JP4932651B2

JP4932651B2 - Opposite piston type disc brake

Info

Publication number: JP4932651B2
Application number: JP2007237433A
Authority: JP
Inventors: 利史前原
Original assignee: Akebono Brake Industry Co Ltd
Current assignee: Akebono Brake Industry Co Ltd
Priority date: 2007-09-13
Filing date: 2007-09-13
Publication date: 2012-05-16
Anticipated expiration: 2027-09-13
Also published as: JP2009068593A

Description

この発明は、自動車の制動に使用するディスクブレーキのうち、ロータの両側にピストンを、互いに対向する状態で設けた、対向ピストン型ディスクブレーキの改良に関する。 The present invention relates to an improvement of an opposed piston type disc brake in which pistons are provided on both sides of a rotor in a state of facing each other among disc brakes used for braking an automobile.

自動車の制動を行なう為に、ディスクブレーキが広く使用されている。ディスクブレーキによる制動時には、車輪と共に回転するロータの軸方向両側に配置された１対のパッドを、ピストンによりこのロータの両側面に押し付ける。この様なディスクブレーキとして従来から各種構造のものが知られているが、ロータの両側にピストンを、互いに対向する状態で設けた、対向ピストン型ディスクブレーキは、安定した制動力を得られる事から、近年使用例が増えている。この様な対向ピストン型ディスクブレーキとして従来から、例えば特許文献１〜１０に記載された構造のものが知られている。このうちの特許文献８の記載に基づいて、対向ピストン型ディスクブレーキの基本的構造を図６により、具体的構造を図７〜１０により、それぞれ説明する。 Disc brakes are widely used to brake automobiles. At the time of braking by the disc brake, a pair of pads arranged on both sides in the axial direction of the rotor rotating together with the wheels are pressed against both side surfaces of the rotor by the piston. Conventionally, various types of disc brakes have been known. However, the opposed piston type disc brake, which is provided with pistons on both sides of the rotor so as to face each other, can obtain a stable braking force. In recent years, use cases have increased. Conventionally, for example, a structure described in Patent Documents 1 to 10 is known as such an opposed piston type disc brake. Of these, the basic structure of the opposed piston type disc brake will be described with reference to FIG. 6 and the specific structure will be described with reference to FIGS.

図６に示す様に対向ピストン型のディスクブレーキ１は、車輪と共に回転するロータ２を挟む位置に、アウタボディ部３及びインナボディ部４から成るキャリパ５を設けている。又、これら各ボディ部３、４内にアウタシリンダ及びインナシリンダを、それぞれの開口部を上記ロータ２を介して互いに対向させた状態で設けている。そして、これらアウタシリンダ及びインナシリンダ内にアウタピストン及びインナピストンを、液密に、且つ上記ロータ２の軸方向に関する変位を可能に嵌装している。又、上記アウタボディ部３にはアウタパッドを、上記インナボディ部４にはインナパッドを、それぞれ上記ロータ２の軸方向に関する変位を可能に支持している。制動時には、上記アウタシリンダ及びインナシリンダ内に圧油を送り込み、上記アウタピストン及びインナピストンにより、上記アウタパッド及びインナパッドを、上記ロータ２の内外両側面に押し付ける。 As shown in FIG. 6, the opposed piston type disc brake 1 is provided with a caliper 5 including an outer body portion 3 and an inner body portion 4 at a position sandwiching a rotor 2 that rotates together with wheels. Further, an outer cylinder and an inner cylinder are provided in each of the body portions 3 and 4 in a state where the respective opening portions face each other through the rotor 2. The outer piston and the inner piston are fitted in the outer cylinder and the inner cylinder in a liquid-tight manner and capable of displacement in the axial direction of the rotor 2. Further, an outer pad is supported on the outer body portion 3 and an inner pad is supported on the inner body portion 4 so as to be capable of displacement in the axial direction of the rotor 2. During braking, pressure oil is fed into the outer cylinder and the inner cylinder, and the outer pad and the inner pad are pressed against both the inner and outer side surfaces of the rotor 2 by the outer piston and the inner piston.

又、図７〜１０に示した、より具体的なディスクブレーキ１ａも、ロータ２を跨ぐ状態で配置されたキャリパ５ａを備える。このキャリパ５ａは、アルミニウム合金製の素材により一体に造ったもので、上記ロータ２の軸方向（図７、９の表裏方向、図８の上下方向、図１０の左右方向）両側に配置されたアウタボディ部３ａ及びインナボディ部４ａと、これら両ボディ部３ａ、４ａの周方向（図７〜９の左右方向）両端部同士を連結する１対の連結部６、６とを備える。そして、図示の例の場合には、上記両ボディ部３ａ、４ａにそれぞれ３個ずつ、合計６個のアウタ、インナ各シリンダ７、７（８、８）を設け、これら各シリンダ７、７（８、８）にアウタ、インナ各ピストン９、９（１０、１０）を嵌装している。そして、これら各ピストン９、９（１０、１０）により、上記ロータ２を挟んで上記両ボディ部３ａ、４ａに支持されたアウタ、インナ両パッド１１、１２を、上記ロータ２に押圧する事で、制動を行なう様に構成している。 The more specific disc brake 1a shown in FIGS. 7 to 10 also includes a caliper 5a disposed across the rotor 2. This caliper 5a is integrally made of an aluminum alloy material, and is arranged on both sides of the rotor 2 in the axial direction (front and back directions in FIGS. 7 and 9, the up and down direction in FIG. 8, and the left and right direction in FIG. 10). The outer body portion 3a and the inner body portion 4a, and a pair of connecting portions 6 and 6 that connect both ends of the body portions 3a and 4a in the circumferential direction (the left-right direction in FIGS. 7 to 9) are provided. In the case of the illustrated example, a total of six outer and inner cylinders 7 and 7 (8 and 8) are provided in each of the body parts 3a and 4a, and the cylinders 7 and 7 ( 8 and 8) are fitted with outer and inner pistons 9 and 9 (10 and 10), respectively. Then, by the pistons 9 and 9 (10 and 10), the outer and inner pads 11 and 12 supported by the body parts 3a and 4a are pressed against the rotor 2 with the rotor 2 interposed therebetween. It is configured to perform braking.

上記アウタボディ部３ａとインナボディ部４ａとの周方向中間部で上記両連結部６、６の間に位置する部分のうち、径方向外端部同士の間に、１対のトルク受けピン１３、１３と１本の結合ピン１４とを、それぞれ上記両ボディ部３ａ、４ａ同士の間に掛け渡す状態で設けている。これら各ピン１３、１４のうち、両トルク受けピン１３、１３は、上記アウタ、インナ両パッド１１、１２のプレッシャプレート１５、１５を、上記ロータ２の回転方向に関して両側から挟む位置で、ロータ２の外周縁よりも径方向外寄り部分に設けている。又、上記結合ピン１４は、上記両パッド１１、１２よりも径方向外側で上記両トルク受けピン１３、１３の間部分に設けている。これら両トルク受けピン１３、１３は、制動時に上記ロータ２と上記両パッド１１、１２を構成するライニング１６、１６との摩擦に基づいて上記両プレッシャプレート１５、１５に伝達されたブレーキトルクを、上記キャリパ５ａを介して車体（懸架装置）に伝達する為のものである。この為に、上記両トルク受けピン１３、１３の一部外周面は、上記アウタ、インナ両パッド１１、１２を構成するプレッシャプレート１５、１５の周方向両端縁に、当接若しくは近接対向させている。 A pair of torque receiving pins 13 between the radially outer ends of the portions located between the connecting portions 6 and 6 in the circumferential intermediate portion between the outer body portion 3a and the inner body portion 4a, 13 and one connecting pin 14 are provided in a state of being spanned between the body parts 3a and 4a. Among these pins 13, 14, the torque receiving pins 13, 13 are located at positions where the pressure plates 15, 15 of the outer and inner pads 11, 12 are sandwiched from both sides in the rotational direction of the rotor 2. It is provided in the radially outer portion than the outer peripheral edge. Further, the coupling pin 14 is provided in a portion between the torque receiving pins 13 and 13 at a radially outer side than the pads 11 and 12. These torque receiving pins 13 and 13 receive the brake torque transmitted to the pressure plates 15 and 15 based on the friction between the rotor 2 and the linings 16 and 16 constituting the pads 11 and 12 during braking. This is for transmission to the vehicle body (suspension device) via the caliper 5a. For this purpose, the partial outer peripheral surfaces of the torque receiving pins 13 and 13 are brought into contact with or in close proximity to the circumferential edges of the pressure plates 15 and 15 constituting the outer and inner pads 11 and 12, respectively. Yes.

これに対して上記結合ピン１４は、上記アウタボディ部３ａとインナボディ部４ａとの間隔が、制動の為の加圧時の反力で拡がる方向に変形する事を極力阻止する役目を果たす。又、上記結合ピン１４と、上記両パッド１１、１２のプレッシャプレート１５、１５の径方向外周縁との間に、パッドクリップ１７を設けて、これら両プレッシャプレート１５、１５に、径方向内方に向く弾力と、互いに離れる方向の弾力とを付与している。 On the other hand, the connecting pin 14 serves to prevent the gap between the outer body portion 3a and the inner body portion 4a from being deformed in a direction in which it is expanded by a reaction force during pressurization for braking. Further, a pad clip 17 is provided between the coupling pin 14 and the radially outer peripheral edges of the pressure plates 15 and 15 of the pads 11 and 12, and the pressure plates 15 and 15 are radially inward. And elasticity in a direction away from each other.

更に、前記アウタボディ部３ａ及びインナボディ部４ａの径方向内寄り部分に、これら両ボディ部３ａ、４ａ毎に独立した係止ピン１８、１８を、これら両ボディ部３ａ、４ａ毎に２本ずつ設けている。これら各係止ピン１８、１８はそれぞれ、これら両ボディ部３ａ、４ａの径方向内端部で周方向両端部近傍位置に、それぞれ固定している。この状態で上記各係止ピン１８、１８の一部外周面に、上記両パッド１１、１２のプレッシャプレート１５、１５の径方向内端縁が、上記パッドクリップ１７の弾力に基づいて押し付けられる。上記各係止ピン１８、１８は、上記両パッド１１、１２が前記キャリパ５ａから、前記ロータ２の径方向内方に抜け出る事を防止すると共に、非制動時に上記両パッド１１、１２ががたつく事を防止する。 Furthermore, two locking pins 18 and 18 that are independent for each of the two body portions 3a and 4a are provided on the radially inward portions of the outer body portion 3a and the inner body portion 4a. Provided. These locking pins 18 and 18 are respectively fixed to the positions in the vicinity of both ends in the circumferential direction at the radially inner ends of the body portions 3a and 4a. In this state, the radially inner end edges of the pressure plates 15 and 15 of the pads 11 and 12 are pressed against the partial outer peripheral surfaces of the locking pins 18 and 18 based on the elasticity of the pad clip 17. The locking pins 18 and 18 prevent the pads 11 and 12 from coming out of the caliper 5a inward in the radial direction of the rotor 2, and the pads 11 and 12 rattle when not braked. To prevent.

上述の様に構成する対向ピストン型ディスクブレーキによる制動時には、前記各アウタシリンダ７、７及びインナシリンダ８、８に圧油を送り込む。そして、前記アウタピストン９、９及びインナピストン１０、１０を押し出して、上記アウタ、インナ両パッド１１、１２を前記ロータ２の両側面に押圧する。この結果、これら両パッド１１、１２を構成するライニング１６、１６と上記ロータ２の両側面との摩擦により、制動が行なわれる。尚、この摩擦に基づいて上記両パッド１１、１２に加わる制動トルクは、前記両トルク受けピン１３、１３のうちのアンカ側（ロータ２の回出側）のトルク受けピン１３により支承する。即ち、制動時には、上記両パッド１１、１２のプレッシャプレート１５、１５のうち、上記ロータ２の回転方向前端縁が上記アンカ側のトルク受けピン１３に押し付けられて、上記制動トルクをこのトルク受けピン１３に伝達する。 At the time of braking by the opposed piston type disc brake configured as described above, pressure oil is fed into each of the outer cylinders 7 and 7 and the inner cylinders 8 and 8. Then, the outer pistons 9 and 9 and the inner pistons 10 and 10 are pushed out to press the outer and inner pads 11 and 12 against both side surfaces of the rotor 2. As a result, braking is performed by friction between the linings 16 and 16 constituting the pads 11 and 12 and both side surfaces of the rotor 2. The braking torque applied to the pads 11 and 12 based on this friction is supported by the torque receiving pin 13 on the anchor side (rotating side of the rotor 2) of the torque receiving pins 13 and 13. That is, during braking, the front end edge of the rotor 2 in the rotational direction of the pressure plates 15 and 15 of both the pads 11 and 12 is pressed against the torque receiving pin 13 on the anchor side, and the braking torque is applied to the torque receiving pin. 13 is transmitted.

上述の様な従来構造の場合、制動時に上記制動トルクを支承するトルク受けピン１３の外周面と、上記両プレッシャプレート１５、１５の前端縁との当接面積が狭い。即ち、曲率半径の小さな円筒面である、上記トルク受けピン１３の外周面と、平面状である上記両プレッシャプレート１５、１５の前端縁とが当接する為、当接部の接触状態は線接触に近い状態となり、この当接部の弾性変形を考慮したとしても、当接面積は極く限られる。この為、制動時に、上記両ライニング１６、１６と上記ロータ２の両側面との摩擦に基づいて振動が発生した場合、上記当接部が振動し易く、制動時に発生する、所謂ブレーキノイズを低減する面から不利になる。更には、上記当接部で、塑性変形や摩耗が生じ易く、生じた場合には、上記両パッド１１、１２の挙動が不安定になり易く、上記ブレーキノイズ低減の面から一層不利になる。 In the case of the conventional structure as described above, the contact area between the outer peripheral surface of the torque receiving pin 13 that supports the braking torque during braking and the front end edges of the pressure plates 15 and 15 is small. That is, since the outer peripheral surface of the torque receiving pin 13, which is a cylindrical surface having a small radius of curvature, abuts the front end edges of the two pressure plates 15, 15 which are flat, the contact state of the abutting portion is a line contact. Even if the elastic deformation of the contact portion is taken into consideration, the contact area is extremely limited. For this reason, when vibration is generated based on the friction between the linings 16 and 16 and both side surfaces of the rotor 2 during braking, the abutting portion is likely to vibrate, and so-called brake noise generated during braking is reduced. It becomes disadvantageous from the aspect to do. Furthermore, plastic deformation and wear are likely to occur at the abutting portion. In such a case, the behavior of the pads 11 and 12 is likely to be unstable, which is further disadvantageous in terms of reducing brake noise.

特開平５−１０６６６２号公報JP-A-5-106662 特開平７−１２７６７４号公報Japanese Patent Laid-Open No. 7-127674 特開平８−１５９１８５号公報JP-A-8-159185 特開平８−２５４２２８号公報JP-A-8-254228 特開平９−２５７０６３号公報Japanese Patent Laid-Open No. 9-257063 特開２００３−１２０７２４号公報JP 2003-120724 A 特開２００４−１８３９０４号公報JP 2004-183904 A 特開２００５−１２１１７４号公報JP 2005-121174 A 特開２００５−２９９９３０号公報JP 2005-299930 A 特表２００５−５１７８７７号公報JP 2005-517877 A

本発明は、上述の様な事情に鑑みて、各パッドのプレッシャプレートの端縁と、制動トルクを支承する部材との当接部の当接面積を広くできる構造を実現すべく発明したものである。 The present invention has been invented to realize a structure capable of widening the contact area of the contact portion between the edge of the pressure plate of each pad and the member that supports the braking torque in view of the circumstances as described above. is there.

本発明の対向ピストン型ディスクブレーキは、前述した従来から知られている対向ピストン型ディスクブレーキと同様に、キャリパと、複数のシリンダと、複数のピストンと、複数枚のパッドと、少なくとも１本のトルク受けピンとを備える。
このうちのキャリパは、車輪と共に回転するロータを挟んで設けられたアウタ、インナ両ボディ部、及び、このロータの回転方向に関しこれら両ボディ部の両端部同士を上記ロータの外周縁よりも径方向外方位置で連結する１対の連結部から成る。
又、上記各シリンダは、上記両ボディ部に、互いに対向して設けられている。
又、上記各ピストンは、上記各シリンダ内に、液密に、且つ、上記ロータの軸方向に関する変位を可能に嵌装されている。
又、上記各パッドは、上記軸方向に関する変位を可能として上記両ボディ部の内側面（上記ロータを介して互いに対向する面）に対向する部分に、それぞれ支持されている。
又、上記トルク受けピンは、上記ロータの回転方向に関してこれら両パッドを構成するプレッシャプレートの少なくとも一方の端縁に対向する部分で、上記ロータの外周縁よりも径方向外寄り部分に、上記両ボディ部同士の間に掛け渡す状態で設けられている。 The opposed piston type disc brake of the present invention is similar to the previously known opposed piston type disc brake, and includes a caliper, a plurality of cylinders, a plurality of pistons, a plurality of pads, and at least one pad. A torque receiving pin.
Of these, the caliper is arranged such that both the outer and inner body portions provided across the rotor rotating together with the wheels, and both ends of these body portions in the radial direction from the outer peripheral edge of the rotor with respect to the rotation direction of the rotor. It consists of a pair of connecting parts connected in the outward position.
The cylinders are provided opposite to each other on the body parts.
The pistons are fitted in the cylinders in a fluid-tight manner and capable of displacement in the axial direction of the rotor.
Each of the pads is supported by a portion that can be displaced in the axial direction and that faces the inner side surfaces (surfaces facing each other via the rotor) of the two body portions.
Further, the torque receiving pin is a portion facing at least one end edge of the pressure plate constituting both the pads with respect to the rotation direction of the rotor, and the both ends of the torque receiving pin are arranged on the radially outer side than the outer periphery of the rotor. It is provided in a state of being spanned between body parts.

特に、本発明の対向ピストン型ディスクブレーキに於いては、上記トルク受けピンのうち、断面円形の杆部の周囲に、中心孔の内周面が円筒面で外周面の少なくとも一部に平面部を設けた、トルク受けスリーブを外嵌している。そして、このトルク受けスリーブの外周面に設けられた平面部と上記両パッドのプレッシャプレートの端縁に形成された平坦面とを、互いに当接させている。
この様な本発明を実施する場合に好ましくは、例えば請求項２に記載した様に、上記トルク受けスリーブの軸方向両端外周縁部の一部と、上記キャリパの一部内面との係合により、上記トルク受けピンを中心とする上記トルク受けスリーブの回動を制限する。 In particular, in the opposed piston type disc brake of the present invention, among the torque receiving pins , the inner peripheral surface of the center hole is a cylindrical surface and the flat surface portion is at least part of the outer peripheral surface around the flange portion having a circular cross section. The torque receiving sleeve provided with is externally fitted. Then, a flat portion provided on the outer peripheral surface of the torque receiving sleeve and a flat surface formed on the edge of the pressure plate of both pads are brought into contact with each other .
In the case of carrying out the present invention as described above, preferably, as described in claim 2, for example, engagement between a part of the outer peripheral edge portions in the axial direction of the torque receiving sleeve and a part of the inner surface of the caliper is performed. Rotation of the torque receiving sleeve around the torque receiving pin is limited.

或いは、請求項３に記載した様に、上記トルク受けピンを構成する杆部の一部に形成した小径部に、自由状態での外径がこの杆部の残部の外径よりも大きな弾性スリーブを設置し、この弾性スリーブの外周面を上記トルク受けスリーブの内周面に、弾性的に当接させる。
この様な請求項３に記載した発明を実施する場合に好ましくは、請求項４に記載した様に、上記杆部の軸方向２個所位置で上記トルク受けスリーブの両端部内周面と対向する部分に形成した小径部に、それぞれ弾性スリーブを設置する。 Alternatively, as described in claim 3, an elastic sleeve having a small outer diameter formed in a part of the flange portion constituting the torque receiving pin and having an outer diameter in a free state larger than an outer diameter of the remaining portion of the flange portion. The outer peripheral surface of the elastic sleeve is elastically brought into contact with the inner peripheral surface of the torque receiving sleeve.
When the invention described in claim 3 is implemented, preferably, as described in claim 4, the portions facing the inner peripheral surfaces of both ends of the torque receiving sleeve at two axial positions of the flange portion. Elastic sleeves are respectively installed in the small diameter portions formed in the above.

或いは、請求項５に記載した様に、１対のトルク受けピンを、上記ロータの回転方向に関して、上記両パッドを構成するプレッシャプレートの両側に設ける。
この様な請求項５に記載した発明を実施する場合に好ましくは、請求項６に記載した様に、上記ロータの回転方向に関して、上記両パッドを構成するプレッシャプレートの両側縁のうち、このロータの径方向に関して外端部に、それぞれこのロータの回転方向に突出する係止突片を設ける。そして、これら各係止突片と上記両トルク受けピンに外嵌したトルク受けスリーブの外周面との係合により、上記両パッドが上記ロータの径方向内方に抜け出る事を防止する。 Alternatively, as described in claim 5, a pair of torque receiving pins are provided on both sides of the pressure plate constituting the two pads with respect to the rotational direction of the rotor.
In the case of carrying out the invention described in claim 5, preferably, as described in claim 6, with respect to the rotation direction of the rotor, of the both side edges of the pressure plate constituting the pads, the rotor The locking projections projecting in the rotational direction of the rotor are provided at the outer end portions with respect to the radial direction. Further, the engagement between each of the locking projection pieces and the outer peripheral surface of the torque receiving sleeve fitted around the torque receiving pins prevents the pads from coming out radially inward of the rotor.

上述の様に構成する本発明の対向ピストン型ディスクブレーキによれば、各パッドのプレッシャプレートの端縁と、制動トルクを支承する部材であるトルク受けスリーブの外周面との当接部の当接面積を広くして、制動時にこれら各当接部でブレーキノイズに結び付く振動が発生したり、これら各当接部に塑性変形や摩耗が生じる事を抑えられる。
即ち、上記トルク受けピンに外嵌したトルク受けスリーブは、このトルク受けピンを中心として、少なくとも若干の回動が可能である。この為、上記各パッドのプレッシャプレートの端縁に形成された平坦面を上記トルク受けスリーブの外周面に設けた平面部に突き当てると、このトルク受けスリーブが上記トルク受けピンに対し回動して、この平面部と上記平坦面とを広い面積で当接させる。又、このトルク受けピンの外周面と上記トルク受けスリーブの内周面との嵌合は、曲率半径が近い円筒面同士の嵌合であるから、これら両周面同士の当接面積も十分に広くなる。この結果、上記当接部の当接面積を広くして、上記効果を得られる。
又、請求項２に記載した構造を採用すれば、上記トルク受けピンを中心とする上記トルク受けスリーブの回動量を必要最小限に止める事で、対向ピストン型ディスクブレーキの組立時に、このトルク受けスリーブと上記各パッドのプレッシャプレートの端縁とを係合させる作業を容易に行なえる。 According to the opposed piston type disc brake of the present invention configured as described above, the contact of the contact portion between the edge of the pressure plate of each pad and the outer peripheral surface of the torque receiving sleeve which is a member for supporting the braking torque. By increasing the area, it is possible to suppress the occurrence of vibrations associated with brake noise at the respective contact portions during braking and the occurrence of plastic deformation and wear at the respective contact portions.
That is, the torque receiving sleeve fitted on the torque receiving pin can be rotated at least slightly around the torque receiving pin. For this reason, when the flat surface formed on the edge of the pressure plate of each pad is abutted against the flat surface provided on the outer peripheral surface of the torque receiving sleeve, the torque receiving sleeve rotates with respect to the torque receiving pin. Thus, the flat portion and the flat surface are brought into contact with each other over a wide area. In addition, since the fitting between the outer peripheral surface of the torque receiving pin and the inner peripheral surface of the torque receiving sleeve is a fitting between cylindrical surfaces having close curvature radii, the contact area between the two peripheral surfaces is sufficient. Become wider. As a result, the contact area of the contact portion can be widened to obtain the above effect.
Further, if the structure described in claim 2 is adopted, the torque receiving sleeve around the torque receiving pin is minimized so that the torque receiving sleeve is assembled at the time of assembly of the opposed piston type disc brake. The operation of engaging the sleeve and the edge of the pressure plate of each pad can be easily performed.

又、請求項３に記載した様に、上記トルク受けピンと上記トルク受けスリーブとの間に弾性スリーブを設ければ、走行時や制動時の振動に伴ってこのトルク受けピンの周囲でこのトルク受けスリーブががたつく事を防止して、走行時や制動時に異音が発生する事を防止できる。特に、請求項４に記載した様に、上記トルク受けスリーブの両端部内周面と対向する部分にそれぞれ弾性スリーブを設置すれば、制動時に上記トルク受けピンに対し上記トルク受けスリーブが傾斜する方向に大きなモーメントが作用する事を防止できる。そして、このトルク受けスリーブの外周面に設けた平面部と上記プレッシャプレートの端縁に形成された平坦面との当接状態を安定させて、上記ブレーキノイズに結び付く振動の発生を、より有効に防止できる。 According to a third aspect of the present invention, if an elastic sleeve is provided between the torque receiving pin and the torque receiving sleeve, the torque receiving pin is surrounded around the torque receiving pin due to vibration during running or braking. The sleeve can be prevented from rattling, and abnormal noise can be prevented during running and braking. In particular, as described in claim 4, if an elastic sleeve is installed in each of the portions opposite to the inner peripheral surfaces of both ends of the torque receiving sleeve, the torque receiving sleeve is inclined with respect to the torque receiving pin during braking. A large moment can be prevented from acting. Further, it stabilizes the contact state between the flat portion provided on the outer peripheral surface of the torque receiving sleeve and the flat surface formed at the end edge of the pressure plate, so that the generation of vibrations associated with the brake noise can be made more effective. Can be prevented.

又、請求項５に記載した様に１対のトルク受けピンを設ければ、車両が前進、後退、何れの方向に走行する場合の制動時にも、上記ブレーキノイズに結び付く振動の発生を防止できる。
更に、請求項６に記載した構成を採用すれば、前述の図７〜１０に示した従来構造に於ける係止ピン１８、１８の如き、各パッドがキャリパからロータの径方向内方に抜け出るのを防止する為の専用の機構を設ける必要がなくなり、対向ピストン型ディスクブレーキの構造の簡略化による製造コストの低減を図れる。 In addition, if a pair of torque receiving pins is provided as described in claim 5, it is possible to prevent the occurrence of vibrations associated with the brake noise during braking when the vehicle travels in either forward or reverse direction. .
Furthermore, if the structure described in claim 6 is adopted, each pad is pulled out from the caliper inward in the radial direction of the rotor, such as the locking pins 18 and 18 in the conventional structure shown in FIGS. Therefore, it is not necessary to provide a dedicated mechanism for preventing this, and the manufacturing cost can be reduced by simplifying the structure of the opposed piston type disc brake.

［実施の形態の第１例］
図１〜４は、請求項１、２、５、６に対応する、本発明の実施の形態の第１例を示している。本例のディスクブレーキ１ｂを構成するキャリパ５ｂは、アルミニウム合金をダイキャスト成形する事により一体に造られたもので、アウタボディ部３ｂ及びインナボディ部４ｂと、ロータ２（図６、８〜１０参照）の回転方向に関してこれら両ボディ部３ｂ、４ｂの両端部同士を、上記ロータ２の外周縁よりも径方向外側部分で連結した、１対の連結部６ａ、６ａとを備える。更に本例の場合には、これら両ボディ部３ｂ、４ｂ同士の間に、ブリッジ部１９を掛け渡している。このブリッジ部１９は、１対の脚部２０、２０とこれら両脚部２０、２０の先端部同士を連結する連結部２１とから成る門型である。この様なブリッジ部１９は、上記両脚部２０、２０の基端部を上記両ボディ部３ｂ、４ｂの外周面に連続させる事により、上記両ボディ部３ｂ、４ｂと一体に設けている。本例の場合には、上記ブリッジ部１９を、前進状態での制動時に於けるアンカ側（図１〜３の右側）に偏らせた状態で設けている。又、上記両ボディ部３ｂ、４ｂには、それぞれアンカ側と反アンカ側とに分けて１対ずつのシリンダを設けているが、それぞれのアンカ側のシリンダの内径を反アンカ側のシリンダの内径よりも大きくしている。この構成により、アウタパッド１１ａ及びインナパッド１２ａを上記ロータ２の側面に押し付ける力を、アンカ側で反アンカ側よりも大きくしている。 [First example of embodiment]
1-4 show a first example of an embodiment of the present invention corresponding to claims 1, 2, 5, and 6. FIG. The caliper 5b constituting the disc brake 1b of this example is integrally formed by die-casting an aluminum alloy, and the outer body portion 3b, the inner body portion 4b, and the rotor 2 (see FIGS. 6, 8 to 10). ) Is provided with a pair of connecting portions 6a and 6a in which both end portions of both the body portions 3b and 4b are connected to each other at a radially outer portion than the outer peripheral edge of the rotor 2. Furthermore, in the case of this example, the bridge part 19 is spanned between these both body parts 3b and 4b. The bridge portion 19 has a gate shape including a pair of leg portions 20 and 20 and a connecting portion 21 that connects the tip portions of both the leg portions 20 and 20. Such a bridge part 19 is provided integrally with the body parts 3b and 4b by connecting the base ends of the leg parts 20 and 20 to the outer peripheral surfaces of the body parts 3b and 4b. In the case of this example, the bridge portion 19 is provided in a state of being biased toward the anchor side (right side in FIGS. 1 to 3) during braking in the forward movement state. Each of the body portions 3b and 4b is provided with a pair of cylinders separately for the anchor side and the anti-anchor side. The inner diameter of each anchor side cylinder is set to the inner diameter of the anti-anchor side cylinder. Is bigger than. With this configuration, the force for pressing the outer pad 11a and the inner pad 12a against the side surface of the rotor 2 is made larger on the anchor side than on the anti-anchor side.

又、上記両ボディ部３ｂ、４ｂの両端外径寄り部分で上記両連結部６ａ、６ａの近傍部分に、本発明の特徴部分である、２組のトルク受けピン１３ａ、１３ａとトルク受けスリーブ２２、２２とを、それぞれ着脱可能に設けている。これら両トルク受けピン１３ａ、１３ａは、ステンレス鋼、軸受鋼等の鉄系合金の様に、ヤング率が高く（弾性変形しにくく、引っ張り方向の力に対する剛性が高く）、耐摩耗性（好ましくは更に耐食性）が優れた金属材料により造られている。上記両トルク受けピン１３ａ、１３ａの形状及び構造は、上記両ボディ部３ｂ、４ｂ同士の間に確実に支持固定できるものであれば、特に問わない。図示の例の場合、上記両トルク受けピン１３ａ、１３ａは、断面円形の杆部２３と、この杆部２３の基端部に固設した、外向フランジ状で小判形の鍔部２４と、この杆部２３の先端部にこの杆部２３と同心に形成された、この杆部２３よりも小径の雄ねじ部２５とを備える。 Further, two sets of torque receiving pins 13a and 13a and a torque receiving sleeve 22 which are characteristic portions of the present invention are provided in the vicinity of the both connecting portions 6a and 6a at the both ends of both body portions 3b and 4b. , 22 are detachably provided. These torque receiving pins 13a and 13a have a high Young's modulus (not easily elastically deformed and have a high rigidity against the force in the pulling direction), and wear resistance (preferably, like iron-based alloys such as stainless steel and bearing steel). Furthermore, it is made of a metal material having excellent corrosion resistance. The shape and structure of the torque receiving pins 13a and 13a are not particularly limited as long as they can be reliably supported and fixed between the body parts 3b and 4b. In the case of the illustrated example, both the torque receiving pins 13a and 13a include a flange portion 23 having a circular cross section, an outwardly flanged oval flange portion 24 fixed to the proximal end portion of the flange portion 23, A distal end portion of the flange portion 23 is provided with a male screw portion 25 having a diameter smaller than that of the flange portion 23 formed concentrically with the flange portion 23.

又、上記両トルク受けスリーブ２２、２２も、上記両トルク受けピン１３ａ、１３ａと同様の金属材料により造られている。これら両トルク受けスリーブ２２、２２は、全体を管状に造られたもので、中心孔２６の内周面を円筒面としている。又、この中心孔２６の内径を、上記両トルク受けピン１３ａ、１３ａを構成する上記杆部２３の外径よりも僅かに（例えば０．０５〜０．２０mm）大きくしている。従って、上記中心孔２６内には上記杆部２３を、ほぼ隙間なく挿入できる。又、上記両トルク受けスリーブ２２、２２の外周面は、隅角部に面取り部２７、２７を形成した（円周方向に関して面取り部２７、２７と平面部２８、２８とを交互に連続させた）、略四角（異形八角）筒面としている。又、上記両トルク受けスリーブ２２、２２の軸方向長さＬ₂₂は、上記両ボディ部３ｂ、４ｂの互いに対向する１対の軸方向内側面２９、２９同士の間隔Ｄ₂₉よりも少し短く、前記両連結部６ａ、６ａの円周方向内側面のうちの平面部３０、３０部分の軸方向寸法Ｌ₃₀よりも大きい（Ｌ₃₀＜Ｌ₂₂＜Ｄ₂₉）。 The torque receiving sleeves 22 and 22 are also made of the same metal material as the torque receiving pins 13a and 13a. Both the torque receiving sleeves 22 and 22 are formed in a tubular shape as a whole, and the inner peripheral surface of the center hole 26 is a cylindrical surface. In addition, the inner diameter of the center hole 26 is slightly larger (for example, 0.05 to 0.20 mm) than the outer diameter of the flange portion 23 that constitutes the torque receiving pins 13a and 13a. Therefore, the flange 23 can be inserted into the center hole 26 with almost no gap. Further, the outer peripheral surfaces of the torque receiving sleeves 22 and 22 are formed with chamfered portions 27 and 27 at corner portions (the chamfered portions 27 and 27 and the flat portions 28 and 28 are alternately continued in the circumferential direction). ), A substantially square (an irregular octagon) cylindrical surface. The axial length L ₂₂ of the torque receiving sleeves 22 and ₂₂ is slightly shorter than the distance D ₂₉ between the pair of axially inner surfaces 29 and 29 facing each other of the body portions 3b and 4b. the two joining portions 6a, greater than the axial dimension L ₃₀ of the flat portion 30, 30 parts of the circumferential inner surface of _{_{6a (L 30 <L 22 <}} D 29).

上記両トルク受けスリーブ２２、２２の軸方向長さＬ₂₂を上記両軸方向内側面２９、２９及び上記両平面部３０、３０の寸法Ｄ₂₉、Ｌ₃₀との関係で上述の様に規制する事により、上記両トルク受けスリーブ２２、２２の長さ方向両端面外周縁と、前記キャリパ５ｂの内面のうちで、上記両軸方向内側面２９、２９と上記両平面部３０、３０との連続部に存在する曲面部３１、３１とを係合可能としている。即ち、上記両トルク受けスリーブ２２、２２を、上記両平面部３０、３０と平行に、且つ、これら両平面部３０、３０と適切な間隔をあけて配置した状態で、上記両トルク受けスリーブ２２、２２の長さ方向両端面外周縁のうち、上記各平面部２８、２８のうちの何れかの平面部２８の長さ方向両端部に対応する端縁が、上記各曲面部３１、３１と係合する様にしている。そして、係合した状態で、上記両トルク受けスリーブ２２、２２の、上記両トルク受けピン１３ａ、１３ａを中心とする回動を制限する（回動量を必要最小限に規制する）様にしている。 The axial length L ₂₂ of the torque receiving sleeves 22 and ₂₂ is restricted as described above in relation to the axial inner side surfaces 29 and 29 and the dimensions D ₂₉ and L ₃₀ of the flat portions 30 and _30. Thus, among the outer peripheral edges of both end surfaces in the length direction of the torque receiving sleeves 22 and 22 and the inner surface of the caliper 5b, the inner side surfaces 29 and 29 in the axial direction and the flat portions 30 and 30 are continuous. The curved surface portions 31 and 31 existing in the portion can be engaged. That is, both the torque receiving sleeves 22, 22 are arranged in parallel with the two flat portions 30, 30 and at an appropriate distance from the flat portions 30, 30. , 22 of the outer peripheral edges of both end surfaces in the length direction are edges corresponding to both end portions in the length direction of the plane portion 28 of each of the plane portions 28, 28. It engages. Then, in the engaged state, the rotation of the torque receiving sleeves 22 and 22 around the torque receiving pins 13a and 13a is limited (the amount of rotation is restricted to the minimum necessary). .

上述の様な１対のトルク受けスリーブ２２、２２は、それぞれ、上記両トルク受けピン１３ａ、１３ａにより、上記キャリパ５ｂの内部空間のうちで、上記両連結部６ａ、６ａの近傍部分に支持される。この為に、上記両トルク受けスリーブ２２、２２を、前記アウタ、インナ、両ボディ部３ｂ、４ｂ同士の間の所定位置に配置した状態で、上記両トルク受けピン１３ａ、１３ａの杆部２３を、上記両ボディ部３ｂ、４ｂの両端寄り外径寄り部分に形成した通孔３２ａ、３２ｂ及び上記両トルク受けスリーブ２２、２２の中心孔２６に挿通する。そして、前記鍔部２４を、上記アウタボディ部３ｂの外側面に形成した係合凹部３３に係合させる。この状態で、上記トルク受けピン１３ａの回転が阻止されるので、このトルク受けピン１３ａの先端部に形成した雄ねじ部２５にナット３４を螺合させる。そして、これらナット３４と上記鍔部２４との間で、上記両ボディ部３ｂ、４ｂの外側面両端寄り部分を抑え付ける。この状態で、上記両トルク受けスリーブ２２、２２の長さ方向両端面外周縁が、上記各曲面部３１、３１と係合し、上記両トルク受けピン１３ａ、１３ａに対する上記両トルク受けスリーブ２２、２２の回動量が規制（必要最小限に制限）される。 The pair of torque receiving sleeves 22 and 22 as described above are supported by the torque receiving pins 13a and 13a in the vicinity of the connecting portions 6a and 6a in the caliper 5b. The For this purpose, the flange portions 23 of the torque receiving pins 13a and 13a are placed in a state where the torque receiving sleeves 22 and 22 are arranged at predetermined positions between the outer, inner and both body portions 3b and 4b. The body portions 3b and 4b are inserted into through holes 32a and 32b formed in the outer diameter portions near both ends and the center holes 26 of the torque receiving sleeves 22 and 22, respectively. And the said collar part 24 is engaged with the engagement recessed part 33 formed in the outer surface of the said outer body part 3b. In this state, since the rotation of the torque receiving pin 13a is prevented, the nut 34 is screwed into the male screw portion 25 formed at the tip of the torque receiving pin 13a. And between these nut 34 and the said collar part 24, the part near the outer surface both ends of the said body parts 3b and 4b is suppressed. In this state, the outer peripheral edges of both end surfaces of the torque receiving sleeves 22 and 22 are engaged with the curved surface portions 31 and 31, respectively, and the torque receiving sleeves 22 and 22 with respect to the torque receiving pins 13a and 13a. The amount of rotation 22 is restricted (limited to the necessary minimum).

又、前記ロータ２の回転方向に関して、前記アウタパッド１１ａ及び前記インナパッド１２ａを構成するプレッシャプレート１５ａ、１５ａの両端縁は、上記両トルク受けピン１３ａ、１３ａに支持された上記両トルク受けスリーブ２２、２２の外周面に、当接若しくは近接対向している。上記両プレッシャプレート１５ａ、１５ａの両端縁で上記ロータ２の径方向に関して外端部は、これら両プレッシャプレート１５ａ、１５ａの中心線αに対してほぼ平行な方向に存在する、平坦面３５、３５としている。そして、これら各平坦面３５、３５と、上記両トルク受けスリーブ２２、２２の外周面に設けた平面部２８、２８とを、当接若しくは近接対向させている。これら両トルク受けスリーブ２２、２２は、それぞれの長さ方向両端面外周縁が上記各曲面部３１、３１に衝合しない範囲で、上記両トルク受けピン１３ａ、１３ａの周囲で回動可能である為、上記各平坦面３５、３５と上記各平面部２８、２８とは、対向する部分の全面に亙り、広い面積で均一に当接する。 Further, with respect to the rotation direction of the rotor 2, both end edges of the pressure plates 15a, 15a constituting the outer pad 11a and the inner pad 12a are both torque receiving sleeves 22 supported by the torque receiving pins 13a, 13a, 22 is in contact with or in close proximity to the outer peripheral surface. The flat end surfaces 35, 35 have outer end portions of the both end edges of the pressure plates 15a, 15a in a direction substantially parallel to the center line α of the pressure plates 15a, 15a. It is said. The flat surfaces 35 and 35 and the flat portions 28 and 28 provided on the outer peripheral surfaces of the torque receiving sleeves 22 and 22 are in contact with or in close proximity to each other. Both the torque receiving sleeves 22 and 22 are rotatable around the torque receiving pins 13a and 13a in such a range that the outer peripheral edges of the both longitudinal end surfaces do not collide with the curved surface portions 31 and 31, respectively. Therefore, the flat surfaces 35 and 35 and the flat portions 28 and 28 are uniformly in contact with each other over a wide area over the entire opposing portion.

又、上記ロータ２の回転方向に関して、上記両パッド１１ａ、１２ａを構成するプレッシャプレート１５ａ、１５ａの両側縁のうち、上記ロータ２の径方向に関して外端部に、それぞれこのロータ２の回転方向に突出する係止突片３６、３６を設けている。そして、これら各係止突片３６、３６と上記両トルク受けピン１３ａ、１３ａに外嵌したトルク受けスリーブ２２、２２の外周面とを係合させている。本例の場合、上記各係止突片３６、３６のうちの、上記ロータ２の径方向内側の側面を、上記両トルク受けスリーブ２２、２２の外周面に設けた平面部２８、２８のうち、上記両プレッシャプレート１５ａ、１５ａの両端縁が当接している平面部２８、２８の隣の平面部２８、２８に当接させている。そして、上記両パッド１１ａ、１２ａが、上記ロータ２の径方向内方に抜け出る事を防止している。又、上記両プレッシャプレート１５ａ、１５ａの外周縁と、前記ブリッジ部１９の内周側面と、反アンカ側のトルク受けピン１３ａに外嵌したトルク受けスリーブ２２との間にパッドクリップ１７ａを設け、上記両プレッシャプレート１５ａ、１５ａの係止突片３６、３６を上記両トルク受けスリーブ２２、２２に向け弾性的に押圧して、非制動時に上記両パッド１１ａ、１２ａががたつく事を防止している。 Further, with respect to the rotational direction of the rotor 2, out of both side edges of the pressure plates 15 a, 15 a constituting both the pads 11 a, 12 a, at the outer end portion with respect to the radial direction of the rotor 2, respectively in the rotational direction of the rotor 2. Protruding locking protrusions 36 and 36 are provided. The engaging protrusions 36 and 36 are engaged with the outer peripheral surfaces of the torque receiving sleeves 22 and 22 that are externally fitted to the torque receiving pins 13a and 13a. In the case of this example, out of the flat portions 28, 28 provided on the outer peripheral surfaces of the torque receiving sleeves 22, 22 on the radially inner side surface of the rotor 2, of the locking protrusions 36, 36. The pressure plates 15a and 15a are in contact with the flat surface portions 28 and 28 adjacent to the flat surface portions 28 and 28 with which both end edges are in contact. The two pads 11a and 12a are prevented from coming out inward in the radial direction of the rotor 2. Also, a pad clip 17a is provided between the outer peripheral edges of the pressure plates 15a, 15a, the inner peripheral side surface of the bridge portion 19, and the torque receiving sleeve 22 fitted on the torque receiving pin 13a on the anti-anchor side, The locking projections 36, 36 of the pressure plates 15a, 15a are elastically pressed toward the torque receiving sleeves 22, 22 to prevent the pads 11a, 12a from rattling during non-braking. .

上述の様に構成する本例の対向ピストン型ディスクブレーキによれば、上記両パッド１１ａ、１２ａのプレッシャプレート１５ａ、１５ａのアンカ側端縁に設けた平坦面３５、３５と、制動トルクを支承する部材である、上記両トルク受けスリーブ２２、２２の外周面に設けた平面部２８、２８との当接部の当接面積を広くできる。そして、制動時にこれら各当接部でブレーキノイズに結び付く振動が発生したり、これら各当接部に塑性変形や摩耗が生じる事を抑えられる。しかも、上記両トルク受けスリーブ２２、２２は、上記両トルク受けピン１３ａ、１３ａに対して若干の回動を可能に支持している為、制動トルク等によって、上記両パッド１１ａ、１２ａに、アンカ側のトルク受けスリーブ２２との当接部を中心として回転する等の挙動が生じた場合でも、両トルク受けスリーブ２２、２２は、外周面に設けた平面部２８、２８と上記各平坦面３５、３５とを面当たり（面接触）させながら追従する。又、これら各平坦面３５、３５と上記各平面部２８、２８との平行度を厳密に規制しなくても、これら各面３５、２８同士を、互いに対向する面同士のほぼ全体に亙り、均一に当接させられる。従って、上記当接部の面積を確保する為に、各部の形状精度を厳密に規制する必要性も低く、製造コストが嵩む事もない。又、上記両トルク受けピン１３ａの外周面と上記両トルク受けスリーブ２２、２２の内周面との嵌合は、曲率半径が近い凸円筒面と凹円筒面との嵌合であるから、これら両周面同士の当接面積も十分に広くなる。この為、これら両周面同士の当接部に関しても、制動時にこれら各当接部でブレーキノイズに結び付く振動が発生したり、これら各当接部に塑性変形や摩耗が生じる事はない。 According to the opposed piston type disc brake of the present example configured as described above, the braking torque is supported by the flat surfaces 35 and 35 provided at the end edges of the pressure plates 15a and 15a of the pads 11a and 12a on the anchor side. The abutting area of the abutting portion with the flat portions 28 and 28 provided on the outer peripheral surfaces of the torque receiving sleeves 22 and 22 as members can be increased. Further, it is possible to suppress the occurrence of vibrations associated with the brake noise at each of the contact portions during braking and the occurrence of plastic deformation and wear at each of the contact portions. Moreover, since both the torque receiving sleeves 22 and 22 support the torque receiving pins 13a and 13a so as to be slightly rotatable, the two torque receiving sleeves 22 and 22 are anchored to the pads 11a and 12a by the braking torque or the like. Even when a behavior such as rotation about the contact portion with the torque receiving sleeve 22 on the side occurs, both the torque receiving sleeves 22 and 22 are provided with the flat portions 28 and 28 provided on the outer peripheral surface and the flat surfaces 35 described above. , 35 are made to follow each other (surface contact). Further, even if the parallelism between the flat surfaces 35 and 35 and the flat portions 28 and 28 is not strictly regulated, the surfaces 35 and 28 are spread over almost the entire surfaces facing each other. Uniform contact. Therefore, in order to secure the area of the contact portion, it is not necessary to strictly regulate the shape accuracy of each portion, and the manufacturing cost does not increase. Further, the fitting between the outer peripheral surface of the torque receiving pins 13a and the inner peripheral surfaces of the torque receiving sleeves 22 and 22 is a fitting between a convex cylindrical surface and a concave cylindrical surface having a close curvature radius. The contact area between the two peripheral surfaces is also sufficiently wide. For this reason, also with respect to the abutting portions between these two peripheral surfaces, vibrations associated with brake noise are not generated at each abutting portion during braking, and plastic deformation and wear do not occur at each abutting portion.

又、本例の構造の場合には、上記両トルク受けスリーブ２２、２２の長さ方向両端面外周縁と前記各曲面部３１、３１との係合により、これら両トルク受けスリーブ２２、２２の回動量を規制（上記各面３５、２８同士を均一に当接させる為に必要とされる最小限に制限）している。従って、上記両トルク受けスリーブ２２、２２同士の間に上記両パッド１１ａ、１２ａを組み付ける以前の状態でも、これら両トルク受けスリーブ２２、２２の外周面のうち、何れかの面取り部２７が上記両パッド１１ａ、１２ａを組み付けるべき空間部分に向け、大きく突出する事はない。この為、対向ピストン型ディスクブレーキの組立時に、上記両トルク受けスリーブ２２、２２と上記両パッド１１ａ、１２ａのプレッシャプレート１５ａ、１５ａの端縁とを係合させる作業を容易に行なえる。 Further, in the case of the structure of this example, the torque receiving sleeves 22 and 22 are engaged with each other by the engagement between the outer peripheral edges of both end surfaces in the length direction and the curved surface portions 31 and 31. The amount of rotation is restricted (restricted to the minimum required to bring the surfaces 35 and 28 into contact with each other uniformly). Therefore, even in a state before the pads 11a and 12a are assembled between the torque receiving sleeves 22 and 22, the chamfered portion 27 of the outer peripheral surfaces of the torque receiving sleeves 22 and 22 is not The pads 11a and 12a do not protrude greatly toward the space where the pads 11a and 12a are to be assembled. Therefore, when assembling the opposed piston type disc brake, it is possible to easily engage the torque receiving sleeves 22 and 22 with the edges of the pressure plates 15a and 15a of the pads 11a and 12a.

又、本例の構造の場合には、上記両パッド１１ａ、１２ａを、前記ロータ２の回転方向に関して両側から挟む状態で、上記両トルク受けピン１３ａ、１３ａ及び上記両トルク受けスリーブ２２、２２を設けているので、車両が前進、後退、何れの方向に走行する場合の制動時にも、上記ブレーキノイズに結び付く振動の発生を防止できる。
しかも本例の場合には、上記両トルク受けピン１３ａ、１３ａ及び上記両トルク受けスリーブ２２、２２を利用して（これら両トルク受けスリーブ２２、２２と前記各係止突片３６、３６との係合により）、上記両パッド１１ａ、１２ａが、前記キャリパ５ｂから上記ロータ１の径方向内方に抜け出るのを防止している。この為、本例の構造によれば、前述の図７〜１０に示した従来構造に於ける係止ピン１８、１８の如き、上記両パッド１１ａ、１２ａが前記キャリパ５ｂから前記ロータ２の径方向内方に抜け出るのを防止する為の専用の機構を設ける必要がなくなり、対向ピストン型ディスクブレーキの構造の簡略化による製造コストの低減を図れる。 Further, in the case of the structure of this example, the two torque receiving pins 13a and 13a and the two torque receiving sleeves 22 and 22 are held in a state where the two pads 11a and 12a are sandwiched from both sides with respect to the rotation direction of the rotor 2. Since it is provided, it is possible to prevent the occurrence of vibrations associated with the brake noise even during braking when the vehicle travels forward or backward.
In addition, in the case of this example, the torque receiving pins 13a and 13a and the torque receiving sleeves 22 and 22 are used (the torque receiving sleeves 22 and 22 and the locking protrusions 36 and 36 are connected to each other). Thus, the pads 11a and 12a are prevented from coming out of the caliper 5b inward in the radial direction of the rotor 1. Therefore, according to the structure of this example, such as in the locking pin 18, 18 in the conventional structure shown in FIGS. 7-10 of the aforementioned, the two pads 11a, 12a from the caliper 5b of the rotor 2 diameter It is no longer necessary to provide a dedicated mechanism for preventing the inward movement of the direction, and the manufacturing cost can be reduced by simplifying the structure of the opposed piston type disc brake.

更に、本例の対向ピストン型のディスクブレーキ１ｂによれば、前記アウタ、インナ両ボディ部３ｂ、４ｂの変形を有効に抑えられ、しかもこれら両ボディ部３ｂ、４ｂの薄肉化による軽量化を図り易い構造を実現できる。即ち、これら両ボディ部３ｂ、４ｂは、前記ブリッジ部１９により互いの中間部同士を結合している。従って、制動時にこれら両ボディ部３ｂ、４ｂ同士の間に加わる、これら両ボディ部３ｂ、４ｂ同士の間隔を拡げる方向の力に拘らず、これら両ボディ部３ｂ、４ｂ同士の間隔が拡がる事はなく、制動時にもこれら両ボディ部３ｂ、４ｂの変形を有効に抑えられる。 Furthermore, according to the opposed piston type disc brake 1b of this example, deformation of the outer and inner body portions 3b and 4b can be effectively suppressed, and weight reduction can be achieved by thinning the body portions 3b and 4b. Easy structure can be realized. That is, both the body parts 3 b and 4 b are connected to each other by the bridge part 19. Accordingly, the distance between the body parts 3b and 4b is increased regardless of the force applied between the body parts 3b and 4b during braking to increase the distance between the body parts 3b and 4b. In addition, the deformation of both the body parts 3b and 4b can be effectively suppressed even during braking.

又、本例の場合には、上記ブリッジ部１９をアンカ側に偏らせると共に、反アンカ側のトルク受けピン１３ａを着脱可能としているので、上記ブリッジ部１９による上記両ボディ部３ｂ、４ｂ同士の結合剛性の確保と上記キャリパ５ｂの小型・軽量化を図りつつ、このキャリパ５ｂへの前記両パッド１１ａ、１２ａの着脱作業を容易に行なえる。この着脱作業の際には、図４に示す場合（図４はアンカ側のトルク受けピン１３ａを示している）と同様に、上記反アンカ側のトルク受けピン１３ａを取り外した状態で、上記両パッド１１ａ、１２ａを、上記ブリッジ部１９と反アンカ側の連結部６ａとの間の隙間を通じて、１対の連結部６ａ、６ａ同士の間に抜き差しする。尚、この際、アンカ側のトルク受けピン１３ａ及びトルク受けスリーブ２２は、上記キャリパ５ｂに結合したままである。上記両パッド１１ａ、１２ａの装着作業時に、上記反アンカ側のトルク受けピン１３ａ及びトルク受けスリーブ２２は、上記両パッド１１ａ、１２ａを、上記両連結部６ａ、６ａ同士の間に或る程度差し込んだ後（これら両パッド１１ａ、１２ａの反アンカ側部分が、図３に示す状態よりも、ロータ２の径方向に関して少しだけ外側に存在する状態で）、上記両ボディ部３ｂ、４ｂ同士の間に掛け渡す。上記両パッド１１ａ、１２ａの取り外し作業時には、ほぼ同じ状態で、上記反アンカ側のトルク受けピン１３ａ及びトルク受けスリーブ２２を上記両ボディ部１１ａ、１２ａ同士の間から取り外す。これら両パッド１１ａ、１２ａを上記両連結部６ａ、６ａ同士の間に組み付けた状態では、図１〜３に示す様に、上記反アンカ側のトルク受けピン１３ａを上記両ボディ部３ｂ、４ｂ同士の間に掛け渡すと共に、前記パッドクリップ１７ａを装着する。 Further, in the case of this example, the bridge portion 19 is biased toward the anchor side, and the anti-anchor side torque receiving pin 13a is detachable. It is possible to easily attach and detach the pads 11a and 12a to / from the caliper 5b while securing the coupling rigidity and reducing the size and weight of the caliper 5b. At the time of this attaching / detaching operation, in the same manner as in the case shown in FIG. 4 (FIG. 4 shows the anchor side torque receiving pin 13a), both the above-described anti-anchor side torque receiving pins 13a are removed. The pads 11a and 12a are inserted and removed between the pair of connecting portions 6a and 6a through the gap between the bridge portion 19 and the anti-anchor side connecting portion 6a. At this time, the anchor side torque receiving pin 13a and the torque receiving sleeve 22 remain coupled to the caliper 5b. During the mounting operation of the pads 11a and 12a, the torque receiving pin 13a and the torque receiving sleeve 22 on the anti-anchor side insert the pads 11a and 12a between the connecting portions 6a and 6a to some extent. After that (with the anti-anchor side portions of these pads 11a, 12a slightly outside of the state shown in FIG. 3 in the radial direction of the rotor 2), between the two body portions 3b, 4b. Hang over. When removing the pads 11a and 12a, the anti-anchor side torque receiving pin 13a and the torque receiving sleeve 22 are removed from between the body parts 11a and 12a in substantially the same state. When these pads 11a and 12a are assembled between the connecting portions 6a and 6a, the anti-anchor side torque receiving pin 13a is connected to the body portions 3b and 4b as shown in FIGS. And the pad clip 17a is attached.

［実施の形態の第２例］
図５は、請求項３、４に対応する、本発明の実施の形態の第２例に組み込むトルク受けピン１３ｂを示している。本例の対向ピストン型ディスクブレーキに組み込むトルク受けピン１３ｂは、杆部２３の外周面の軸方向に離隔した２個所位置に、それぞれ小径部３７、３７を形成している。そして、これら両小径部３７、３７にそれぞれ、硬質ゴム、硬質ビニルの如きエラストマー製で円筒状の弾性スリーブ３８、３８を設置している。これら両弾性スリーブ３８、３８の自由状態での外径は、上記杆部２３の残部、即ち、上記小径部３７、３７以外の部分の外径よりも少しだけ大きい。又、これら両小径部３７、３７を形成する位置は、上記トルク受けピン１３ｂとトルク受けスリーブ２２（図１〜４参照）とを組み立てた状態で、このトルク受けスリーブ２２の軸方向両端部内周面に対向する位置としている。従って、このトルク受けスリーブ２２を上記杆部２３に外嵌した状態では、上記両弾性スリーブ３８、３８の外周面が上記トルク受けスリーブ２２の両端部内周面に、それぞれ全周に亙り弾性的に当接する。 [Second Example of Embodiment]
FIG. 5 shows a torque receiving pin 13b to be incorporated in a second example of the embodiment of the invention corresponding to claims 3 and 4. The torque receiving pin 13b incorporated in the opposed piston type disc brake of this example has small diameter portions 37 and 37 formed at two positions spaced apart in the axial direction of the outer peripheral surface of the flange portion 23, respectively. Further, cylindrical elastic sleeves 38, 38 made of an elastomer such as hard rubber and hard vinyl are installed in both the small diameter portions 37, 37, respectively. The outer diameters of these elastic sleeves 38, 38 in a free state are slightly larger than the outer diameters of the remaining portions of the flange 23, that is, the portions other than the small diameter portions 37, 37. The positions where these small diameter portions 37 and 37 are formed are the inner circumferences of both ends in the axial direction of the torque receiving sleeve 22 in a state where the torque receiving pin 13b and the torque receiving sleeve 22 (see FIGS. 1 to 4) are assembled. The position is opposite to the surface. Therefore, in a state where the torque receiving sleeve 22 is externally fitted to the flange 23, the outer peripheral surfaces of the elastic sleeves 38 and 38 are elastically applied to the inner peripheral surfaces of both ends of the torque receiving sleeve 22 over the entire periphery. Abut.

この様な、それぞれが１対の弾性スリーブ３８、３８を装着した上記トルク受けピン１３ｂを使用した本例の対向ピストン型ディスクブレーキの場合には、両弾性スリーブ３８、３８の減衰力により、上記トルク受けピン１３ｂと上記トルク受けスリーブ２２との相対変位が緩徐に行なわれる様になる。そして、走行時や制動時の振動に伴って上記トルク受けピン１３ｂの周囲で上記トルク受けスリーブ２２ががたつく事を防止して、走行時や制動時に異音が発生する事を防止できる。 In the case of the opposed piston type disc brake of this example using the torque receiving pins 13b each having a pair of elastic sleeves 38, 38 mounted thereon, the damping force of both elastic sleeves 38, 38 causes the above-mentioned The relative displacement between the torque receiving pin 13b and the torque receiving sleeve 22 is performed slowly. Further, it is possible to prevent the torque receiving sleeve 22 from rattling around the torque receiving pin 13b due to vibration during traveling or braking, and to prevent abnormal noise from being generated during traveling or braking.

更に、本例の構造の場合には、上記トルク受けスリーブ２２の両端部内周面と対向する部分に、それぞれ弾性スリーブ３８、３８を設置している。又、この弾性スリーブ３８、３８を設置した軸方向位置は、アウタ、インナ両パッド１１ａ、１２ａを構成するプレッシャプレート１５ａ、１５ａ（図１〜３参照）の端縁に整合する位置でもある。この為本例の構造の場合には、制動時に上記両プレッシャプレート１５ａ、１５ａから上記トルク受けスリーブ２２の両端部に、ほぼ同じ大きさの力が同じく方向に加わる。この為、このトルク受けスリーブ２２を上記トルク受けピン１３ｂに対し傾斜させる方向に大きなモーメントが作用する事を防止できる。そして、上記トルク受けスリーブ２２の外周面に設けた平面部２８（図１〜４参照）と上記両プレッシャプレート１５ａ、１５ａの端縁との当接状態を安定させて、上記ブレーキノイズに結び付く振動の発生を、より有効に防止できる。上記トルク受けピン１３ｂに上記両弾性スリーブ３８、３８を装着した点以外の構成及び作用は、前述した実施の形態の第１例と同様であるから、重複する図示並びに説明は省略する。 Further, in the case of the structure of this example, elastic sleeves 38 are provided at portions facing the inner peripheral surfaces of both end portions of the torque receiving sleeve 22, respectively. The axial position where the elastic sleeves 38 and 38 are installed is also a position aligned with the edges of the pressure plates 15a and 15a (see FIGS. 1 to 3) constituting the outer and inner pads 11a and 12a. For this reason, in the case of the structure of this example, substantially the same force is applied in the same direction from both the pressure plates 15a, 15a to both ends of the torque receiving sleeve 22 during braking. For this reason, it is possible to prevent a large moment from acting in a direction in which the torque receiving sleeve 22 is inclined with respect to the torque receiving pin 13b. Then, the vibrations that stabilize the contact state between the flat surface portion 28 (see FIGS. 1 to 4) provided on the outer peripheral surface of the torque receiving sleeve 22 and the edges of the pressure plates 15a and 15a and lead to the brake noise. Can be more effectively prevented. Since the configuration and operation other than the point that both the elastic sleeves 38, 38 are attached to the torque receiving pin 13b are the same as those in the first example of the above-described embodiment, overlapping illustration and description are omitted.

本発明は、制動時にパッドに加わる制動トルクを、アウタ、インナ、両ボディ部同士の間に掛け渡したトルク受けピンにより支承する対向ピストン型ディスクブレーキであれば、図１〜４に示した構造に限らず、例えば、前述の図７〜１０に示した構造でも実施できる。
又、アウタ、インナ両パッドをトルク受けピン及びトルク受けスリーブにより支持する場合に、プレッシャプレート両端部にコ字形の延出部を設け、この部分により上記トルク受けスリーブの外周面を外径側及び内径側から挟み込む様にしても良い。この様な構成を採用すれば、制動時にパッドに作用するモーメントによりこのパッドが浮き上がる事を防止できる。 The present invention has the structure shown in FIGS. 1 to 4 as long as it is an opposed piston type disc brake that supports the braking torque applied to the pad during braking by a torque receiving pin that is spanned between the outer, inner and both body portions. For example, the structure shown in FIGS.
In addition, when both the outer and inner pads are supported by the torque receiving pin and the torque receiving sleeve, U-shaped extending portions are provided at both ends of the pressure plate, and the outer peripheral surface of the torque receiving sleeve is provided on the outer diameter side by this portion. It may be sandwiched from the inner diameter side. By adopting such a configuration, it is possible to prevent the pad from being lifted by a moment acting on the pad during braking.

本発明の実施の形態の第１例を、アウタ寄りの径方向外側から見た状態で示す斜視図。The perspective view which shows the 1st example of embodiment of this invention in the state seen from the radial direction outer side near outer. 同径方向外側から見た正投影図。The orthographic view seen from the same radial direction outer side. 図２のイ−イ断面図。II sectional drawing of FIG. 図１の右部の分解斜視図。The exploded perspective view of the right part of FIG. トルク受けピンの別例を示す斜視図で、（Ａ）は弾性スリーブと組み合わせた状態を、（Ｂ）は弾性スリーブを取り外した状態を、それぞれ示している。It is a perspective view which shows another example of a torque receiving pin, (A) has shown the state combined with the elastic sleeve, (B) has each shown the state which removed the elastic sleeve. 従来から知られているディスクブレーキの第１例を示す斜視図。The perspective view which shows the 1st example of the disk brake conventionally known. 同第２例をインナ側から見た状態で示す正投影図。The orthographic projection figure which shows the 2nd example in the state seen from the inner side. 図７の上方である、径方向外方から見た図。The figure seen from the radial direction outer side which is the upper part of FIG. 図８のロ−ロ断面図。FIG. 9 is a cross-sectional view of FIG. 図９のハ−ハ断面図。FIG. 10 is a cross-sectional view of FIG.

Explanation of symbols

１、１ａ、１ｂディスクブレーキ
２ロータ
３、３ａ、３ｂアウタボディ部
４、４ａ、４ｂインナボディ部
５、５ａ、５ｂキャリパ
６、６ａ連結部
７アウタシリンダ
８インナシリンダ
９アウタピストン
１０インナピストン
１１、１１ａアウタパッド
１２、１２ａインナパッド
１３、１３ａ、１３ｂトルク受けピン
１４結合ピン
１５、１５ａプレッシャプレート
１６ライニング
１７、１７ａパッドクリップ
１８係止ピン
１９ブリッジ部
２０脚部
２１連結部
２２トルク受けスリーブ
２３杆部
２４鍔部
２５雄ねじ部
２６中心孔
２７面取り部
２８平面部
２９軸方向内側面
３０平面部
３１曲面部
３２ａ、３２ｂ通孔
３３係合凹部
３４ナット
３５平坦面
３６係止突片
３７小径部
３８弾性スリーブ DESCRIPTION OF SYMBOLS 1, 1a, 1b Disc brake 2 Rotor 3, 3a, 3b Outer body part 4, 4a, 4b Inner body part 5, 5a, 5b Caliper 6, 6a Connection part 7 Outer cylinder 8 Inner cylinder 9 Outer piston 10 Inner piston 11, 11a Outer pad 12, 12a Inner pad 13, 13a, 13b Torque receiving pin 14 Coupling pin 15, 15a Pressure plate 16 Lining 17, 17a Pad clip 18 Locking pin 19 Bridge portion 20 Leg portion 21 Connecting portion 22 Torque receiving sleeve 23 Hook portion 24 Threaded portion 25 Male thread portion 26 Center hole 27 Chamfered portion 28 Planar portion 29 Axial inner side surface 30 Planar portion 31 Curved portion 32a, 32b Through hole 33 Engaging recess 34 Nut 35 Flat surface 36 Locking protrusion 37 Small diameter portion 38 Elastic sleeve

Claims

The outer and inner body portions provided with the rotor rotating together with the wheels, and both ends of the both body portions are connected at a radially outward position from the outer peripheral edge of the rotor with respect to the rotation direction of the rotor. A caliper composed of a pair of connecting parts, a plurality of cylinders provided opposite to each other on both body parts, and a fluid-tight fit in each of the cylinders so as to allow displacement in the axial direction of the rotor. A plurality of pistons, a plurality of pads that are respectively supported on portions facing the inner side surfaces of the two body portions that can be displaced in the axial direction, and a pressure that constitutes both the pads with respect to the rotational direction of the rotor. In a state where it is spanned between the two body parts at a portion that is opposed to at least one end edge of the plate and is radially outside the outer peripheral edge of the rotor. Vignetting and, at the opposed piston type disc brake provided with at least one torque receiving pin of the torque receiving pin, the outer circumference around the circular cross section of the rod portion, the inner peripheral surface of the center hole in the cylindrical surface A torque receiving sleeve provided with a flat portion on at least a part of the surface is rotatably fitted, and formed on the flat portion provided on the outer peripheral surface of the torque receiving sleeve and the edge of the pressure plate of both pads . An opposed piston type disc brake characterized in that flat surfaces are brought into contact with each other .

The rotation of the torque receiving sleeve around the torque receiving pin is limited by engagement between a part of the outer peripheral edge portions of both ends in the axial direction of the torque receiving sleeve and a part of the inner surface of the caliper. Item 2. The opposed piston type disc brake according to item 1.

An elastic sleeve whose outer diameter in a free state is larger than the outer diameter of the remaining portion of the flange portion is installed in a small diameter portion formed in a part of the flange portion constituting the torque receiving pin, and the outer peripheral surface of the elastic sleeve is The opposed piston type disc brake according to any one of claims 1 to 2, wherein the opposed piston type disc brake is elastically brought into contact with an inner peripheral surface of the torque receiving sleeve.

The opposed piston type disk according to claim 3, wherein the elastic sleeves are respectively installed in small diameter portions formed at portions facing the inner peripheral surfaces of both ends of the torque receiving sleeve at two axial positions of the flange portion. brake.

The opposed piston type disk according to any one of claims 1 to 4, wherein a pair of torque receiving pins are provided on both sides of the pressure plate constituting the two pads with respect to the rotational direction of the rotor. brake.

With respect to the rotation direction of the rotor, among the both side edges of the pressure plate constituting the pads, locking protrusions that protrude in the rotation direction of the rotor are provided at outer end portions with respect to the radial direction of the rotor. The engagement between each of the locking protrusions and the outer peripheral surface of the torque receiving sleeve fitted around the torque receiving pins prevents the pads from coming out radially inward of the rotor. Item 6. The opposed piston type disc brake according to item 5.