JP2002276700A - Disc brake - Google Patents

Abstract

PROBLEM TO BE SOLVED: To correct a rotor-shaft-directional swing of the outer circumference of a disk rotor having high sensitivity to brake vibration in the braking due to micro abrasion of the disk rotor formed by both pads in the braking without developing the thickness difference of the disk rotor. SOLUTION: This disk brake is so formed that an inner pad 62 and an outer pad 61 are supported to a mounting 40 movably in the rotor shaft direction. The both pads 61 and 62 are rotatable relative to the mounting 40 with a line L connecting rotor turn-in side support parts of the outer circumference of the disk rotor in the both pads 61 and 62 to rotor turn-out side support parts 61b and 62b of the inner circumference of the disk rotor set to a rotation axis, and the rotor turn-out sides 61c and 62c of the outer circumference of the disk rotor in the both pads 61 and 62 are mutually connected by a spring and energized to the disk rotor 50 by a micro load.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disc brake, and more particularly, to a disc brake in which an inner pad and an outer pad are supported by a mounting so as to be movable in an axial direction of a rotor.

[0002]

2. Description of the Related Art A large number of disc brakes of this type have been proposed. In such disc brakes, the vibration in the rotor axial direction on the outer periphery of the disc rotor, which is highly sensitive to brake vibration during braking, has been proposed. It is a fact that sufficient measures have not been taken against brake vibration during braking caused by the difference in thickness of the disk rotor. SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to suppress a brake vibration at the time of braking caused by a runout of the outer periphery of a disk rotor in a rotor axial direction and a difference in thickness of the disk rotor.

[0003]

In order to solve the above-mentioned problems, the present invention provides a disk brake in which an inner pad and an outer pad are supported by a mounting so as to be movable in the axial direction of a rotor. The two pads are rotatable with respect to the mounting with a line connecting the rotor revolving-side support portion on the outer periphery of the disk rotor and the rotor revolving-side support portion on the inner periphery of the disk rotor as the rotation axis. Are connected to each other by a spring and biased toward the disk rotor with a small load (the invention according to claim 1).

In this case, it is desirable to connect the ends of the outer circumference of the disk rotor on both sides of the disk rotor on the rotor reciprocating side with a spring and urge the pads in a direction away from the disk rotor (the invention according to claim 2). The rotor inflow-side support portion on the outer periphery of the disk rotor and the rotor outflow-side support portion on the inner circumference of the disk rotor in both pads have a circular shape centered on the rotation axis. Invention) is desirable.

[0005]

In the disk brake according to the present invention (the invention according to claim 1), the rotor pad on the outer periphery of the disk rotor and the rotor outlet side support on the inner periphery of the disk rotor are connected at both pads. With the line as the axis of rotation, both pads can be rotated for mounting,
The ends of the outer circumference of the disk rotor on the rotor outlet side were connected to each other by a spring and urged toward the disk rotor with a small load. For this reason, it is possible to always press the end of the outer periphery of the disk rotor of both pads on the rotor leading-out side against the disk rotor with a small load of the spring, and to always follow the deflection of the outer circumference of the disk rotor in the rotor axial direction.

[0006] Therefore, the small wear (the outer peripheral wear amount) of the outer periphery of the disk rotor due to both pads obtained during the non-braking operation is the amount of wear that continuously increases and decreases over the entire circumference of the rotor in accordance with the amount of run-out in the axial direction of the rotor. Can be
The vibration in the rotor axis direction on the outer periphery of the disk rotor, which is highly sensitive to brake vibration during braking, can be corrected without growing the thickness difference of the disk rotor, and the brake vibration during braking caused by the thickness difference of the disk rotor can be corrected. Can be effectively suppressed.

Further, when the present invention is carried out, the rotor inflow-side ends of the outer periphery of the disk rotor in both pads are connected to each other by a spring and urged in a direction away from the disk rotor (an invention according to claim 2). In this case, it is possible to simply configure a configuration in which only the rotor leading-out end of the outer periphery of the disk rotor in both pads accurately follows the deflection in the rotor axial direction of the outer periphery of the disk rotor.

In implementing the present invention, each of the pads has a rotor inlet side support portion on the outer periphery of the disk rotor and a rotor outlet side support portion on the inner circumference of the disk rotor having a circular portion centered on the rotation axis. In the case of the shape (the invention according to claim 3), both pads can be smoothly rotated around the rotation axis with respect to the mounting.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. 1 to 4 show an embodiment in which the present invention is applied to a disk brake A for a vehicle. In this disk brake A, a caliper 10 has a pair of pin sliding means 20, 3
The mounting member 40 is supported by the two supporting portions 41 and 42 of the mounting 40 via the base member 0 so as to be movable in the rotor axial direction. The caliper 10 and the mounting 40 are formed so as to straddle the disk rotor 50 that rotates in the counterclockwise direction in FIG.

The caliper 10 has an arch-shaped reaction force arm 13 for pressing the outer pad 61 toward the disk rotor 60 on the outer side.
12 and a cylinder part 14 having a bottom. The reaction force arm portion 13 is formed in a shape inclined by a predetermined amount θ in the rotor radial direction (closed shape on the inner circumference) as exaggeratedly shown in FIG. 2, and is deformed so that the caliper 10 warps at the time of braking. In such a state, the entirety thereof comes into contact with the back surface of the outer pad 61. The cylinder portion 14 is open toward the disk rotor 50, and a piston 15 for pressing the inner pad 62 toward the disk rotor 50 is inserted into the cylinder portion 14 via a seal ring 16 so as to be slidable in the axial direction. ing. A boot 17 is mounted between the open end of the cylinder portion 14 and the outer periphery of the protruding portion of the piston 15.

As shown in FIG. 1, each of the pin slide means 20 and 30 is provided with a corresponding one of the support portions 41 and 4 of the mounting 40.
The slide pins 21 and 31 which are movably fitted in the axial direction into mounting holes (not shown) provided in the mounting member 2, and the slide pins 21 and 31 are integrally connected to the arm portions 11 and 12 of the caliper 10. And each of the pin bolts 22 and 32
Pin boots 23 and 33 for sealing are mounted on the outer periphery of portions of the slide pins 21 and 31 protruding from the mounting holes.

The outer pad 61 and the inner pad 62
3, it is formed in a symmetrical shape, and is supported by the mounting 40 so as to be movable in the rotor axis direction. In addition, both pads 61 and 62 have, as a rotation axis, a line (axis) L connecting the rotor entrance side support ends 61a and 62a on the outer periphery of the disk rotor and the rotor exit side support ends 61b and 62b on the disk rotor inner periphery. , Can be rotated with respect to the mounting 40.

The support ends 61c, 62c of the outer periphery of the disk rotor on both pads 61, 62 are shown in FIG.
Are connected to each other by a tension spring S1 and are urged toward the disk rotor 50 with a very small load. On the other hand, both the pads 61 and 62 have the rotor entrance side support end portions 61a and 62a on the outer periphery of the disk rotor.
Are connected to each other by a compression spring S2 and are urged with a small load in a direction away from the disk rotor 50.

In addition, the both ends 61a, 62 of the disk rotor outer rotor side support end portions 61a, 62a on the outer periphery.
As shown in FIG. 8, the portion supported by the mounting 40 has a circular shape centered on the rotation axis of the pads 61 and 62, that is, the axis L.
On the other hand, the rotor outlet side support end 61 on the inner periphery of the disk rotor
b and 62b are such that the portion supported by the mounting 40 has a circular shape around the rotation axis of the pads 61, 62, that is, the axis L, as shown in FIG. I have. The rotor outlet side support ends 61c and 62c on the outer periphery of the disk rotor are formed in the same shape as the rotor inlet side support ends 61a and 62a on the outer periphery of the disk rotor, and the rotor inlet side support ends on the disk rotor inner circumference. The portions 61d and 62d are formed in the same shape as the rotor outlet side support end portions 61b and 62b on the inner circumference of the disk rotor.

In the embodiment constructed as described above, when braking is performed in a state where the disk rotor 50 is rotating in the direction of the arrow in FIGS. 3 and 4 (the forward running state of the vehicle),
The piston 15 moves the inner pad 62 to the disk rotor 50.
The reaction arm 13 of the caliper 10 presses the outer pad 61 toward the disk rotor 50 by the reaction force pressing toward the disk rotor 50, and the outer pad 61 and the inner pad 62 sandwich the disk rotor 50, so that the disk rotor 50 Be braked.

In the disk brake A of the present embodiment, both pads 61 and 62 are rotatable with respect to the mounting 40 about the axis L, and the rotor outlet side support end portions 61c and 62c on the outer periphery of the disk rotor are connected. They were connected to each other by a tension spring S1 and urged toward the disk rotor 50 with a slight load. For this reason, the rotor leading-out side support end portions 61c and 62c of the outer periphery of the disk rotor in both pads 61 and 62 can be constantly pressed against the disk rotor 50 by the slight load of the tension spring S1, and the rotor axial direction of the outer periphery of the disk rotor can be achieved. Can always be followed. 9 exaggerates the behavior of both pads 61 and 62 on the outer peripheral side of the disk rotor, and shows both pads 6 and 6 on the inner peripheral side of the disk rotor.
1, 62 are exaggeratedly shown.

Therefore, the minute wear (the amount of wear on the outer peripheral portion) of the outer periphery of the disk rotor due to the pads 61 and 62 obtained during the non-braking operation is exaggerated in FIG. The wear amount can be continuously increased or decreased over the entire circumference of the rotor in accordance with the runout amount. Correction can be performed without causing growth, and brake vibration during braking caused by a difference in wall thickness of the disk rotor 50 can be effectively suppressed.

FIG. 10 is an exaggerated view of the outer peripheral wear amount and the inner peripheral wear amount of the disk rotor 50 for comparison. FIG. Can be corrected without growing the thickness difference of the disk rotor 50, but wear occurs only at a portion where the amount of runout in the rotor axis direction is large on the inner circumference of the disk rotor, and the runout in the rotor axis direction is reduced. It can be seen that the thickness difference of the disk rotor 50 cannot be corrected without growing.

In the disk brake A of the present embodiment, the support ends 61a, 62a on both the pads 61, 62 on the outer periphery of the disk rotor are connected to each other by a compression spring S2 and separated from the disk rotor 50. , The rotor leading-out side support end portions 61c, 61c of the outer periphery of the disk rotor in both pads 61, 62.
It is possible to simply configure a configuration in which only the shaft 62c accurately follows the deflection of the outer periphery of the disk rotor in the rotor axis direction.

In the disc brake A of the present embodiment, the rotor 61 has a pad 61, 62 on the outer periphery of the disk rotor, and the rotor support side 61a, 62a on the inner periphery of the disk rotor. 62b,
Because of the shape having the circular shape portion about the axis L, both pads 61 and 62 can be smoothly rotated with respect to the mounting 40 about the axis L.

[Brief description of the drawings]

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

FIG. 2 is a central longitudinal sectional view of FIG.

FIG. 3 is a side view showing a relationship between both pads, a mounting, and a disk rotor shown in FIG. 2;

FIG. 4 is a plan view showing a relationship between both pads and a disk rotor shown in FIG. 3 and both springs omitted in FIG. 3;

FIG. 5 is a front view of both pads alone.

FIG. 6 is a plan view of both pads alone.

FIG. 7 is a left side view of both pads alone.

FIG. 8 is a right side view of both pads alone.

FIG. 9 is a diagram exaggeratingly showing the behavior of both pads on the outer peripheral side of the disk rotor and exaggerating the behavior of both pads on the inner peripheral side of the disk rotor.

FIG. 10 is an exaggerated view of an outer peripheral wear amount and an inner peripheral wear amount of the disk rotor for comparison;

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... caliper, 11, 12 ... arm part, 13 ... reaction force arm part, 14 ... cylinder part, 15 ... piston, 16 ... seal ring, 20, 30 ... pin sliding means, 40 ... mounting, 41, 42 ... support part , 50 ... Disc rotor, 61 ... Outer pad, 62 ... Inner pad, 61
a, 62a: rotor inflow-side support end on the outer periphery of the disk rotor; 61b, 62b: rotor outflow-side support end on the disk rotor inner circumference; 61c, 62c: rotor outflow-side support end on the outer circumference of the disk rotor; 61d , 62d: support end of the inner side of the disk rotor on the side of the rotor entrance, L: axis (rotary axis), S
1, S2 ... spring.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Ryoichi Kurasako 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Corporation F-term (reference) 3J058 AA43 AA48 AA53 AA63 AA73 AA77 AA83 AA87 BA23 CA58 CA65 CC25 FA01 GA92

Claims (3)

[Claims] 1. A disk brake in which an inner pad and an outer pad are supported by a mounting so as to be movable in an axial direction of a rotor. With the line connecting the outgoing side support as the rotation axis,
The two pads are rotatable with respect to the mounting, and the rotor outlet side ends of the outer periphery of the disk rotor in both the pads are connected to each other by a spring and biased with a small load toward the disk rotor. Disc brake to do. 2. The disk brake according to claim 1, wherein the rotor reciprocating side ends of the outer periphery of the disk rotor of the two pads are connected to each other by a spring and urged in a direction away from the disk rotor. Disc brake to do. 3. The disk brake according to claim 1, wherein the rotor pad on the outer periphery of the disk rotor and the rotor outlet side support on the inner periphery of the disk rotor of the two pads are centered on the rotation shaft. A disc brake having a shape having a circular portion.