JPH0777229A - Disk brake system - Google Patents

Abstract

PURPOSE:To improve the extent of braking noise preventing effect in a disk brake system. CONSTITUTION:A pair of pads 20 consisting of a back plate 21 and a frictional material 25 are supported on a mounting 10 locked in close proximity to a part of the circumferential part of a disk rotor 19, and this frictional material is pressed to both sides of this disk rotor by a caliper 15. Each braking torque receiving surface 23 at both ends in the direction of an action line L of braking force to be added to the pads is formed in the back plate, and likewise an anchor surface 13 contacting with each braking torque receiving surface and receiving the braking force being added to the pads is formed in the mounting 10. In this case, at least one of respective braking torque receiving surfaces and anchor surfaces is made a projecting arced surface toward the action line from a position distant from the action line of the braking force, while a reaction receiving surface 22a in contact with the mounting 10 almost parallel with the action line is installed in a part of the back plate 21.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disc brake device used in a vehicle such as an automobile, and more particularly to a disc brake device having an excellent function of preventing noise (brake squeal) caused by braking.

[0002]

2. Description of the Related Art As shown in FIGS. 1 and 2, for example, a disc brake device includes a pair of pads 20 provided on both sides of a part of the circumference of a disc rotor 19 which rotates with a wheel.
Is movably supported by a mounting 10 fixed to the vehicle body, and the pads 20 are pressed against both side surfaces of the disk rotor 19 by a caliper 15 to generate a braking force Fi.

FIG. 12 shows a conventional disc brake device.
As shown in FIG. 3, each pad 20 is composed of a friction material 6 that contacts the disk rotor 19 and a back metal 3. The ears 4 at both ends of the back metal 3 are located in the groove 1 formed in the mounting 10 and are movable a little. When the pads 20 are supported and pressed against both side surfaces of the disk rotor 19 by the operation of the caliper 15, the tip of the ear portion 4 on the rotational direction side of the disk rotor 19 (the right side in FIG. 1, hereinafter simply referred to as the trailing side). The braking force Fi applied to the pad 20 by the braking torque receiving surface 5 contacting the anchor surface 2 formed by the bottom surface of the groove portion 1
I'm supposed to take it. In this prior art, the braking torque receiving surface 5 of the ear portion 4 is formed in a plane shape orthogonal to the line of action L of the braking force Fi, and the anchor surface 2 is formed in a plane which comes into contact with the entire braking torque receiving surface 5 at the same time. It was In such a technique, when the disc brake device is actuated, the braking reaction force F0 that receives the braking force Fi applied to the pad 20 is generated on the braking force Fi line of the braking torque receiving surface 5. Therefore, the pad 20 was in contact with the mounting 10 only on the braking torque receiving surface 5 on the trailing side.

In the disc brake device, noise (brake squeal) due to self-excited vibration caused by stick-slip phenomenon between the disc rotor 19 and the friction material 25 during operation.
In order to prevent this, conventionally, an anti-squeal shim is provided between the backing plate 21 of the pad 20 and the brake piston 16 (see FIG. 2). A small angle is formed at both ends of the friction surface of the friction material 6. Although the chamfer 6a is formed and the shape and size of each part of the disc brake device are changed to shift the resonance frequency, the effect is not necessarily sufficient. Further, in the above-mentioned conventional technique, since the pad 20 is only in contact with the mounting 10 on the braking torque receiving surface 5 on the trailing side, the pad 20 itself does not have a function of preventing the brake squeal.

On the other hand, in Japanese Unexamined Patent Publication No. 61-59031, a first receiving portion, which abuts on the mounting and receives a braking force acting on the pad, is provided on the back metal on the outer peripheral portion side of the disk rotor on the trailing side. A second receiving portion for receiving the rotation of the pad generated by the braking force and the braking reaction force is provided on the back metal at the inner peripheral portion of the disc rotor on the leading side, and the second receiving portion is brought into contact with the mounting by the rotation of the pad. ing. According to this conventional technique, the movement of the pad is restrained between the second receiving portion and the mounting, so that it is expected to be effective in preventing the brake squeal.

[0006]

However, even in the second prior art described above, the braking torque receiving surface formed at the tip of the first receiving portion is a plane shape orthogonal to the line of action of the braking force, and the anchor surface of the mounting. Is formed on a plane that comes into contact with the entire braking torque receiving surface at the same time, the braking reaction force generated between the anchor surface and the braking torque receiving surface moves to the action line side of the braking force when the pad rotates. Therefore, the moment for rotating the pad is reduced or eliminated, and the pressing force between the second receiving portion and the mounting is also reduced or eliminated, so that it may not be possible to obtain a sufficient brake squeal prevention effect. An object of the present invention is to provide a disc brake device that solves such a problem and can improve the brake squeal prevention effect.

[0007]

To this end, the disc brake device according to the present invention, as illustrated in FIGS. 1 to 11, has a disc rotor that rotates together with a wheel and a part of a circumferential portion of the disc rotor. A pad support member fixed to the vehicle body close to the vehicle body, and a friction member fixed to one side surface of the back metal so that the friction member can contact both side surfaces of the disk rotor and the disk rotor from a predetermined reference position. A pair of pads supported by the pad support member so as to be able to move a little distance in the radial direction and the circumferential direction, and a caliper provided on the vehicle body or the like for pressing the friction material of each pad against the disk rotor; A braking torque receiving surface formed substantially orthogonal to the line of action at both ends of the backing metal in the line of action of the braking force applied to the pad by pressing on the disc rotor,
In the disc brake device including an anchor surface formed on the pad support member corresponding to each of the braking torque receiving surfaces and receiving a braking force applied to the pad by contacting with the corresponding braking torque receiving surface, the braking torques contacting each other. At least one of the receiving surface and the anchor surface is a convex arc surface that starts in a direction orthogonal to the line of action from a position distant from the line of action of the braking force applied to the pad at the reference position and proceeds toward the line of action, In the circumferential direction of the disk rotor, a part of the backing metal opposite to the convex arc surface is provided with a reaction force receiving surface which is formed substantially parallel to the line of action and abuts against the pad supporting member. It is what

[0008]

[Operation] When the disc brake device operates, the pad moves to the trailing side due to the braking force generated in the friction material,
The braking torque receiving surface on the trailing side of the backing metal and the anchor surface formed on the pad support member corresponding to the braking torque receiving surface are abutted against each other at a position apart from the line of action of the braking force and are pressed against the braking force. An offset braking reaction force is generated. Due to the rotation moment due to the braking force and the braking reaction force, the reaction force receiving surface formed on the opposite side of the backing metal from the trailing side is brought into contact with a part of the pad support member, and the reaction force receiving surface is proportional to the braking force. The momentary reaction force pushes against the pad support material. A convex arc surface is formed on at least one of the braking torque receiving surface and the anchor surface that abut each other, and the rotation of the pad due to the rotation moment is slight, so that the braking force at the point of action of the braking reaction force accompanying this rotation is small. Is slightly moved in the direction of the line of action. Therefore, the reaction force of the moment when the reaction force receiving surface presses the pad support member does not substantially decrease due to the rotation of the pad, and always has a predetermined value according to the braking force.

[0009]

As described above, according to the present invention, the pad is supported not only on the braking torque receiving surface pressed by the anchor surface of the pad supporting member but also on the reaction force receiving surface opposite to the braking torque receiving surface. A moment reaction force for pressing the material is generated, and this moment reaction force is not substantially reduced by the rotation of the pad. Therefore, due to the friction due to the moment reaction force, stable damping of vibration is given to the pad, so that the brake squeal prevention effect of the disc brake device including the pad can be improved.

[0010]

1 to 5 show a first embodiment of a disc brake device according to the present invention. First, referring to FIGS. 1 and 2, the disc brake device as a whole will be described. In the vehicle body of an automobile, a part of the circumference of a disc rotor 19 which is fixed to a hub of a wheel and rotates together is approached, and a caliper 15 is provided. And 1
The mounting 10 serving as a pad support member that supports the pair of pads 20 is fixed. The caliper 15 that is floatingly supported by the mounting 10 so as to be movable in the axial direction via the support pin 14 that is parallel to the rotation axis of the disc rotor 19 includes a reaction portion 15a and a cylinder portion 15c located on both sides of the circumferential portion of the disc rotor 19. And a bridge portion 15b connecting them, and a piston 16 is provided on the cylinder portion 15c so as to be movable in parallel with the support pin 14. A pad 20 is provided between the reaction portion 15a and the cylinder portion 15c and the disc rotor 19, and when hydraulic pressure is applied to the working chamber 17 on the rear surface of the piston 16, the friction material 25 of the pad 20 on the piston 16 side presses the disc rotor 19. At the same time, the floating-supported caliper 15 moves, and the reaction portion 15a also presses the friction material 25 of the pad 20 on the opposite side against the disc rotor 19 to generate a braking force.

As shown in FIGS. 1 to 4, each pad 20 has a friction material 25 fixed to one side surface of a flat backing metal 21 by adhesion or the like, and has the same shape. As shown in FIGS. 1, 3 and 4, a pair of ears 22 are formed symmetrically on the back metal 21, and a pair of grooves 1 are formed on the mounting 10.
1 are formed to face each other. By inserting the ears 22 into the grooves 11 with a slight clearance, the pad 20 can be moved slightly vertically and horizontally from the reference position and can be moved forward and backward.
Supported by. In the first embodiment, the tip end surface of each ear portion 22 forms the braking torque receiving surface 23, and the bottom surface of the groove portion 11 forms the anchor surface 13 that can come into contact with the braking torque receiving surface 23. In these figures, the gap between each ear 22 and the groove 11 is exaggerated. The reference position is a position where the pad 20 which receives no external force other than gravity is supported by the mounting 10. In this first embodiment, as shown in FIG. It is a position supported on the lower inner surface.

When the pad 20 is in the reference position shown in FIG. 3, the action line of the braking force Fi applied to the friction material 25 (the resultant force of the friction forces generated at the respective contact portions between the disk rotor 19 and the friction material 25). L is parallel to the line connecting the corresponding portions of the both ears 22 and is displaced from the center of the width of the braking torque receiving surface 23. Each braking torque receiving surface 23 is formed as a convex arc surface having a large radius R in a range S extending upward from a position P that is raised by a round chamfer from the lower side surface 22b of the ear portion 22, and the center of the convex arc surface. Is a line K connecting the left and right positions P
It is above. Since this line K passes through the position P and is parallel to the action line L at the reference position, each braking torque receiving surface 23 starts from the position P distant from the action line L in a direction orthogonal to the action line L and then the action line L. It becomes a convex arc surface facing in the direction. The upper edge of each ear portion 22 forms a reaction force receiving surface 22a that is parallel to the line of action L of the braking force Fi and is capable of contacting with the corresponding upper inner surface of the groove portion 11. The anchor surface 13 of the mounting 10 that can come into contact with the braking torque receiving surface 23 is a plane orthogonal to the line of action L.

When the vehicle is moving forward, the disk rotor 19
Is rotating in the direction of arrow D shown in FIG.
If hydraulic pressure is applied to the working chamber 17 in this state, each pad 20
The friction material 25 is pressed by the disc rotor 19 to generate a braking force Fi. This braking force Fi causes the pad 20 to move to the position shown in FIG.
And as shown in FIG. 3, the trailing side (see FIGS. 1 and 3
To the right side), the braking torque receiving surface 23 on the trailing side of the backing metal 21 and the anchor surface 13 correspondingly formed on the mounting 10 are brought into contact with each other at the position P and pressed. A braking reaction force F0 that is offset with respect to the braking force Fi is generated. The pad 20 is slightly rotated in the clockwise direction by the rotation moment M due to the braking force Fi and the braking reaction force F0, and the reaction force receiving surface 22a formed at the upper edge of the ear portion 22 on the side opposite to the trailing side is mounted. The rotation of the pad 20 is stopped by coming into contact with the upper inner surface of the groove 11 formed on the left side of the groove 10, and the reaction force receiving surface 22a is pressed against the upper inner surface of the groove 11 by a moment reaction force W proportional to the rotation moment M. To be done.

With the rotation of the pad 20, the point of action of the braking reaction force F0 moves from the position P to the direction of the line of action L as shown in FIG. 5, but this rotation is slight, and the braking torque is received. Since the convex arc surface is formed on the surface 23, the movement of the braking reaction force F0 from the position P of the action point due to this rotation is slight. Therefore, the offset amount between the braking force Fi and the braking reaction force F0 hardly decreases, so that the moment reaction force W acting between the reaction force receiving surface 22a and the upper inner surface of the groove portion 11 does not substantially decrease.

In the disc brake device, a brake squeal may occur due to self-excited vibration caused by a stick-slip phenomenon between the disc rotor 19 and the friction material 25 during operation. The squeal of the brake is caused by the disk rotor 19, the pad 20, the caliper 15, and the piston 16 vibrating in association with each other. One of them, the pad 20, is a reaction force on the opposite side of the braking torque receiving surface 23. On the receiving surface 22a, the moment reaction force W is pressed against the upper inner surface of the groove portion 11 of the mounting 10, and the moment reaction force W is not substantially reduced by the rotation of the pad 20, so that the reaction force receiving surface 22a The stable sliding friction between the upper inner surfaces of the grooves 11 provides damping of the vibration of the pad 20. Therefore, vibrations of the disc rotor 19, the pad 20, the caliper 15, and the piston 16 which are related to each other are also suppressed, and the brake squeal is reduced.

In the first embodiment, the radius R of the convex arc surface is larger than half the distance between the left and right braking torque receiving surfaces 23. However, the braking force Fi causes the braking torque receiving surface 23 and the anchor surface 13 to move. If the contact stress generated between them is within the allowable limit,
The value of the radius R is arbitrary.

The second embodiment shown in FIG. 6 is different from the first embodiment only in the shape of the braking torque receiving surface 23 at the tip of the ear portion 22 of the pad 20. In the second embodiment, the braking torque receiving surface 23 extends upward from a position P that is raised by a radius chamfer and a range T from the lower side surface 22b of the ear portion 22.
Is formed in a convex arcuate surface having a large radius R, and the center of this convex arcuate surface connects the left and right positions P apart from the action line L and is parallel to the action line L at the reference position, as in the first embodiment. It is on the extending line K. Therefore, also in this embodiment, the braking torque receiving surface 23 is a convex arc surface that starts from the position P in a direction orthogonal to the line of action L and extends in the direction of the line of action L. The range T is a straight line orthogonal to the action line L.

Also in this embodiment, the movement of the point of application of the braking reaction force F0 from the position P due to the rotation of the pad 20 is slight, so that the reaction force receiving surface 22a on the left side and the inner surface on the upper side of the groove portion 11 are separated. The moment reaction force W acting on is not substantially reduced. Therefore, the stable sliding friction between the reaction force receiving surface 22a and the upper inner surface of the groove portion 11 also suppresses the vibrations of the components including the pad 20 which are related to each other and reduces the brake squeal.

The third embodiment shown in FIG. 7 is the same as the first embodiment except that the braking torque receiving surface 23 is formed upside down. That is, a convex arc surface having a large radius R is formed between a range P extending downward from the upper side surface 22c of the ear portion 22 by a chamfered portion, and the center of the convex arc surface is the same as that of the first embodiment. Similarly, each of the left and right positions P separated from the line of action L is connected to the line K extending in parallel with the line of action L at the reference position. Therefore, also in this embodiment, the braking torque receiving surface 23 is a convex arc surface that starts from the position P in a direction orthogonal to the line of action L and extends in the direction of the line of action L.

When the disc brake device is operated in the third embodiment, the pad 20 is moved by the braking force Fi as described above, and the braking torque receiving surface 23 on the trailing side is obtained.
The corresponding anchor surfaces 13 are pressed against each other at the position P to generate a braking reaction force F0 offset with respect to the braking force Fi. By the rotation moment M in the counterclockwise rotation direction due to the braking force Fi and the braking reaction force F0,
The reaction force receiving surface 22a on the side opposite to the trailing side has a corresponding groove portion 1 with a moment reaction force W proportional to the rotation moment M.
1 is pressed against the inner surface of the lower side.

The pad 20 rotates in the counterclockwise direction, and the point of action of the braking reaction force F0 moves from the position P to the direction of the line of action L, but this rotation is slight, and the braking torque is received. Since the convex arc surface is formed on the surface 23, the movement of the braking reaction force F0 from the position P of the action point due to this rotation is slight. Therefore, as in the above-described embodiment, the reaction force receiving surface 22a
The moment reaction force W acting between the inner surface of the groove 11 and the lower inner surface of the groove portion 11 does not substantially decrease, so that the reaction force receiving surface 22a.
By the stable sliding friction between the lower inner surface of the groove 11 and the groove 11,
Vibrations associated with the parts including the pad 20 are also suppressed, and brake squeal is reduced.

In the fourth embodiment shown in FIG. 8, a pair of protrusions 2 that replace the ears 22 are provided on the upper and left ends of the back metal 21 of the pad 20.
2A is formed, and braking torque receiving surfaces 23 are formed on both sides of the back metal 21 below the 2A. Each pad 20 is provided with a protrusion 22A from above in a notch 11A formed facing the upper part of the mounting 10 so that each pad 20 can be slightly moved vertically and horizontally from a reference position where it receives no external force other than gravity, and Mountable to move forward and backward 10
Supported by. The lower surface of each projection 22A forms a reaction force receiving surface 22a, and the braking torque receiving surface 23 is centered on a point on the line K located equidistantly below each reaction force receiving surface 22a, and is located on the line K at a position P. Is formed as a convex arc surface having a radius R extending downward from. The surface that extends upward from the position P to the reaction force receiving surface 22a continuously with the braking torque receiving surface 23 is a plane orthogonal to the line K in the present embodiment, but is a convex arc surface obtained by extending the braking torque receiving surface 23. Good. A pair of anchor surfaces 13 formed below the notches 11A of the mounting 10 facing the braking torque receiving surfaces 23 are planes orthogonal to the action line L of the braking force Fi. At the reference position according to FIG. 3, the action line L of the braking force Fi applied to the pad 20 is parallel to the line K and is located below the line K.

When the disc brake device is actuated in the fourth embodiment, the pad 20 moves to the trailing side, and the braking torque receiving surface 23 on the trailing side and the anchor surface 13 corresponding thereto move at the position P. A braking reaction force F0 that is pressed against each other and offset with respect to the braking force Fi is generated. Due to the rotation moment M in the counterclockwise rotation direction due to the braking force Fi and the braking reaction force F0, the reaction force receiving surface 22a on the side opposite to the trailing side has a rotation moment M.
It is pressed against the upper surface of the notch 11A by a moment reaction force W proportional to.

The pad 20 rotates in the counterclockwise direction, and the action point of the braking reaction force F0 moves from the position P to the direction of the action line L in accordance with this rotation. The accompanying movement of the braking reaction force F0 from the position P of the action point is slight. Therefore, the moment reaction force W acting between the reaction force receiving surface 22a and the upper surface of the notch 11A does not substantially decrease, and the pad due to the sliding friction between the reaction force receiving surface 22a and the upper surface of the notch 11A. Vibrations associated with each of the components including 20 are also suppressed and brake squeal is reduced. .

Next, a fifth embodiment shown in FIG. 9 is a pad 20.
Although the backing metal 21 and the mounting 10 of the first embodiment have the ears 22 and the groove 11 similar to those in the first to third embodiments, the braking torque receiving surface 23 and the anchor surface 13 have the ears 22 and the groove 1.
1 is different from that of FIG. Pad 2
The backing metal 21 of 0 has a braking torque receiving surface 23 formed below the left and right ears 22. The braking torque receiving surface 23 is formed as a convex arc surface having a large radius R in a range S extending upward from a position P that is considerably lower than the lower side surface 22b of the ear portion 22, and the center of this convex arc surface is the first. Similar to the embodiment, it is on a line K that connects the left and right positions P apart from the action line L and extends parallel to the action line L at the reference position. Therefore, the braking torque receiving surface 23 is a convex arc surface that starts from the position P in a direction orthogonal to the line of action L and extends in the direction of the line of action L. By inserting the ears 22 of the backing metal 21 into the groove 11 of the mounting 10, the pads 20 are supported by the mounting 10 so as to be movable up and down, left and right, and forward and backward from the reference position. . Each braking torque receiving surface 2
A pair of anchor surfaces 13 formed on the lower side of each groove 11 of the mounting 10 so as to face 3 are planes orthogonal to the action line L of the braking force Fi.

When the disc brake device is actuated in the fifth embodiment, the pad 20 moves to the trailing side, and the braking torque receiving surface 23 on the trailing side and the anchor surface 13 corresponding thereto move at the position P. A braking reaction force F0 that is pressed against each other and offset with respect to the braking force Fi is generated. The pad 20 slightly rotates in the clockwise direction by the rotation moment M due to the braking force Fi and the braking reaction force F0, and the reaction force receiving surface 22a at the upper edge of the ear portion 22 on the side opposite to the trailing side corresponds to the mounting 10. The pad 20 is stopped from rotating by coming into contact with the upper inner surface of the groove 11, and the reaction force receiving surface 22a is pressed against the upper inner surface of the groove 11 by a moment reaction force W proportional to the rotation moment M.

With the rotation of the pad 20, the action point of the braking reaction force F0 moves from the position P in the direction of the action line L.
Since this movement is slight as in the third embodiment, the moment reaction force W acting between the reaction force receiving surface 22a and the upper inner surface of the groove portion 11 is not substantially reduced. Therefore, due to the sliding friction between the reaction force receiving surface 22a and the upper inner surface of the groove portion 11,
Vibrations associated with the parts including the pad 20 are also suppressed, and brake squeal is reduced.

The sixth embodiment shown in FIG. 10 is an embodiment of the opposed type caliper. Long holes 22B are formed at two places on the upper and right sides of the backing metal 21 of the pad 20, and the pins 11B supported by the cylinder 30 are inserted into the long holes 22B in parallel with the rotation axis of the disc rotor 19, so that each pad 20 is gravitated. Other than the reference position where external force is not applied, it is supported so as to be able to move in the up and down and left and right directions to some extent and in the front and back directions. In this embodiment, the reaction force receiving surface 22a is formed by the upper inner surface of each slot 22B. The braking torque receiving surface 23 is formed as a convex arcuate surface having a radius R extending downward from the position P on the line K with a point on the line K positioned equidistantly below the respective elongated holes 22B as the center. The surface that extends upward from the position P continuously with the braking torque receiving surface 23 is a plane orthogonal to the line K in the present embodiment, but it may be a convex arc surface that is an extension of the braking torque receiving surface 23. The pair of anchor surfaces 13 formed on the mounting 10 so as to face the braking torque receiving surfaces 23 are planes orthogonal to the action line L of the braking force Fi. The action line L of the braking force Fi applied to the pad 20 at the reference position is the line K.
Is parallel to and is located below the line K. In the sixth embodiment, the caliper 15 that presses each pad 20 against the disk rotor 19 is of a facing type.

When the disc brake device is actuated in the sixth embodiment, the pad 20 moves to the trailing side, and the braking torque receiving surface 23 on the trailing side and the anchor surface 13 corresponding thereto are at the position P. A braking reaction force F0 that is pressed against each other and offset with respect to the braking force Fi is generated. Due to the rotation moment M due to the braking force Fi and the braking reaction force F0, the reaction force receiving surface 22a on the side opposite to the trailing side is pressed against the upper surface of the pin 11B by the moment reaction force W proportional to the rotation moment M.

Although the pad 20 rotates in the counterclockwise direction, the moment reaction force W acting between the reaction force receiving surface 22a and the pin 11B does not substantially decrease, as in the above-mentioned cases. Due to the stable sliding friction between the reaction force receiving surface 22a and the pin 11B, the vibrations of the components including the pad 20 associated with each other are also suppressed, and the brake squeal is prevented.

In each of the above-described embodiments, the braking torque receiving surface 23 and the anchoring surface 13, which are in contact with each other, on the pad 20 side are formed as convex arc surfaces.
In the seventh embodiment shown in, the anchor surface 13 on the mounting 10 side is formed as a convex arc surface. In the seventh embodiment, the braking torque receiving surfaces 23 at the ends of the ears 22 at both ends of the back metal 21 of the pad 20 are the same as those in the conventional technique shown in FIG.
It is formed in a plane shape orthogonal to the action line L of the braking force Fi at the reference position where an external force other than gravity is not applied to the pad 20. On the other hand, the anchor surface 13 formed by the bottom surfaces of the pair of groove portions 11 formed so as to face the mounting 10 has a range S extending upward from the position P that is the same distance from the inner and lower surfaces of each groove portion 11. Large radius R
Is formed on a convex arc surface of, and the center of this convex arc surface is on a line K passing through the two positions P. This line K is parallel to the line of action L of the braking force Fi applied to the friction material 25 when the pad 20 is at the reference position, so that the anchor surface 13 changes from the position P away from the line of action L to the line of action L. It becomes a convex arc surface which starts in the direction orthogonal to the direction of the line of action L. Similar to the first embodiment, the upper edge of each ear portion 22 forms a reaction force receiving surface 22a which is parallel to the line of action L of the braking force Fi and is capable of contacting the upper inner surface of the corresponding groove portion 11.

When the disc brake device is operated in the seventh embodiment, the pad 20 moves to the trailing side, and the braking torque receiving surface 23 on the trailing side and the anchor surface 13 corresponding to the braking torque receiving surface 23 at the position P. A braking reaction force F0 that is pressed against each other and offset with respect to the braking force Fi is generated. The pad 20 slightly rotates in the clockwise direction by the rotation moment M due to the braking force Fi and the braking reaction force F0, and the reaction force receiving surface 22a at the upper edge of the ear portion 22 on the side opposite to the trailing side corresponds to the mounting 10. The pad 20 is stopped from rotating by coming into contact with the upper inner surface of the groove 11, and the reaction force receiving surface 22a is pressed against the upper inner surface of the groove 11 by a moment reaction force W proportional to the rotation moment M.

The action point of the braking reaction force F0 moves in the direction of the action line L from the position P with the rotation of the pad 20, but this movement is slight as in the first embodiment, so the reaction force receiving surface 22a.
The moment reaction force W acting between the groove and the upper inner surface of the groove portion 11 does not substantially decrease. Therefore, the reaction force receiving surface 22
Due to the sliding friction between a and the upper inner surface of the groove portion 11, the vibrations of the disc rotor 19, the pad 20, the caliper 15 and the piston 16 related to each other are also suppressed and the brake squeal is reduced. .

In the seventh embodiment, instead of the braking torque receiving surface 23 in the first embodiment, the anchor surface 13 is a convex arc surface, but in any of the second to sixth embodiments, the braking It is possible to obtain a modified example in which instead of the torque receiving surface 23, the anchor surface 13 that contacts the torque receiving surface 23 is a convex arc surface. Further, in each of the above embodiments, the braking torque receiving surface 2
It is also possible to form both 3 and the anchor surface 13 into a convex arc surface. Furthermore, in each of the above-described embodiments, the braking torque receiving surfaces 23 on both sides in the circumferential direction of the pad 20 or the anchor surfaces 13 corresponding thereto or both of them are convex arc surfaces, but one side of the pad 20 in the circumferential direction ( For example, the present invention can be implemented with only the braking torque receiving surface 23 as a convex arc surface only on the trailing side when the vehicle is moving forward.

[Brief description of drawings]

FIG. 1 is a front view of an embodiment of a disc brake device according to the present invention.

FIG. 2 is a central longitudinal sectional view of the embodiment shown in FIG.

3 is a front view showing the pad and its related portion in the standard state of the embodiment shown in FIG. 1. FIG.

FIG. 4 is a front view showing the pad and its related portion in an operating state of the embodiment shown in FIG.

5 is a partial front view showing an enlarged part of FIG. 4. FIG.

FIG. 6 is a front view corresponding to FIG. 4 of the second embodiment.

FIG. 7 is a front view corresponding to FIG. 4 of the third embodiment.

FIG. 8 is a front view corresponding to FIG. 4 of the fourth embodiment.

FIG. 9 is a front view corresponding to FIG. 4 of the fifth embodiment.

FIG. 10 is a front view of a sixth embodiment corresponding to FIG.

FIG. 11 is a front view corresponding to FIG. 4 of the seventh embodiment.

FIG. 12 is a front view corresponding to FIG. 4 of the prior art.

[Explanation of symbols]

10 ... Mounting, 13 ... Anchor surface, 15 ... Caliper, 19 ... Disk rotor, 20 ... Pad, 21 ... Back metal, 22a ... Reaction force receiving surface, 23 ... Braking torque receiving surface, 25 ...
Friction material, L ... Line of action of braking force, P ... Position.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hidetoshi Shimizu 1 Toyota-cho, Toyota-cho, Aichi Prefecture, Toyota Motor Co., Ltd. (72) Inventor Yasushi Yasushi 1-cho, Toyota-cho, Aichi, Toyota Motor Co., Ltd. ( 72) Inventor Hiromichi Yamazaki 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Automobile Co., Ltd.

Claims (1)

[Claims] 1. A disk rotor that rotates together with a wheel,
A pad support material that is fixed to the vehicle body by approaching a part of the circumference of the disk rotor, and a friction material is fixed to one side surface of the back metal, and the friction material can contact both side surfaces of the disk rotor. And a pair of pads supported by the pad support member so as to be movable to some distance in the radial direction and the circumferential direction with respect to the disk rotor from a predetermined reference position, and a friction material for each pad provided on the vehicle body or the like. A caliper for pressing the disk rotor against the disk rotor, and a braking torque receiving surface formed at both ends of the backing metal in a direction substantially perpendicular to the line of operation of the braking force applied to the pad by pressing the disk rotor. And a disc brake including an anchor surface formed on the pad support member corresponding to each braking torque receiving surface and contacting a corresponding braking torque receiving surface to receive a braking force applied to the pad. Position, at least one of the braking torque receiving surface and the anchor surface that abut each other starts from a position distant from the line of action of the braking force applied to the pad at the reference position in a direction orthogonal to the line of action and the line of action. A part of the back metal which is opposite to the convex arc surface in the circumferential direction of the disk rotor and which is formed substantially parallel to the line of action and contacts the pad support member. A disc brake device having a force receiving surface.