, 6 a ′ are slightly loose in the radial direction and freely displace in the axial direction. It can be fitted.
- the both guide pins 5 a, 5 a 'rest in the large diameter portion of the 20 a, 2 0 is a portion deviated in the axial direction from a small-diameter portion 28 a, 28 b, 28 a ' N 28
- the outer diameter of each of the small diameter portions 28a, 28b, 28a, 28b ' is made slightly different depending on the size of the brake size and the easiness of the deformation of the rotor 1.
- the two guide pins 5a and 5a each having the large-diameter portion 20a, 20a 'at the axial middle portion, FIG. 1 and FIG. Mother Kaizumi
- the shape is trapezoidal.
- the axial length L 22 of the cylindrical surface portion 22 except the inclined surface portion 2 1, 21 at both ends, 10 and about 2 Oram, the cars Of the guide pins 5a, 5a, the length L5a (for example, about 50 to 8 Oram) of the portion inserted into both the guide holes 6a, 6a is sufficiently (for example, 14 to 14). below) is shorter (L 22 "L 5 J.
- an elastic material such as rubber is provided at two axial positions of the guide pins 5a, 5a, that is, at a portion sandwiching the large-diameter portions 20a, 20a 'between the distal end portion and the base end portion.
- the rings 23 a s 23 b, 23 a ′ and 23 b ′ are fitted outside. Of these rings 23a, 23b, 23a ', and 23b', the rings 23a and 23a 'that are externally fitted to the tips of the guide pins 5a and 5a' are simply cylindrical.
- the two guide pins 5a, 5a are externally fitted to and supported by small-diameter locking steps 24 formed at the distal ends of the guide pins 5a.
- the rings 23b, 23b 'fitted to the base ends of the guide pins 5a, 5a' are formed on the outer peripheral surfaces of the base ends of the guide pins 5a, 5a and the two ends. It is formed integrally with the dustproof boots 7a, 7a 'provided between the guide holes 6a, 6a, and the opening. Regarding any ring 23a, 23b, 23a ', 23b', between the outer peripheral surface of both guide pins 5a, 5a 'and the inner peripheral surface of both holes 6a 6a' In addition, it is provided in a radially compressed state.
- the floating caliper type disc brake of the present embodiment configured as described above has a structure in which the caliper 2a is provided with respect to the support 3a, and the large diameter portions 20a, 20a of the two guide pins 5a, 5a. , And the inner peripheral surface of both the guide holes 6a, 6a, can be swung about the engaging portion. Therefore, even if the rotor 1 is deformed in the axial direction due to the temperature rise due to braking, as indicated by the dashed line in FIG. 24, the inner surface of the claw portion 13a and the screw 14 The tip surface can be parallel to both side surfaces of the rotor 1.
- both pads 10a When the linings 15 and 15 of 10b are pressed against both side surfaces of the rotor 1, the inner surface of the claw portion 13a and the tip end surface of the piston 14 A force acts in a direction parallel to both side surfaces of 1. Then, based on this force, the caliper 2a swings with respect to the support 3a as described above. At this time, each of the rings 23a, 23b, 23a and 23b 'is connected to the outer peripheral surface of the two guide pins 5a and 5a' and the two guide holes 6a and 6a '.
- This swing is caused by compressing a part of the pair of rings 23a and 23b in the circumferential direction around the large-diameter portion 20a which is a part of the guide pin 5a.
- the angle ⁇ 2 is possible until the distal end portion or the proximal end portion of the above-mentioned portion comes into contact with the inner peripheral surface of the inner hole 6a.
- the swingable angle of theta 2 can be adjusted by changing the outer diameter of the portion deviated in the axial direction from the large-diameter portion 2 0 a in the remainder of the draft ⁇ pin 5 a.
- the inside of the claw portion 13a can be adjusted.
- the linings 11, 11 of both pads 10 a, 10 b can be pressed uniformly on both side surfaces of the rotor 1 by making the side surface and the tip surface of the piston follow the inclination of the rotor 1.
- the shape of the guide pins 5a and 5a ' is slightly changed so that the caliper 2a is slightly different from the support 3a. It is supported so that it can swing freely.
- the two guide pins 5a and 5a ' are solid bodies entirely made of a hard metal such as stainless steel, and have sufficient strength and rigidity. Therefore, the above two guide pins 5a and 5a '
- the above-mentioned carrier and the support strength of 2 a for the support 3 a can be sufficiently secured.
- the large-diameter portions 20a and 20a 'of the guide pins 5a and 5a' are radially fitted into the inner holes 6a and 6a '. .
- each ring 2 3 a, 2 3 b, 2 3 a 's 2 3 b force the large diameter portion 20 a, 20 a' to positions sandwiching the both sides in the axial direction, it is ⁇ compressed in the radial direction It is provided in the state where it was set. Therefore, the caliper 2a is stabilized with respect to the support 3a when the brake is not applied, and the rattle sound generated when the brake is not activated can be reduced.
- the shape of the large-diameter portion of the guide pin to provide the above function to the floating caliper type disc brake is the same as that shown in Figs. 2 (B) and 2 (C).
- the guide pin 5b shown in (B) has a cylindrical large-diameter portion 20b formed in the middle part in the axial direction, and a pair of curved surfaces whose respective generatrix is a convex arc having a large radius of curvature.
- the part sandwiched from both sides in the axial direction and inserted into the guide hole has a beer barrel shape.
- the guide pin 5c shown in (C) is made of a metal or hard synthetic resin and a cylindrical sleep 25 is externally fixed to an intermediate portion in the axial direction, and the outer peripheral surface of the sleep 25 is large in diameter. Part 20c. Further, although not shown in the drawings, the portion where the generatrix is a straight line may be omitted from the shape of FIG. 2 (B), and the entire large diameter portion may be a curved surface whose generatrix is a convex arc.
- FIG. 4 shows a second example of the reference example of the present invention.
- the large-diameter portion 20a is formed only on the guide pin 5a on one (retracting side).
- rings 23a, 23b ' are provided between the two positions of the inner peripheral surface of the guide hole 6a' and the two positions of the outer peripheral surface of the other guide pin 5d, and when braking is not performed. This prevents the other guide pin 5 d from rattling inside the guide hole 6 a ′.
- a pair of small-diameter portion 2 8 a 's 2 8 b one between portion in the axial direction intermediate portion of the outer peripheral surface of the guide pin 5 d is a fourth diameter portion according to claim 4 , The extended small diameter portion 29.
- FIGS. a first embodiment of the present invention shown in FIGS.
- a pair of pads 10a, 10b and a pair of pawls 13a and a piston 14 are provided.
- a shim plate is provided to apply a friction between the linings 15 and 15 of the pair of pads 10a and 10b and both sides of the rotor 1 during braking.
- the applied braking torque is hardly transmitted to the caliper 2a. That is, the sliding property between the shim plates during braking is improved so that a large braking torque is not input to the caliper 2a.
- the behavior of the caliper 2a becomes unstable when a large braking torque is transmitted to the caliper 2a. Easy to be.
- the guide pin 5 a, 5 a 'N 5 b, 5 outer circumferential surface and the guide hole of the c 6 a, 6 a' for a narrow contact area see FIG. 1-3
- the following configuration makes it difficult for the braking torque applied to both pads 10a and 10b to be transmitted to the caliper 2a during braking.
- pressed side shim plates 26a and 26b are respectively attached to the back surfaces of the back plates 11 and 11 constituting the pads 10a and 10b, respectively.
- the pressing shim plates 27a, 2a are provided on the tip surface of the biston 14 built into the inner side of the caliper 2a and the inner surface of the claw 13a provided at the outer end of the caliper 2a. 7b is attached to each.
- One side of each of the pressed side shim plates 26a and 26b and one side of each of the pressed side shim plates 27a and 27b are slidably butted against each other.
- Each of the shim plates 26a, 26b, 27a, 27b is made of a metal plate such as a stainless steel plate, and has an elastic lock for locking each to a member to be attached. A piece is provided.
- the shape of each of the shim plates 26a, 26b, 27a, and 27b, and the mounting structure to the mating member are described in Patent Documents 4 to 10 described above. For this reason, it is the same as a conventionally known shim plate, and detailed illustration and description are omitted.
- the flat portions of 7a abut each other so that they can be displaced in the plane direction.
- the flat plate portions are pressed against each other so that they can be displaced in the plane direction.
- a darryse is applied between the flat plate portions butted against each other, or a polyamide resin, a polytetrafluoroethylene resin, or the like is applied to one or both butted surfaces of the flat plate portions.
- a film made of a material with low friction coefficient is formed.
- the braking torque applied to both pads 10a, 10b during braking is provided. Can hardly be transmitted to the caliper 2a. That is, the braking torque applied to the pads 10a and 10b during braking is supported by the support 3a (see FIG. 1) that supports the pads 10a and 10b, but a part of the braking torque is applied. It is transmitted to the caliper 2a via the piston 14 and the claw portion 13a.
- the both ends in the axial direction of the guide pin 5 a, 5 a 'N 5 b, 5 c force the rotor 1, the guide pin 5 a, 5 a one, 5 b, 5 a small-diameter portion 28a, 28b, 28a ', 28b' having a predetermined gap or more between the guide holes 6a, 6a ' 5a, 5a ', 5b, 5c
- the moment acting on the caliper 2a as a whole based on the force applied to the caliper 2a from the rotor 1 during braking can be reduced as a whole, and the caliper 2a can be inclined with respect to the surface direction of the rotor 1. , Can be suppressed more effectively. As a result, it is possible to more effectively suppress the occurrence of uneven wear in the linings 15 and 15 of the pads 10a and 10b, and to generate noise and judder called braking noise. Can be suppressed more effectively.
- FIG. 8 shows each of the guide pins 5 and 5 and the guide holes 6 and 6 fitted with the respective guide pins 5 and 5, as in the case of the conventional structure shown in FIGS.
- This shows a structure in which only the axial displacement is freely engaged with each other. Then, between the inner surface of the claw portion 13a of the caliper 2a and the back surface of the back plate 11 of the pad 10b on the auta side, and between the tip end surface of the piston 14 and the pad 10a on the inner side.
- a pressed-side shim plate 26a, 26b and a pressed-side shim plate 27a, 27b which are the same as in the present embodiment, are respectively provided between the back plate 11 and the back surface of the back plate 11. As a result, it is locked to the mating member to be attached.
- Such a structure shown in FIG. 8 also belongs to the technical scope of the present invention. In the case of the structure shown in FIG. 8 as described above, the frictional force acting between one side of the shim plates 26a, 26b, 27a, and 27b on both the pressed and pressed sides is reduced. It can be made small enough.
- the moment ⁇ 2 which is based on the force acting on the pawl 13 a and the piston 14 from the rotor 1 via the pads 10 a and 10 b during braking, can be sufficiently reduced. Therefore, the caliper 2a can be hardly inclined with respect to the surface direction of the rotor 1 during braking, and the occurrence of uneven wear on the pads 10a and 10 can be suppressed.
- the moment acting on the claw 13a is large due to the large length between the center of inclination and the claw 13a. 'Is larger than the moment M 2 ' acting on the piston 14.
- both the pressed side and the pressed side shim plates 26b and 27b are provided between the inner surface of the claw portion 13a and the back surface of the back plate 11 of the pad 10b on the auter side.
- the effect of saying that the inclination of the caliper 2a can be suppressed is that the tip of the piston 14 and the back plate 11a of the pad 10a on the female side This is more remarkable than the effect obtained by providing both the pressed side and the pressed side shim plates 26a and 27a between the back side and the back side.
- the pressed shim plates 26a and 26b are respectively attached to the back plates 11 and 11 of the pads 1a and 10b, and the claws are provided. Since the pressing side shim plates 27a and 27b are respectively locked to the parts 13a and the bistons 14 by locking pieces, both the pressed side and the pressing side shim plates 26a, The relative displacement in the plane direction between 26 b, 27 a, and 27 b is not restricted.
- each guide pin 5 e has a guide hole 6 a in which the guide pin 5 e is fitted at both ends in the axial direction of the rotor 1.
- the small diameter portions 28a and 28b are provided with a small-diameter portion 28a and 28b having a predetermined gap or more between them, and each of the above-mentioned guide pins 5e force is provided at an intermediate portion in the axial direction of the rotor 1. It has a large-diameter portion 20 d with a larger diameter than that. Therefore, with respect to the axial direction of the rotor 1, the inner side surface of the claw portion 13a and the sliding contact portion of the pressing shim plate 27b on the autter side, the tip end surface of the piston 14 and the pressing side shim plate on the inner side.
- An engaging portion o between the guide pin 5e and the guide hole 6a can be located between the sliding contact portion 27a and the sliding contact portion 27a.
- This engaging portion o is based on the force applied to the claw portion 13a from the rotor 1 via the pad 10b on the autter side and the shim plates 26b, 27b on the pressed side and the pressing side during braking.
- the center of rotation of the moment IV ⁇ acting on the claw 13a Pads 10a on the inner side from the rotor 1 and the shims 26a on the pressed side and the pressed side
- the two moments, M 2 are in opposite directions to each other and act so as to cancel each other out during braking, so that the moment acting on the caliper 2 a as a whole can be made smaller, and the effect of preventing the inclination of the caliper 2 a is obtained. Can be obtained more effectively. As a result, it is possible to more effectively suppress the occurrence of uneven wear in the linings 15 and 15 of the pads 10a and 10b, and to reduce noise and judder called braking noise. It can be suppressed more effectively.
- FIG. 9 shows the moment M i acting on the caliper 2 a when the entire generatrix of the large-diameter portion 20 d formed at the axially intermediate portion of the guide pin 5 e is a convex arc. M 2 and its center of rotation o are shown. However, as shown in FIGS. 2 (A) to 2 (C), the large-diameter portion of the guide pin 5e can be used even when the bus shape of the intermediate portion is straight.
- each guide pin 5 e has a small-diameter portion 28 a having a predetermined gap or more between the guide hole 6 a fitted with the guide pin 5 e at both ends in the axial direction of the rotor 1.
- a large-diameter portion 20d which is larger than the small-diameter portions 28a and 28b, at the intermediate portion of each of the guide pins 5e in the axial direction of the rotor 1. According to this, the moment acting on the caliper 2a as a whole during braking can be made smaller, and the effect of preventing the inclination of the caliper can be obtained more effectively.
- Comparative product 1 has the conventional structure shown in FIGS. 21 to 22 described above, and has shims attached only to the backs of the backs 11 and 11 of the pads 10a and 10b. No shim plate is attached to the inner surface of the claw portion 13a and the tip surface of the biston 14.
- Comparative product 2 has the same structure as that described in Patent Document 7. That is, the back plate of the inner pad 10a
- the pressing side and pressed side shim plates are attached only to the back surface of 11 and the tip end surface of the biston 14. Further, in the comparative product 3, the pressing side and the pressed side shim plates are mounted only on the back surface of the back plate 11 of the pad 10b on the auta side and on the inner side surface of the claw portion 13a.
- FIG. 10 shows the results of experiments performed in this manner.
- solid lines a and b represent the products 1 and 2, respectively, and the dotted lines c to e represent the comparative products 1 to 3, respectively.
- the pressed shim plates 26a and 26b and the pressed shim plates 27a and 27b on both the inner and outer sides of the rotor 1 In the case of the product 1 provided in each case, the inclination angle of the caliper 2a at the time of braking could be sufficiently reduced to about 50% of that in the case of the comparative products 1 and 2.
- the large diameter portions 20a, 20b, 20c, 20a 'and the small diameter are located in the middle of each plan pin 5a, 5b, 5c, 5a'.
- Parts 28a, 28a ', 28b, 28b' are provided between the small diameter parts 28a, 28a ', 28b, 28 and the guide holes 6a, 6a, In the case of the product 2 having a predetermined gap or more, the inclination angle of the caliper 2a at the time of braking could be made smaller than that of the product 1.
- FIGS. 11 to 13 show a second embodiment of the present invention.
- the four locking pieces 30 and 30 are bent at the center of the pressing-side shim plate 27 a on the inner side by bending the inside of the U-shaped notch, thereby forming the piston 14. It protrudes toward the side (the right side in Fig. 11). These locking pieces 30 are locked inside the open end of the piston 14.
- one outer diameter side locking piece 3 1 is provided on the outer diameter side peripheral edge of the pressed shim plate 26 a on the inner side, and a pair of inner diameter side locking pieces 3 2, 3 are also provided on the inner diameter side peripheral edge. 2 are formed so as to be bent toward the back plate 11 side (left side in FIG. 11) of the pad 10a on the inner side, respectively.
- the locking grooves 3 3 a and 3 3 b formed on the outer peripheral edge and the inner peripheral edge of the back plate 11 are respectively provided with the outer and inner locking pieces 3 1 and 3. 3 2 is locked.
- two locking pieces 34, 34 are bent at the center of the pressing-side shim plate 27b on the auta side by bending the inside of the U-shaped notch so that the claw portion 1 is formed. 3 Protrudes toward the a side (the right side in Fig. 12). These locking pieces 34, 34 are locked inside a turning portion 35 provided at the center of the claw portion 13a.
- Fig. 13 shows the distance between the pair of pressing pieces 36 and 36 that constitutes the claw portion 13a and presses the pad 10b on the autter side toward the rotor 1. It is smaller (smaller) at the tip.
- the respective locking pieces 3 4, 3 4 spacing 34 between, these pressing piece 3 6, 3 6 larger than the tip distance L 36 between the (L 34> L 36) Things Accordingly, the pressing side shim plate 27b can be prevented from displacing the claw portion 13a downward in FIGS.
- the outer peripheral side edge and the inner peripheral side edge of the pressed side shim plate 26 b on the outer side are locked on the outer diameter side in the same manner as the case of the pressed side shim plate 26 a on the inner side.
- the piece 31 and the inner diameter side locking pieces 32, 32 are formed respectively.
- the locking grooves 33a and 33b formed on the outer peripheral edge and the inner peripheral edge of the back plate 11 of the pad 10b on the outer side, respectively, have the above-mentioned outer and inner diameter side locking pieces 3 1 The 3 and 2 are locked. With this configuration, the radial displacement and the circumferential displacement of the rotor 1 with respect to the rotor-side pad 10b of the pressed-side shim plate 26b on the rotor side are restricted.
- Each of the pressed side and pressed side shim plates 26a, 26b, 27a, 27b is made of a metal plate such as a stainless steel plate. And, the side of the inner side pressing side shim plate 27a facing the piston 14 and the side of the outer side pressing side shim plate 27b facing the claw portion 13a, Each has a rubber coating. Also, of the two side surfaces of the inner-side pressed shim plate 26a, the side surface that comes into sliding contact with the inner-side pressed shim plate 27a, and both side surfaces of the outer-side pressed shim plate 26b. Of these, a fluorine coating is applied to each of the side surfaces in sliding contact with the press-side shim plate 27a on the data side.
- each of the pressed side and the pressed side shim plates 27 a, 27 b, 2 6 a s 2 6 b can be more easily displaced relative to each other, and the generation of abnormal noise can be further suppressed.
- the present invention is not limited to the structure of the present embodiment, and the pressed shims 26a, 27a, 26b, and 27b of the inner and outer sides of each of the pressed sides and the rubber coating It can be made of a metal plate such as a simple stainless steel plate, which does not have any coating or fluorine coating.
- the outer diameter of the pressing shim plate 27 b on the auter side is the same as that of the first embodiment shown in FIGS. 5 to 7 or the second embodiment shown in FIGS. Folds toward the pad 10b side on the outer side, which is not locked to any member in the normal state
- a bent piece can also be provided. When such a bent piece is provided, this bent piece is locked to the upper end edge of the pad 10b on the autter side or the shim plate 26b on the pressed side on the autter side, whereby The displacement of the pressing side shim plate 27 b toward the center of the rotor 1 (downward in FIGS. 12 to 13) is restricted.
- a bent piece bent toward the anti-rotor 1 may be provided on the inner peripheral edge of the pressed shim plate 26a on the inner side.
- the pressing shim plate 27a on the inner side is locked to the bent piece so that the pressing shim plate 27a on the inner side faces the center of the rotor 1 (see FIG. 11). (Downward) displacement is regulated.
- the structure of the first embodiment shown in FIGS. 5 to 7 or the second embodiment shown in FIGS. 11 to 13 can more effectively reduce the generation of abnormal noise during braking.
- the tip surface of the piston 14 and the inner surface of the claw portion 13a, and the pressed shim plate A shim plate coated with a rubber coating on both sides may be held between at least one of the gaps between 27a and 27b.
- the pads 10a and 10b and the pressed side shims are suppressed.
- a shim board with resin coating for heat insulation on both sides can be sandwiched.
- FIG. 14 shows a third embodiment of the present invention.
- the width direction of the pressing side shim plate 27 b on the outer side (left-right direction in FIG. 14)
- a pair of locking projections 41, 41, each having a circular cross section are formed so as to protrude (protrude) toward the claw 13a side.
- locking holes 42, 42 having a circular cross section are provided on the inner side surfaces (the front side surface in FIG. 14) of the pair of pressing pieces 36, 36 constituting the claw portion 13a. .
- each of the locking holes 42, 42 on the side opposite to the rotor may or may not penetrate the outer surface (the back surface in FIG. 14) of each of the pressing pieces 36, 36. . Then, the locking projections 41, 41 are pressed into the locking holes 42, 42 to lock the locking holes 42, 42, respectively. are doing. With this configuration, the pressing-side shim plate 27b is prevented from moving in the surface direction of the pressing-side shim plate 27b with respect to the claw portion 13a.
- FIG. 15 shows a fourth embodiment of the present invention.
- the center of the shim plate 27 b on the auta side is directed toward the claw portion 13 a.
- a projection 43 is formed in a protruding shape (a raised shape) and has a bell-shaped cross section.
- the locking projection 43 is pressed into the inside of the concave portion 35 provided at the center of the claw portion 13a, thereby locking the claw portion 13a. Even with this configuration, the pressing-side shim plate 27b is restricted from moving in the surface direction of the pressing-side shim plate 27b with respect to the claw portion 13a.
- the shape of the locking projection 43 for locking the inside of the concave portion 35 of the claw portion 13a is not limited to the shape shown in FIG. 15 but may be, for example, as shown in FIG.
- the locking projection 43a may have a substantially circular cross-sectional shape.
- FIG. 17 shows a fifth embodiment of the present invention.
- the structure of the embodiment 2 shown in FIGS. 11 to 13 described above is used, and the width direction of the pressing side shim plate 27a on the inner side (the horizontal direction in FIG. 17) is applied to both ends.
- a pair of locking projections 44 and 44 each having a circular cross section are formed so as to protrude (protrude) toward the piston 14 side. Then, each of the locking projections 44, 44 is pressed into the inside of the circular opening of the piston 14 to lock the piston 14. For this reason, in the case of the present embodiment, before each of the locking projections 44, 44 is pressed into the inside of the piston 14, the locking projections 44, 44 are formed.
- FIG. 18 shows a sixth embodiment of the present invention.
- the structure of the embodiment 2 shown in FIGS. 11 to 1.3 described above is used, and the center of the pressing side shim plate 27a on the inner side projects toward the piston 14 side.
- a locking projection 45 having a semicircular cross section is formed (protruded). Then, the locking projection 45 is pressed into the inside of the circular opening of the piston 14 to lock the piston 14. Even with this configuration, the pressing shim plate 27a is restricted from moving in the surface direction of the pressing shim plate 27a with respect to the piston 14.
- FIGS. 19 to 20 show a seventh embodiment of the present invention.
- the inner side of the pressing side shim plate 27b on the outer side (lower end of FIGS. 19 and 20) is positioned in the width direction toward the claw 13a (FIG. 19).
- An R-shaped section 37 having an arc-shaped cross section is provided which is curved over the entire length.
- a cylindrical portion parallel to the center axis of the rotor 1 is provided in the first half of the R portion 37.
- a bent piece 38 is provided at the outer diameter side end of the pressing side shim plate 27b, which is bent over the entire length in the width direction toward the pad 10b on the outer side.
- the bent piece 38 plays a role of preventing even if the force of the pressing side shim plate 27 b on the auter side attempts to fall off from the claw portion 13 a to the inner diameter side.
- the inner side and the outer side of the inner shim plate 27a on the inner side are arc-shaped in cross-section at both ends, and are curved over the entire length in the width direction (the front and back directions in FIG. 19) toward the piston 14 side.
- the inner diameter side and outer diameter side R portions 39 and 40 are provided.
- an R portion 37 provided on the pressing-side shim plate 27 b on the outer side, and an inner-diameter side and an outer-diameter-side R portion 39, 40 provided on the inner-side pressing shim plate 27 a are provided.
- the carrier 2a swings in the direction indicated by the arrow in FIG. 19 independently of the mouth 1 and the pads 1a, 10b for some reason.
- the shims 26a, 26b, 27a, and 27b on the pressed and pressed sides can slide smoothly with each other, and the desired braking force can be stably obtained.
- the caliper 2a swings counterclockwise as shown in Figs. 19 and 20 with respect to the pads 10b and 10a on the auta side and the finner side
- the brake From the 13a force when the brake From the 13a force, the pressed shim plate 26b attached to the pad 10b on the autter side stably passes through the R part 37 provided on the pressed shim plate 27b on the auta side.
- a pressing force can be applied.
- a pressed side shim plate 26 a attached to the pad 10 a on the toner side and an outer diameter side R portion provided on the pressed side shim plate 27 a of the toner side Pressing force can be applied stably via 40. If the caliper 2a swings clockwise in Fig. 19 and 20 with respect to the pads 10b and 10a for some reason, the piston 14 A stable pressing force is applied to the pressed shim plate 26 a attached to the inner pad 10 a via the inner diameter side R portion 39 provided to the pressed shim plate 27 a on the inner side. it can.
- each pressed side shim plate 26a, 26b and each pressed side shim plate 27a, 27b are opposite to the back plate 11, 1 1 of each pad 10a, 10b. It can also be fixed to the surface on the rotor 1 side and the pressing side of the piston 14 and the claw portion 13a by bonding or the like.
- each of the pressed shim plates is fixed or locked to the back plate, and each of the pressed shim plates is fixed or locked to the claw portion and the pressing side of the piston. Therefore, the relative displacement in the surface direction between the pressed side and the pressed side shim plate is not restricted. For this reason, these two shim plates are easily moved, and the moment acting on the claw portion and the biston during braking is effectively reduced, so that the effect of preventing the inclination of the caliper can be obtained effectively. As a result, according to the present invention, the occurrence of uneven wear on each pad can be more effectively suppressed, and the occurrence of noise and judder called squeal during braking can be more effectively suppressed.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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EP04725167A EP1519069A4 (en) | 2003-04-03 | 2004-04-01 | FLOATING CALIPER DISC BRAKE |
US10/522,793 US20060049008A1 (en) | 2003-04-03 | 2004-04-01 | Floating caliper disc brake |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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JP2003-99949 | 2003-04-03 | ||
JP2003099949 | 2003-04-03 | ||
JP2004071419A JP3939304B2 (ja) | 2003-04-03 | 2004-03-12 | フローティングキャリパ型ディスクブレーキ |
JP2004-71419 | 2004-03-12 |
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WO2004090367A1 true WO2004090367A1 (ja) | 2004-10-21 |
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PCT/JP2004/004771 WO2004090367A1 (ja) | 2003-04-03 | 2004-04-01 | フローティングキャリパ型ディスクブレーキ |
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US (1) | US20060049008A1 (ja) |
EP (1) | EP1519069A4 (ja) |
JP (1) | JP3939304B2 (ja) |
WO (1) | WO2004090367A1 (ja) |
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JP5454352B2 (ja) * | 2010-05-20 | 2014-03-26 | 株式会社アドヴィックス | ディスクブレーキ装置 |
US9181998B2 (en) * | 2011-06-07 | 2015-11-10 | Toyota Jidosha Kabushiki Kaisha | Disc brake device and caliper slide mechanism |
DE102011051534A1 (de) * | 2011-07-04 | 2013-01-10 | Dr. Ing. H.C. F. Porsche Ag | Radbremse für ein Kraftfahrzeug |
JP5847561B2 (ja) * | 2011-11-29 | 2016-01-27 | 日立オートモティブシステムズ株式会社 | ディスクブレーキ |
US9394954B2 (en) * | 2013-03-15 | 2016-07-19 | Kelsey-Hayes Company | Guide pin for disc brake assembly and disc brake assembly including such a guide pin |
US9587686B2 (en) | 2012-11-01 | 2017-03-07 | Kelsey-Hayes Company | Guide pin for disc brake assembly and disc brake assembly including such a guide pin |
EP2914866B1 (en) * | 2012-11-01 | 2018-12-05 | Kelsey-Hayes Company | Guide pin for disc brake assembly, disc brake assembly including such a guide pin and method for producing a disc brake assembly including such a guide pin |
JP6338346B2 (ja) * | 2013-10-15 | 2018-06-06 | 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 |
FR3013411B1 (fr) * | 2013-11-18 | 2017-03-31 | Chassis Brakes Int Bv | "frein a disque a etrier coulissant a evacuation de l'air entre colonnettes et alesages" |
US10054175B2 (en) | 2016-11-18 | 2018-08-21 | Kelsey-Hayes Company | Controlled contact guide pin for vehicle disc brakes |
DE102018219752A1 (de) * | 2018-11-19 | 2020-05-20 | Mando Corporation | Bremsanordnung |
DE102021118890A1 (de) | 2021-07-21 | 2023-01-26 | Zf Cv Systems Europe Bv | Bremssattel für eine Fahrzeugbremse |
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JP3774068B2 (ja) * | 1998-07-29 | 2006-05-10 | 日産自動車株式会社 | ディスクブレーキ |
-
2004
- 2004-03-12 JP JP2004071419A patent/JP3939304B2/ja not_active Expired - Fee Related
- 2004-04-01 EP EP04725167A patent/EP1519069A4/en not_active Withdrawn
- 2004-04-01 WO PCT/JP2004/004771 patent/WO2004090367A1/ja active Application Filing
- 2004-04-01 US US10/522,793 patent/US20060049008A1/en not_active Abandoned
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JPS54161486U (ja) * | 1978-04-28 | 1979-11-12 | ||
JPS55123029A (en) | 1979-03-12 | 1980-09-22 | Watanabe Eng Kk | Disc brake |
JPS57149331U (ja) | 1981-03-16 | 1982-09-20 | ||
JPS5919730A (ja) | 1982-07-22 | 1984-02-01 | Nissan Motor Co Ltd | デイスクブレ−キ |
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JPH01224530A (ja) * | 1988-03-02 | 1989-09-07 | Akebono Brake Ind Co Ltd | 浮動キャリパ型ディスクブレーキ |
JPH02124330U (ja) | 1989-03-24 | 1990-10-12 | ||
JPH03124031U (ja) | 1990-03-30 | 1991-12-17 | ||
JPH0542779U (ja) | 1991-11-06 | 1993-06-11 | 住友電気工業株式会社 | デイスクブレーキの鳴き防止装置 |
JP2596090Y2 (ja) | 1992-11-11 | 1999-06-07 | 日信工業株式会社 | 車両用ディスクブレーキ |
JPH09503849A (ja) * | 1993-10-14 | 1997-04-15 | アライドシグナル フレニ ソシエタ ペル アチオニ | 摺動キャリパ型ディスクブレーキ及びこのディスクブレーキのためのガイドピン |
JPH0893808A (ja) | 1994-09-28 | 1996-04-12 | Sumitomo Electric Ind Ltd | ディスクブレーキの鳴き防止装置 |
JPH10184744A (ja) * | 1996-12-27 | 1998-07-14 | Sumitomo Electric Ind Ltd | ディスクブレーキ |
JPH10308301A (ja) | 1997-05-08 | 1998-11-17 | Tdk Corp | 抵抗型温度センサー |
JPH10318301A (ja) * | 1997-05-16 | 1998-12-04 | Tokico Ltd | ディスクブレーキ |
JPH1144331A (ja) | 1997-07-29 | 1999-02-16 | Tokico Ltd | ディスクブレーキ装置 |
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Non-Patent Citations (1)
Title |
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See also references of EP1519069A4 * |
Also Published As
Publication number | Publication date |
---|---|
US20060049008A1 (en) | 2006-03-09 |
JP3939304B2 (ja) | 2007-07-04 |
EP1519069A4 (en) | 2007-04-25 |
JP2004316899A (ja) | 2004-11-11 |
EP1519069A1 (en) | 2005-03-30 |
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