JP2009204018A - Disc brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disc brake device capable of stably supporting a brake pad during braking.
A disc brake device 1 is arranged so as to straddle brake pads 4A and 4B provided on both sides of the disc rotor 3 and the outer periphery of the disc rotor 3, and receives both ends of the brake pads 4A and 4B. And a caliper 7 that is connected to the mounting 5 and has a piston 14 that presses the brake pad 4 </ b> A against the disk rotor 3. Between the brake pad 4A and the piston 14, permanent magnets 17 and 18 are provided side by side in the rotational axis direction of the disk rotor 3, and between the brake pad 4B and each claw portion 13, the permanent magnets 15 and 16 are provided. Are arranged in the same direction. The permanent magnets 15 and 16 and the permanent magnets 17 and 18 are arranged so that the same poles face each other.
[Selection] Figure 2

Description

  The present invention relates to a disc brake device which is one of braking devices for vehicles and the like.

As a conventional disc brake device, for example, one disclosed in Patent Document 1 is known. The disc brake device described in Patent Document 1 includes an inner brake pad and an outer brake pad that are mounted and supported on both sides of a disk-shaped disc rotor, and a disc axial direction that extends across the outer periphery of the disc rotor. And a caliper supported so as to be slidable. The caliper has a brake piston inserted into the inner cylinder and an outer claw that contacts the back surface of the outer brake pad.
JP-A-8-193633

  However, in the above prior art, the frictional force and moment force generated when the brake pad is pressed against the disc rotor change due to the influence of the contact between the back surface of the brake pad and the outer claw, and the support of the brake pad by mounting is not possible. May become stable. In this case, since the brake pad is likely to vibrate, the squealing of the brake occurs.

  An object of the present invention is to provide a disc brake device that can stably support a brake pad during braking.

  The disc brake device according to the present invention is arranged so as to straddle the outer periphery of the disc rotor and a pair of brake pads that press against both sides of the disc rotor to generate a braking force, and receives and supports both ends of the brake pad. And a caliper that is coupled to the mounting and has a piston that presses the brake pad against the disc rotor, and includes a region between the brake pad and the piston and a region between the brake pad and the pad pressing wall portion of the caliper. In at least one of the regions, a plurality of magnetic bodies are provided side by side in the direction of the rotation axis of the disk rotor, and each magnetic body is disposed so that the same poles face each other. It is.

  As described above, in the disc brake device of the present invention, a plurality of magnetic bodies are arranged in the region between the brake pad and the piston so that the same poles face each other, so that repulsive force acts between the magnetic bodies. A minute gap is generated between the magnetic bodies. Accordingly, there is a gap in the region between the brake pad and the piston, and no frictional force acts between the two, so that the brake pad is easy to move in the shear direction (rotation direction of the disk rotor). Further, by arranging a plurality of magnetic bodies in the region between the brake pad and the pad pressing wall portion of the caliper so that the same poles face each other, the repulsive force acting between the magnetic bodies as described above is used. A minute gap is generated between the bodies. Accordingly, there is a gap in the region between the brake pad and the pad pressing wall portion of the caliper, and no frictional force acts between the two, so that the brake pad can easily move in the shear direction. Thereby, the both ends of a brake pad can be stably supported by mounting at the time of braking.

  Preferably, a heat insulating material is interposed between the brake pad and the magnetic body. In this case, since the deterioration of the magnetic body due to heat is prevented, the effect of repulsive force acting between the magnetic bodies can be maintained for a long period of time.

  According to the present invention, the brake pad can be stably supported during braking. Thereby, it is possible to suppress the vibration of the brake pad and prevent the occurrence of brake squeal.

  DESCRIPTION OF EMBODIMENTS Hereinafter, preferred embodiments of a disc brake device according to the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a perspective view showing an appearance of an embodiment of a disc brake device according to the present invention, and FIG. 2 is a partial sectional view schematically showing the disc brake device shown in FIG. In each figure, the disc brake device 1 of this embodiment is provided in a vehicle such as an automobile.

  The disc brake device 1 includes a disc rotor 3 that is fixed to an axle hub 2 and rotates integrally, brake pads 4A and 4B provided on both sides of the disc rotor 3, and suspension parts of a vehicle body (not shown). ) And a mounting 5 disposed so as to straddle the outer peripheral portion of the disk rotor 3, and a mounting 5 disposed so as to straddle the outer peripheral portion of the disc rotor 3. And a floating caliper 7 slidably connected in the direction of the rotation axis of the disk rotor 3.

  The brake pads 4A and 4B are friction material parts that are pressed against the rotor surfaces 3A and 3B of the disc rotor 3 to generate a braking force. The brake pads 4 </ b> A and 4 </ b> B are composed of a back metal 8 and a pad main body 9 joined to the back metal 8. The inner brake pad 4A is disposed so that the pad body 9 faces the inner rotor surface 3A of the disk rotor 3, and the outer brake pad 4B is disposed so that the pad body 9 faces the outer rotor surface 3B of the disk rotor 3. Is arranged.

  As shown in FIG. 3, torque transmission protrusions 10 having a rectangular cross section are provided at both ends of the back metal 8 of the brake pads 4 </ b> A and 4 </ b> B. Also, the mounting 5 is formed with a pair of torque receiving grooves 11 that receive and support each torque transmitting projection 10 in the direction opposite to the rotational direction of the disk rotor 3. The torque transmitting projection 10 is engaged with the torque receiving groove 11 so as to be slidable in the rotation axis direction of the disk rotor 3.

  The caliper 7 has a cylinder portion 12 provided on the back surface side (inside) of the brake pad 4A and a pair of claw portions (pad pressing wall portions) 13 provided on the back surface side (outside) of the brake pad 4B. is doing. A piston 14 having a concave cross section that presses the brake pad 4 </ b> A against the disc rotor 3 is disposed in the cylinder portion 12. The piston 14 is configured to move in the direction of the rotation axis of the disc rotor 3 in accordance with the brake hydraulic pressure of the hydraulic oil supplied to the cylinder portion 12 via a brake pipe (not shown).

  Permanent magnets 15 and 16 are arranged side by side in the rotational axis direction of the disk rotor 3 between the outer brake pad 4B and each claw portion 13 of the caliper 7. Specifically, a flat permanent magnet 15 is bonded to the back surface of the back metal 9 of the brake pad 4B. A block-shaped permanent magnet 16 is embedded in a recess opening in the inner wall surface of each claw portion 13.

  At this time, as shown in FIG. 4, the permanent magnets 15 and 16 are arranged so that the same poles (here, S poles) face each other. As a result, a repulsive force acts between the permanent magnets 15 and 16, so that a minute gap is generated between the permanent magnets 15 and 16, and the two are floated. Therefore, a load (pressing force) as a reaction force of the repulsive force acting between the permanent magnets 15 and 16 acts on the brake pad 4B with respect to the rotation axis direction of the disk rotor 3.

  Between the inner brake pad 4 </ b> A and the piston 14, permanent magnets 17 and 18 are arranged side by side in the rotational axis direction of the disk rotor 3. Specifically, a flat permanent magnet 17 is joined to the back surface of the back metal 8 of the brake pad 4A. A block-shaped permanent magnet 18 is joined to the bottom surface of the recess of the piston 14. These permanent magnets 17 and 18 are also arranged so that the same poles face each other, like the permanent magnets 15 and 16 described above.

  In the present embodiment, the block-shaped permanent magnets 16 and 18 are used in consideration of downsizing and space efficiency of the disc brake device 1. However, instead of the permanent magnet 16, a plate-shaped permanent magnet is used as the claw portion 13. The plate-shaped permanent magnet may be bonded to the upper end surface of the piston 14 instead of the permanent magnet 18.

  In the disc brake device 1 configured as described above, when a brake pedal (not shown) of the vehicle is depressed, hydraulic oil corresponding to the depression amount is supplied to the cylinder portion 12, and the hydraulic pressure of the hydraulic oil at that time is supplied. Accordingly, the piston 14 moves toward the disk rotor 3. Then, the piston 14 presses the brake pad 4A through the permanent magnets 18 and 17. Further, each claw portion 13 of the caliper 7 moves toward the disc rotor 3 by a reaction force when the piston 14 moves toward the disc rotor 3 with respect to the cylinder portion 12. And each claw part 13 presses brake pad 4A via permanent magnets 16 and 15. As a result, the pad main body 9 of the brake pads 4A and 4B comes into frictional contact with the rotor surfaces 3A and 3B of the disc rotor 3, and a braking force is generated.

  At this time, since the torque transmission projections 10 provided at both ends of the back metal 8 of the brake pads 4A and 4B are supported by the torque receiving grooves 11 of the mounting 5, the rotational torque of the disc rotor 3 is applied to the brake pad 4A. , 4B to be received by the mounting 5.

  By the way, in the conventional general disc brake device in which shims are attached to the back metal 8 of the brake pads 4A and 4B without providing the permanent magnets 15 to 18, the following problems occur.

  That is, when the brake pads 4A and 4B are pressed against the disc rotor 3, as shown in FIG. 3, a frictional force and a moment force in the shearing direction are generated. 5 will be supported at two points. At this time, the frictional force fluctuates depending on the braking environment, the support points of the brake pads 4A and 4B become unstable, the contact area between the shim and the claw portion 13 and the piston 14, the influence of uneven surface pressure distribution, etc. Since the local contact occurs, the moment force fluctuates, the brake pads 4A and 4B are twisted, and the support points of the brake pads 4A and 4B become unstable. For this reason, in the worst case, there is no load on one support point Q, and the brake pads 4A and 4B are supported only by the other support point P. As a result, the restraining force of the brake pads 4A and 4B by the mounting 5 is reduced, and the brake pads 4A and 4B are liable to vibrate, so that the brake noise is generated.

  In order to solve such a problem, there is a method of smoothing the sliding of the brake pads 4A and 4B in the shearing direction by overlapping two shims. However, in this case, when the braking history is added, the shims are rubbed and scratched, and unevenness is generated on the surface of the shim. As a result, the slip of the brake pads 4A and 4B may be deteriorated.

  On the other hand, in the present embodiment, the permanent magnets 15 and 16 are disposed between the brake pad 4B and the claw portion 13 of the caliper 7 so that the same poles face each other. The repulsive force causes a minute gap between the permanent magnets 15 and 16 (see FIG. 4). For this reason, since the frictional force in the shearing direction that hinders the sliding of the brake pad 4B does not act between the brake pad 4B and the claw portion 13, the brake pad 4B easily moves in the shearing direction. In addition, since the permanent magnets 17 and 18 are disposed between the brake pad 4A and the piston 14 so that the same poles face each other, the shear direction between the brake pad 4A and the piston 14 is the same as described above. Thus, the brake pad 4A easily moves in the shearing direction.

  As a result, during braking, the torque transmitting protrusions 10 of the brake pads 4A and 4B can be received by the torque receiving of the mounting 5 without being affected by the contact area with the claw portion 13 and the piston 14 or the uneven surface pressure distribution. It is possible to stably contact the inner wall surface of the groove portion 11, and both end portions of the brake pads 4 </ b> A and 4 </ b> B can be stably supported by the mounting 5.

  Moreover, since permanent magnets 15 to 18 effective for preventing rust are used instead of shims, it is possible to prevent deterioration of brake quality due to rust.

  FIG. 5 is a partial sectional view schematically showing another embodiment of the disc brake device according to the present invention. In the drawing, the same reference numerals are given to the same or equivalent members as those of the above-described embodiment, and the description thereof is omitted.

  In the figure, a disc brake device 20 of the present embodiment is obtained by adding heat insulating materials 21 and 22 to the disc brake device 1 described above. The heat insulating material 21 prevents heat from the brake pad 4 </ b> A from being transmitted to the permanent magnets 17 and 18, and is interposed between the brake pad 4 </ b> A and the permanent magnet 17. The heat insulating material 22 prevents heat from the brake pad 4 </ b> B from being transmitted to the permanent magnets 15 and 16, and is interposed between the brake pad 4 </ b> B and the permanent magnet 15. As the heat insulating materials 21 and 22, for example, an aluminum sheet or the like is used.

  By providing such heat insulating materials 21 and 22, even when normal permanent magnets 15 to 18 having low heat resistance are used, deterioration of the permanent magnets 15 to 18 due to heat can be prevented. Thereby, as shown in FIG. 6, the effect of the repulsive force which acts between the permanent magnets 15 and 16 is maintained. The same applies to the effect of repulsive force acting between the permanent magnets 17 and 18. Therefore, the torque transmitting projections 10 of the brake pads 4A and 4B can be stably brought into contact with the torque receiving grooves 11 of the mounting 5 over a long period of time.

  The present invention is not limited to the above embodiment. For example, in the above embodiment, the permanent magnets 17 and 18 are disposed between the brake pad 4A and the piston 14, and the permanent magnets 15 and 16 are disposed between the brake pad 4B and the claw portion 13 of the caliper 7. However, a plurality of permanent magnets may be disposed only between the brake pad 4A and the piston 14, or a plurality of permanent magnets may be disposed only between the brake pad 4B and the claw portion 13 of the caliper 7. .

  In the above embodiment, the floating caliper 7 is provided. However, the present invention is also applicable to a disc brake device having a fixed caliper in which pistons are provided on both the inner and outer sides of the disc rotor 3. .

1 is a perspective view showing an appearance of an embodiment of a disc brake device according to the present invention. FIG. 2 is a partial sectional view schematically showing the disc brake device shown in FIG. 1. FIG. 3 is a cross-sectional view showing a support structure for the brake pad shown in FIG. 2. It is an expansion conceptual diagram which shows the polarity relationship of the permanent magnet shown in FIG. 2 with a brake pad. It is a fragmentary sectional view showing roughly other embodiments of a disc brake device concerning the present invention. It is an expansion conceptual diagram which shows the polarity relationship of the permanent magnet shown in FIG. 5 with a brake pad and a heat insulating material.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Disc brake device, 3 ... Disc rotor, 3A ... Inner rotor surface, 3B ... Outer rotor surface, 4A, 4B ... Brake pad, 5 ... Mounting, 7 ... Caliper, 13 ... Claw part (pad pressing wall part), 14 ... Piston, 15, 16 ... Permanent magnet (magnetic body), 17, 18 ... Permanent magnet (magnetic body), 20 ... Disc brake device, 21, 22 ... Insulating material.

Claims (2)

A pair of brake pads that press against both sides of the disc rotor to generate braking force;
A mounting that is arranged so as to straddle the outer periphery of the disk rotor, and receives and supports both ends of the brake pad;
A caliper coupled to the mounting and having a piston for pressing the brake pad against the disc rotor;
In at least one of a region between the brake pad and the piston and a region between the brake pad and the pad pressing wall portion of the caliper, a plurality of magnetic bodies are arranged in the rotation axis direction of the disk rotor. It is provided side by side,
Each of the magnetic bodies is disposed such that the same poles face each other. 2. The disc brake device according to claim 1, wherein a heat insulating material is interposed between the brake pad and the magnetic body.

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