JPH08254231A - Disc brake - Google Patents

Disc brake

Info

Publication number
JPH08254231A
JPH08254231A JP8474395A JP8474395A JPH08254231A JP H08254231 A JPH08254231 A JP H08254231A JP 8474395 A JP8474395 A JP 8474395A JP 8474395 A JP8474395 A JP 8474395A JP H08254231 A JPH08254231 A JP H08254231A
Authority
JP
Japan
Prior art keywords
rotor
piston
caliper
friction
friction member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP8474395A
Other languages
Japanese (ja)
Inventor
Yutaka Nishikawa
裕 西川
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Akebono Brake Industry Co Ltd
Original Assignee
Akebono Brake Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Akebono Brake Industry Co Ltd filed Critical Akebono Brake Industry Co Ltd
Priority to JP8474395A priority Critical patent/JPH08254231A/en
Priority to DE1996110276 priority patent/DE19610276A1/en
Publication of JPH08254231A publication Critical patent/JPH08254231A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/0006—Noise or vibration control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/06—Pistons

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

PURPOSE: To provide a disc brake which can stabilize braking action and also can reduce occurrence of a noise during braking time. CONSTITUTION: Width L in a rotor circumferential direction passed through the piston center of inner and outer frictional pads 16 is set to be 1.0-1.8 times of the diameter D of a piston, and distance in the rotor circumferential direction in a position passed through the piston center of a caliper claw by which the outer frictional pad 16 is brought in pressure contact with a rotor, is set to be 0.8-1.5 times of the diameter D of the piston.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は、ディスクブレーキの摩
擦パッドの改良に係り、特にロータの両側に配置した摩
擦パッドの一方をピストンによって、他方をキャリパ爪
によってロータに圧接するフィストタイプのディスクブ
レーキに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improved friction pad for a disc brake, and more particularly to a fist type disc brake in which one of the friction pads arranged on both sides of the rotor is pressed against the rotor by a piston and the other by a caliper pawl. Regarding

【０００２】[0002]

【従来の技術】フィストタイプのディスクブレーキは、
車体に固定したサポートがロータの外周縁部に配置して
あり、このサポートにガイドピンを含む支持装置を介し
てキャリパをロータの軸方向に移動可能に組み付けてい
る。また、サポートは、ロータの両側に配置した摩擦パ
ッドを支持し、ロータの軸方向に摺動案内するようにな
っている。一方、キャリパは、ロータのインナ側に、イ
ンナ摩擦パッドをロータに圧接する液圧装置のピストン
を有し、アウタ側のキャリパボディにアウタ摩擦パッド
をロータに圧接するキャリパ爪が設けてある。そして、
制動作用は、液圧装置に液圧を導入してインナ摩擦パッ
ドをピストンによってロータに圧接し、その反力によっ
てキャリパがガイドピンに沿ってロータの軸方向に移動
し、アウタ側のキャリパ爪がアウタ摩擦パッドをロータ
に圧接することにより行われる。2. Description of the Related Art Fist type disc brakes are
A support fixed to the vehicle body is arranged on the outer peripheral edge of the rotor, and a caliper is movably attached to the support via a support device including guide pins in the axial direction of the rotor. Further, the support supports friction pads arranged on both sides of the rotor and slides and guides in the axial direction of the rotor. On the other hand, the caliper has a piston of a hydraulic device that presses the inner friction pad against the rotor on the inner side of the rotor, and a caliper claw that presses the outer friction pad against the rotor is provided on the outer caliper body. And
The braking action is to introduce hydraulic pressure into the hydraulic device to press the inner friction pad against the rotor by the piston, and the reaction force causes the caliper to move along the guide pin in the axial direction of the rotor, causing the outer caliper claw to move. This is done by pressing the outer friction pad against the rotor.

【０００３】[0003]

【発明が解決しようとする課題】従来、アウタ摩擦パッ
ドは、摩擦部材（パッド）の形状に合わせてキャリパ爪
の形状を設定することができるため、パッドをロータに
圧接したときのパッドの面圧を比較的均一にすることが
可能である。しかし、インナ摩擦パッドは、円筒状のピ
ストンによって摩擦部材をロータに圧接するようになっ
ているため、均一に圧接することが困難であって、パッ
ドの中央部の面圧が大きく、端部の面圧が小さくなる。
このため、摩擦パッドが振動してノイズが発生するなど
の問題を生ずる。従って、パッドの面圧をできるだけ均
一にできるようなパッドの形状が望まれる。Conventionally, in the outer friction pad, since the shape of the caliper claw can be set according to the shape of the friction member (pad), the surface pressure of the pad when the pad is pressed against the rotor. Can be made relatively uniform. However, in the inner friction pad, since the friction member is pressed against the rotor by the cylindrical piston, it is difficult to press the friction member uniformly, and the surface pressure at the center of the pad is large, and The surface pressure decreases.
As a result, the friction pad vibrates and noise occurs. Therefore, the shape of the pad is desired so that the surface pressure of the pad can be made as uniform as possible.

【０００４】本発明は、前記従来技術の欠点を解消する
ためになされてもので、制動作用の安定化が図れ、制動
時におけるノイズの発生を低減できるようにすることを
目的としている。The present invention has been made to solve the above-mentioned drawbacks of the prior art. Therefore, it is an object of the present invention to stabilize the braking action and reduce the generation of noise during braking.

【０００５】[0005]

【課題を解決するための手段】発明者等は、適正なブレ
ーキ力が得られ、摩擦パッドの面圧をできるだけ均一に
するために種々検討し、実験を行った結果、ピストンに
よってロータに圧接するインナ摩擦パッドの摩擦部材の
ロータ周方向におけるピストン中心を通る幅（ロータ周
方向幅）は、ピストン直径の１．０〜１．８倍程度にす
るとよいこと、またキャリパ爪によってロータに圧接す
るアウタ摩擦パッドの摩擦部材のロータ周方向幅は、キ
ャリパ爪の外側端間の距離の１．０〜１．２倍程度にす
るとよいことを見出した。Means for Solving the Problems The inventors of the present invention conducted various studies and experiments to obtain a proper braking force and make the surface pressure of the friction pad as uniform as possible. As a result, the piston was pressed against the rotor. The width of the friction member of the inner friction pad passing through the piston center in the rotor circumferential direction (rotor circumferential width) should be about 1.0 to 1.8 times the piston diameter, and the outer diameter of the outer member pressed against the rotor by the caliper pawls. It has been found that the rotor circumferential width of the friction member of the friction pad should be about 1.0 to 1.2 times the distance between the outer ends of the caliper claws.

【０００６】本発明は、上記の知見に基づいてなされた
もので、本発明に係るディスクブレーキは、インナ摩擦
パッドをキャリパに設けたピストンによってロータに圧
接し、アウタ摩擦パッドをキャリパ爪によって前記ロー
タに圧接するディスクブレーキにおいて、前記ピストン
の先端部における直径をＤ、前記インナおよびアウタ摩
擦パッドの摩擦部材のピストン中心を通るロータ周方向
幅をＬ、前記キャリパ爪の、前記ピストン中心を通る位
置におけるロータ周方向の距離をＴとしたときに、The present invention has been made on the basis of the above findings. In the disc brake according to the present invention, the inner friction pad is pressed against the rotor by the piston provided on the caliper, and the outer friction pad is pressed by the caliper claw. In the disc brake that presses against, the diameter at the tip of the piston is D, the rotor circumferential width of the friction member of the inner and outer friction pads passing through the piston center is L, and the caliper pawl at the position passing through the piston center. When the distance in the rotor circumferential direction is T,

【数３】Ｌ／Ｄ＝１．０〜１．８ かつ、## EQU3 ## L / D = 1.0 to 1.8, and

【数４】Ｔ／Ｄ＝０．８〜１．５ である構成となっている。[Formula 4] T / D = 0.8 to 1.5.

【０００７】[0007]

【作用】発明者等の研究によると、ピストンの先端開口
部における直径（以下、端にピストン直径という）をＤ
とし、インナ摩擦パッドの摩擦部材のロータ周方向にお
けるピストンの中心を通る幅（以下、単にロータ周方向
幅という）をＬとすると、Ｌ／Ｄ＝１．０において摩擦
部材に作用する面圧が最も一様となる。しかし、Ｌ／Ｄ
＜０．１の場合、摩擦部材に作用する面圧が局部的に大
きくなり、特にロータ周方向の端部付近において高くな
る。これは、ピストンが摩擦パッドのモールドから外れ
た部分を押すことによる。従って、摩擦部材は、Ｌ／Ｄ
≧１．０とすることが望ましい。また、摩擦部材のＬ／
Ｄ＞１．８の部分は、ブレーキ作用に寄与しないことを
見出した。このため、摩擦部材は、Ｌ／Ｄ≦１．８とす
るとよい。すなわち、インナ摩擦パッドの摩擦部材のロ
ータ周方向幅Ｌとピストン直径Ｄとの関係は、According to the research conducted by the inventors, the diameter at the tip opening of the piston (hereinafter referred to as the piston diameter at the end) is D
And L is the width of the friction member of the inner friction pad passing through the center of the piston in the rotor circumferential direction (hereinafter simply referred to as rotor circumferential width), the surface pressure acting on the friction member at L / D = 1.0 Most uniform. However, L / D
In the case of <0.1, the surface pressure acting on the friction member locally increases, and becomes high especially near the end portion in the rotor circumferential direction. This is because the piston pushes the unmolded portion of the friction pad. Therefore, the friction member is L / D
It is desirable that ≧ 1.0. Also, the friction member L /
It was found that the portion of D> 1.8 does not contribute to the braking action. Therefore, the friction member may have L / D ≦ 1.8. That is, the relationship between the rotor circumferential width L of the friction member of the inner friction pad and the piston diameter D is

【数５】１．０≦Ｌ／Ｄ≦１．８ とするのがよい。## EQU5 ## It is preferable that 1.0 ≦ L / D ≦ 1.8.

【０００８】一方、キャリパ爪によってロータに押圧さ
れるアウタ摩擦パッドの摩擦部材に作用する面圧は、摩
擦部材ドのロータ周方向幅Ｌ、キャリパ爪の両端外側端
間の、ピストンの中心を通る位置における距離（以下、
単にキャリパ爪幅という）をＴとしたとき、Ｌ／Ｔ＜
１．０の場合、摩擦部材に作用する面圧の最大値と最小
値との差が急激に大きいくなり、特にロータ周方向の端
部における面圧が非常に高くなる。このため、摩擦部材
は、Ｌ／Ｔ≧１．０とするとよい。また、Ｌ／Ｔ＞１．
２となると、摩擦部材に作用する面圧の最大値と最小値
との差が大きくなるとともに、ロータ周方向における摩
擦部材端部の面圧が急速に低下する。従って、キャリパ
爪によってロータに押圧される摩擦パッドの摩擦部材
は、Ｌ／Ｔ≦１．２とするのがよい。すなわち、アウタ
側摩擦部材のロータ周方向幅Ｌとキャリパ爪幅Ｔとの関
係は、On the other hand, the surface pressure acting on the friction member of the outer friction pad pressed against the rotor by the caliper claw passes through the rotor circumferential width L of the friction member and the center of the piston between both outer ends of the caliper claw. Distance at position (hereinafter,
When the caliper claw width is simply T), L / T <
In the case of 1.0, the difference between the maximum value and the minimum value of the surface pressure acting on the friction member suddenly becomes large, and particularly the surface pressure at the end portion in the rotor circumferential direction becomes extremely high. Therefore, the friction member may have L / T ≧ 1.0. Also, L / T> 1.
When it becomes 2, the difference between the maximum value and the minimum value of the surface pressure acting on the friction member becomes large, and the surface pressure at the end portion of the friction member in the rotor circumferential direction rapidly decreases. Therefore, the friction member of the friction pad that is pressed against the rotor by the caliper pawl is preferably L / T ≦ 1.2. That is, the relationship between the rotor circumferential width L of the outer side friction member and the caliper claw width T is

【数６】１．０≦Ｌ／Ｔ≦１．２ とするのがよい。## EQU6 ## It is preferable that 1.0 ≦ L / T ≦ 1.2.

【０００９】上記の〔数７〕と〔数８〕とから、キャリ
パ爪幅Ｔとピストン直径Ｄとの関係を求めると、From the above [Equation 7] and [Equation 8], the relationship between the caliper claw width T and the piston diameter D is obtained.

【数７】０．８≦Ｔ／Ｄ≦１．５ となる。## EQU7 ## 0.8 ≦ T / D ≦ 1.5.

【００１０】これにより、発生させる制動力になんら影
響がないばかりでなく、摩擦パッド（摩擦部材）に作用
する面圧を比較的均一にすることができ、ブレーキの効
きが安定するなど、制動作用の安定化が図れるととも
に、制動時における摩擦パッドの振動を少なくしてノイ
ズを低減することができる。As a result, the generated braking force is not affected at all, and the surface pressure acting on the friction pad (friction member) can be made relatively uniform, so that the braking effectiveness is stabilized. It is possible to reduce the noise by reducing the vibration of the friction pad during braking.

【００１１】[0011]

【実施例】本発明に係るディスクブレーキの好ましい実
施例を、添付図面に従って詳細に説明する。図３は、本
発明の実施例に係るフィストタイプのディスクブレーキ
をアウタ側から見た図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A preferred embodiment of the disc brake according to the present invention will be described in detail with reference to the accompanying drawings. FIG. 3 is a view of the fist type disc brake according to the embodiment of the present invention as viewed from the outer side.

【００１２】図３において、ディスクブレーキ１０は、
図示しない車体に固定したサポート１２がロータ（図示
せず）の外周縁部に配置してある。このサポート１２
は、ロータを跨ぐように断面Ｕ字状に形成してあるとと
もに、ロータのインナ側とアウタ側とのロータ周方向中
央部に、インナ摩擦パッド１６とアウタ摩擦パッド１８
とを配置するための開口部２０が設けてあって、凹状を
成している。In FIG. 3, the disc brake 10 is
A support 12 fixed to a vehicle body (not shown) is arranged on the outer peripheral edge of a rotor (not shown). This support 12
Is formed in a U-shaped cross-section so as to straddle the rotor, and the inner friction pad 16 and the outer friction pad 18 are provided at the rotor circumferential center portions of the inner side and the outer side of the rotor.
An opening 20 for arranging and is provided, and has a concave shape.

【００１３】インナ摩擦パッド１６とアウタ摩擦パッド
１８とは、左右対称に形成されており、裏金２２と摩擦
部材２４とから構成してあって、摩擦部材２４がロータ
に対面した裏金２２の前面に固定してある。また、各摩
擦パッド１６、１８は、ロータの周方向両側部に突起２
６、２８が張り出して設けてあり、これらの突起２６、
２８を介してサポート１２に支持されている。The inner friction pad 16 and the outer friction pad 18 are formed symmetrically and are composed of a back metal 22 and a friction member 24. The friction member 24 is provided on the front surface of the back metal 22 facing the rotor. It is fixed. Further, the friction pads 16 and 18 are provided with protrusions 2 on both sides in the circumferential direction of the rotor.
6, 28 are provided so as to project, and these protrusions 26,
It is supported by the support 12 via 28.

【００１４】すなわち、サポート１２は、ロータ周方向
の両側部に、ロータの外周部を跨いで形成したアーム部
３０、３２を有し、これらのアーム部３０、３２の対向
面側に設けたガイド溝３１、３３に突起２６、２８の先
端部が挿入してあって、突起２６、２８を介して摩擦パ
ッド１６、１８を支持してロータの軸方向に摺動案内す
るようになっている。また、突起２６、２８とガイド溝
３１、３３との間には、パッドクリップ３４、３６が配
置してあって、インナ摩擦パッド１６とアウタ摩擦パッ
ド１８とのロータ軸方向の移動を円滑に行えるようにし
てあるとともに、突起２６、２８およびガイド溝３１、
３３の摩耗の低減を図っている。That is, the support 12 has arm portions 30 and 32 formed on both sides in the circumferential direction of the rotor so as to straddle the outer peripheral portion of the rotor, and guides provided on the facing surfaces of these arm portions 30 and 32. The tips of the protrusions 26 and 28 are inserted into the grooves 31 and 33, and the friction pads 16 and 18 are supported via the protrusions 26 and 28 to be slidably guided in the axial direction of the rotor. Further, pad clips 34 and 36 are arranged between the protrusions 26 and 28 and the guide grooves 31 and 33, so that the inner friction pad 16 and the outer friction pad 18 can be smoothly moved in the rotor axial direction. And the projections 26, 28 and the guide groove 31,
The wear of 33 is reduced.

【００１５】キャリパ４０は、ロータの外周部を跨いで
断面Ｕ字状に形成してある。このキャリパ４０は、サポ
ート１２のアーム部３０、３２に設けたガイドピン４
２、４４が挿入されるガイド孔を有していて、ガイドピ
ン４２、４４に案内されてロータの軸方向に移動できる
ようになっている。そして、キャリパ４０のインナ側に
は、液圧装置であるシリンダ部が設けてあって、このシ
リンダ部が形成するシリンダボアに、インナ摩擦パッド
１６の摩擦部材２４をロータに圧接するピストン４６が
軸方向移動自在に挿入してある。このピストン４６は、
インナ摩擦パッド１６に対面した先端側が開口した有底
円筒状となっていて、シリンダボアに液圧が導入される
ことにより、インナ摩擦パッド１６の背面を押し、摩擦
部材２４をロータに押しつける。The caliper 40 is formed in a U-shaped cross section straddling the outer peripheral portion of the rotor. The caliper 40 includes guide pins 4 provided on the arm portions 30 and 32 of the support 12.
It has guide holes into which 2 and 44 are inserted so that it can be moved in the axial direction of the rotor by being guided by the guide pins 42 and 44. A cylinder portion, which is a hydraulic device, is provided on the inner side of the caliper 40, and a piston 46 for pressing the friction member 24 of the inner friction pad 16 to the rotor is axially attached to a cylinder bore formed by the cylinder portion. It is inserted freely. This piston 46
It has a bottomed cylindrical shape with an open front end facing the inner friction pad 16, and when hydraulic pressure is introduced into the cylinder bore, the rear surface of the inner friction pad 16 is pressed and the friction member 24 is pressed against the rotor.

【００１６】一方、キャリパ４０のアウタ側には、ロー
タの周方向に一対のキャリパ爪４８、５０が設けてあ
る。これらのキャリパ爪４８、５０は、ピストン４６が
インナ摩擦パッド１６をロータに圧接したときの反力に
より、キャリパ４０がロータの軸方向に移動したときに
アウタ摩擦パッド１８の背面を押し、アウタ摩擦パッド
１８の摩擦部材２４をロータに押しつける。そして、各
摩擦パッド１６、１８の摩擦部材２４のロータ周方向に
おけるピストン４６の中心を通る幅（ロータ周方向幅）
Ｌは、キャリパ爪４８の外側端（図３の左側端）とキャ
リパ爪５０の外側端（図３の右側端）との間の、ピスト
ン４６の中心を通る位置における距離（キャリパ爪幅）
Ｔの１．０〜１．２倍にしてある。また、各摩擦部材２
４のロータ周方向幅Ｌは、ピストン４６の開口側端部直
径Ｄの１．０〜１．８倍となっている。そして、前記し
たキャリパ爪幅Ｔとピストン直径Ｄとの比（Ｔ ／Ｄ）
は、０．８〜１．５にしてある。On the other hand, on the outer side of the caliper 40, a pair of caliper claws 48, 50 are provided in the circumferential direction of the rotor. These caliper pawls 48, 50 push the back surface of the outer friction pad 18 when the caliper 40 moves in the axial direction of the rotor by the reaction force when the piston 46 press-contacts the inner friction pad 16 with the rotor, and thus the outer friction. The friction member 24 of the pad 18 is pressed against the rotor. The width of the friction member 24 of each friction pad 16 and 18 passing through the center of the piston 46 in the rotor circumferential direction (rotor circumferential direction width).
L is the distance between the outer end of the caliper pawl 48 (the left end in FIG. 3) and the outer end of the caliper pawl 50 (the right end in FIG. 3) at the position passing through the center of the piston 46 (the caliper pawl width).
It is set to 1.0 to 1.2 times T. Also, each friction member 2
The rotor circumferential width L of No. 4 is 1.0 to 1.8 times the opening side end diameter D of the piston 46. The ratio of the caliper claw width T and the piston diameter D (T / D)
Is 0.8 to 1.5.

【００１７】図１と図２とは、上記の摩擦部材２４のロ
ータ周方向幅Ｌとキャリパ爪４８、５０のキャリパ爪幅
Ｔとを定めるために求めた、摩擦部材２４に作用する面
圧の計算結果を示したものである。図１は、ピストン４
６によってロータに圧接させられるインナ摩擦パッド１
６の摩擦部材２４の面圧分布を示している。ただし、ピ
ストン４６の先端開口部における直径（外径）Ｄは５６
ｍｍ、ピストン４６に作用する液圧は３０ｋｇｆ／ｃｍ
2 であって、摩擦部材２４の幅Ｌは、ピストン４６の中
心を通るロータ周方向の値である（図３参照）。FIGS. 1 and 2 show the surface pressure acting on the friction member 24, which is obtained to determine the rotor circumferential width L of the friction member 24 and the caliper pawl width T of the caliper pawls 48, 50. The calculation results are shown. FIG. 1 shows the piston 4
Inner friction pad 1 pressed against rotor by 6
6 shows the surface pressure distribution of the friction member 24 of No. 6. However, the diameter (outer diameter) D at the tip opening of the piston 46 is 56
mm, hydraulic pressure acting on the piston 46 is 30 kgf / cm
2 , the width L of the friction member 24 is a value in the rotor circumferential direction passing through the center of the piston 46 (see FIG. 3).

【００１８】また、図２は、図１と同様の条件下におい
て、一対のキャリパ爪４８、５０によってロータに圧接
されるアウタ摩擦パッド１８の摩擦部材２４に作用する
面圧の分布を示したものである。ただし、図２におい
て、キャリパ爪４８の外側端（図３の左側端）とキャリ
パ爪５０の外側端（図３の右側端）との間の距離（キャ
リパ爪幅）Ｔは８０ｍｍであって、ピストン４６の中心
を通る位置における値であり、摩擦部材２４のロータ周
方向の幅Ｌは、ピストン４６の中心を通る位置における
値である。Further, FIG. 2 shows the distribution of the surface pressure acting on the friction member 24 of the outer friction pad 18 pressed against the rotor by the pair of caliper claws 48 and 50 under the same conditions as in FIG. Is. However, in FIG. 2, the distance (caliper claw width) T between the outer end of the caliper claw 48 (the left end in FIG. 3) and the outer end of the caliper claw 50 (the right end in FIG. 3) is 80 mm, It is a value at a position passing through the center of the piston 46, and the width L of the friction member 24 in the rotor circumferential direction is a value at a position passing through the center of the piston 46.

【００１９】図１から明らかなように、インナ摩擦パッ
ド１６の摩擦部材２４のロータ周方向幅Ｌとピストン４
６の直径Ｄとの比、すなわちＬ／Ｄが１．０の場合、摩
擦部材２４に作用する面圧は、摩擦パッド１６の中心部
において約３０ｋｇｆ／ｃｍ 2 の谷を形成し、ピストン
４６の内周面に近いところで約３２．５ｋｇｆ／ｃｍ 2
のピークを形成したのち、摩擦部材２４の端部で３０ｋ
ｇｆ／ｃｍ2 を僅かに下回り、全体として比較的一様な
面圧分布となる。As is apparent from FIG. 1, the inner friction pad is
The width L of the friction member 24 in the rotor 16 in the rotor circumferential direction and the piston 4
If the ratio of 6 to the diameter D, that is, L / D is 1.0,
The surface pressure acting on the rubbing member 24 is the central portion of the friction pad 16.
At about 30 kgf / cm Forming a valley of two and a piston
Approximately 32.5 kgf / cm near the inner surface of 46 2
After forming the peak of 30k, 30k at the end of the friction member 24
gf / cm2 Slightly below and relatively uniform overall
It becomes the surface pressure distribution.

【００２０】しかし、Ｌ／Ｄが０．９の場合、摩擦部材
２４に作用する面圧は全体的に高くなるとともに、ピス
トン４６の内周面に近い端部付近において面圧の高い部
分（約４０ｋｇｆ／ｃｍ2 ）が存在するカルデラ状の面
圧分布となる。すなわち、Ｌ／Ｄ＝０．９の場合、面圧
は、摩擦パッド１６の中心部において約３５ｋｇｆ／ｃ
ｍ2 程度の谷を有し、ピストン４６の内周面よりやや内
側において約４０ｋｇｆ／ｃｍ2 のピークを形成し、摩
擦部材２４の端に向うほど急速に低下して端部において
約３３ｋｇｆ／ｃｍ2 となる。従って、インナ摩擦パッ
ド１６の摩擦部材２４のロータ周方向幅Ｌは、Ｌ／Ｄ≧
１．０がよい。However, when L / D is 0.9, the surface pressure acting on the friction member 24 becomes high as a whole, and a portion having a high surface pressure (approx. The surface pressure distribution has a caldera shape in which 40 kgf / cm 2 ) exists. That is, when L / D = 0.9, the surface pressure is about 35 kgf / c at the center of the friction pad 16.
It has a trough of about m 2 and forms a peak of about 40 kgf / cm 2 slightly inside the inner peripheral surface of the piston 46, and decreases rapidly toward the end of the friction member 24 and about 33 kgf / cm at the end. It becomes 2 . Therefore, the rotor circumferential width L of the friction member 24 of the inner friction pad 16 is L / D ≧
1.0 is good.

【００２１】また、Ｌ／Ｄ＞１．０となると、面圧は、
摩擦部材２４の中心部がほぼい一定のピーク値（約２
７．５ｋｇｆ／ｃｍ2 ）となって、端部にいくほど面圧
が小さくなる山形となり、実線に示したＬ／Ｄ＝２．０
の曲線に一致してくる。そして、摩擦部材２４の幅Ｌが
ピストン直径Ｄの約１．８倍である１００ｍｍになる
と、その部分の面圧は零となり、Ｌ＞１００ｍｍでは負
の面圧となる。従って、インナ摩擦パッド１６の摩擦部
材２４のロータ周方向幅Ｌは、ピストン４６の直径Ｄの
１．８倍より大きくしても意味がなく、Ｌ／Ｄ≦１．８
とするのが望ましい。When L / D> 1.0, the surface pressure becomes
The center of the friction member 24 has a substantially constant peak value (about 2
7.5 kgf / cm 2 ), and the surface pressure becomes smaller toward the end, resulting in a mountain shape, and L / D = 2.0 indicated by the solid line.
Comes to match the curve of. When the width L of the friction member 24 becomes 100 mm, which is about 1.8 times the piston diameter D, the surface pressure at that portion becomes zero, and when L> 100 mm, the surface pressure becomes negative. Therefore, there is no point in making the rotor circumferential width L of the friction member 24 of the inner friction pad 16 larger than 1.8 times the diameter D of the piston 46, and L / D ≦ 1.8.
Is desirable.

【００２２】アウタ摩擦パッド１８の場合、図２に示す
ように、摩擦部材２４のロータ周方向幅Ｌは、キャリパ
爪４８、５０のキャリパ爪幅Ｔの１．０〜１．２倍がよ
い。すなわち、Ｌ／Ｔ＝１．０の場合、摩擦部材２４の
面圧は、中央部が低く（約１４．５ｋｇｆ／ｃｍ2 ）、
キャリパ爪４８、５０に近づくに従って高くなり、両端
部で最高となる（約３８ｋｇｆ／ｃｍ2 ）。そして、Ｌ
／Ｔ＜１．０となると、摩擦部材２４の端部に向うほど
急速に面圧が高くなり、その差がより一層大きくなって
面圧の均一化が困難である。In the case of the outer friction pad 18, as shown in FIG. 2, the rotor circumferential width L of the friction member 24 is preferably 1.0 to 1.2 times the caliper pawl width T of the caliper pawls 48, 50. That is, when L / T = 1.0, the surface pressure of the friction member 24 is low in the central portion (about 14.5 kgf / cm 2 ),
It becomes higher as it approaches the caliper claws 48, 50, and becomes the highest at both ends (about 38 kgf / cm 2 ). And L
When /T<1.0, the surface pressure increases rapidly toward the end of the friction member 24, and the difference becomes even larger, making it difficult to make the surface pressure uniform.

【００２３】一方、Ｌ／Ｔ＝１．２では、摩擦部材２４
の中央部における面圧の極小値が約１７ｋｇｆ／ｃｍ2
とＬ／Ｔ＝１．０の場合に比較して大きくなるととも
に、両端部の面圧が約１９ｋｇｆ／ｃｍ2 と大幅に小さ
くなる。そして、各キャリパ爪４８、５０の中心位置付
近において面圧が約２４．５ｋｇｆ／ｃｍ2 のピークを
示し、面圧の分布が比較的一様となる。しかし、Ｌ／Ｔ
＞１．２では、面圧が摩擦部材２４の端部にいくほど急
速に低下する。そして、Ｌ／Ｔ＝１．３における面圧
は、摩擦部材２４の中心部に約１５ｋｇｆ／ｃｍ2 の極
小値を示し、各キャリパ爪４８、５０の中心部よりやや
外側において約２３ｋｇｆ／ｃｍ2 程度のピークを示し
たのち、端部において約１０ｋｇｆ／ｃｍ2 となる。従
って、アウタ摩擦パッド１８の摩擦部材２４のロータ周
方向幅Ｌは、キャリパ爪４８、５０のキャリパ爪幅Ｔの
１．０〜１．２倍がよい。On the other hand, when L / T = 1.2, the friction member 24
The minimum value of the surface pressure at the center of the is about 17 kgf / cm 2
And L / T = 1.0, the surface pressure at both ends is significantly reduced to about 19 kgf / cm 2 . Then, the surface pressure exhibits a peak of about 24.5 kgf / cm 2 near the center position of each caliper claw 48, 50, and the distribution of the surface pressure becomes relatively uniform. However, L / T
At> 1.2, the surface pressure rapidly decreases toward the end of the friction member 24. Then, L / surface pressure at T = 1.3, the friction member shows a minimum value of about 15 kgf / cm 2 in the center of 24, about 23kgf / cm 2 in a slightly outside the center of the caliper claw 48 After showing a peak of about 10 kgf / cm 2 at the end. Therefore, the rotor circumferential width L of the friction member 24 of the outer friction pad 18 is preferably 1.0 to 1.2 times the caliper pawl width T of the caliper pawls 48, 50.

【００２４】インナ摩擦パッド１６とアウタ摩擦パッド
１８とは、同一の形状に形成されているため、ロータ周
方向幅Ｌは等しく、上記の摩擦部材のロータ周方向幅Ｌ
とピストン直径Ｄとの関係、および摩擦部材のロータ周
方向幅Ｌとキャリパ爪幅Ｔとの関係から、キャリパ爪幅
Ｔとピストン直径Ｄとの関係を求めると、Since the inner friction pad 16 and the outer friction pad 18 are formed in the same shape, the rotor circumferential width L is the same and the rotor circumferential width L of the friction member is the same.
From the relationship between the rotor circumferential width L of the friction member and the caliper claw width T, the relationship between the caliper claw width T and the piston diameter D is calculated as follows:

【数８】０．８≦Ｔ／Ｄ≦１．５ が得られる。(8) 0.8 ≦ T / D ≦ 1.5 is obtained.

【００２５】従って、フィストタイプにおける摩擦部材
２４の形状は、上記のことから、インナ摩擦パッド１
６、１８の摩擦部材２４のロータ周方向幅Ｌは、Therefore, from the above, the shape of the friction member 24 of the fist type is the inner friction pad 1
The rotor circumferential width L of the friction members 24 of 6 and 18 is

【数９】Ｌ＝（１．０〜１．８）Ｄ にするとともに、## EQU9 ## While setting L = (1.0 to 1.8) D,

【数１０】Ｔ＝（０．８〜１．５）Ｄ とすることが望ましい。ただし、上記したように、Ｄは
ピストン開口部における外径であり、Ｔは一対のキャリ
パ爪の外側端間の距離（キャリパ爪幅）である。## EQU10 ## It is desirable that T = (0.8 to 1.5) D. However, as described above, D is the outer diameter of the piston opening, and T is the distance between the outer ends of the pair of caliper pawls (caliper pawl width).

【００２６】これにより、インナ摩擦パッド１６のロー
タ周方向の幅を狭くして摩擦部材に作用する面圧を比較
的均一にでき、またピストン直径とキャリパ爪幅とをで
きるだけ近づけ、インナ、アウタともパッド面圧が比較
的均一で面圧の変化を少なくでき、これにより安定した
制動力が得られ、制動時におけるパッドの振動を小さく
してノイズの少ないディスクブレーキが得られる。As a result, the width of the inner friction pad 16 in the rotor circumferential direction can be narrowed to make the surface pressure acting on the friction member relatively uniform, and the piston diameter and the caliper pawl width can be made as close as possible to each other, so The pad surface pressure is relatively uniform and changes in the surface pressure can be reduced, so that a stable braking force can be obtained, and vibration of the pad during braking can be reduced to obtain a disc brake with less noise.

【００２７】なお、前記実施例においては、前記実施例
においては、キャリパ爪を一対設けたキャリパ４０につ
いて説明したが、キャリパ爪を３つ以上設けたものでも
よい。In the above embodiment, the caliper 40 having a pair of caliper pawls has been described in the above embodiment, but three or more caliper pawls may be provided.

【００２８】[0028]

【発明の効果】以上に説明したように、本発明によれ
ば、摩擦パッドの面圧を比較的均一にすることができ、
制動作用の安定化が図れるとともに、制動時のノイズを
低減することができる。As described above, according to the present invention, the surface pressure of the friction pad can be made relatively uniform,
The braking action can be stabilized, and noise during braking can be reduced.

【図面の簡単な説明】[Brief description of drawings]

【図１】ピストンがロータに圧接するインナ摩擦パッド
の面圧の分布を示す図である。FIG. 1 is a diagram showing a distribution of surface pressure of an inner friction pad in which a piston is in pressure contact with a rotor.

【図２】キャリパ爪がロータに圧接するアウタ摩擦パッ
ドの面圧の分布を示す図である。FIG. 2 is a diagram showing a distribution of surface pressure of an outer friction pad where a caliper claw is in pressure contact with a rotor.

【図３】実施例に係るディスクブレーキをアウタ側から
見た図である。FIG. 3 is a diagram of the disc brake according to the embodiment as viewed from the outer side.

【符号の説明】[Explanation of symbols]

１０ ディスクブレーキ １２ サポート １６ インナ摩擦パッド １８ アウタ摩擦パッド ２４ 摩擦部材 ４０ キャリパ ４６ ピストン ４８、５０ キャリパ爪 10 Disc Brake 12 Support 16 Inner Friction Pad 18 Outer Friction Pad 24 Friction Member 40 Caliper 46 Piston 48, 50 Caliper Claw

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】 インナ摩擦パッドをキャリパに設けたピ
ストンによってロータに圧接し、アウタ摩擦パッドをキ
ャリパ爪によって前記ロータに圧接するディスクブレー
キにおいて、前記ピストンの先端部における直径をＤ、
前記インナおよびアウタ摩擦パッドの摩擦部材のピスト
ン中心を通るロータ周方向幅をＬ、前記キャリパ爪の、
前記ピストン中心を通る位置におけるロータ周方向の距
離をＴとしたときに、 【数１】Ｌ／Ｄ＝１．０〜１．８ かつ、 【数２】Ｔ／Ｄ＝０．８〜１．５ であることを特徴とするディスクブレーキ。1. In a disc brake in which an inner friction pad is pressed against a rotor by a piston provided on a caliper, and an outer friction pad is pressed against the rotor by a caliper claw, a diameter at a tip portion of the piston is D,
The width in the rotor circumferential direction passing through the piston center of the friction members of the inner and outer friction pads is L, and the caliper pawl has
Letting T be the distance in the rotor circumferential direction at the position passing through the center of the piston, L / D = 1.0 to 1.8 and T / D = 0.8 to 1. A disc brake characterized by being 5.
JP8474395A 1995-03-16 1995-03-16 Disc brake Pending JPH08254231A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP8474395A JPH08254231A (en) 1995-03-16 1995-03-16 Disc brake
DE1996110276 DE19610276A1 (en) 1995-03-16 1996-03-15 Disk brake for vehicle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP8474395A JPH08254231A (en) 1995-03-16 1995-03-16 Disc brake

Publications (1)

Publication Number Publication Date
JPH08254231A true JPH08254231A (en) 1996-10-01

Family

ID=13839180

Family Applications (1)

Application Number Title Priority Date Filing Date
JP8474395A Pending JPH08254231A (en) 1995-03-16 1995-03-16 Disc brake

Country Status (2)

Country Link
JP (1) JPH08254231A (en)
DE (1) DE19610276A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005038301A1 (en) * 2005-08-12 2007-02-15 Federal-Mogul Friction Products Gmbh Brake pad with brake parts molded onto the back plate

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5211374A (en) * 1975-07-17 1977-01-28 Tokico Ltd Disc brake
FR2498276B2 (en) * 1980-02-12 1986-08-14 Valeo FRICTION ELEMENT, ESPECIALLY BRAKE PAD
DE8809123U1 (en) * 1988-07-15 1989-11-16 Lucas Industries P.L.C., Birmingham, West Midlands Partial disc brake

Also Published As

Publication number Publication date
DE19610276A1 (en) 1996-10-31

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