JP2013155761A - Disk brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disk brake device that can reduce a noise in braking.SOLUTION: A disk brake device includes a disk rotor 2, a friction pad 3, and a pad connection 81. The disk rotor 2 is provided so as to be integrally rotatable with a wheel. The friction pad 3 is in contact with or separated from the disk rotor 2 when a caliper is slidably moved to a mounting. The friction pad 3 includes a friction material and a backing strip 32. The pad connection 81 has a projection 82 projected from a cylinder claw member 73 and a recess 83 provided on the backing strip 32 and penetrated with the projection 82. A vertical face 82a and a vertical inner face 83a mutually received with a load in braking are provided between the center P and ends 32a and 32b of the backing strip 32, and also in a position closer to the center P (containing center Pa) than the centers Pa and Pb between the center P of the backing strip 32 and the ends 32a and 32b of the backing strip 32.

Description

  The present invention relates to a disc brake device.

  Conventionally, a disc brake device (see, for example, Patent Document 1) applies a braking force to a wheel by a frictional force generated by pressing a friction pad against a friction surface of a disc rotor that rotates with the wheel.

JP 2008-144890 A

  By the way, the disc brake device described in Patent Document 1 as described above has room for further improvement in terms of reduction of squeal during braking, for example.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a disc brake device that can reduce noise during braking.

  In order to achieve the above object, a disc brake device according to the present invention is provided with a mounting attached to a vehicle body, a disc rotor integrally provided with a wheel so as to be rotatable around an axis, and a sliding movement on the mounting. And when the caliper is slid to the mounting by the driving force of the braking force driving source, the frictional surface of the disk rotor is provided. A friction pad having a friction material slidably contacted with the friction material, a back pad fixed to the friction material and connected to the braking force drive source, and provided on one of the braking force drive source and the back plate. A pad connecting portion having a convex portion and a concave portion that is provided on the other side and into which the convex portion enters, and when the friction material is in sliding contact with the friction surface The contact surfaces of the convex portions and the concave portions that receive loads from each other are between the center of the disk rotor in the rotational direction and the end portion of the back metal in the rotational direction when viewed in the axial direction, and It is characterized by being provided closer to the center of the back metal in the rotational direction than the center between the center of the back metal in the rotational direction and the end of the back metal in the rotational direction.

  Further, in the disc brake device, when the friction material is slidably contacted with the friction surface, the contact surface of the convex portion and the concave portion, which receive a load from each other, has the rotation direction of the back metal in the axial direction view. And a center between the end of the back metal and the one end in the rotation direction.

  The disc brake device according to the present invention can suppress the frictional force fluctuation between the friction pad and the disc rotor by suppressing the bending of the friction pad during braking, and can reduce so-called in-plane noise. There is an effect.

FIG. 1 is a schematic configuration diagram illustrating a disc brake device according to an embodiment. FIG. 2 is a cross-sectional view showing a main part of the disc brake device according to the embodiment. FIG. 3 is a side view showing the positional relationship between the disc rotor and the friction pad of the disc brake device according to the embodiment. FIG. 4 is a cross-sectional view (a cross-sectional view taken along line IV-IV in FIG. 3) showing the positional relationship between the disk rotor and the friction pad of the disk brake device according to the embodiment. FIG. 5 is a cross-sectional view showing the positional relationship between the disc rotor and the friction pad in the braking state of the disc brake device according to the embodiment.

  Hereinafter, embodiments of a disc brake device according to the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same.

[Embodiment]
FIG. 1 is a schematic configuration diagram showing a disc brake device according to the embodiment, FIG. 2 is a cross-sectional view showing a main part of the disc brake device according to the embodiment, and FIG. 3 is a disc rotor of the disc brake device according to the embodiment. FIG. 4 is a side view showing the positional relationship between the friction pad and the friction pad, and FIG. 4 is a sectional view showing the positional relationship between the disk rotor and the friction pad of the disc brake device according to the embodiment (sectional view taken along line IV-IV in FIG. FIG. 5 is a cross-sectional view showing the positional relationship between the disc rotor and the friction pad in the braking state of the disc brake device according to the embodiment.

  A disc brake device (hereinafter simply referred to as a brake device) 1 of the present embodiment shown in FIGS. 1 and 2 is typically mounted on a vehicle and brake force is applied to a wheel rotatably supported on the vehicle body of the vehicle. Is given. The brake device 1 generates a braking force by pressing the friction pads 3 and 4 against the disc rotor 2 by a floating caliper 5 supported by the mounting 6. In this caliper floating brake device 1, the caliper 5 is slidably supported with respect to the mounting 6 in the direction of the rotation axis L of the wheel (indicated by an arrow in FIG. 1 and corresponding to the axis of the claims). Has been.

  Specifically, as shown in FIG. 1, the brake device 1 includes a disk rotor 2, a pair of friction pads 3, 4, a mounting 6, a caliper 5, a caliper slide mechanism 7, and a pad connection portion 81 ( (Shown in FIG. 3).

  The disk rotor 2 is formed in a substantially disk shape. The disc rotor 2 is attached to the axle and is provided integrally with the wheel so as to be rotatable about an axle rotation axis L (indicated by a one-dot chain line in FIG. 1). That is, the disk rotor 2 rotates in the direction of arrow M shown in FIG. 1 (hereinafter referred to as the rotation direction of the disk rotor 2) along the circumferential direction centered on the rotation axis L. That is, the rotation direction M is a direction intersecting (orthogonal in the illustrated example) with respect to the rotation axis L as a slide movement direction of the caliper 5 with respect to the mounting 6.

  The friction pads 3 and 4 are provided to face the friction surfaces 2a and 2b on both sides of the disk rotor 2, respectively. The friction pads 3 and 4 have a rectangular parallelepiped appearance. As shown in FIG. 3, the longitudinal direction of the friction pads 3, 4 is the longitudinal center P (shown in FIG. 3) of the back metal 32, 42 of the friction pads 3, 4 (only the friction pad 3 is shown in FIG. 3). ) Perpendicular to the radial direction of the disk rotor 2 in FIG. The friction pads 3 and 4 are configured by the friction materials 31 and 41 being fixed to the back metal 32 and 42, respectively. The friction pad 3 is disposed on the side of a cylinder support 53 of a caliper body 51 to be described later, forms an inner pad and corresponds to the friction pad of the claims, and the friction pad 4 is on the reaction part 54 side of the caliper body 51. The outer pad is arranged. In the friction pad 3, the back metal 32 is connected to a cylinder pawl member 73, which will be described later, of the cylinder mechanism 52 via a pad connection portion 81, and the back metal 32 is superimposed on the cylinder support portion 53. In the friction pad 4, the back metal 42 is supported by the reaction part 54 of the caliper 5 so as to be fixed or movable. Thus, the friction pads 3 and 4 are provided on the caliper 5. As will be described later, the friction pads 3 and 4 are provided on the caliper 5 so that the caliper 5 is slid in the direction of the rotation axis L with respect to the mounting 6 by the caliper slide mechanism 7 so as to be able to contact with and separate from the friction surfaces 2a and 2b. It has been. In addition, approaching / separating means approaching or leaving.

  The mounting 6 is attached to the vehicle body via a suspension, an intermediate beam, and the like. The mounting 6 is integrally provided with a pair of sleeves 61 provided at intervals in the rotational direction M of the disk rotor 2 and a connecting portion 62 that connects the pair of sleeves 61. Each of the sleeves 61 is formed in a cylindrical shape having one end opened and the other end closed. Inside the sleeve 61, a hole 63 having a circular cross section and a constant inner diameter in the longitudinal direction is formed. As for the hole 63 of each sleeve 61, one end of the caliper 5 on the side of the arm portion 59 described later opens at the end surface of the sleeve 61 and the other end on the side away from the arm portion 59 is closed in the sleeve 61. . The hole 63 of each sleeve 61 extends along the rotation axis L of the disk rotor 2.

  The caliper 5 includes a caliper body 51 and a switching unit 60. As schematically shown in FIG. 2, the caliper body 51 includes a cylinder support portion 53 that is opposed to the one friction surface 2a of the disk rotor 2 with a gap and a reaction that is opposed to the other friction surface 2b. The cross-sectional shape cut | disconnected in the rotating shaft L direction is formed in the U-shape including the connection part 55 which connected the part 54, the cylinder support part 53, and the reaction part 54. As shown in FIG. The caliper body 51 includes a cylinder support portion 53 and a reaction portion 54 that are spaced from both the friction surfaces 2 a and 2 b, so that the caliper body 51 is arranged in a manner that straddles the disc rotor 2. The caliper body 51, that is, the caliper 5 is slidably moved along the rotation axis L with respect to the mounting 6 by the caliper slide mechanism 7.

  The switching unit 60 includes a cylinder mechanism 52 as a braking force drive source and a boot 72. The cylinder mechanism 52 is provided on the cylinder support portion 53 of the caliper body 51. That is, the cylinder mechanism 52 is provided in the caliper 5. As shown in FIG. 2, the cylinder mechanism 52 is attached to the cylinder body 56 integrally provided in the cylinder support portion 53, a piston 57 slidably provided in the cylinder body 56, and the piston 57. And a cylinder claw member 73. The cylinder body 56 is formed in a bottomed cylindrical shape with one end facing the disc rotor 2 opened. A packing 58 is provided on the inner surface of the cylinder body 56 to form a seal mechanism that keeps the inner surface of the cylinder body 56 and the piston 57 fluid-tight. The piston 57 is in contact with the base end surface of the back metal 32 of the friction pad 3 through the cylinder pawl member 73. The cylinder pawl member 73 is formed in a thick flat plate shape, and is attached to the piston 57 so as to be superimposed on the front end surface of the piston 57. The cylinder pawl member 73 is provided between the tip surface of the piston 57 and the friction pad 3. In the cylinder body 56, hydraulic oil is supplied from the master cylinder in response to the driver's depression operation of the brake pedal.

  The boot 72 is made of an elastic material such as rubber and is formed in a bellows-like cylindrical shape. The boot 72 is mounted between a sleeve 61 of the mounting 6 and a base end portion of the slide pin 71 through a slide pin 71 described later on the inside. The boot 72 is attached to both the sleeve 61 and the base end portion of the slide pin 71. The boot 72 covers a gap between the sleeve 61 of the mounting 6 and the proximal end portion of the slide pin 71. The boot 72 can prevent foreign matter from entering the hole 63. When the caliper 5 slides along the rotation axis L with respect to the mounting 6, the boot 72 is elastically deformed so that the entire length is enlarged and reduced.

  When hydraulic oil is supplied into the cylinder body 56 of the cylinder mechanism 52, the switching unit 60 causes the piston 57 to approach one friction surface 2a by the hydraulic pressure of the hydraulic oil, and the friction pad 3 is moved to the friction surface 2a of the disc rotor 2. Press on. Further, the switching unit 60 slides the caliper 5 to press the friction pad 4 against the friction surface 2 b of the disk rotor 2. Further, when the hydraulic fluid is not supplied into the cylinder main body 56 of the cylinder mechanism 52 without depressing the brake pedal, the switching unit 60 depressurizes the hydraulic oil in the cylinder main body 56. Then, the switching unit 60 is in a neutral state in which the entire length is reduced by the elastic restoring force and the boot 72 is not elastically deformed, and the friction pads 3 and 4 are separated from the friction surfaces 2 a and 2 b of the disk rotor 2. For this reason, when the hydraulic fluid is supplied into the cylinder body 56 of the cylinder mechanism 52, the switching unit 60 enters a braking state in which the friction pads 3 and 4 are pressed against the friction surfaces 2a and 2b of the disc rotor 2. The switching unit 60 enters a non-braking state in which the friction pads 3, 4 are separated from the friction surfaces 2 a, 2 b of the disk rotor 2 unless hydraulic fluid is supplied into the cylinder body 56. Thus, the switching unit 60 can switch between the braking state and the non-braking state depending on whether hydraulic oil is supplied into the cylinder body 56, that is, whether the brake pedal is depressed. Yes. Further, the switching unit 60 moves the caliper 5 with respect to the mounting 6 so that the friction pads 3 and 4 contact and separate from the friction surfaces 2a and 2b in conjunction with switching between the braking state and the non-braking state. Move the slide. Thus, when the caliper 5 is slid to the mounting 6 by the driving force of the cylinder mechanism 52 of the switching unit 60, the friction material 31 of the friction pad 3 is brought into sliding contact with the friction surface 2a of the disk rotor 2.

  The caliper slide mechanism 7 supports the caliper 5 on the mounting 6 so as to be slidable along the rotation axis L. The caliper slide mechanism 7 includes the above-described holes 63 and slide pins 71 corresponding to the holes 63. The slide pin 71 is fixed to an arm portion 59 whose base end portion protrudes forward and backward in the rotational direction M from the outer edge of the cylinder support portion 53 of the caliper body 51. A total of two slide pins 71 are provided. The slide pin 71 is formed in a cylindrical shape parallel to the rotation axis L. The tip of the slide pin 71 is movably inserted into the hole 63. In the caliper slide mechanism 7 having the above-described configuration, the slide pin 71 is inserted into the hole 63 so that the caliper 5 is slidably supported on the mounting 6 along the rotation axis L via the slide pin 71. .

  As shown in FIGS. 3, 4, and 5, the pad connecting portion 81 is provided on the cylinder pawl member 73 of the cylinder mechanism 52 and protrudes from the cylinder pawl member 73 toward the back metal 32 of the friction pad 3. And a recess 83 provided in the back metal 32 of the friction pad 3. Two protrusions 82 and two recesses 83 are provided. The convex portion 82 and the concave portion 83 each extend linearly.

  The two convex portions 82 are provided in parallel to each other with a gap in the longitudinal direction of the friction pad 3. When viewed from a position away from the rotation axis L, that is, as viewed in the direction of the rotation axis L, the convex portion 82 has a longitudinal direction of the back metal 32 of the friction pad 3, that is, a center P in the rotation direction M (shown in FIG. 3). It is provided between the longitudinal direction of the back metal 32, that is, the end in the rotational direction M (corresponding to one end and the other end) 32a and 32b. The longitudinal direction of the convex portion 82 intersects the rotational direction M. In other words, the convex portion 82 extends linearly so as to intersect the rotational direction M. The convex portion 82 is formed in a rectangular shape whose cross-sectional shape intersecting the longitudinal direction is convex from the surface of the back metal 32. That is, the convex portion 82 includes two vertical surfaces 82 a and 82 b (corresponding to the outer surface) orthogonal to the surface of the back metal 32, and a parallel surface that connects the vertical surfaces 82 a and 82 b and is parallel to the surface of the back metal 32. 82c (corresponding to the outer surface). The vertical surfaces 82a of the two protrusions 82 are, as viewed in the direction of the rotation axis L, the longitudinal direction of the back metal 32 of the friction pad 3, that is, the center P in the rotational direction M (shown in FIG. 3) and the longitudinal direction of the back metal 32 of the friction pad 3. Between the ends 32a and 32b in the direction of rotation M, and closer to the center P than the centers Pa and Pb (shown in FIG. 3) between the center P and the ends 32a and 32b. ing. Of the two protrusions 82, the vertical surface 82a of the upper one protrusion 82 in FIG. 3 is the longitudinal direction of the back metal 32 of the friction pad 3, that is, the center P in the rotation direction M (see FIG. 3). And a center Pa between the longitudinal direction of the back metal 32 of the friction pad 3, that is, one end 32 a in the rotation direction M.

  The two recesses 83 are provided in parallel to each other with a gap in the longitudinal direction of the friction pad 3. The longitudinal direction of the recess 83 intersects the rotation direction M. That is, the recess 83 extends linearly so as to intersect the rotational direction M. The recess 83 is formed in a rectangular shape having a cross-sectional shape intersecting with the longitudinal direction and recessed from the surface of the cylinder claw member 73. That is, the recess 83 connects two vertical inner surfaces 83 a and 83 b (corresponding to the inner surface) perpendicular to the surface of the cylinder claw member 73 and the vertical inner surfaces 83 a and 83 b and is parallel to the surface of the cylinder claw member 73. And a parallel inner surface 83c (corresponding to the inner surface). The concave portion 83 is formed slightly larger than the convex portion 82. The concave portion 83 allows the convex portion 82 to enter inside. The pad connecting portion 81 connects the back metal 32 of the friction pad 3 and the cylinder claw member 73 by causing the convex portion 82 to enter the concave portion 83. The vertical surface 82a and the vertical inner surface 83a form a contact surface that is in close contact with each other and receives (acts with) each other when braking, that is, when the friction material 31 is slidably contacted with the friction surface 2a. Yes.

  In the brake device 1 having the above-described configuration, for example, when the driver does not depress the brake pedal, the switching unit 60 is in a non-braking state, and as shown in FIG. The friction surfaces 2a and 2b are spaced from each other (only the friction pad 3 is shown in FIG. 4). In the brake device 1, for example, when the driver depresses the brake pedal, the hydraulic oil is supplied into the cylinder body 56 of the cylinder mechanism 52, and the hydraulic oil causes the piston 57 and the cylinder pawl member 73 to move. Pressure is applied toward the friction surface 2 a of the disk rotor 2. Then, the piston 57 and the cylinder claw member 73 move forward in the direction of arrow B in FIG. 2, and the cylinder claw member 73 attached to the tip surface of the piston 57 presses the back metal 32 of the friction pad (inner pad) 3. The friction pad 3 is brought close to the friction surface 2 a of the disk rotor 2. Further, at this time, the caliper 5 moves forward in the direction opposite to the piston 57 and the cylinder pawl member 73, that is, in the direction of arrow C in FIG. The pad (outer pad) 4 is brought close to the friction surface 2b of the disc rotor 2, and an elastic restoring force is generated in a direction in which the boot 72 extends and the overall length decreases.

  In the brake device 1, the switching unit 60 is switched to the braking state, and the friction pads 3 and 4 are pressed against the friction surfaces 2 a and 2 b of the disk rotor 2 to sandwich the disk rotor 2. As shown in FIG. 5, the brake device 1 is configured such that the friction materials 31 and 41 of the friction pads 3 and 4 are brought into sliding contact with the friction surfaces 2 a and 2 b of the disk rotor 2, A frictional resistance is generated between the disk rotor 2 and the disk rotor 2 rotating together (only the friction pad 3 is shown in FIG. 5). The brake device 1 applies a predetermined rotational resistance force to the disk rotor 2 and applies a braking force to the disk rotor 2 and the wheels that rotate integrally therewith. When the friction materials 31 and 41 are slidably contacted with the friction surfaces 2a and 2b, the vertical surface 82a as the outer surface of the convex portion 82 and the vertical inner surface 83a as the inner surface of the concave portion 83 are in close contact with each other. Contact each other and receive a load on each other. The vertical surface 82a and the vertical inner surface 83a that receive these loads are rotated between the center P in the rotational direction M of the back metal 32 and the end portions 32a and 32b and viewed from the rotation axis L direction. It is provided closer to the center P in the rotation direction M of the back metal than the centers Pa and Pb between the center P in the direction M and the end portions 32a and 32b. Further, in the one convex portion 82 and the concave portion 83 in the upper part in FIG. 3, the vertical surface 82a and the vertical inner surface 83a that receive loads from each other when viewed in the direction of the rotational axis L are the center P in the rotational direction M of the back metal 32 and It is provided at the center Pa between the end 32a. As described above, the vertical surface 82a and the vertical inner surface 83a as contact surfaces in the present invention are the center P in the rotational direction M of the disc rotor 2 of the back metal 32 and the rotational direction M of the back metal 32 when viewed in the direction of the rotation axis L. Between the ends 32a and 32b, and between the centers Pa and Pb between the center P in the rotational direction M of the back metal 32 and the ends 32a and 32b in the rotational direction M of the back metal 32, the rotational direction M of the back metal 32 is larger. Providing closer to the center P means that the vertical surface 82a and the vertical inner surface 83a are provided near the centers Pa and Pb and closer to the center P than the centers Pa and Pb.

  In addition, when the brake pedal 1 is no longer depressed by the driver, the brake device 1 does not supply hydraulic oil to the cylinder main body 56 of the cylinder mechanism 52, and removes the pressure of the hydraulic oil in the cylinder main body 56. Pressed. Then, in the brake device 1, the piston 57 and the cylinder claw member 73 are retracted and the caliper body 51 is retracted by the elastic restoring force of the boot 72, so that the switching unit 60 is switched to the non-braking state, and the friction pads 3 and 4 are Separated from the rotor 2. Thus, in the brake device 1, when the driver does not depress the brake pedal, the switching unit 60 enters the non-braking state. As described above, the switching unit 60 switches between the non-braking state and the braking state depending on whether or not the brake pedal is depressed.

  In the brake device 1 configured as described above, the vertical surface 82a of the convex portion 82 and the vertical inner surface 83a of the concave portion 83 that receive loads from each other when the pad connecting portion 81 is braked rotate the back metal 32 in the direction of the rotation axis L. It is provided between the center P in the direction M and the ends 32a and 32b and closer to the center P than the centers Pa and Pb between the center P and the ends 32a and 32b. For this purpose, the distance D between the center P of the back plate 32, which is the point of action of the reaction force acting on the back plate 32 of the friction pad 3 from the disk rotor 2 during braking, and the aforementioned vertical surface 82a and vertical inner surface 83a that receive the load. , D ′ (shown in FIG. 3) can be suppressed. Therefore, the bending of the back metal 32, that is, the friction pad 3 at the time of braking can be suppressed.

  Here, it is known that the frictional force fluctuation between the disk rotor 2 and the friction pads 3 and 4 acts on the disk rotor 2 as a vibration force generated in the circumferential direction and an in-plane (extension / contraction) vibration. In addition, when the frictional force fluctuation between the disk rotor 2 and the friction pads 3 and 4 increases, the vibration force generated in the circumferential direction of the disk rotor 2 and the in-plane (extension / contraction) vibration increase, so-called in-plane noise, that is, during braking. It is known that the squeal becomes louder.

  Therefore, the brake device 1 can suppress deformation of the friction pads 3 and 4 during braking, and can suppress fluctuations in the frictional force between the friction pads 3 and 4 and the disk rotor 2 due to a load acting during braking. Therefore, the brake device 1 can suppress the vibration force generated in the circumferential direction of the disc rotor 2, and can reduce so-called in-plane noise, that is, noise during braking.

  Further, in the upper convex portion 82 and the concave portion 83 in FIG. 3, the vertical surface 82a and the vertical inner surface 83a that receive loads from each other at the time of braking, It is provided at the center Pa between the end 32a. For this purpose, the distance D between the center P of the back plate 32, which is the point of action of the reaction force acting on the back plate 32 of the friction pad 3 from the disk rotor 2 during braking, and the aforementioned vertical surface 82a and vertical inner surface 83a that receive the load. Can be reliably suppressed. Therefore, the bending of the back metal 32, that is, the friction pad 3 during braking can be reliably suppressed. Therefore, the brake device 1 can surely suppress the vibration force generated in the circumferential direction of the disc rotor 2, and can reliably reduce so-called in-plane noise, that is, noise during braking.

  In the brake device 1 described above, the pad connecting portion 81 includes two convex portions 82 and two concave portions 83. However, in the present invention, the vertical surface 82a and the vertical inner surface 83a described above are the center P and one end portion 32a. May be provided with one or three or more convex portions 82 and concave portions 83. That is, in the present invention, if the convex portion 82 and the concave portion 83 are provided closer to the center P than the centers Pa and Pb between the center P and one end portion 32a, the number of the convex portions 82 and the concave portions 83 is provided. May be. Further, when a plurality of the convex portions 82 and the concave portions 83 are provided, the convex portions 82 and the concave portions 83 may not be provided in a straight line. Moreover, the vertical surface 82a of the at least one convex portion 82 and the vertical inner surface 83a of the concave portion 83 that are in close contact with each other at the time of braking may be provided at the center Pa between the center P and the one end portion 32a. In addition, as long as at least a part of the outer surface and the inner surface can be configured as contact surfaces that can receive loads from each other at the time of braking, the convex portion 82 and the concave portion 83 are not limited to the above-described embodiment, and may have various shapes. Can do.

  The brake device 1 according to the present invention described above is not limited to the above-described embodiment, and various modifications can be made within the scope described in the claims.

DESCRIPTION OF SYMBOLS 1 Disc brake device 2 Disc rotor 2a Friction surface 3 Friction pad 5 Caliper 6 Mounting 31 Friction material 32 Back metal 32a One end 52 Cylinder mechanism (braking force drive source)
81 Pad connection part 82 Convex part 82a Vertical surface (contact surface)
83 Concave part 83a Vertical inner surface (contact surface)
L Rotation axis (axis)
M Rotation direction P Center D Distance

Claims (2)

Mounting mounted on the car body,
A disc rotor provided integrally with the wheel so as to be rotatable about an axis, and
A caliper provided slidably on the mounting;
A braking force drive source provided in the caliper;
A friction material provided on the caliper and slidably contacted with a friction surface of the disk rotor when the caliper is slid to the mounting by a driving force of the braking force driving source; and fixed to the friction material; A friction pad having a backing metal connected to a braking force drive source;
A pad connecting portion having a convex portion provided on one of the braking force drive source and the back metal and a concave portion provided on the other and into which the convex portion enters,
When the friction material is slidably contacted with the friction surface, the contact surfaces of the convex portion and the concave portion that receive a load are the center of the back rotor in the rotation direction of the disc rotor and the back metal in the axial direction view. Between the end in the rotation direction of the back metal and closer to the center of the back metal in the rotation direction than the center between the center in the rotation direction of the back metal and the end in the rotation direction of the back metal. It is characterized by
Disc brake device. When the friction material is slidably contacted with the friction surface, the contact surface of the convex portion and the concave portion that receive a load is the center of the back metal in the rotational direction and the rotation of the back metal in the axial direction view. Provided in the center between one end of the direction,
The disc brake device according to claim 1.

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