JP2005201417A - Disk brake - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To effectively prevent uneven wear of a brake pad. <P>SOLUTION: In a disk brake 10 wherein a disk rotor 14 is provided between an inner pad 51 and an outer pad 52, the outer pad 52 is supported by a mounting member 20 so as to be movable in a predetermined direction Y1 within a plane nearly in parallel to a disk rotor face, while the inner pad 51 is supported by the mounting member 20 so as to be movable in a direction Y2 nearly opposite to the predetermined direction. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a disc brake in which a disc rotor is disposed between an inner pad and an outer pad.

Conventionally, convex portions formed at both ends of a brake pad (inner pad and outer pad) are fitted and supported through a pad support member in a groove (guide groove) formed in a mounting (caliper) of a disc brake. A known disc brake is known (for example, see Patent Document 1). In this disc brake, a frictional force is generated between the one side surface of the convex portion of the brake pad and one side wall of the mounting groove portion by a rotational force acting on the brake pad when the brake is operated, The vibration of the brake pad is attenuated by the frictional force, and so-called brake squeal is suppressed.
Japanese Patent Laid-Open No. 11-63035

  By the way, in the above-mentioned prior art, in order to prevent rattling of the convex part of the brake pad supported in the groove part of the mounting, the pad support member has one side surface of the convex part of the brake pad as one side of the mounting groove part. A spring for biasing toward the side wall is set. However, this spring can prevent rattling only by urging the convex part of the brake pad from one direction and abutting against the side wall of the mounting groove. No new proposal has been made regarding the urging direction of the pad or the relative relationship between the urging direction of the inner pad and the outer pad.

  Accordingly, the present invention focuses on the fact that the support mode of the brake pad with respect to the mounting affects the uneven wear of the brake pad, and provides a new support mode of the brake pad with the object of preventing the uneven wear of the brake pad. Provide disc brakes.

In order to solve the above problems, according to one aspect of the present invention, in a disc brake in which a disc rotor is disposed between an inner pad and an outer pad,
The outer pad is supported by the mounting member so as to be movable in a predetermined direction in a plane substantially parallel to the disk rotor surface, and the inner pad is supported by the mounting member so as to be movable in a direction substantially opposite to the predetermined direction. A disc brake is provided.

  According to this aspect, since the inner pad and the outer pad can move in the opposite directions, the degree of freedom of rotation of the cylinder of the disc brake is increased, and uneven wear of the brake pad can be effectively prevented. The predetermined direction is a direction that should be defined depending on the mounting position of the disc brake in the wheel circumferential direction. When the disc brake is mounted on the upper side in the vertical direction, the predetermined direction is substantially vertical. The direction may be downward, and roughly corresponds to the direction from the outer peripheral side to the inner peripheral side of the pad (or disk rotor).

  In this aspect, the outer pad and the inner pad may be supported so as to reciprocate in the predetermined direction. This allows forward and reverse rotation of the disc brake cylinder. In addition, a pad support member that urges the pad from two directions along the predetermined direction to elastically support the pad may be set for each of the inner pad and the outer pad. The two directions along the predetermined direction correspond to the two directions indicated by arrows Y1 and Y2 in FIG. Moreover, this aspect WHEREIN: The elastic support position of the pad by the said pad support member may oppose in the said predetermined direction. Further, the rotation of the cylinder supported rotatably with respect to the mounting member is assisted by the movement of the outer pad and the inner pad with respect to the mounting member.

  According to the present invention, uneven wear of a brake pad can be effectively prevented.

  The best mode for carrying out the present invention will be described below with reference to the drawings.

  FIG. 1 is a top view showing an embodiment of a disc brake 10 according to the present invention, and FIG. 2 is a cross-sectional view taken along line AA of FIG. The disc brake 10 of the present embodiment includes a mounting bracket 20 (hereinafter simply referred to as “mounting 20”). A cylinder 30 is attached to the mounting 20 by a slide pin (not shown). The mounting 20 supports brake pads (an inner pad 51 and an outer pad 52) by a support structure 40 described later. The inner pad 51 and the outer pad 52 are disposed so as to sandwich the disk rotor 14 that rotates together with the wheels from the inside and outside of the vehicle.

  The disc brake 10 includes a cylinder body (caliper) 30 (hereinafter simply referred to as “cylinder 30”). The cylinder 30 is attached to the mounting 20 via a slide pin or the like (not shown). In other words, the cylinder 30 is supported by the mounting 20 via the slide pin and the bush that straddle the disk rotor 14 in the vehicle inside / outside direction. The cylinder 30 includes a piston 34 and a claw portion 32 that are disposed so as to sandwich the inner pad 51 and the outer pad 52 from the inside and outside of the vehicle. Typically, a master cylinder (not shown) communicates with the cylinder 30 via a hydraulic passage. When the high-pressure fluid is supplied to the cylinder 30, the piston 34 moves in the direction of the claw 32, and the inner pad 51 and the outer pad 52 are pressure-bonded so as to sandwich both sliding surfaces of the disk rotor 14, thereby realizing the brake operation. . The disc brake 10 may be disposed at any angular position in the wheel circumferential direction with respect to the disc rotor 14.

  FIG. 3 is an enlarged view of a portion X in FIG. 1 showing details of the support structure 40. Here, the support structure 40 related to the outer pad 52 will be described, but the support structure 40 related to the inner pad 51 may be the same unless otherwise specified. As shown in FIGS. 1 and 3, the outer pad 52 includes convex portions 52 a at both ends. The convex portion 52 a of the outer pad 52 is supported by a concave portion (groove portion) 22 formed in the mounting 20 via a pad support member (pad support) 24. The pad support member 24 is configured to support the convex portion 52a of the outer pad 52 in a floating state in the concave portion 22 of the mounting 20. The pad support member 24 shown in FIG. 3 includes a pair of spring portions (springs) 24a that urges both side surfaces of the convex portion 52a of the outer pad 52 from the inner and outer peripheral directions of the outer pad 52 (see arrow Y in FIG. 3). Have. The pair of spring portions 24 a holds the convex portion 52 a of the outer pad 52 in a state of being separated from the side wall 22 a of the concave portion 22 of the mounting 20.

  4 and 5 are explanatory views showing the operation of the disc brake 10 of this embodiment when the brake is operated. As shown in FIG. 4A, when the brake is operated, the claw portion 32 is deformed and the pressing center of the outer pad 52 moves to the outer peripheral side. For this reason, the deformation of the claw portion 32 usually causes uneven wear in which the outer peripheral side of the brake pad is worn more than the inner peripheral side.

  FIG. 4B is a diagram showing the reaction force F (and the rotational moment M) acting on the cylinder 30 when the brake is operated by an arrow. As described above, since the pressing center of the outer pad 52 moves to the outer peripheral side due to the deformation of the claw portion 32, a deviation occurs between the pressing center of the outer pad 52 and the pressing center of the inner pad 51. As a result, the cylinder 30 has a claw portion. A rotational moment M is generated in a direction in which 32 is directed toward the inner peripheral side of the outer pad 52 and the piston 34 is directed toward the outer peripheral side of the inner pad 51. At this time, in this embodiment, as shown in FIG. 4C, the inner pad 51 and the outer pad 52 can be displaced in the inner and outer peripheral directions with respect to the mounting 20 (see the arrow in the figure), so that the cylinder 30 is It can rotate (tilt) in the direction of action of the rotational moment M (counterclockwise in the figure). In other words, the cylinder 30 that receives the rotational moment M is displaced in the inner circumferential direction of the outer pad 52 (Y1 direction in FIG. 4C) and in the inner circumferential direction of the inner pad 51 (Y2 direction in FIG. 4C). It is rotated with a displacement of. Note that a predetermined clearance (gap) for enabling the rotation (inclination) of the cylinder 30 is set in the slide pin and the piston 34 of the cylinder 30.

  When the above-described rotation of the cylinder 30 occurs, as shown in FIG. 5A, the pressing center of the outer pad 52 and the pressing center of the inner pad 51 coincide with each other, and an offset load is applied to the inner pad 51 and the outer pad 52 as a reaction force. It will not be granted. As described above, according to the present embodiment, the outer pad 52 can be displaced in the inner circumferential direction and the inner pad 51 can be displaced in the outer circumferential direction, so that a relatively large amount of rotation of the cylinder 30 is allowed. Uneven wear of the brake pad due to the deformation of the claw portion 32 during operation can be effectively prevented.

  On the other hand, as shown in FIG. 5B, in the conventional configuration in which the outer pad 52 and the inner pad 51 can be displaced only in the same direction (for example, only in the inner circumferential direction), the outer pad 52 Although the inner pad 51 cannot be displaced in the outer circumferential direction, the rotation of the cylinder 30 is limited. That is, in such a conventional configuration, the cylinder 30 can only rotate around the pad (in this example, the inner pad 51) that cannot move when receiving the rotational moment M, so that the slide with a high degree of rotational freedom is achieved. Compared with a configuration in which the cylinder 30 can rotate around the pin, it is not possible to effectively prevent uneven wear of the brake pad. In such a conventional configuration, since the rotation of the cylinder 30 is limited, the rotational moment M continues to act on the cylinder 30 during the braking operation. On the other hand, according to the present embodiment, as described above, the pressing center of the outer pad 52 and the pressing center of the inner pad 51 coincide with each other, and the rotational moment M does not continue to act on the cylinder 30 (FIG. 5 ( B)), which is advantageous from the viewpoint of durability of the cylinder 30.

  In this embodiment, during braking, the convex portion 52 a of the outer pad 52 abuts on the inner peripheral side wall 22 a of the concave portion 22 of the mounting 20, and the convex portion 52 a of the inner pad 51 is in contact with the concave portion 22 of the mounting 20. The rotational torque acting on each of the pads 52 and 51 in contact with the outer peripheral side wall 22a is transmitted to the mounting 20, and the vibration of the outer pad 52 and the inner pad 51 is attenuated by the frictional force at that time. . The torque receiving portions of the pads 52 and 51 do not need to have a convex shape like the convex portion 52a, and may be set at a location different from the convex portion 52a. In the present embodiment, since the convex portion 52a is normally held in a floating state separated from the side wall 22a of the concave portion 22 of the mounting 20, the convex portion 52a is in contact with the side wall 22a of the concave portion 22 at the normal time. Compared to the configuration (see FIG. 6A), not only the degree of freedom of rotation of the cylinder 30 is increased as described above, but also the contact state of the torque receiving portion with the mounting 20 is affected by the dimensional tolerance of the brake pad. It is difficult to make the contact state of the torque receiving portion uniform.

  In the present embodiment, the pair of spring portions 24a are preferably configured and arranged so as to act on opposing positions on both side surfaces of the convex portion 52a of the outer pad 52, as shown in FIG. That is, the action points of the pair of spring portions 24a are opposed to each other. Therefore, in this embodiment, the pad support member 24 is not easily inclined from the normal position during the brake operation, and the outer pad 52 is easily returned to the original floating position after the brake operation. The state in which the degree is secured is reliably maintained. On the other hand, in the conventional configuration shown in FIG. 6A, when the outer pad 52 is displaced in the inner circumferential direction, the pad support member 24 is inclined from the normal position as shown in FIG. 6B. However, the rotational degree of freedom of the cylinder 30 is further restricted. Further, in this embodiment, by causing the contact positions of the pair of spring portions 24a to face each other, normally, the rotational moment does not act on the support end (the convex portion 52a) of the outer pad 52, and within the concave portion 22 of the mounting 20 The position of the convex portion 52a of the outer pad 52 is stabilized.

  However, as long as the pair of spring portions 24a can bias and support the convex portion 52a of the outer pad 52 so that the convex portion 52a of the outer pad 52 can be displaced in the inner and outer peripheral directions within the concave portion 22 of the mounting 20, The aspect may be sufficient. For example, even if the pair of spring portions 24a urge and support the convex portion 52a of the outer pad 52 in a manner in which the rotational moment is generated at one support end of the outer pad 52, the rotational moment is the other support end. It is sufficient if the relationship is balanced with the rotational moment at. The pair of spring portions 24a is not limited to being formed by bending, and may be formed by curl bending as shown in FIG. Further, even if the connecting portion connecting the two spring portions is in contact with the bottom portion of the concave portion 22 of the mounting 20 (see FIG. 3), the connecting portion is in the inner and outer directions of the concave portion 22 of the mounting 20. It may be in contact with the side surface (see FIG. 7). Further, the pair of spring portions 24 a do not necessarily need to be configured by a leaf spring as shown in FIG. 3, and need not be formed integrally with the pad support member 24.

  The preferred embodiments of the present invention have been described in detail above. However, the present invention is not limited to the above-described embodiments, and various modifications and substitutions can be made to the above-described embodiments without departing from the scope of the present invention. Can be added.

  For example, as long as the convex portion 52a of the outer pad 52 is biased and supported so that the convex portion 52a of the outer pad 52 can be displaced in the inner and outer peripheral directions within the concave portion 22 of the mounting 20, the convex portion 52a of the outer pad 52 and the concave portion 22 of the mounting 20 are supported. Any of the individual detailed shapes and their shape relationships may be used.

FIG. 1 is a top view showing an embodiment of a disc brake 10 according to the present invention. It is AA sectional drawing of FIG. It is an enlarged view of the X section of Drawing 1 showing details of support structure 40. It is explanatory drawing which shows the behavior of the disc brake 10 of a present Example at the time of a brake action. FIG. 5 (A) shows the behavior of the disc brake 10 of the present embodiment when the brake is operated, and FIG. 5 (A) is an explanatory diagram showing the behavior of a conventional disc brake as a comparative example. It is a figure which shows the conventional support structure as a comparative example. It is a perspective view which shows the alternative Example of the spring part 24a.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Disc brake 14 Disc rotor 20 Mounting 22 Concave 24 Pad support member 24a Spring part 30 Cylinder 32 Claw part 34 Piston 40 Support structure 51 Inner pad 52 Outer pad 52a Convex part

Claims (5)

In the disc brake in which the disc rotor is disposed between the inner pad and the outer pad,
The outer pad is supported by the mounting member so as to be movable in a predetermined direction in a plane substantially parallel to the disk rotor surface, and the inner pad is supported by the mounting member so as to be movable in a direction substantially opposite to the predetermined direction. A disc brake characterized by   The disc brake according to claim 1, wherein the outer pad and the inner pad are supported so as to be reciprocable in the predetermined direction.   The disc brake according to claim 2, wherein a pad support member that urges the pad from two directions along the predetermined direction to elastically support the pad is provided for each of the inner pad and the outer pad.   The disc brake according to claim 3, wherein the elastic support position of the pad by the pad support member is opposed in the predetermined direction.   The disc brake according to claim 1, wherein rotation of the cylinder rotatably supported with respect to the mounting member with respect to the mounting member is assisted by the movement of the outer pad and the inner pad with respect to the mounting member.

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