JP2008138738A - Disc brake - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent "low-speed and very low-pressure noise" easily occurring during light brake operation halfway through running at a low speed. <P>SOLUTION: A back metal 17 of a friction pad 16 is formed of: a strip-shaped plate 17B disposed radially inward of a disc 1, extending and connecting right and left ears 17A, 17A in a strip shape; and a fan-like plate 17C projecting from the strip-like plate 17B radially outward of the disc 1, extending circumferentially of the disc 1 in an almost fan-like shape as a single flat plate body. A lining 18 of the friction pad 16 is arranged in a fan-like plate 17C side radially outward of the disc 1 from the strip-shape plate 17B to connect the right and left ears 17A. Thus, the lining 18 made of a friction material is configured to cover the fan-like plate 17C of the back plate 17 with a wide area. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a disc brake that is preferably used to give a braking force to a vehicle or the like, for example.

  Generally, a disc brake configured to apply a braking force to a vehicle by supplying a brake fluid pressure from a master cylinder when a brake pedal or the like of the vehicle is depressed is known (for example, Patent Document 1, Patent Document 1). 2).

  A disc brake according to this type of prior art has a pair of arm portions spaced apart in the circumferential direction of the disc and straddling the outer periphery of the disc, and is attached to a non-rotating portion of the vehicle, and each arm portion of the attachment member A caliper supported slidably via a slide pin or the like and straddling both sides of the disk between the arms, and between the arms of the mounting member located on both sides of the disk The inner side and the outer side friction pads, which are movably attached and pressed against both sides of the disk by the caliper, are configured.

  Here, at the time of brake operation of the vehicle, for example, a piston provided on the inner side of the caliper is slid and displaced toward the disk side by supplying hydraulic pressure from the outside, thereby pressing the friction pad on the inner side against the disk. At this time, the caliper is displaced toward the inner side by receiving a reaction force from the disk, and applies a braking force to the disk by pressing the friction pad on the outer side against the disk.

  A pad spring that elastically biases the friction pad toward the outer side in the radial direction of the disk is provided between the arm portion of the mounting member and the friction pad, and is movable between the arm portions of the mounting member. The behavior of the friction pad attached to the pad is kept stable by a pad spring.

JP-A-6-330966 JP-A-6-294426

  By the way, with the above-described conventional disc brake, almost sufficient countermeasures and improvements have been made to the brake operation performed in the middle of normal driving, and the brake squeal such as a so-called key-key sound can be satisfactorily suppressed. As for the brake squeal on the high frequency side, the problem is almost solved.

  However, when a light brake operation is performed in the middle of traveling at low speed, a phenomenon called “low-speed squealing” occurs under certain circumstances, which gives the vehicle driver discomfort. There is a problem.

  As for this phenomenon called “slow low-pressure squeal”, the mechanism of its occurrence has not always been fully elucidated. For example, as one reason, the contact surface pressure accompanying the braking torque when the friction pad is pressed against the surface of the disk causes the direction of the rotational moment of the friction pad to become unstable, which is called “couple loss”. Therefore, it is conceivable that a squeal occurs because the friction pad cannot be restrained on the side of the mounting member of the mounting member.

  That is, in the conventional disc brake, the friction pad lining extends from the inner side to the outer side in the radial direction of the disc with respect to the pad guide portion or the torque receiving portion provided on the arm portion of the mounting member. The state before the friction pad behavior (direction of rotational moment) is likely to become unstable due to the contact surface pressure when pressed against the disk, and the ear of the friction pad is not restrained by the torque receiving part of the mounting member. Thus, the phenomenon of “slow low-pressure squeal” has occurred.

  The present invention has been made in view of the above-described problems of the prior art, and the object of the present invention is “low-speed squeal” that is likely to occur when a light brake operation is performed while the vehicle is traveling at low speed. It is an object of the present invention to provide a disc brake that can suppress problems such as discomfort to a driver of a vehicle and the like.

  In order to solve the above-described problems, the present invention provides an attachment member that is attached to a non-rotating portion of a vehicle and that has a pad guide portion provided at a position facing the circumferential direction of the disk, and is movably supported by the attachment member. A caliper that is displaced in the axial direction of the disc, and a friction pad that is movably attached to each pad guide portion of the mounting member and is pressed against the disc by the caliper, and the friction pad extends in the circumferential direction of the disc. In addition, the present invention is applied to a disc brake including a back metal provided with ears that are fitted to the pad guides of the mounting member on both ends thereof, and a lining provided on the disk-facing surface side of the back metal.

  A feature of the configuration adopted by the invention of claim 1 is that the lining of the friction pad is arranged at a position that is radially outward of the disk from a virtual straight line connecting the ear portions. There is.

  According to a second aspect of the present invention, each pad guide portion of the mounting member is formed as a U-shaped notch recess, and a braking torque from the friction pad is received on the bottom side of the notch recess. And a lining of the friction pad is disposed on the outer side in the radial direction of the disk than the position of the torque receiving portion.

  According to a third aspect of the present invention, the back plate of the friction pad is located on the radially inner side of the disk and extends in a band shape between the ear parts, and is connected to the disk from the band plate part. It is formed as a single flat plate by a fan-shaped plate portion protruding outward in the radial direction and extending in a substantially fan shape in the circumferential direction of the disk, and the lining is provided only on the fan-shaped plate portion.

  As described above, the invention according to claim 1 is configured such that the friction pad lining is disposed at a position on the outer side in the radial direction of the disc with respect to the virtual straight line connecting the respective ear portions on the disc facing surface side of the back metal. Therefore, when the lining is pressed against the disk surface in accordance with the braking operation (braking operation) of the vehicle, the friction pad is radially outward from the ear portion of the back metal fitted to the pad guide portion of the mounting member. At this position, a rotational moment along the rotational direction of the disc is received, and the rotational moment in other directions can be kept small.

  For this reason, even when a light braking operation is performed while the vehicle is traveling at low speed, the pad behavior when the friction pad lining is pressed against the disk surface can be stabilized. The ear part side of the friction pad can be restrained from the initial stage of braking on the guide part side. As a result, the improvement of brake squeal can be achieved, so-called “slow low-pressure squeal” can be satisfactorily suppressed, and discomfort can be prevented from being given to the driver of the vehicle.

  According to the second aspect of the present invention, each pad guide portion of the mounting member is formed as a U-shaped notch recess, a torque receiving portion is provided on the bottom side of the notch recess, and the friction pad lining is Since the configuration is such that the torque receiving portion is disposed on the outer side in the radial direction of the disk, the ear portion side of the friction pad is restrained from the initial stage of braking by the pad guide portion and the torque receiving portion of the mounting member. And the behavior of the friction pad can be stabilized.

  Furthermore, in the invention according to claim 3, since the back plate of the friction pad is formed as a single flat plate body by the belt-like plate portion and the fan-like plate portion, the belt-like plate portion located on the radially inner side of the disk is used. The fan-like plate portion protruding radially outward can be formed as a wide plate-like body extending in a substantially fan shape in the circumferential direction of the disk. Thus, the lining can be arranged with a large area so as to cover the entire surface of the fan-shaped plate portion, and a wide lining surface for applying a sufficient braking force to the disk can be secured.

  Hereinafter, a case where the disc brake according to the embodiment of the present invention is applied to a vehicle such as a four-wheel automobile will be described in detail with reference to the accompanying drawings.

  Here, FIG. 1 to FIG. 7 show a first embodiment of the present invention. In the figure, reference numeral 1 denotes a disk that rotates together with a vehicle wheel. The disk 1 has a rotation center O as shown in FIGS. It is what is done.

  Reference numeral 2 denotes an attachment member fixedly attached to a non-rotating portion of the vehicle. The attachment member 2 is formed of an elongated, substantially rectangular frame-like body as shown in FIG. Product). The mounting member 2 includes a first side frame plate 3, a second side frame plate 5, and left and right joint frame plates 6 and 6, which will be described later.

  Reference numeral 3 denotes a one-side frame plate of the mounting member 2, and the one-side frame plate 3 extends in the circumferential direction of the disk 1 at a position radially inward of the disk 1 with respect to a friction pad 16 described later, for example, as shown in FIG. The mounting plate portion 3A and a pair of left and right protruding plate portions 3B and 3B protruding from both sides in the length direction of the mounting plate portion 3A toward the outer side in the radial direction of the disk 1. The mounting plate portion 3A and each protruding plate portion 3B of the one side frame plate 3 are located on one side (inner side) of the disk 1 as shown in FIG. It extends.

  Further, as shown in FIG. 6, the protruding plate portions 3 </ b> B of the one-side frame plate 3 are arranged at positions where inner friction pads 16 described later are sandwiched from both sides in the circumferential direction of the disk 1. A joint frame plate 6 to be described later is integrally formed on the projecting end side of the projecting plate portion 3B, and a flat surface portion 3C having a substantially horizontal surface is formed between the pad guide portion 3D and the joint frame plate 6 to be described later. It has become.

  Here, on both sides in the length direction of the mounting plate portion 3A, as shown in FIGS. 6 and 7, the left and right positions are located on the inner side in the radial direction of the disk 1 with respect to the pad guide portion 3D and pin fitting hole 4A described later. A pair of screw holes 3A1, 3A1 is formed. A fixing bolt (not shown) is screwed into these screw holes 3A1, and the mounting plate portion 3A of the mounting member 2 is a knuckle portion (not shown) which becomes a non-rotating portion of the vehicle by the fixing bolt. It is attached in a fixed state.

  Further, the left and right protruding plate portions 3B and 3B are provided with inner side pad guide portions 3D and 3D at positions on the inner side in the radial direction of the disc 1 with respect to the flat surface portion 3C. As shown in FIGS. 6 and 7, it is formed as a U-shaped notch recess. And in this pad guide part 3D, the ear | edge part 17A of the friction pad 16 (back metal 17) mentioned later is slidably inserted via the pad spring 19, respectively.

  Further, the bottom side of each pad guide portion 3D constitutes an inner side torque receiving portion 3E, and these inner side torque receiving portions 3E send braking torque from the friction pad 16 via a pad spring 19 described later. It will be accepted.

  4 and 4 are pin guide cylindrical protrusions integrally formed on the protruding plate portions 3B and 3B of the mounting member 2 (one side frame plate 3), and each cylindrical protrusion 4 is as shown in FIG. Is formed as a stepped cylindrical body projecting outwardly in the axial direction of the disc 1 from each projecting plate portion 3B of the one side frame plate 3, and its inner peripheral side is the thickness direction of the projecting plate portion 3B (the axis of the disc 1). It is a bottomed pin fitting hole 4A extending in the direction). A slide pin 13 described later is slidably inserted into the pin fitting hole 4A.

  Here, these pin fitting holes 4A are arranged at positions where the overall length is closer to the inner side than the disk 1 as shown in FIG. 2, and for the left and right torque receiving portions 3E, 3E, for example, As shown by a dotted line in FIG. 6, they are arranged at positions adjacent to each other in the circumferential direction of the disk 1.

  Reference numeral 5 denotes the other side frame plate of the mounting member 2, and the other side frame plate 5 is disposed at a position facing the one side frame plate 3 with the disk 1 interposed therebetween as shown in FIG. 5. The other side frame plate 5 extends substantially in parallel along the other side surface of the disc 1 so as to integrally connect between the below-described joint frame plates 6 and 6 on the outer side (other side) of the disc 1. . Here, the other side frame plate 5 has an elongated bar-like connecting beam portion 5A extending in the left and right directions (circumferential direction of the disk 1) as shown in FIG. 1, and the length of the connecting beam portion 5A. It is composed of a pair of left and right protruding plate portions 5B and 5B protruding from both sides in the vertical direction toward the outside in the radial direction of the disk 1.

  As shown in FIG. 1, the connecting beam portion 5A of the other side frame plate 5 extends in the circumferential direction of the disk 1 at a position radially inward of the disk 1 with respect to a friction pad 16 described later, and protrudes left and right. The plate portions 5B and 5B are integrally connected with rigidity. In addition, each protruding plate portion 5B of the other side frame plate 5 has a flat surface portion 5C, an outer side pad guide portion 5D, and an outer side torque, respectively, in substantially the same manner as the protruding plate portion 3B of the one side frame plate 3 described above. A receiving portion 5E and the like are formed.

  6 and 6 are a pair of left and right joint plates extending in the axial direction of the disc 1 so as to straddle the outer periphery of the disc 1, and the joint plates 6 and 6 are arranged as shown in FIGS. The one side frame plate 3 and the other side frame plate 5 that are arranged at positions that straddle the outer periphery of the disk 1 and extend in parallel with each other along both surfaces of the disk 1 are integrated on both sides in the length direction (circumferential direction of the disk 1). To be linked.

  Here, each joint frame plate 6 is formed as a thin plate body slightly curved along the outer periphery of the disk 1 as shown in FIG. 6, and the plate thickness t is the thickness of the arm portion described in the prior art. The thickness is set to 1/2 or less (for example, t = about 5 to 10 mm). As a result, the radius R (outer diameter dimension) of the disk 1 can be increased by, for example, about 8 to 15 mm compared to the current product, and the heat capacity of the disk 1 can be increased.

  7 is a caliper supported by the mounting member 2 so as to be movable. The caliper 7 includes a bridge portion 8 extending in the axial direction across the outer peripheral side of the disk 1 as shown in FIGS. A cylinder portion 9 as an inner leg portion that is integrally formed on one side and disposed on the inner side of the disc 1 and an outer leg that is integrally formed on the other side of the bridge portion 8 and disposed on the outer side of the disc 1. The outer leg portion 10 includes claws 10A and 10A having a bifurcated shape as shown in FIG.

  The caliper 7 is integrally provided with a pair of attachment portions 11, 11 that protrude in a substantially L shape from both the left and right sides of the cylinder portion 9 and extend in the circumferential direction of the disk 1. As shown in FIG. 2, a later-described slide pin 13 is fixedly attached by a fastening bolt 14. Further, as shown in FIG. 4, a cylinder bore 9A is formed in the cylinder portion 9 of the caliper 7, and a piston 12 is slidably inserted into the cylinder bore 9A.

  Reference numerals 13 and 13 denote slide pins provided in the respective attachment portions 11 of the caliper 7, and the respective slide pins 13 are attached to the respective attachment portions on the cylinder portion 9 side on the base end side via fastening bolts 14 and 14, as shown in FIG. 11, and the distal end side is slidably inserted into the pin fitting hole 4 </ b> A of the mounting member 2. Accordingly, the caliper 7 is slidably supported by the mounting member 2 via the slide pin 13.

  Reference numerals 15 and 15 denote protective boots for protecting the slide pins 13 from the outside. The protective boots 15 are formed in an accordion shape using, for example, an elastic resin material, and the cylindrical protrusions 4 of the mounting member 2 and the slide pins. 13 is attached. The protective boot 15 covers the periphery of the proximal end side of the slide pin 13 to prevent foreign matters such as rainwater and dust from entering between the slide pin 13 and the pin fitting hole 4A.

  Reference numerals 16 and 16 denote inner and outer friction pads disposed on both sides of the disk 1. Each of the friction pads 16 is a back metal formed in a substantially fan shape as shown in FIG. 4, FIG. 6, FIG. 17 and a lining 18 described later. Each of the back metal 17 has a convex shape at both ends in the length direction corresponding to the inner side pad guide portion 3D (outer side pad guide portion 5D as shown in FIG. 1) as shown in FIGS. Ear parts 17A, 17A are formed in a protruding manner.

  Here, the back metal 17 of the friction pad 16 is located in the radial direction of the disk 1 as illustrated in FIG. 7 and has a width that substantially corresponds to the ear portion 17A and extends between the ear portions 17A and is connected in a band shape. A plate portion 17B and a substantially fan shape in which one long side of a rectangle having a longitudinal direction in the circumferential direction of the disc 1 is projected in an arc shape from the strip-like plate portion 17B and projecting outward in the radial direction of the disc 1 The fan-shaped plate portion 17 </ b> C extended to form a single flat plate.

  Reference numeral 18 denotes a lining that constitutes the friction pad 16 together with the back metal 17, and the lining 18 is made of a friction material that is fixedly attached so as to overlap the surface side of the back metal 17. As shown in FIG. 7, the lining 18 is disposed at a position on the outer side in the radial direction of the disk 1 with respect to the straight line AA formed by a virtual line connecting the left and right ear portions 17A.

  That is, the lining 18 is disposed at a position on the outer side in the radial direction of the disk 1 with respect to the strip-shaped plate portion 17B connecting the left and right ear portions 17A, and covers the surface side of the fan-shaped plate portion 17C with a large area. Is provided. Thus, the lining 18 of the friction pad 16 can secure a wide lining surface (area) necessary and sufficient for applying a braking force to the disk 1.

  Here, the inner friction pad 16 is slidably inserted into the inner side pad guide part 3D via pad springs 19 described later, as shown in FIGS. Has been. Further, the outer side friction pad 16 is slidably inserted into the outer side pad guide part 5D via a pad spring 19 described later, as shown in FIG.

  As shown in FIG. 4, the friction pads 16 are arranged to face both sides of the disk 1, and the piston 12 is pushed by the brake hydraulic pressure in accordance with the brake operation of the vehicle, so that the claw portion of the caliper 7. The disk 1 is pressed between 10A and the piston 12 so as to sandwich the disk 1 from both sides, thereby applying a braking force to the disk 1.

  In this case, braking torque when each friction pad 16 is pressed against the disk 1 by the caliper 7 is transmitted from the ear portion 17A of the friction pad 16 (back metal 17) to the torque receiving portions 3E and 5E of the mounting member 2, and the mounting member. The two projecting plate portions 3B, 5B and the like receive the rotational torque (braking torque) from the disk 1.

  Reference numerals 19 and 19 denote a pair of left and right pad springs that are spaced apart in the circumferential direction of the disk 1 and are attached to the pad guide portions 3D and 5D of the attachment member 2, and each pad spring 19 is a pad of the attachment member 2. The inner and outer friction pads 16 together with the guide portions 3D and 5D are guided through the respective ear portions 17A of the back metal 17 so as to be slidable in the axial direction of the disk 1.

  The pad spring 19 has a pad urging portion 19A that comes into contact with the fan-shaped plate portion 17C of the back metal 17 from below, and the pad urging portion 19A causes the friction pad 16 to be directed radially outward of the disk 1. Energize elastically. As a result, the pad spring 19 stabilizes and smoothes the movement (sliding displacement) of the friction pad 16 in the axial direction of the disk 1.

  The disc brake according to the present embodiment has the above-described configuration, and the operation thereof will be described next.

  First, when brake fluid pressure from a master cylinder (not shown) is supplied into the cylinder portion 9 (cylinder bore 9A shown in FIG. 4) of the caliper 7 in accordance with the brake operation of the vehicle, the piston 12 in the cylinder portion 9 is The brake fluid pressure at this time slides and displaces in the axial direction of the disk 1 and presses the friction pad 16 on the inner side (cylinder portion 9 side) toward one side of the disk 1.

  At this time, the caliper 7 as a whole moves the disc relative to the mounting member 2 so that the slide pin 13 is displaced relative to the pin fitting hole 4A in the direction indicated by the arrow B in FIG. 1, the claw portions 10 </ b> A of the outer leg portion 10 press the outer friction pad 16 toward the other side surface of the disk 1.

  For this reason, the disk 1 is strongly sandwiched by the inner friction pad 16 and the outer friction pad 16 from both sides, and applies a braking force to a running vehicle, for example. Further, when the brake operation is released, the friction pads 16 are separated from both sides of the disc 1 and the braking force on the vehicle is released.

  Further, when the inner and outer friction pads 16 are pressed against both surfaces of the disk 1 in order to apply braking force to the vehicle, the rotational torque (braking torque) from the disk 1 causes the ears 17A of the friction pads 16 and the like. Are added to the torque receiving portions 3E and 5E of the mounting member 2 and are also added to the cylinder portion 9 and the outer leg portion 10 of the caliper 7.

  The mounting member 2 fixed to the non-rotating portion of the vehicle can stably support the braking torque received by the torque receiving portions 3E and 5E on the inner side and the outer side of the disc 1 with the entire mounting member 2. it can. Further, the braking torque applied to the caliper 7 on the cylinder portion 9 side is received between the pin fitting hole 4 </ b> A of the cylindrical projection 4 provided on the one side frame plate 3 of the mounting member 2 and the slide pin 13. Thus, the deformation of the cylinder portion 9 and the like of the caliper 7 due to the influence of the braking torque can be suppressed by the slide pin 13 and the like inserted into the pin fitting hole 4A.

  Further, left and right pad springs 19 provided between the mounting member 2 and the friction pad 16 are elastically arranged so that the back metal 17 of the friction pad 16 is directed radially outward of the disk 1 by a pad urging portion 19A or the like. By continuing to be urged, the behavior of the friction pad 16 in which the ear portions 17A are movably attached between the pad guide portions 3D and 5D of the attachment member 2 can be kept stable by the pad spring 19. it can.

  By the way, in the current product disc brake, when a light brake operation is performed while the vehicle is traveling at low speed, a phenomenon called “low-speed squealing” occurs under certain circumstances. The problem of giving unpleasant feeling to the driver of the vehicle has arisen.

  Therefore, in the present embodiment, the back plate 17 of the friction pad 16 is located on the radially inner side of the disk 1 as illustrated in FIG. A single flat plate body is formed by the fan-shaped plate portion 17 </ b> C projecting from the strip-shaped plate portion 17 </ b> B toward the outer side in the radial direction of the disk 1 and extending in a substantially fan shape in the circumferential direction of the disk 1.

  Then, the lining 18 of the friction pad 16 is positioned on the outer side in the radial direction of the disk 1 with respect to the belt-like plate portion 17B (for example, a virtual straight line AA shown in FIG. 7) connecting the left and right ear portions 17A. The fan-shaped plate portion 17C of the back metal 17 is covered with a lining 18 made of a friction material with a wide area.

  Thus, when the lining 18 of the friction pad 16 is pressed against the surface of the disk 1 in accordance with the braking operation (braking operation) of the vehicle, for example, the inner friction pad 16 is applied to the pad guide portion 3D of the mounting member 2. A rotational moment along the rotational direction of the disc 1 (for example, the direction indicated by the arrow C in FIG. 7) is received at a position that is radially outward from each ear portion 17A of the fitted back metal 17, and other than this. The rotational moment in the direction can be kept small. This point is not limited to the inner friction pad 16 but the same applies to the outer friction pad 16.

  In this case, when the rotational moment acting on the lining 18 in the braking state is examined, a line connecting the rotation center O of the disk 1 and the outer edge corner portion (outer edge of the torque receiving portion 3E) of the pad guide portion 3D shown in FIG. It is known that, in the minute 20, the virtual circle 21 having the radius R1 centered on the midpoint N serves as a reference for determining the direction of the rotational moment (see, for example, Patent Document 2 described above).

  That is, in the outer region 18A of the lining 18 positioned outside the virtual circle 21, a rotational moment along the direction indicated by the arrow C in FIG. On the other hand, in the inner region 18B of the lining 18 positioned inside the virtual circle 21 (the inner region 18B indicated by hatching in FIG. 7), for example, the arrow D direction ( It is considered that a rotational moment along the direction opposite to the rotational direction of the disk 1 acts.

  In the friction pad 16 employed in the present embodiment, the outer region 18A of the lining 18 has a sufficiently larger area (contact area with the disk 1) than the inner region 18B by the configuration as described above. Therefore, the friction pad 16 is greatly affected by the rotational moment along the arrow C direction, and for example, the influence of the rotational moment along the arrow D direction can be kept small.

  In particular, in the present embodiment, a so-called structure in which the disc 1 is gripped from the outer peripheral side as shown in FIG. 4 between the cylinder portion 9 (piston 12) and the outer leg portion 10 (claw portion 10A) of the caliper 7. A fist type caliper is used. For this reason, the contact surface pressure when the lining 18 of the friction pad 16 is pressed against the disk 1 can be further increased on the outer peripheral side than on the inner peripheral side of the disk 1, and the friction pad 16 has an arrow C direction. It is possible to effectively give the influence of the rotational moment along

  The pad spring 19 (particularly, the pad spring 19 located on the entrance side in the rotation direction of the disk 1) attached between the attachment member 2 and the friction pad 16 is attached to the back plate 17 of the friction pad 16 by the pad urging portion 19A. Since the disk 1 is elastically biased toward the outside in the radial direction, the ear portion 17A of the friction pad 16 (back metal 17) can be kept in a stable restrained state in the pad guide portion 3D of the mounting member 2. The behavior of the friction pad 16 rattling inside and outside in the radial direction of the disk 1 can be suppressed.

  On the other hand, the inner region 18B (region shown by hatching in FIG. 7) of the lining 18 based on the imaginary circle 21 having the radius R1 described above has an area equal to or larger than the outer region 18A. In the case (conventional disc brake), for example, the influence of the rotational moment along the direction indicated by the arrow D is greatly affected, and the entire friction pad tends to be loose in the radial direction of the disc. .

  Thus, according to the present embodiment, the friction pad 16 is configured as described above, and the outer region 18A of the lining 18 has a sufficiently larger area than the inner region 18B. The pad behavior when pressed against the surface of the disk 1 can be stabilized, and the ear 17A side of the friction pad 16 on the pad guide portions 3D and 5D side of the mounting member 2 is kept in a stable restrained state from the beginning of braking. be able to.

  Therefore, it is possible to improve the brake squeal, and even when a light brake operation is performed while the vehicle is traveling at a low speed, it is possible to satisfactorily suppress the occurrence of a so-called “low speed squeal”. . As a result, it is possible to satisfactorily perform a brake operation during low-speed traveling, and to solve problems such as discomfort to the driver of the vehicle.

  Further, the mounting member 2 employed in the present embodiment includes a first side frame plate 3 and a second side frame plate 5 that extend in parallel with each other along both surfaces of the disk 1, and the first side frame plate 3 and the second side frame plate 5. From the left and right joint frame plates 6 and 6 connected across the outer periphery of the disk 1, both ends in the longitudinal direction are integrally formed as a long and narrow rectangular frame body (see FIG. 5) having high rigidity. ing. Therefore, the mounting member 2 can be formed in a sturdy structure while being reduced in size and weight, and the braking torque received by the torque receiving portions 3E and 5E on the inner side and the outer side of the disk 1 is applied to the entire mounting member 2. Can be supported stably.

  Moreover, on the inner side of the disc 1, the torque receiving portion 3E and the pin fitting hole 4A provided in the protruding plate portion 3B of the one side frame plate 3 are adjacent to each other in the circumferential direction of the disc 1 as shown in FIG. Placed in position. For this reason, it can suppress that the bending moment which acts on the one side frame board 3 (projection board part 3B) etc. of the attachment member 2 with the said braking torque can be suppressed, and the bending deformation of the attachment member 2 whole is suppressed small. Can be reduced.

  In the above-described embodiment, the disk brake has been described as an example in which the slide pin 13 provided on the caliper 7 side is slidably inserted into the pin fitting hole 4A of the mounting member 2. However, the present invention is not limited to this. For example, the present invention is also applicable to a disc brake in which a slide pin is fixedly provided on the mounting member side and a pin fitting hole into which the slide pin is inserted is provided on the caliper side. It can be done.

  In the above embodiment, the case where the cylinder portion 9 of the caliper 7 is provided with a single cylinder bore 9A (piston 12) has been described as an example. However, the present invention is not limited to this, and can also be applied to, for example, a disc brake having a configuration in which two or more pistons are provided in a caliper.

1 is a front view showing a disc brake according to an embodiment of the present invention. FIG. 2 is a partially cutaway plan view of the disc brake of FIG. 1 as viewed from above. It is the rear view which looked at the disc brake from the opposite side to FIG. It is sectional drawing which expanded the disc brake from the arrow IV-IV direction in FIG. It is the top view which looked at the attachment member in FIG. It is sectional drawing which looked at the attachment member and the friction pad of the inner side in the state which removed the caliper from the arrow VI-VI direction in FIG. It is the elements on larger scale in FIG. 6 which shows an attachment member and the friction pad of an inner side.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Disc 2 Mounting member 3 One side frame board 3A Mounting plate part 3B, 5B Projection board part 3D Inner side pad guide part 3E Inner side torque receiving part 4 Cylindrical protrusion 4A Pin fitting hole 5 Other side frame board 5A Connecting beam part 5D Outer side pad guide part 5E Outer side torque receiving part 6 Joint frame plate (part straddling the outer peripheral side of the disk)
7 Caliper 8 Bridge 9 Cylinder (Inner Leg)
DESCRIPTION OF SYMBOLS 10 Outer leg part 11 Attachment part 12 Piston 13 Slide pin 14 Fastening bolt 16 Friction pad 17 Back metal 17A Ear part 17B Strip | belt-shaped board part 17C Fan-shaped board part 18 Lining 19 Pad spring

Claims (3)

An attachment member attached to a non-rotating portion of the vehicle and provided with a pad guide portion at a position facing the circumferential direction of the disc, a caliper that is movably supported by the attachment member and displaced in the axial direction of the disc, and the attachment A friction pad that is movably attached to each pad guide portion of the member and pressed against the disk by the caliper;
The friction pad extends in the circumferential direction of the disk, and is provided on the opposite side of the disk with a back metal provided with ears that fit the pad guides of the mounting member on both ends thereof. In disc brakes consisting of linings,
The disc brake according to claim 1, wherein the lining of the friction pad is disposed at a position that is radially outward of the disc from a virtual straight line connecting the ear portions.   Each pad guide portion of the mounting member is formed as a U-shaped notch recess, and a torque receiving portion for receiving a braking torque from the friction pad is provided on the bottom side of the notch recess, and the friction pad The disc brake according to claim 1, wherein the lining is arranged on the outer side in the radial direction of the disc than the position of the torque receiving portion.   The friction pad back metal is located on the radially inner side of the disk and extends in a band shape between the ears and is connected to the belt, and projects from the belt-shaped plate part toward the radially outer side of the disk. The disc brake according to claim 1 or 2, wherein the disc brake is formed as a single flat plate by a fan-shaped plate portion extending in a substantially fan shape in a circumferential direction, and the lining is provided only on the fan-shaped plate portion.

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