JP2018100750A - Disk brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disk brake device for suppressing occurrence of an unusual sound by attenuating vibration of a disk rotor in braking.SOLUTION: A disk rotor 11 of a disk brake device 10 is configured to include a first rotor member 12 and a second rotor member 13 including slide contact parts 12b, 13b, and a support member 14 for the first rotor member 12 and the second rotor member 13 so as to be separated and oppose each other in a direction of a rotor shaft. The first rotor member 12 and the second rotor member 13 move such that opposing surfaces 12c, 13c are in contact when the slide contact parts 12b, 13b are pressed by a brake pad 16, and are supported by the support member 14 so as to be capable of moving relatively in a circumferential direction of a rotor in braking. The disk brake device 10 includes a first attenuation member 17 and a second attenuation member 18 that are interposed between the opposing surfaces 12c, 13c and attenuate vibration generated from the first rotor member 12 and the second rotor member 13 in braking.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a disc brake device that brakes a vehicle.

  Conventionally, for example, a disc brake device including a disc rotor disclosed in Patent Document 1 below is known. In this conventional disc brake device, a slit is formed in the hat portion or sliding portion of the disc rotor, and the slit is filled with a damping material that attenuates the vibration of the disc rotor generated during braking. Thereby, the vibration generated in the disk rotor is attenuated.

JP-A-10-26159

  However, in the conventional disc brake device, the area for filling the damping material is limited to the hat portion or the sliding portion, and the volume of the slit that can be formed to ensure the durability of the disc rotor is also limited. Further, when the slit provided in the sliding portion is filled with the damping material, the damping material is worn by sliding contact with the pair of brake pads. For these reasons, there is a possibility that the conventional disc brake device cannot sufficiently exhibit the damping performance for damping the vibration of the disc rotor during braking. In addition, in the conventional disc brake device, the disc rotor is formed as one member from one metal material. Therefore, it is difficult for the disk rotor itself to exhibit vibration damping performance during braking. As a result, there is a high possibility that the caliper and the disc rotor will resonate to generate abnormal noise (so-called brake noise).

  The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a disc brake device that attenuates the vibration of the disc rotor during braking and suppresses the generation of abnormal noise.

  In order to solve the above problems, a disc brake device according to a first aspect of the present invention includes a disc-like disc rotor that is coupled to a rotating member of a vehicle and rotates integrally with the rotating member, and an outer periphery in the circumferential direction of the disc rotor. The caliper is provided so as to straddle part of the part, is fixed to the non-rotating member of the vehicle, and is assembled to the caliper, and is pressed toward the disc rotor from both sides in the axial direction of the disc rotor to come into sliding contact with the disc rotor A disc brake device comprising a pair of brake pads, wherein the disc rotor is provided in an annular shape, and has a first rotor member having a sliding contact portion that is in sliding contact with each of the pair of brake pads on one surface side, and The first rotor member and the second rotor member are arranged so that the second rotor member and the first rotor member and the second rotor member are spaced apart from each other in the axial direction. A support member that supports the peripheral portion, and the first rotor member and the second rotor member are movable in the axial direction when the sliding contact portion is pressed by the pair of brake pads, and The first rotor member and the second rotor member are supported by the support member so that the first rotor member and the second rotor member can be relatively moved in the circumferential direction during braking in sliding contact with the pair of brake pads. .

  According to this, the disc brake device moves when pressed in the axial direction by the pair of brake pads, and is supported by the support member so as to be relatively movable in the circumferential direction during braking. And a second rotor member. That is, in the disc brake device, the outer peripheral portion of the disc rotor that is in sliding contact with the pair of brake pads is formed of two members, the first rotor member and the second rotor member. As a result, during braking, the pair of brake pads press the sliding contact portion, so that the first rotor member and the second rotor member move in a direction in which they abut against each other. The first rotor member and the second rotor member restrict the movement of each other, so that the pair of brake pads and the sliding contact portions of the first rotor member and the second rotor member are in sliding contact with each other and frictionally engaged, A braking force can be generated.

  In addition, when vibration is generated in the first rotor member and the second rotor member during braking, at least the first rotor member and the second rotor member relatively move in the circumferential direction, that is, have an amplitude in the circumferential direction. Can vibrate. In this way, the first rotor member and the second rotor member vibrate in the circumferential direction, thereby consuming vibration energy and reducing (attenuating) the generated vibration. Accordingly, the disk rotor itself having the first rotor member and the second rotor member can exhibit the vibration damping performance, and therefore, it is possible to effectively prevent the resonance with the caliper. As a result, the occurrence of abnormal noise (brake squeal) during braking can be reduced.

1 is an overall view of a disc brake device according to an embodiment of the present invention. FIG. 2 is a partial cross-sectional view schematically showing a first rotor member and a second rotor member, a first damping member, and a second damping member that constitute the disk rotor of FIG. 1. It is a figure for demonstrating the action | operation at the time of braking. It is a partial cross section figure showing roughly the 1st rotor member and the 2nd rotor member which constitute the disc rotor of the 1st modification, and a damping member. It is a partial sectional view showing roughly the 1st rotor member and the 2nd rotor member which constitute the disc rotor of the 2nd modification, the 1st damping member, and the 2nd damping member.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments and modifications, the same or equivalent portions are denoted by the same reference numerals in the drawings. Each figure used for explanation is a conceptual diagram, and the shape of each part may not necessarily be exact.

  As shown in FIG. 1, the disc brake device 10 includes a disc-like disc rotor 11 that is connected to a rotating member of a vehicle and rotates integrally. In the following description, as shown in FIGS. 1 and 2, the axial direction of the disk rotor 11 is referred to as “rotor axial direction”, and the circumferential direction of the disk rotor 11 is referred to as “rotor circumferential direction”.

  As shown in FIGS. 1 and 2, the disk rotor 11 includes a pair of a first rotor member 12 and a second rotor member 13, and a support member 14. The 1st rotor member 12 and the 2nd rotor member 13 are provided in the disk shape so that the outer peripheral part of the disk rotor 11 may be formed, for example from metal materials, such as cast iron (it is formed in the disk shape). As shown in FIG. 1, the first rotor member 12 and the second rotor member 13 have a holding portion 12 a and a holding portion 13 a that are held with respect to the support member 14 on their inner peripheral portions. The holding | maintenance part 12a and the holding | maintenance part 13a have the semicircle-shaped notch part formed corresponding to the axial part 14a of the support member 14 mentioned later. Since the first rotor member 12 and the second rotor member 13 have the holding portion 12a and the holding portion 13a, the first rotor member 12 and the second rotor member 13 are assembled to the support member 14 so as to be separated from each other in the rotor axial direction.

  As shown in FIG. 2, the support member 14 is formed in a stepped columnar shape having a small diameter portion and a large diameter portion, and a bolt and a nut with respect to an axle J which is a rotating member of a vehicle not shown. Are assembled together. The support member 14 is fixed to the large-diameter portion, and has a shaft portion 14 a that extends in the rotor axial direction and engages with the holding portions 12 a and 13 a of the first rotor member 12 and the second rotor member 13. In the present embodiment, the support member 14 is provided with four shaft portions 14a. The shaft portion 14a is formed so that the outer peripheral portion that comes into contact with the notched portions of the holding portions 12a and 13a is smooth. Accordingly, the first rotor member 12 and the second rotor member 13 are supported so as to be movable in the rotor axial direction with respect to the shaft portion 14a in a state assembled to the shaft portion 14a of the support member 14.

  Further, a clearance (clearance) is provided in the circumferential direction of the rotor between the outer peripheral portion of the shaft portion 14a and the notched portions of the holding portions 12a and 13a. Thereby, while the 1st rotor member 12 and the 2nd rotor member 13 are the state assembled | attached to the axial part 14a of the supporting member 14, while being supported so that relative movement with respect to the axial part 14a is possible in a rotor circumferential direction, The first rotor member 12 and the second rotor member 13 are supported so as to be relatively movable in the rotor circumferential direction.

  Here, an elastic member (for example, a spring material or a rubber material) is interposed in a gap (clearance) between the notched portions of the holding portions 12a and 13a and the outer peripheral portion of the shaft portion 14a (not shown). As described above, when the elastic member is interposed, the first rotor member 12 and the second rotor member 13 that are opposed to each other are relatively deformed relative to the support member 14 in the rotor circumferential direction by elastic deformation of the elastic member. It becomes possible to move. In addition, the first rotor member 12 and the second rotor member 13 facing each other can be relatively moved in the circumferential direction of the rotor during braking by elastically deforming the elastic member.

  Further, the disc brake device 10 includes a caliper 15 that straddles a part of the outer peripheral portion of the disc rotor 11 (that is, the first rotor member 12 and the second rotor member 13). The caliper 15 is fixed to a non-rotating member (for example, a vehicle body not shown) of the vehicle. The caliper 15 is assembled with a piston P that displaces the pair of brake pads 16 in the rotor axial direction (see FIG. 3). In this embodiment, a floating caliper is used. However, for example, a piston-facing caliper can also be used.

  As shown in FIGS. 2 and 3, the pair of brake pads 16 incorporated in the caliper 15 is configured so that the outer periphery of the disk rotor 11 (that is, the first rotor member 12) from both sides in the rotor axial direction by the operation of the piston P. And the second rotor member 13) are pressed against the disk rotor 11 (that is, the first rotor member 12 and the second rotor member 13). Each of the pair of brake pads 16 includes a back plate 16a and a lining 16b that is a friction material fixed to the back plate 16a. The back plate 16a is formed in a plate shape, and one of the pair of back plates 16a is pressed toward the rotor axis by the piston P. The lining 16b moves in the rotor axial direction together with the back plate 16a and is pressed by the disk rotor 11, that is, the first rotor member 12 and the second rotor member 13. As a result, the pair of linings 16b are pressed and slidably contacted by the sliding contact portion 12b extending in the circumferential direction of the rotor on the one surface side of the first rotor member 12, and on the one surface side of the second rotor member 13. The sliding contact portion 13b extending in the circumferential direction of the rotor is pressed and brought into sliding contact.

  Further, the disc brake device 10 is provided on the first damping member 17 fixed to the opposing surface 12c which is the other surface side of the first rotor member 12 facing each other and the opposing surface 13c which is the other surface side of the second rotor member 13. A fixed second damping member 18 is provided. The first damping member 17 and the second damping member 18 are, for example, a rubber material or a resin material, or a metal material (for example, aluminum) different from the forming material (for example, cast iron) of the first rotor member 12 and the second rotor member 13. From, it forms in the annular | circular shape of a thin plate. In the present embodiment, the first damping member 17 is bonded and fixed to the entire surface of the opposing surface 12 c of the first rotor member 12 on one side. In the present embodiment, the second damping member 18 is bonded and fixed to the entire surface of the opposing surface 13 c of the second rotor member 13 on one side. As a result, when the first rotor member 12 and the second rotor member 13 move in the direction in which they abut each other in the rotor axial direction by sliding contact with the pair of brake pads 16 during braking, the first damping member 17 and the second damping member 17 The attenuation members 18 are configured such that the other surface sides come into contact with each other.

  In the disc brake device 10 configured in this way, for example, when a driver depresses a brake pedal (not shown), the piston P incorporated in the caliper 15 moves forward as shown in FIG. As a result, the pair of brake pads 16 move along the rotor axial direction, respectively, and start sliding contact with the sliding contact portions 12 b and 13 b of the first rotor member 12 and the second rotor member 13 constituting the disk rotor 11. To do. When the piston P further advances and the pair of brake pads 16 press the first rotor member 12 and the second rotor member 13, the first rotor member 12 and the second rotor member 13 are guided by the shaft portion 14 a of the support member 14. Then, they move in directions opposite to each other along the rotor axial direction, that is, in directions in which they abut (be close to) each other.

  As described above, when the first rotor member 12 and the second rotor member 13 move in the rotor axial direction, the first rotor member 12 and the second rotor member 13 are fixed to the opposing surfaces 12c and 13c, the first damping member 17 being fixed. And abutment via the second damping member 18. As a result, the movement of the first rotor member 12 and the second rotor member 13 in the rotor axial direction is restricted, and the sliding of the pair of brake pads 16 and the first rotor member 12 and the second rotor member 13 pressed by the piston P is performed. The contact portions 12b and 13b are frictionally engaged. As a result, the disc brake device 10 generates a braking force for braking a wheel (not shown).

  By the way, the 1st rotor member 12 and the 2nd rotor member 13 have the sliding contact parts 12b and 13b used as a thin plate compared with the plate | board thickness of the sliding contact part in the disk rotor which consists of one conventional member, for example. Accordingly, when vibration is generated when the pair of brake pads 16 are frictionally engaged, the first rotor member 12 and the second rotor member 13 are generated by vibrating so as to have an amplitude in the rotor axial direction. Consume vibration energy of vibration. As a result, the first rotor member 12 and the second rotor member 13 reduce (attenuate) vibration in the rotor axial direction and prevent resonance with the caliper 15 (more specifically, the pair of brake pads 16).

  Further, the holding portions 12 a and 13 a of the first rotor member 12 and the second rotor member 13 have a clearance (clearance) in the rotor circumferential direction with respect to the shaft portion 14 a of the support member 14. As a result, when vibration is generated when the pair of brake pads 16 are frictionally engaged, the first rotor member 12 and the second rotor member 13 are moved relative to each other in the circumferential direction of the rotor and vibrate. Consume vibration energy. As a result, the first rotor member 12 and the second rotor member 13 reduce (attenuate) vibration in the circumferential direction of the rotor and prevent resonance with the caliper 15 (more specifically, the pair of brake pads 16).

  Here, for example, when the driver depresses the depression of the brake pedal (not shown), the pressure by the piston P is released and the sliding contact (friction) between the pair of brake pads 16 and the sliding contact portions 12b and 13b is released. Engagement) is released. In this case, although illustration is omitted, for example, the return member (spring member or the like) provided on the caliper 15 causes the opposing surfaces 12c and 13c of the first rotor member 12 and the second rotor member 13 to face each other in the rotor axial direction. Press in directions away from each other. Thereby, the 1st rotor member 12 and the 2nd rotor member 13 move to the direction mutually spaced apart in a rotor axial direction. As described above, when the first rotor member 12 and the second rotor member 13 are separated from each other, the opposing surfaces 12c and 13c on the other surface side also circulate in the vicinity of the disk rotor 11 in addition to the sliding contact portions 12b and 13b on the one surface side. Touch the air. As a result, in the first rotor member 12 and the second rotor member 13, heat generated by frictional engagement with the pair of brake pads 16 and heat generated by consuming vibration energy as described above are generated. Cools quickly.

  In the disc brake device 10, the first damping member 17 and the second damping member 18 are fixed to the opposing surfaces 12 c and 13 c of the first rotor member 12 and the second rotor member 13. As a result, as described above, when the first rotor member 12 and the second rotor member 13 move in the direction in which they abut against each other, the first damping member 17 and the second damping member 18 abut against each other.

  By the way, in the state where the first damping member 17 and the second damping member 18 are in contact with each other (in close contact), vibration having amplitude in the rotor axial direction is generated in the first rotor member 12 and the second rotor member 13. In this case, the first damping member 17 and the second damping member 18 are elastically deformed in the rotor axial direction. Thereby, the first damping member 17 and the second damping member 18 consume the vibration energy of the vibration in the rotor axial direction generated in the first rotor member 12 and the second rotor member 13. As a result, the first damping member 17 and the second damping member 18 reduce (attenuate) vibration in the rotor axial direction, and the first rotor member 12, the second rotor member 13, and the caliper 15 (more specifically, a pair of Resonance with the brake pad 16) is prevented.

  Further, when vibration having amplitude in the rotor circumferential direction is generated in the first rotor member 12 and the second rotor member 13, the first damping member 17 and the second damping member 18 are elastic in the rotor circumferential direction, that is, in the shear direction. Deform. As a result, the first damping member 17 and the second damping member 18 consume vibration energy of the rotor circumferential vibration generated in the first rotor member 12 and the second rotor member 13. As a result, the first damping member 17 and the second damping member 18 reduce (attenuate) vibration in the rotor circumferential direction, and the first rotor member 12, the second rotor member 13 and the caliper 15 (more specifically, a pair of Resonance with the brake pad 16) is prevented.

  As can be understood from the above description, the disc brake device 10 includes a disc-like disc rotor 11 that is connected to an axle J that is a rotating member of the vehicle and rotates integrally with the axle J, and a rotor circumferential direction of the disc rotor 11. The caliper 15 is provided so as to straddle part of the outer peripheral portion and is fixed to the vehicle body which is a non-rotating member of the vehicle, and the disc rotor 11 is assembled to the caliper 15 from both sides of the disc rotor 11 in the rotor axial direction. The disc brake device includes a pair of brake pads 16 that are pressed toward the outer peripheral portion of the disc and slidably contact the disc rotor 11.

  The disc rotor 11 is provided in an annular shape so as to form an outer peripheral portion (formed in an annular shape), and has first and second sliding contact portions 12b and 13b that are in sliding contact with each of the pair of brake pads 16 on one surface side. Of the first rotor member 12 and the second rotor member 13, the first rotor member 12 and the second rotor member 13 and the first rotor member 12 and the second rotor member 13 are spaced apart from each other in the rotor axial direction. And a support member 14 that supports the holding portions 12a and 13a provided on the periphery by the shaft portion 14a. The first rotor member 12 and the second rotor member 13 are slidably contacted by a pair of brake pads 16. The first rotor member 12 and the second rotor member 13 are slidably in contact with the pair of brake pads 16 when the portions 12b and 13b are pressed. So as to be relatively movable in the rotor circumferential direction at the time of braking that, first rotor member 12 and the second rotor member 13 is supported by the support member 14.

  According to this, the disc brake device 10 is supported by the support member 14 so as to move when pressed in the rotor axial direction by the pair of brake pads 16 and to be relatively movable at least in the circumferential direction of the rotor during braking. The first rotor member 12 and the second rotor member 13 can be provided. Thereby, at the time of braking, the pair of brake pads 16 press the sliding contact portions 12b and 13b, so that the first rotor member 12 and the second rotor member 13 move in a direction in which they contact each other. The first rotor member 12 and the second rotor member 13 restrict the movement of each other, so that the pair of brake pads 16 and the sliding contact portions 12b and 13b are frictionally engaged, and a braking force can be generated.

  Further, at the time of braking, if vibration occurs in the first rotor member 12 and the second rotor member 13 with the first rotor member 12 and the second rotor member 13 in contact with each other, at least the first rotor member 12 and the second rotor member 12 The two rotor members 13 can move relative to each other in the circumferential direction of the rotor, that is, vibrate so as to have an amplitude in the circumferential direction of the rotor. Thus, when the first rotor member 12 and the second rotor member 13 vibrate in the rotor circumferential direction, vibration energy can be consumed, and the generated vibration can be reduced (attenuated). Therefore, the disk rotor 11 itself having the first rotor member 12 and the second rotor member 13 can exhibit the vibration damping performance, so that the resonance with the caliper 15 can be effectively prevented. As a result, the occurrence of abnormal noise (brake squeal) during braking can be reduced.

  In this case, the first rotor member 12 and the second rotor member 13 are interposed between the opposing surfaces 12c and 13c, which are the other surfaces of the first rotor member 12 and the second rotor member 13, respectively. It can have the 1st damping member 17 and the 2nd damping member 18 which are the disk shaped damping members which attenuate the generated vibration.

  According to this, at the time of braking, the first attenuating member 17 and the second attenuating member 18 are in contact with each other first, thereby preventing the first rotor member 12 and the second rotor member 13 from directly contacting each other. Can do. Thereby, generation | occurrence | production of the contact sound which arises when the 1st rotor member 12 and the 2nd rotor member 13 contact | abut directly at the time of braking can be prevented.

  Further, when the first rotor member 12 and the second rotor member 13 are vibrated with amplitude in the rotor axial direction during braking, the first damping member 17 and the second damping member 18 that are in contact with each other are moved to the rotor. It can be elastically deformed in the axial direction. Thereby, the 1st damping member 17 and the 2nd damping member 18 can reduce (attenuate) the vibration in the rotor axial direction of the 1st rotor member 12 and the 2nd rotor member 13. FIG.

  Further, when vibrations having an amplitude in the circumferential direction of the rotor are generated in the first rotor member 12 and the second rotor member 13 during braking, the first damping member 17 and the second damping member 18 that are in contact with each other are moved to the rotor. It can be elastically deformed in the circumferential direction (shear direction). Thereby, the first damping member 17 and the second damping member 18 can reduce (attenuate) vibrations in the circumferential direction of the first rotor member 12 and the second rotor member 13. Accordingly, it is possible to more reliably prevent the pair of brake pads 16 and the pair of first rotor member 12 and second rotor member 13 from resonating during braking, and abnormal noise (brake squeal) during braking can be prevented. Generation | occurrence | production can be suppressed effectively.

(First modification of embodiment)
In the above embodiment, the first damping member 17 and the second damping member 18 are fixed to the facing surfaces 12c and 13c of the first rotor member 12 and the second rotor member 13, respectively. In this way, instead of using the two first damping members 17 and the second damping member 18, as shown in FIG. 4, one disposed between the first rotor member 12 and the second rotor member 13. It is also possible to use a single damping member 19. In this case, the damping member 19 is also a thin circular plate made of, for example, a rubber material or a resin material, or a metal material (for example, aluminum) different from the material for forming the first rotor member 12 and the second rotor member 13 (for example, cast iron). It is formed in an annular shape. The damping member 19 is adhered and fixed to at least one of the opposing surface 12c of the first rotor member 12 and the opposing surface 13c of the second rotor member 13.

  Also in the first modified example, similarly to the above-described embodiment, the first rotor member 12 and the second rotor member 13 reduce (attenuate) vibration in the rotor axial direction, and the caliper 15 (more specifically, a pair of calipers 15). Resonance with the brake pad 16) can be prevented. Also in this first modification, as in the above embodiment, the first rotor member 12 and the second rotor member 13 reduce (attenuate) vibration in the rotor circumferential direction, and calipers 15 (more specifically, a pair of calipers 15). Resonance with the brake pad 16) can be prevented.

  The damping member 19 in the first deformation is elastically deformed in the rotor axial direction when vibration having an amplitude in the rotor axial direction is generated in the first rotor member 12 and the second rotor member 13. Thereby, the damping member 19 consumes the vibration energy of the vibration in the rotor axial direction generated in the first rotor member 12 and the second rotor member 13. As a result, the damping member 19 reduces (attenuates) vibration in the rotor axial direction, and the first rotor member 12, the second rotor member 13, and the caliper 15 (more specifically, the pair of brake pads 16) resonate. To prevent that.

  Further, the damping member 19 is elastically deformed in the rotor circumferential direction, that is, in the shearing direction when vibration having an amplitude in the rotor circumferential direction is generated in the first rotor member 12 and the second rotor member 13. Thereby, the damping member 19 consumes the vibration energy of the vibration in the rotor circumferential direction generated in the first rotor member 12 and the second rotor member 13. As a result, the damping member 19 reduces (attenuates) vibration in the rotor circumferential direction, and the first rotor member 12, the second rotor member 13, and the caliper 15 (more specifically, the pair of brake pads 16) resonate. To prevent that.

  As can be understood from the above description, according to the first modified example, the first rotor member 12 is interposed between the opposing surfaces 12c and 13c of the first rotor member 12 and the second rotor member 13, and is braked during braking. A disc-shaped damping member 19 that attenuates vibrations generated in the 12 and second rotor members 13 is fixed to at least one of the facing surface 12 c of the first rotor member 12 and the facing surface 13 c of the second rotor member 13.

  According to this, since the damping member 19 is interposed between the opposing surfaces 12c and 13c of the first rotor member 12 and the second rotor member 13 during braking, the first rotor member 12 and the second rotor member It can prevent that 13 mutually contact | abuts directly. Accordingly, it is possible to prevent the contact noise between the first rotor member 12 and the second rotor member 13 during braking. Further, in this case, the damping member 19 is effective for the vibration having amplitude in the rotor axial direction and the vibration having amplitude in the rotor circumferential direction generated in the first rotor member 12 and the second rotor member 13 during braking. Can be reduced (attenuated). Therefore, even in the case of this first modification, it is possible to effectively suppress the occurrence of abnormal noise (brake squeal) during braking.

(Second modification of the embodiment)
In the embodiment and the first modified example, the first damping member 17 and the second damping member 18 or the damping is applied to the entire opposing surfaces 12c and 13c of the first rotor member 12 and the second rotor member 13. The member 19 was adhered and fixed. Instead, as shown in FIG. 5, the opposing surfaces 12 c and 13 c are formed so as to correspond to the sliding contact portions 12 b and 13 b of the first rotor member 12 and the second rotor member 13 pressed by the pair of brake pads 16. It is also possible to fix the first damping member 17 and the second damping member 18 or the damping member 19. In other words, in the second modification, the first damping member 17 and the second damping member 18 or the damping member 19 that are damping members are arranged at least on one surface side in the rotor axial direction on the opposing surfaces 12c and 13c. It is provided in a portion corresponding to the sliding contact portions 12b and 13b. FIG. 5 illustrates the case where the first damping member 17 and the second damping member 18 are fixed to the facing surfaces 12c and 13c.

  Thus, even when the first damping member 17 and the second damping member 18 or the damping member 19 are provided on a part of the facing surfaces 12c and 13c of the first rotor member 12 and the second rotor member 13, As in the above embodiment and the first modification, it is possible to suppress the occurrence of contact noise and abnormal noise (brake squeal) during braking. Further, the first damping member 17 is provided on the opposing surfaces 12c and 13c on the opposite side of the sliding contact portions 12b and 13b in the rotor axial direction, which is a portion corresponding to the sliding contact portions 12b and 13b pressed by the pair of brake pads 16. The second damping member 18 or the damping member 19 is fixed to prevent deformation of the first rotor member 12 and the second rotor member 13 even when pressed by the pair of brake pads 16 during braking. it can. Further, in the second modification, the first damping member 17 and the second damping member 18 or the damping member 19 can be partially provided. As a result, it is possible to reduce the weight of the disc brake device 10 and reduce the manufacturing cost.

  In carrying out the present invention, the present invention is not limited to the above embodiment and each of the above modifications, and various modifications can be adopted within the scope of the present invention.

  For example, in the said embodiment and each modification, the 1st damping member 17 and the 2nd damping member 18, or the damping member 19 is provided between the opposing surfaces 12c and 13c of the 1st rotor member 12 and the 2nd rotor member 13. It was made to intervene. Alternatively, the first damping member 17 and the second damping member 18 or the damping member 19 can be omitted. Even in this case, as described in the above embodiment, the first rotor member 12 and the second rotor member 13 vibrate so as to have an amplitude in the rotor axial direction, and the first rotor member 12 and the second rotor member 13 Vibration energy can be consumed by oscillating so as to have an amplitude in the circumferential direction of the rotor. Therefore, even when the first damping member 17, the second damping member 18, and the damping member 19 are omitted, the resonance between the first rotor member 12, the second rotor member 13, and the caliper 15 (the pair of brake pads 16). The effect which prevents can be expected.

  In the above embodiment, the first damping member 17 is fixed to the facing surface 12 c of the first rotor member 12, and the second damping member 18 is fixed to the facing surface 13 c of the second rotor member 13. In the first modification, the damping member 19 is fixed to at least one of the facing surface 12 c of the first rotor member 12 and the facing surface 13 c of the second rotor member 13. In these cases, the first damping member 17, the second damping member 18, and the damping member 19 may be fixed to the first rotor member 12 and the second rotor member 13 without being fixed. Even if the first damping member 17, the second damping member 18, and the damping member 19 are interposed between the opposing surfaces 12c, 13c of the first rotor member 12 and the second rotor member 13 without being fixed, the above-described implementation is performed. The same effect as the embodiment and the first modification can be expected.

DESCRIPTION OF SYMBOLS 10 ... Disc brake apparatus, 11 ... Disc rotor, 12 ... 1st rotor member, 12a ... Holding part, 12b ... Sliding contact part (one surface side), 12c ... Opposite surface (other surface side), 13 ... Second rotor member, 13a ... Holding portion, 13b ... Sliding contact portion (one surface side), 13c ... Opposing surface (other surface side), 14 ... Support member, 14a ... Shaft portion, 15 ... Caliper, 16 ... Brake pad, 16a ... Back plate, 16b ... Lining, 17 ... First damping member, 18 ... Second damping member, 19 ... Damping member, J ... Axle, P ... Piston

Claims (4)

A disk-shaped disk rotor connected to a rotating member of a vehicle and rotating integrally with the rotating member;
A caliper provided so as to straddle a part of the outer peripheral portion in the circumferential direction of the disk rotor, and fixed to a non-rotating member of the vehicle;
A disc brake device comprising: a pair of brake pads assembled to the caliper and pressed against the disc rotor from both sides in the axial direction of the disc rotor, and in sliding contact with the disc rotor;
The disk rotor is
A first rotor member and a second rotor member which are provided in an annular shape and have sliding contact portions which are in sliding contact with each of the pair of brake pads on one surface side;
A support member that supports inner peripheral portions of the first rotor member and the second rotor member such that the first rotor member and the second rotor member face each other in the axial direction so as to be separated from each other. Configured,
The first rotor member and the second rotor member are movable in the axial direction when the sliding contact portion is pressed by the pair of brake pads, and
The first rotor member and the second rotor member are relatively movable in the circumferential direction during braking in sliding contact with the pair of brake pads.
A disc brake device in which the first rotor member and the second rotor member are supported by the support member. Interposed between opposing surfaces on the other side of each of the first rotor member and the second rotor member,
The disc brake device according to claim 1, further comprising a damping member that damps vibrations generated in the first rotor member and the second rotor member during the braking. The damping member is
In the facing surface, at least,
The disc brake device according to claim 2, wherein the disc brake device is provided in a portion corresponding to the sliding contact portion on the one surface side in the axial direction. The damping member is
A first damping member fixed to the facing surface of the first rotor member;
The disc brake device according to claim 2 or 3, comprising a second damping member that is fixed to the facing surface of the second rotor member.

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