JP4998327B2 - Disc rotor mounting structure - Google Patents

Description

  The present invention relates to a technique for reducing vibrations of a disc rotor of a disc brake device attached to a wheel during operation of a disc brake device that brakes the wheel.

As an invention for suppressing a brake sound due to vibration of a disk rotor, there has been conventionally known an invention as described in Patent Document 1, for example.
In the disc brake device described in Patent Document 1, a disc rotor of the disc brake device is attached to a hub that is the center of a wheel by bolt fastening. An annular groove is provided on the outer edge of the hub on the outer diameter side of the bolt, and an annular vibration-proof rubber is disposed in the groove, and the vibration-proof rubber is disposed between the groove and the disk rotor. Is compressed and inserted. As a result, the pressure receiving portion pressed by the vibration isolating rubber is used as a surface contact to eliminate stress concentration and suppress an unpleasant brake sound called a so-called brake squeal.
JP-A-6-280910

  However, the conventional disc brake device still has problems as described below. In other words, since the damping by the damping material such as the damping rubber can be obtained by the deformation of the damping material, a general disc that does not use the damping rubber so as not to disturb the deformation action of the damping rubber. The fastening force of the bolts had to be reduced compared to the rotor mounting location. Therefore, the disc brake device of Patent Document 1 cannot secure a necessary fastening force.

  On the other hand, there are various vibration modes of the disc rotor that generates the brake sound, and one of them is an in-plane density mode. The side view of FIG. 2 (a) and the front view of FIG. 2 (b) are three-dimensional drawings in which a disk rotor that repeatedly undergoes deformation in the in-plane density mode is exaggerated for easy understanding. The applicant of the present application does not deform the outer edge of the disk rotor in the direction of the axis O, that is, out-of-plane direction, while the disk portion of the disk rotor is sandwiched between the friction members for braking, and the outer edge of the disk rotor is exaggerated in FIG. As shown in the figure, we studied the existence of a vibration mode that expands and contracts in the direction of the circumferential arrow, that is, an in-plane density mode. As a result, during vibration in the in-plane density mode, the wrinkle due to the circumferential deformation of the outer edge of the disk rotor extends to the disk rotor center, and the center of the disk rotor near the axis O also extends in the direction of the axis O as shown in FIG. I found it to transform.

  During operation of the disc brake device, the disc rotor emits a brake sound in this in-plane density mode. When the anti-vibration rubber described in Patent Document 1 is provided between the hub and the disc brake, since the fastening force of the bolt is low as described above, the brake noise due to the in-plane density mode cannot be eliminated.

  In view of the above circumstances, an object of the present invention is to propose a disc rotor mounting structure that can effectively prevent the occurrence of an in-plane density mode.

For this purpose, the disk rotor mounting structure according to the present invention is:
At the disc rotor attachment location where the disc rotor central part of the disc brake device is attached to the joint between the wheel and the axle,
The wheel and / or the axle has a surface contact portion in surface contact with the disk rotor at the attachment location, and the surface contact portion and the disc are fastened by fastening a bolt at the attachment location with a predetermined fastening force. The rotor is pressed against each other and combined,
The contact area is ensured so that the fastening pressure per unit area obtained by dividing the predetermined fastening force by the contact area between the surface contact portion and the disk rotor is a predetermined value or less ,
One of the surface contact portion and the disk rotor is formed with a protrusion that protrudes toward the other, and a recess that receives the protrusion is formed on the other .

According to the configuration of the present invention, the surface contact portion and the disk rotor are pressed against each other by being fastened with a predetermined fastening force. The brake sound due to the mode can be eliminated.
In addition, by ensuring the contact area so that the fastening pressure between the surface contact portion and the disk rotor is not more than a predetermined value, the brake sound due to other vibration modes that have been solved by the conventional disk brake device is also combined. Can be solved.

Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings.
FIG. 1 is a longitudinal sectional view showing a disk rotor mounting structure according to an embodiment of the present invention.
A metal road wheel 1 made of iron, aluminum, or titanium includes a cylindrical rim portion 1r on a radially outer edge. The shape of the rim portion 1r itself is well-known and fits with a well-known tire (not shown). One end of the rim portion 1r in the direction of the axis O is coupled to one end of a known spoke portion 1s extending in the radial direction. The other end of the spoke portion 1s is coupled to the road wheel center portion 1c centering on the axis O. The road wheel center portion 1c is coupled to an axle that is rotatably supported, and the road wheel 1 functions as a wheel. In this embodiment, as shown in FIG. 1, the axle includes a metal hub 2, and the central portion of the metal disk rotor 3 is interposed between the hub 2 and the road wheel 1. Although not shown in the drawing, the central portion of the disk rotor 3 may be attached only to the hub 2 or only to the road wheel 1.

  A disc rotor 3 constituting a disc brake device and a brake caliper (not shown) are arranged in an inner space of the road wheel 1 defined by the rim portion 1r, the spoke portion 1s and the center portion 1c of the road wheel 1. The brake caliper is attached to the vehicle body side member, and presses the friction material against both surfaces of the disk rotor 3 to brake the rotating disk rotor 3.

The hub 2 forms the outer width end of the axle. A plurality of bolts 4 are arranged in the hub 2 at equal intervals in the circumferential direction around the axis O. The bolt 4 is serrated with the hub 2, and the tip of the bolt 4 protrudes from the hub 2 to the outside of the vehicle width of the axle O.
Bolt holes 3 h are drilled in the disk rotor 3 in the same arrangement as the plurality of bolts 4, and bolt holes 1 h are drilled in the load wheel in the same arrangement as the plurality of bolts 4. Then, the disk rotor 3 and the load wheel 1 are sequentially inserted into the front ends of the bolts 4 protruding from the hub 2, and then a nut 5 having a taper is bolted, so that the disk rotor 3 and the load wheel 1 are tightened. To the hub 2.

  When the nut 5 is fastened, the taper of the nut 5 advances toward the inside of the axle O and presses the bolt hole 1 h of the road wheel 1 toward the hub 2. Since the hub 2 receives this pressing force, the disk rotor 3 is clamped between the load wheel 1 and the hub 2.

  In this way, the road wheel 1 serving as a wheel is coupled to the hub 2 serving as an axle at the center thereof. The central portion of the disk rotor 3 is attached to this coupling portion. That is, the connecting portion between the road wheel 1 and the hub 2 is also an attachment location of the disk rotor 3. In this embodiment, it can be said that the disc rotor 3 is attached to the load wheel 1 to be the above-mentioned attachment location, or the disc rotor 3 is attached to the hub 2 to be the above-mentioned attachment location. Alternatively, although not shown in the drawing, the disk rotor 3 may be attached only to the road wheel 1 to be the above-mentioned attachment location, or the disk rotor 3 may be attached only to the hub 2 to be the above-mentioned attachment location. In any case, the disc rotor 3 and the non-attachment member to which the disc rotor 3 is attached are the attachment locations.

  The load wheel 1 has a surface contact portion 1 m that is in surface contact with the disk rotor 3 at an attachment location of the disk rotor 3. As shown in FIG. 1, the surface contact portion 1 m surrounds the substantially outer periphery of the bolt 4. Alternatively, as indicated by a two-dot chain line in FIG. 3, the surface contact portion 1 m may be an annular shape that surrounds the entire circumference of the bolt 4. Alternatively, an annular shape that surrounds the axis O may be used, as in a region indicated by a two-dot chain line in FIG. 4, which is a front view of the disk rotor 4. In FIG. 4, 3h is a bolt hole through which the bolt 4 is inserted.

  Returning to FIG. 1, when the bolt 4 at the mounting location of the disc rotor 3 is fastened with a predetermined fastening force, the surface contact portion 1m of the load wheel 1 and the disc rotor 3 are pressed against each other and coupled.

  It will be understood that the larger the contact area between the surface contact portion 1m and the disc rotor 3, the smaller the fastening pressure per unit area obtained by dividing the fastening force of the bolt 4 by the contact area. In this embodiment, when the load wheel 1 and the disk rotor 3 are designed, the contact area of the surface contact portion 1m is ensured so that the predetermined fastening force of the bolt 4 is equal to or lower than the predetermined pressure of the surface contact portion 1m.

  Explaining this fastening pressure, the disc rotor 3 is sandwiched between the load wheel 1 and the hub 2 and fastened by bolts 4. When firmly fastened, the local behavior in the vicinity of the fastened portion is a vibration form in which 1, 3 and 2 are integrated. In this state, if the fastening pressure per unit area around the bolt 4 is decreased, the vibration forms 1, 3 and 2 are displaced, and the vibration becomes nonlinear. As a result, damping due to vibration hysteresis occurs.

  Therefore, in this embodiment, the contact area is designed so that the fastening pressure is not more than a predetermined value at which attenuation due to hysteresis occurs. Thereby, both the vibration mode by the out-of-plane deformation and the vibration mode by the in-plane deformation can be suppressed, and the brake sound can be eliminated more effectively than before.

  The applicant of the present application conducted an experiment on the damping action in the in-plane density mode according to the embodiment of FIG. The result is shown in FIG. In FIG. 11, the horizontal axis represents the contact area between the surface contact portion 1 m and the disk rotor 3, and the vertical axis represents the viscous damping ratio, that is, the index of the damping action. Here, it was common that the fastening force of the bolt 4 was a predetermined value, and experimental results were obtained for the mounting structures A, B, and C of three disk rotors having different contact areas. According to the present invention, it can be seen that the larger the contact area, the greater the damping effect of the in-plane density mode.

In this embodiment, the mounting position between the load wheel 1 and the disk rotor 3 has been described, but the mounting position between the hub 2 and the disk rotor 3 may be configured similarly.
FIG. 5 is a plan view of a disk rotor mounting location in which the central portion of the disk rotor 3 is mounted on a joint between a road wheel 1 serving as a wheel and a hub 2 serving as an axle. It is an expanded sectional view shown. The basic configuration is the same as the longitudinal sectional view of FIG.

  The disk rotor mounting location indicated by a two-dot chain line in FIG. 5 forms a projecting portion 3m by projecting a portion surrounding the bolt hole 3h in the surface of the disc rotor 3 on the side in contact with the hub 2, and adjacent bolts. The part between the holes 3h and 3h is also protruded to form a protruding part 3n. The tips of these protrusions 3m and 3n are finished to be smooth and at the same height.

  The tips of the protrusions 3m and 3n are in surface contact with the surface contact portions 1m and 1n of the hub 2. And the nut 5 screwed with the volt | bolt 4 provided in these surface contact parts 1m is bolt-fastened with predetermined | prescribed fastening force. Therefore, the disk rotor 3 can be attached to the coupling portion between the hub 2 and the road wheel 1 with an originally required fastening force, and the brake noise due to the in-plane density mode can be eliminated.

In addition, the contact area is secured by these protrusions 3m and 3n so that the fastening pressure at the disk rotor mounting location indicated by a two-dot chain line in FIG. 5 is not more than a predetermined value, so that the vibration of the disk rotor 3 is nonlinear. Therefore, it is easy to attenuate, and it is possible to eliminate the brake sound due to other vibration modes which has been solved by the conventional disc brake device.
Therefore, according to the embodiment shown in FIG. 5, the brake sound can be eliminated more effectively than in the prior art.

Next, another embodiment according to the present invention will be described.
FIG. 6 is an exploded perspective view of the mounting structure of the disk rotor 3 according to another embodiment. Since the basic configuration of this embodiment is common to the embodiment shown in FIG. 1 described above, the same members are denoted by the same reference numerals, description thereof is omitted, and different configurations will be described.

  In FIG. 6, only the road wheel 1 is shown in cross section and a part of the bolt holes 3h is shown. In this embodiment, a surface contact member 6 is inserted between the load wheel 1 and the disk rotor 3. The surface contact member 6 has a flat plate shape, and the bolt holes 6h are drilled in the same arrangement as the plurality of bolts 4, the bolt holes 3h, and the bolt holes 1h, and the bolts 4 are inserted therethrough. A hub 2 (not shown) is interposed between the disk rotor 3 and the head of the bolt 4.

  When the nut 5 is bolted with a predetermined required fastening force, one surface of the surface contact member 6 comes into surface contact with the road wheel 1. The other surface of the surface contact member 6 is in surface contact with the disk rotor 3. And the contact area of the surface contact member 6 is ensured so that the surface contact member 6 and the disk rotor 3 may mutually press with the fastening pressure below a predetermined value.

According to the embodiment shown in FIG. 6, the disk rotor 3 can be attached to the coupling portion between the hub 2 and the road wheel 1 with an originally required fastening force, and the brake noise due to the in-plane density mode can be eliminated. In addition, since the fastening pressure at the disk rotor mounting location is set to a predetermined value or less, the vibration of the disk rotor 3 becomes non-linear and easily damped, and other vibration modes that have been solved by the conventional disk brake device. The brake sound due to can also be eliminated.
Therefore, according to the embodiment shown in FIG. 6, the brake sound can be eliminated more effectively than in the prior art.
Although not shown, the surface contact member 6 may be interposed between the disk rotor 3 and the hub 2.

  The surface contact member described above is not limited to the shape shown in FIG. 6, and a washer-like surface contact member as shown in FIG. Alternatively, a plurality of seal-like surface contact members as shown in FIG. 8 may be arranged on the outer periphery of each bolt 4.

Next, another embodiment of the present invention will be described.
FIG. 9 is a longitudinal cross-sectional view showing a mounting structure of a disk rotor 3 according to another embodiment, broken along a plane including the rotational axis O of the wheel. Since the basic configuration of this embodiment is common to the embodiment shown in FIG. 1 described above, the same members are denoted by the same reference numerals, description thereof is omitted, and different configurations will be described.

  In this embodiment, the road wheel 1 and the disk rotor 3 are common in terms of surface contact, but the road wheel 1 is formed with a convex portion 1p protruding toward the disk rotor 3, and the disk rotor 3 has a convex portion. The difference is that a recess 3p that receives 1p is formed.

  As shown in FIG. 9, the protrusion 1 p is a protrusion that protrudes from the surface contact portion of the road wheel 1 toward the disk rotor 3. The concave portion 3p that uniformly contacts the convex portion 1p while receiving the convex portion 1p is a hollow portion that receives these protrusions. The convex portion 1p and the concave portion 3p have a gradient indicated by a one-dot chain line in FIG. The convex portion 1p and the concave portion 3p are arranged at equal intervals in the circumferential direction with the bolt 4 as the center.

  Alternatively, the convex portions may be formed on the disk rotor 3 and the concave portions may be formed on the load wheel 1, and the arrangement of the two 1p and 3p may be reversed. Alternatively, 1p may be a protrusion, 3p may be a groove, and the protrusion 1p and the groove 3p may be formed in an annular shape with the bolt 4 as the center. In this case, the groove 3p receives the protrusion 1p protrusion.

In the embodiment shown in FIG. 9, by fastening the bolt 5 with a predetermined fastening force, the brake noise due to the in-plane deformation mode of the in-plane deformation that has not been eliminated by the conventional disc brake device with vibration-proof rubber is eliminated. Can do.
Further, since the contact area is secured by 1p and 3p and the fastening pressure at the disk rotor mounting position indicated by a two-dot chain line in FIG. Therefore, the brake sound due to the vibration mode of out-of-plane deformation, which has been solved by the conventional disc brake device, can also be eliminated.
Therefore, according to the embodiment shown in FIG.

  By the way, according to each embodiment described above, the load wheel 1 has the surface contact portion 1m in surface contact with the disk rotor 3 at the mounting position of the disk rotor 3, and the bolt 4 at this mounting position is fixed to the predetermined position with the nut 5. By fastening with the fastening force, the surface contact portion 1m and the disk rotor 3 are pressed and coupled to each other, and this predetermined fastening force is divided by the contact area between the surface contact portion 1m and the disk rotor 3 per unit area. The contact area is ensured so that the fastening pressure is less than or equal to the predetermined value, which makes it possible to attenuate the in-plane density mode compared to the conventional mounting structure with anti-vibration rubber, and also to attenuate the out-of-plane vibration mode. Thus, the brake sound can be effectively eliminated.

  1, 3, 4, and 6 to 9 described above show the technology of the present invention that can be applied to the attachment position of the disk rotor 3 to the load wheel 1. The present invention is not limited to the above, and can be selectively applied to the mounting position of the disc rotor 3 with the hub 2 (axle) indicated by a two-dot chain line in FIG. 10 or the mounting of the disc rotor 3 with the load wheel 1. It can be applied to both the location and the location where the hub 2 is attached.

  The mounting position of the disk rotor 3 in each of the embodiments described above is that the disk rotor 3 is sandwiched between the road wheel 1 (wheel) and the hub 2 (axle), and the disk rotor 3 is mounted on the road wheel 1. Since the disk rotor 3 is brought into surface contact with the hub 2 or the disk rotor 3 is brought into surface contact with the hub 2, the in-plane coarse / dense mode and the out-of-plane vibration mode are attenuated to effectively eliminate the brake sound.

6 to 8, the disk rotor 3 is attached at a place where the surface contact members 6 to 8 are interposed between the road wheel 1 (wheel) and the disk rotor 3 so that the surfaces 1 and 3 are in surface contact with each other. As a result, the in-plane density mode and the out-of-plane vibration mode can be attenuated to effectively eliminate the brake sound.
Alternatively, although not shown, the surface contact members 6 to 8 may be interposed between the hub 2 (axle) and the disk rotor 3 so that both the surfaces 2 and 3 are in surface contact.

  Further, in the embodiment of FIG. 9, the disk rotor 3 is attached at the surface contact portion of the load wheel 1 by forming a convex portion 1 p that protrudes toward the disk rotor 3 and accepts this convex portion 1 p. Since the recess 3p is formed in the disc rotor 3, the in-plane coarse / dense mode and the out-of-plane vibration mode can be attenuated to effectively eliminate the brake sound.

  The above description is merely an example of the present invention, and the present invention can be variously modified without departing from the spirit of the present invention.

FIG. 1 is a longitudinal sectional view showing a mounting structure of a disk rotor according to an embodiment of the present invention together with a connecting portion of a wheel and an axle. It is the three-dimensional drawing which exaggerated and drawn the in-plane coarse / dense mode of a disk rotor for easy understanding, (a) is a front view, (b) is a side view. It is a longitudinal cross-sectional view which shows the modification Example of the surface contact part of the wheel shown in FIG. It is a front view which shows the modification Example of the surface contact part of the wheel shown in FIG. FIG. 3 is a developed cross-sectional view showing a disk rotor mounting structure broken and developed in a plane on a virtual cylindrical surface around an axis. It is a disassembled perspective view of the attachment structure of the disk rotor which becomes another Example of this invention. It is a disassembled perspective view of the attachment structure of the disk rotor which becomes another Example of this invention. It is a disassembled perspective view of the attachment structure of the disk rotor which becomes another Example of this invention. It is a longitudinal cross-sectional view which fractures | ruptures and shows the attachment structure of the disc rotor which becomes another Example of this invention by the plane containing the rotating shaft line of a wheel. It is a longitudinal cross-sectional view for instruct | indicating the attachment location with the axle shaft of a disk rotor. It is explanatory drawing showing the damping effect | action of the in-plane density mode by this invention.

Explanation of symbols

1 Road wheel
2 Disc rotor 3 Hub (axle)
4 Bolt 5 Nut 6 Surface contact member

Claims (3)

At the disc rotor attachment location where the disc rotor central part of the disc brake device is attached to the joint between the wheel and the axle,
The wheel and / or the axle has a surface contact portion in surface contact with the disk rotor at the attachment location, and the surface contact portion and the disc are fastened by fastening a bolt at the attachment location with a predetermined fastening force. The rotor is pressed against each other and combined,
The contact area is ensured so that the fastening pressure per unit area obtained by dividing the predetermined fastening force by the contact area between the surface contact portion and the disk rotor is a predetermined value or less ,
A mounting structure for a disk rotor, wherein a protrusion projecting toward the other is formed on one of the surface contact portion and the disk rotor, and a recess for receiving the protrusion is formed on the other. . In the mounting structure of the disk rotor according to claim 1,
The mounting location is the one where the disk rotor is clamped between the wheel and the axle,
The disk rotor mounting structure, wherein the disk rotor is in surface contact with the wheel, or the disk rotor is in surface contact with the axle. In the mounting structure of the disk rotor according to claim 1,
The mounting location is the one where the disk rotor is clamped between the wheel and the axle,
The surface is brought into contact with a member that becomes the surface contact portion between the wheel and the disk rotor, or the surface that is made with a member that becomes the surface contact portion between the axle and the disk rotor. A disk rotor mounting structure characterized by contact.

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