JPH1163044A - Disc rotor for brake - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a brake squeal by forming some of cooling fins arranged in the circumferential direction to be thick, without marring the cooling capability due to the thick shape of the fins. SOLUTION: This disc rotor has a pair of annular sliding plates 11a, 11b held and pressed by right and left opposed brake pads and a number of cooling fins 12 (12a, 12b, 12c) radially extended inside the annular sliding plates 11a, 11b and arranged along the circumferential direction. Some of the cooling fins 12 are formed to be thicker than the others. The thicker cooling fins 12b have thick portions 17 on the rear face side in the rotating direction A during the positive rotation of the disc rotor 10, the face of the thick portions 17 being parallel to the front face in the rotating direction of the cooling fins 12c adjacent therebehind at least on the outer peripheral side of the cooling fins 12b, 12c.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pair of annular sliding plates sandwiched between left and right brake pads facing each other, and radially extending inside the annular sliding plates and disposed along the circumferential direction. And a plurality of cooling fins, wherein the thickness of some of the cooling fins is greater than the thickness of the other cooling fins.

[0002]

2. Description of the Related Art Conventionally, as this kind of brake disk rotor, for example, Japanese Patent Application Laid-Open No. 58-221026 is known. This is, as shown in FIG. 9, an annular sliding plate 1a, which is pressed by a pair of brake pads (not shown).
1b on the outer peripheral portion, and the annular sliding plates 1a, 1b
A ventilated disk rotor in which a number of radially extending cooling fins 2 are arranged in a circumferential direction inside the fan, and the diameter and diameter of one diameter are reduced so that the mass and rigidity distribution are not uniform in the circumferential direction. A pair of cooling fins 2 located on a line
The thickness of each of the cooling fins a and 2b is formed to be larger than the thickness of the other cooling fins 2, thereby reducing brake noise.

[0003]

However, in the above-mentioned conventional brake disk rotor, the shape of the cooling fins 2a and 2b is not particularly limited, and the space between the adjacent left and right fins is filled. Since the thickness is increased, the surface area of the entire cooling fin is reduced, and there is a possibility that the cooling performance, which is the original purpose of the cooling fin, is impaired.

Accordingly, the present invention reduces brake squeal by forming a part of the cooling fins arranged in the circumferential direction to be thicker, and impairs the cooling performance due to the thicker shape of the fins. The purpose is not to be.

[0005]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a pair of annular sliding plates sandwiched between left and right brake pads facing each other, and radially inside the annular sliding plates. A plurality of cooling fins extending along the circumferential direction, wherein a part of the cooling fins is formed to be thicker than other cooling fins. In the above, the thick cooling fin has a thick portion on the rear surface side in the rotation direction when the disk rotor is normally rotated, and the rotation direction of another cooling fin adjacent to the rear of the surface of the thick portion. Are parallel to each other at least on the outer peripheral side of the cooling fins.

[0006]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a brake disk rotor according to the present invention. 1 and 2 show the structure of a ventilated type brake disk rotor 10, in which a pair of annular sliding plates 11a and 11b are arranged in parallel, and a pair of annular sliding plates 11a and 11b extend radially between the sliding plates. A plurality of cooling fins 12 are provided along the direction, and an inner peripheral portion is provided with a mounting hole 13 for mounting the disk rotor 10 to a wheel hub (not shown).

FIG. 3 schematically shows the cooling air 15 flowing near the cooling fins 12. During traveling, the cooling air 15 flowing through the flow path 14 between the cooling fins 12 flows from the inner peripheral portion of the disk rotor 10 to the outer peripheral portion.
Generally, a separation region 16 having a very low flow velocity or no flow velocity is formed on the rear surface side of each cooling fin 12 with respect to the rotation direction A of the disk rotor 10, and the cooling air 15 flows avoiding the separation region 16. .

FIG. 4 shows a first embodiment of the disk rotor according to the present invention. The disk rotor 1 is arranged so that the mass and rigidity distribution are not uniform in the circumferential direction.
A thick portion 17 is provided on the rear side of some of the cooling fins 12b in the rotation direction A of 0, so that the thickness is larger than that of the other cooling fins 12a and 12c adjacent before and after the cooling fin 12b. The thick portion 17 is provided substantially corresponding to the above-described peeling region 16 formed on the rear surface side of the cooling fin, and has a thickness substantially parallel to the front surface of the adjacent rear cooling fin 12c. It is served. The thick portion 17 is provided for several of the cooling fins 12b.

In the disk rotor configured as described above, the thick portion 17 is set in the separation area 16 of the cooling fin 12b, and the space between the thick portion 17 and the front surface of the adjacent rear cooling fin 12c is set in parallel. The flow of the cooling air 15 is not obstructed in the middle of the flow path 14 so that the flow of the cooling air 15 is not obstructed and the flow velocity of the cooling air 15 flowing through the flow path 14 does not decrease.

Usually, when the purpose is to reduce brake squeal, in order to control the rotor eigenvalue, for example, for a mode having a 6-node diameter of the rotor, thick fins are arranged at six locations on the circumference of the rotor. It is desirable. In this embodiment, since the surface of the thick portion 17 and the front surface of the cooling fin 12c adjacent to the rear side thereof are set substantially parallel, the fin mass for controlling the eigenvalue is distributed closer to the outer periphery. The effect is effective (the increase in the mass toward the inner circumference is not effective because the variation of the eigenvalue is small with respect to the increase in the rotor weight), and the result is that both the brake squeal and the cooling performance are satisfied.

FIG. 5 shows a second embodiment of the present invention, in which a thick portion 17 is provided on the rear surface side of some of the cooling fins 12b as in the previous embodiment, and is adjacent to the cooling fin 12b. The space between the rear cooling fin 12c and the cooling fin 12c is formed substantially in parallel.
Particularly, in this embodiment, a bending point 18 is set in the thick portion 17 at a position near the inner peripheral side of the annular sliding plates 11a and 11b, and the thick portion 17 is enlarged so that the inlet side 14a of the flow path 14 is enlarged. Are inclined to set a wide gap between the adjacent rear cooling fins 12c.

Therefore, also in this embodiment, similarly to the above, the thick portion 1 in the rotation direction A of the disk rotor 10 is provided.
7 is set in the separation area 16 of the cooling fin 12b,
Further, since the space between the adjacent cooling fins 12c is kept parallel, the flow velocity of the cooling air 15 flowing through the flow path 14 does not decrease. In this embodiment, since the bending point 18 of the thick portion 17 is provided near the inner periphery of the disk rotor 10, the fin mass for controlling the eigenvalue is more concentratedly distributed on the outer periphery than in the first embodiment. Accordingly, the increased mass more effectively acts on the eigenvalue control amount, and the opening area of the inlet side 14a of the flow path 14 for introducing the cooling air 15 can be set large, so that the cooling performance is improved.

FIG. 6 shows a third embodiment of the present invention. In this embodiment, thick portions 17a and 17b are provided on two adjacent cooling fins 12b and 12c, respectively, and the cooling fins 12 on the rear side adjacent to each other are provided.
c, 12d are kept parallel to the front surface. In this embodiment, when the control of the eigenvalue is insufficient in the thick portion 17 formed on one cooling fin 12b, it is possible to cope with the increase in mass and rigidity. In addition,
In this embodiment, two adjacent cooling fins 12b and 12
Although the case where thick portions 17a and 17b are provided in c has been described, thick portions may be provided on three or more continuous cooling fins as necessary.

FIG. 7 shows a fourth embodiment of the present invention. In this embodiment, when the lengths of the cooling fins arranged on the circumference are alternately different, the thick portion 17 is formed on the rear surface side of the shorter cooling fin 12b, and the adjacent rear side is formed. The cooling fins 12c are set in parallel. By forming the thick portion 17 on the shorter cooling fin 12b in this way, the fin mass for controlling the eigenvalue can be concentrated and distributed on the outer peripheral portion, and the inlet of the flow path 14 for guiding the cooling air 15 can be formed. Side 14
Because the opening area of a can be large, the cooling efficiency is improved,
The cooling performance distribution of the entire flow path 14, that is, the temperature distribution generated in the rotation direction can be made uniform, and in addition to the above-described embodiment, the occurrence of cracks due to the non-uniform temperature distribution can be suppressed. Becomes

FIG. 8 shows a fifth embodiment of the present invention. In this embodiment, thick portions 17a and 17b are provided on both sides of the cooling fin 12b, and the space between the adjacent cooling fins 12a and 12c is kept parallel. In this embodiment, the flow passage areas B1, B2, B3, and B4 between all the cooling fins are set to be equal (B1
= B2 = B3 = B4).

Therefore, in this embodiment, the thick portion 17a (or 17b (depending on the direction of rotation)) of the cooling fin 12b is set in addition to the above-described peeling region.
By setting 1, B2, B3, and B4 equal, the same effects as in the above-described fourth embodiment can be obtained, and a common disk rotor 10 can be used for the left and right wheels of the vehicle, which reduces manufacturing costs. Reduction is achieved.

[0017]

As described above, according to the brake disk rotor of the present invention, the area where the cooling air generated on the rear surface side of the cooling fin is separated in the rotation direction is padded and the thickness is increased. Since the meat portion and the cooling fin on the rear surface side adjacent to the meat portion are set to be parallel to each other, the flow velocity of the cooling air flowing through the flow path between the cooling fins does not significantly decrease. Therefore, it is possible to effectively control the mass in the circumferential direction without impairing the original cooling performance of the disk rotor, and to reduce brake squeal.

[Brief description of the drawings]

FIG. 1 is an external view of a ventilated disk rotor.

FIG. 2 is a partial sectional view of FIG. 1 showing a cooling fin of a disk rotor.

FIG. 3 is a schematic diagram of cooling air flowing between cooling fins.

FIG. 4 is a conceptual diagram showing a first embodiment of the present invention.

FIG. 5 is a conceptual diagram showing a second embodiment of the present invention.

FIG. 6 is a conceptual diagram showing a third embodiment of the present invention.

FIG. 7 is a conceptual diagram showing a fourth embodiment of the present invention.

FIG. 8 is a conceptual diagram showing a fifth embodiment of the present invention.

FIG. 9 is a front view showing the structure of a conventional disk roller.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Disk rotor 11a, 11b Annular sliding plate 12, 12a, 12b, 12c Cooling fin 17 Thick part A Rotation direction of disk rotor

 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Hiromichi Matsui, Nissan Motor Co., Ltd., 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa Prefecture (72) Inventor Shuichi Nakagawa 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa, Nissan Motor Co., Ltd.

Claims (1)

[Claims] 1. A pair of annular sliding plates sandwiched between left and right brake pads facing each other, and a plurality of cooling fins extending radially inside the annular sliding plate and arranged along the circumferential direction. Wherein the thickness of a part of the cooling fins is greater than the thickness of the other cooling fins. Sometimes, a thick portion is provided on the rear surface side in the rotational direction, and the surface of the thick portion and the front surface in the rotational direction of the cooling fin adjacent to the rear are parallel to each other at least on the outer peripheral side of the cooling fin. Brake disk rotor.