JP2013139848A - Disk rotor and disk brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disk rotor and a disk brake device that can reduce a squeak in braking.SOLUTION: This disk brake device 1 includes a caliper and the disk rotor 2. The caliper is provided with friction pads for contacting with/separating from the disk rotor 2 when slidingly moved to a mounting 6. The disk rotor 2 has an inner rotor 86, an outer rotor 87 superposed at an interval on the inner rotor 86, and fins 88 and connecting parts 90 arranged between the rotors 86 and 87. The inner rotor 86 is divided into a plurality of inner rotor members 86a juxtaposed in the peripheral direction. The outer rotor 87 is divided into a plurality of outer rotor members 87a juxtaposed in the peripheral direction. The connecting part 90 connects the outer rotor member 87a and the inner rotor member 86a mutually adjacent in the peripheral direction.

Description

  The present invention relates to a disc rotor and a disc brake device.

  2. Description of the Related Art Conventionally, a disc brake device 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 (for example, see Patent Document 1) that rotates with the wheel. The disk rotor disclosed in Patent Document 1 is provided between an inner rotor that is in sliding contact with a friction pad as an inner pad, an outer rotor that is superimposed on the inner rotor and that is in sliding contact with a friction pad as an outer pad, and an inner rotor and an outer rotor. And a fin for connecting the two.

JP 2008-95941 A

  By the way, the disk brake device provided with the disk rotor 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 thereof is to provide a disc rotor and a disc brake device that can reduce squeal during braking.

  In order to achieve the above object, the disk rotor according to the present invention is divided into a plurality of inner rotor members arranged in the circumferential direction, and the caliper is slid to the mounting attached to the vehicle body so that the friction pad becomes a friction surface. It is divided into an inner rotor that contacts and separates and a plurality of outer rotor members that are superimposed on the inner rotor in the axial direction and aligned in the circumferential direction, and the caliper slides on the mounting so that the friction pad contacts and separates from the friction surface. An outer rotor member, and the inner rotor and the outer rotor are divided into the plurality of inner rotor members and the plurality of outer rotor members at the same position in the axial direction, and are adjacent to each other in the axial direction view. For connecting the inner rotor member to the inner rotor member Characterized in that it comprises.

  In the disk rotor, the number of divisions of the inner rotor member and the outer rotor member is preferably determined based on the order of the vibration mode.

  The disc brake device according to the present invention comprises: a mounting attached to a vehicle body; a caliper provided with a friction pad; a caliper slide mechanism that slidably supports the caliper on the mounting; and the disc rotor according to claim 1. And.

  The disc rotor and disc brake device according to the present invention can suppress the in-plane (extension / contraction) vibration in the circumferential direction of the inner rotor and the outer rotor, so that the so-called in-plane noise can be reduced.

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 perspective view showing a disc rotor and an axle of the disc brake device according to the embodiment. FIG. 4 is a plan view showing the configuration of the disc rotor of the disc brake device according to the embodiment. FIG. 5 is a partial cross-sectional view (a cross-sectional view taken along line VV in FIG. 4) showing the configuration of the disk rotor of the disk brake device according to the embodiment. FIG. 6 is a plan view showing a configuration of a disc rotor of a disc brake device according to a modified example of 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 plan view showing the configuration of the disc rotor of the disc brake device according to the embodiment, and FIG. 5 is a partial view showing the configuration of the disc rotor of the disc brake device according to the embodiment. It is sectional drawing (sectional drawing in alignment with the VV line in FIG. 4).

  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 supported so as to be slidable with respect to the mounting 6 in the direction of the rotation axis L of the wheel (indicated by an arrow in FIG. 1).

  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, and a caliper slide mechanism 7.

  The disk rotor 2 is formed in a substantially disk shape. The disc rotor 2 is attached to an axle A (shown in FIG. 3), and can rotate around a rotation axis L (shown by a one-dot chain line in FIG. 1 and corresponding to the axis) integrally with the wheel. Is provided. 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 detailed configuration of the disk rotor 2 will be described later.

  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 are configured by the friction materials 31 and 41 being fixed to the back metal 32 and 42, respectively. The friction pad 3 is arranged on the side of a cylinder support 53 of the caliper body 51 described later to form an inner pad, and the friction pad 4 is arranged on the side of the reaction part 54 of the caliper body 51 to form an outer pad. The friction pad 3 is supported by a pair of guide members formed on the mounting 6 at the front and rear ends of the back metal 32, and the back metal 32 is overlaid on the cylinder support 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 supported by the caliper slide mechanism 7 so as to be slidable along the rotation axis L with respect to the mounting 6.

  The switching unit 60 includes a cylinder mechanism 52 as a hydraulic cylinder 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. The cylinder mechanism 52 includes a cylinder main body 56 provided integrally with the cylinder support portion 53 and a piston 57 provided slidably in the cylinder main body 56. 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 face of the back metal 32 of 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.

  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. .

  The disc rotor 2 is a so-called ventilated disc rotor, and as shown in FIGS. 3 and 4, a mounting portion 81 attached to the wheel hub H of the axle A, an annular sliding plate portion 82, And a nut N as a fastening member. The mounting portion 81 includes a cylindrical cylindrical portion 83 erected from an inner edge of an inner rotor 86 (described later) of the sliding plate portion 82, and a disk-shaped disc portion 84 that closes the tip of the cylindrical portion 83. The disc portion 84 is provided with a plurality of mounting holes 85 through which stat bolts HB standing from the wheel hub H are inserted. In the illustrated example, twelve mounting holes 85 and stat bolts HB are provided at equal intervals in the circumferential direction around the rotation axis L.

  The sliding plate portion 82 includes an annular inner rotor 86, an annular outer rotor 87 that is overlapped with the inner rotor 86 in the direction of the rotation axis L with a space therebetween, and a plurality of portions provided between the inner rotor 86 and the outer rotor 87. The fin 88 and the connection part 90 are provided.

  The inner rotor 86 is opposed to the friction pad 3 as an inner pad. As the caliper 5 slides on the mounting 6, the friction pad 3 contacts and separates from the inner rotor 86. In the inner rotor 86, the friction pad 3 is in sliding contact with the surface. That is, the surface of the inner rotor 86 is one friction surface 2a. The inner rotor 86 includes a plurality (four in the embodiment) of inner rotor members 86a arranged in the circumferential direction. That is, the inner rotor 86 is divided into a plurality (four in the embodiment) of inner rotor members 86a arranged in the circumferential direction. The four inner rotor members 86a are formed in the same shape as each other, and the aforementioned cylindrical portion 83 is erected from the inner edge.

  Further, between the inner rotor members 86a adjacent to each other among the four inner rotor members 86a, a gap CI having a predetermined interval is provided as shown in FIG. The intervals of the four gaps CI provided between the inner rotor members 86a adjacent to each other are formed to be equal to each other. The inner rotor 86 is formed in an annular shape as a whole by arranging four inner rotor members 86a in the circumferential direction with a clearance CI between them. In the embodiment, the four inner rotor members 86a have one inner rotor member between 0 degree and 90 degrees, assuming that the circumferential center of the friction pad 3 described above is zero degree and a counterclockwise positive angle in FIG. 86a is arranged. One inner rotor member 86a is disposed between 90 degrees and 180 degrees, one inner rotor member 86a is disposed between 180 degrees and 270 degrees, and one inner rotor member 86a is disposed between 270 degrees and 360 degrees. ing.

  The outer rotor 87 is overlapped with the inner rotor 86 in the direction of the rotation axis L with a space therebetween, and is arranged coaxially with the inner rotor 86. The outer rotor 87 is opposed to the friction pad 4 as an outer pad. The outer rotor 87 slides the caliper 5 on the mounting 6 so that the friction pad 4 comes into contact with and separates from the surface. The outer rotor 87 has the friction pad 4 in sliding contact with the surface. That is, the surface of the outer rotor 87 is the other friction surface 2b. The outer rotor 87 is composed of a plurality (four in the embodiment) of outer rotor members 87a arranged in the circumferential direction. That is, the outer rotor 87 is divided into a plurality (four in the embodiment) of outer rotor members 87a arranged in the circumferential direction. The four outer rotor members 87a are formed in the same shape.

  Further, between the outer rotor members 87a adjacent to each other among the four outer rotor members 87a, a gap CO with a predetermined interval is provided as shown in FIG. The intervals of the four gaps CO provided between the outer rotor members 87a adjacent to each other are formed to be equal to each other. Further, the gap CO between the outer rotor members 87a adjacent to each other is equal to the gap CI between the inner rotor members 86a adjacent to each other. The outer rotor 87 is formed in an annular shape as a whole by arranging the four outer rotor members 87a in the circumferential direction with a gap CO provided therebetween. In the embodiment, the four outer rotor members 87a have one outer rotor member between 0 degree and 90 degrees when the circumferential center of the friction pad 4 described above is zero degrees and the counterclockwise in FIG. 4 is a positive angle. 87a is arranged. One outer rotor member 87a is disposed between 90 degrees and 180 degrees, one outer rotor member 87a is disposed between 180 degrees and 270 degrees, and one outer rotor member 87a is disposed between 270 degrees and 360 degrees. ing.

  Thus, as shown in FIG. 5, the clearance CI between the adjacent inner rotor members 86a and the clearance CO between the adjacent outer rotor members 87a are arranged in the direction of the rotation axis L. That is, the gap CO between the adjacent outer rotor members 87a is provided at a position whose phase (position) coincides with the gap CI between the adjacent inner rotor members 86a in the circumferential direction. Thus, the inner rotor 86 and the outer rotor 87 are divided into a plurality of inner rotor members 86a and a plurality of outer rotor members 87a at the same position in the rotation axis L direction. Further, the inner rotor member 86a and the outer rotor member 87a are provided between 0 degree and 90 degrees, between 90 degrees and 180 degrees, between 180 degrees and 270 degrees, and between 270 degrees and 360 degrees. Thus, if the rotors 86 and 87 are formed in a single ring shape, the above-described gaps CI and CO are provided at a position where the circumferential compressive load becomes maximum and a tensile load becomes maximum. ing. In the present embodiment, the circumferential compressive load is maximized at positions of 90 degrees and 270 degrees, and the circumferential tensile load is maximized at positions of 0 degrees and 180 degrees.

  The fin 88 is erected across the inner rotor member 86a and the outer rotor member 87a arranged in the direction of the rotation axis L, and integrally connects the inner rotor member 86a and the outer rotor member 87a. A plurality of fins 88 are provided at equal intervals in the circumferential direction. The longitudinal direction of the fin 88 is parallel to the radial direction of the disk rotor 2.

  As shown in FIGS. 3, 4, and 5, the connecting portion 90 is formed in a band plate shape and connects the inner rotor member 86 a and the outer rotor member 87 a that are adjacent to each other in the circumferential direction. Thus, when viewed from the position away from the rotation axis L, that is, when viewed in the direction of the rotation axis L, the connecting portion 90 connects the inner rotor member 86a and the outer rotor member 87a adjacent to each other. The connecting portion 90 connects the ends of the inner rotor member 86a and the outer rotor member 87a that are adjacent to each other to be erected. A plurality of (four in the embodiment) connecting portions 90 are provided by connecting the inner rotor member 86a and the outer rotor member 87a adjacent to each other in the circumferential direction. Both surfaces of the plurality of connecting portions 90 are inclined with respect to the rotation axis L. The inclination and the direction of the inclination with respect to the rotation axis L of both surfaces of the plurality of connecting portions 90 are equal to each other as shown in FIG.

  A nut N (only one is shown in FIG. 3 and the others are omitted) is screwed with a stat bolt HB inserted into the mounting hole 85. A plurality of nuts N are provided in the disk rotor 2 at intervals in the circumferential direction by screwing a stat bolt HB inserted into the mounting hole 85.

  In the disk rotor 2 configured as described above, the disk portion 84 of the mounting portion 81 is overlapped with the wheel hub H in a state where the inner rotor 86 is opposed to the friction pad 3 and the outer rotor 87 is opposed to the friction pad 4. At this time, the stat bolt HB is inserted into the mounting hole 85. Then, the nut N as a fastening member is screwed (fastened) into the stat bolt HB inserted into the mounting hole 85, and the disc rotor 2 is attached to the wheel hub H. In this way, the nut N is fastened to the wheel hub H of the axle A by both the disc rotor 2, that is, the inner rotor 86 and the outer rotor 87, when the stat bolt HB inserted into the mounting hole 85 is screwed.

  In the brake device 1 configured as described above, for example, when the driver does not depress the brake pedal, the switching unit 60 is in a non-braking state, and the friction pads 3 and 4 are spaced from the friction surfaces 2a and 2b. Is open. 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 to friction with the disk rotor 2. Pressure is applied toward the surface 2a. Then, the piston 57 advances in the direction of arrow B in FIG. 2, the front surface of the piston 57 presses the back metal 32 of the friction pad (inner pad) 3, and the front surface of the friction pad 3 is brought into contact with the friction surface 2 a of the disc rotor 2. Move closer. At this time, the caliper 5 moves forward in the direction opposite to the piston 57, that is, in the direction of arrow C in FIG. Is brought closer to the friction surface 2b of the disk 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. The brake device 1 generates a frictional resistance force between the friction pads 3 and 4 and the disk rotor 2 that rotates together with the wheels. 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.

  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 is retracted and the caliper body 51 is retracted by the elastic restoring force of the boot 72, the switching unit 60 is switched to the non-braking state, and the friction pads 3 and 4 are separated from the disk 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, when the gap CI between the inner rotor members 86a adjacent to each other and the gap CO between the outer rotor members 87a are formed in a single annular shape, It is provided at a position where the circumferential compressive load is maximized and at a position where the circumferential tensile load is maximized. For this reason, compressive loads or tensile loads in opposite directions act from the inner rotor member 86a and the outer rotor member 87a on the connecting portion 90 that connects the inner rotor member 86a and the outer rotor member 87a adjacent to each other in the circumferential direction.

  For example, mutually opposite compressive loads act on the connecting portion 90 provided at a position where the circumferential compressive load is maximized from the inner rotor member 86a and the outer rotor member 87a. On the connecting portion 90 provided at a position where the tensile load in the circumferential direction is maximized, tensile loads in directions opposite to each other act from the inner rotor member 86a and the outer rotor member 87a. For this reason, the compressive load and the tensile load acting on the inner rotor member 86a and the outer rotor member 87a can be canceled by the connecting portion 90 that connects the inner rotor member 86a and the outer rotor member 87a adjacent to each other in the circumferential direction. For this reason, the inner rotor 86 and the outer rotor 87 are less likely to be displaced in the circumferential direction, and are less likely to vibrate in an in-plane (expandable) manner. Therefore, the circumferential displacement and in-plane (extension / contraction) vibration of the inner rotor 86 and the outer rotor 87 can be suppressed as compared with the case where the inner rotor member 86a and the outer rotor member 87a that are adjacent to each other in the circumferential direction are not provided with a connecting portion. . Therefore, since circumferential displacement and in-plane (extension / contraction) vibration of the inner rotor 86 and the outer rotor 87 during braking can be suppressed, so-called in-plane noise, that is, noise during braking can be reduced.

[Modification]
Next, a modification of the embodiment of the disc brake device according to the present invention will be described in detail with reference to FIG. FIG. 6 is a plan view showing a configuration of a disc rotor of a disc brake device according to a modified example of the embodiment. In this modification, the same parts as those in the above-described embodiment will be described with the same reference numerals.

  In this modification, as shown in FIG. 6, the rotors 86 and 87 are each configured by being divided into two rotor members 86a and 87a. In the example shown in FIG. 6, one inner rotor member 86a and outer rotor member 87a are provided between 0 degree and 180 degrees, and one inner rotor member 86a and outer rotor member 87a are provided between 180 degrees and 360 degrees. Is provided.

  Also in this modified example, since the displacement of the inner rotor 86 and the outer rotor 87 extending and contracting in the circumferential direction during braking can be suppressed as in the above-described embodiment, so-called in-plane noise, that is, noise during braking can be reduced. .

  In the embodiment, the rotor members 86a and 87a are divided every 90 degrees to constitute the rotors 86 and 87, and in the modified example, the rotor members 86a and 87a are divided every 180 degrees to constitute the rotors 86 and 87. However, the present invention is not limited to this. In the present invention, the rotors 86 and 87 may be configured by dividing the rotor members 86a and 87a for each angle obtained by dividing 180 degrees by a natural number (the order of the vibration mode of the rotors 86 and 87). Thus, it is desirable that the number of divisions of the rotor members 86a and 87a is determined for the rotors 86 and 87 based on the order of the vibration mode. For example, when the vibration mode of the rotors 86 and 87 is the primary vibration mode, 180 degrees may be divided by 1 and divided into rotor members 86a and 87a every 180 degrees. When the vibration mode of the rotors 86 and 87 is the secondary vibration mode, 180 degrees may be divided by 2 and divided into rotor members 86a and 87a every 90 degrees. Thus, the rotors 86 and 87 may be divided for each angle corresponding to the order of the vibration mode of the rotors 86 and 87. In the present invention, the number (angle) of the inner rotor members 86a that divide the inner rotor 86 and the number (angle) of the outer rotor members 87a that divide the outer rotor 87 do not necessarily match, but the inner rotor 86 is divided. It is desirable to match the number (angle) of the inner rotor members 86a with the number (angle) of the outer rotor members 87a that divide the outer rotor 87.

  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, 2b Friction surface 3, 4 Friction pad 5 Caliper 6 Mounting 7 Caliper slide mechanism 86 Inner rotor 86a Inner rotor member 87 Outer rotor 87a Outer rotor member 90 Connection part L Rotation axis (axis line)

Claims (3)

An inner rotor that is divided into a plurality of inner rotor members arranged in the circumferential direction and in which the friction pad comes into contact with and separates from the friction surface by sliding the caliper to a mounting attached to the vehicle body;
An outer rotor that is divided into a plurality of outer rotor members that are axially overlapped with the inner rotor and arranged in the circumferential direction, and the friction pad is brought into contact with and separated from the friction surface by sliding the caliper to the mounting. ,
The inner rotor and the outer rotor are divided into the plurality of inner rotor members and the plurality of outer rotor members at the same position in the axial direction; and
In the axial direction view, comprising a connecting portion that connects the outer rotor member and the inner rotor member adjacent to each other,
Disc rotor.   The disk rotor according to claim 1, wherein the number of divisions of the inner rotor member and the outer rotor member is determined based on the order of the vibration mode. Mounting mounted on the car body,
Calipers with friction pads;
A caliper slide mechanism that slidably supports the caliper on the mounting;
A disk rotor according to claim 1,
Disc brake device.

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