JPH0356660Y2

JPH0356660Y2 -

Info

Publication number: JPH0356660Y2
Application number: JP18172987U
Authority: JP
Priority date: 1987-11-27
Filing date: 1987-11-27
Publication date: 1991-12-20
Also published as: JPH0185540U

Description

【考案の詳細な説明】（産業上の利用分野）本考案は車両用ブレーキ装置のデイスクロータ
に関するものであり、自動車、産業用車両等に利
用される。[Detailed Description of the Invention] (Field of Industrial Application) The present invention relates to a disc rotor for a vehicle brake device, and is used in automobiles, industrial vehicles, etc.

（従来の技術）従来、デイスクロータの一側摺動面および他側
摺動面（以下、両摺動面という）には、施削によ
つてロータの軸心回りに平均粗さが２ミクロンな
いし10ミクロンであるスパイラル状の切削目が付
けられている（例えば、特開昭54−5173号公報）。(Prior art) Conventionally, one side sliding surface and the other side sliding surface (hereinafter referred to as both sliding surfaces) of a disc rotor have an average roughness of 2 microns around the axis of the rotor by machining. A spiral cutting pattern having a diameter of 1 to 10 microns is provided (for example, Japanese Patent Application Laid-Open No. 54-5173).

（考案が解決しようとする問題点）両摺動面に付けられたスパイラル状の切削目は
ロータの軸心回りに同方向であるため、両摺動面
に発生する摩擦係合力は相等しいが、ロータを前
記回転方向と逆方向に回転させた場合、前記と同
程度の摩擦係合力が発生しにくいという問題点が
ある。そこで、本考案はかかる問題点を解消する
ためになされたもので、ロータの回転方向に拘ら
ず、所定の摩擦係合力を発生し得るロータを提供
するものである。(Problem to be solved by the invention) Since the spiral cutting marks made on both sliding surfaces are in the same direction around the axis of the rotor, the frictional engagement forces generated on both sliding surfaces are equal. However, there is a problem in that when the rotor is rotated in a direction opposite to the rotational direction, it is difficult to generate the same frictional engagement force as described above. Therefore, the present invention was devised to solve this problem, and provides a rotor that can generate a predetermined frictional engagement force regardless of the rotational direction of the rotor.

（問題点を解決するための手段）本考案は内周側スパイラル溝の円弧状の回転方
向が外周側スパイラル溝の円弧状の回転方向と互
いに逆方向であり、該両スパイラル溝のピツチが
0.01〜0.1mm／回転、該両摺動面の面粗度が2.0〜
10μRZのデイスクロータである。(Means for Solving the Problems) In the present invention, the direction of rotation of the circular arc of the inner spiral groove is opposite to the direction of rotation of the circular arc of the outer spiral groove, and the pitch of both spiral grooves is
0.01~0.1mm/rotation, surface roughness of both sliding surfaces is 2.0~
It is a 10μRZ disc rotor.

（作用）本考案は上述のような構成であるので、ロータ
の回転方向によつて内周側摺動面と外周側摺動面
とに発生する摩擦係合力が多少異なるが、全体的
にはデイスクロータの回転方向に拘らず、所定の
摩擦係合力が発生する。(Function) Since the present invention has the above-described configuration, the frictional engagement force generated between the inner circumferential sliding surface and the outer circumferential sliding surface varies somewhat depending on the rotating direction of the rotor, but overall A predetermined frictional engagement force is generated regardless of the rotational direction of the disc rotor.

（実施例）第１図および第２図は本考案に係るデイスクロ
ータの一実施例であり、デイスクロータの側面に
形成された一側摺動面１ａおよび他側摺動面１ｂ
に軸心回りの内周側スパイラル溝２ａ，３ａのお
よび外周側スパイラル溝２ｂ，３ｂがそれぞれ設
けられ、一対の内周側スパイラル溝２ａ，３ａの
円弧状の回転方向は軸心回りにそれぞれ同方向で
あり、さらに一対の外周側スパイラル溝２ｂ，３
ｂの円弧状の回転方向も軸心回りにそれぞれ同方
向であるが、内周側スパイラル溝２ａ，３ａの円
弧状の回転方向と外周側スパイラル溝２ｂ，３ｂ
の円弧状の回転方向とが互いに逆方向になる様に
形成されている。該両スパイラル溝２ａ，３ａ，
２ｂ，３ｂのピツチが0.01〜0.1mm／回転、該両
摺動面の面粗度が2.0〜10μRZとなる様に形成さ
れ、このような凹凸状を設けることにより、ブレ
ーキ制動時に前記両摺動面１ａ，１ｂとパツド面
（図示せず）とを互いに係合させ、デイスクロー
タの回転、とりわけデイスクロータの高速回転を
制御するものである。(Embodiment) FIGS. 1 and 2 show an embodiment of a disc rotor according to the present invention, in which one sliding surface 1a and the other sliding surface 1b are formed on the side surface of the disc rotor.
Inner circumferential spiral grooves 2a, 3a and outer circumferential spiral grooves 2b, 3b are provided around the axis, respectively, and the arcuate rotation directions of the pair of inner circumferential spiral grooves 2a, 3a are the same around the axis. direction, and a pair of outer circumferential spiral grooves 2b, 3
The circular arc-shaped rotation direction of b is also the same direction around the axis, but the circular arc-shaped rotation direction of the inner circumferential spiral grooves 2a, 3a and the outer circumferential spiral grooves 2b, 3b are the same.
The rotating directions of the circular arcs are opposite to each other. Both spiral grooves 2a, 3a,
The pitch of 2b and 3b is 0.01 to 0.1 mm/rotation, and the surface roughness of both sliding surfaces is 2.0 to 10 μRZ. The surfaces 1a, 1b and a pad surface (not shown) are engaged with each other to control the rotation of the disk rotor, particularly the high speed rotation of the disk rotor.

ブレーキ制動時にパツド（図示せず）がデイス
クロータの摺動面１ａ，１ｂに押圧されると、摺
動面１ａ，１ｂとパツド面（図示せず）とが摩擦
係合する。ロータの回転方向によつて内周側摺動
面１２ａ，１３ａと外周側摺動面１２ｂ，１３ｂ
とに発生する摩擦係合力が多少異なり、相等しく
はないが、全体的にはデイスクロータの回転方向
に拘らず、所定の摩擦係合力が発生する。 When the pads (not shown) are pressed against the sliding surfaces 1a, 1b of the disc rotor during braking, the sliding surfaces 1a, 1b and the pad surfaces (not shown) frictionally engage with each other. Depending on the rotational direction of the rotor, inner circumferential sliding surfaces 12a, 13a and outer circumferential sliding surfaces 12b, 13b
Although the frictional engagement force generated is somewhat different and not equal, overall a predetermined frictional engagement force is generated regardless of the rotational direction of the disc rotor.

（考案の効果）本考案によれば、内周側スパイラル溝の円弧状
の回転方向が外周側スパイラル溝の円弧状の回転
方向と互いに逆方向であり、該両スパイラル溝の
ピツチが0.01〜0.1mm／回転、該両摺動面の面粗
度が2.0〜10μRZであるので、摩擦係合力が低下
せず、常時良好なブレーキ制動力が得られると共
に、ブレーキ効率を高く維持できる。(Effect of the invention) According to the invention, the direction of rotation of the circular arc of the inner spiral groove is opposite to the direction of rotation of the circular arc of the outer spiral groove, and the pitch of both spiral grooves is 0.01 to 0.1. mm/rotation, and the surface roughness of both sliding surfaces is 2.0 to 10 μRZ, so the frictional engagement force does not decrease, good braking force can be obtained at all times, and braking efficiency can be maintained at a high level.

[Brief explanation of drawings]

第１図は本考案に係るデイスクロータの縦断面
図、第２図は第１図の正面図である。２ａ，３ａ……内周側スパイラル溝、２ｂ，３
ｂ……外周側スパイラル溝。 FIG. 1 is a longitudinal sectional view of a disc rotor according to the present invention, and FIG. 2 is a front view of FIG. 1. 2a, 3a...inner circumferential spiral groove, 2b, 3
b...Spiral groove on the outer circumferential side.

Claims

[Scope of utility model registration request]

In a disc rotor in which a spiral groove around the axis is formed on one sliding surface and the other sliding surface,
The circular direction of rotation of the inner spiral groove is opposite to the circular direction of rotation of the outer spiral groove, and the pitch of both spiral grooves is 0.01 to 0.1.
mm/rotation, and the surface roughness of both sliding surfaces is 2.0 to 10 μRZ.