JP2007211806A - Disk brake - Google Patents

Disk brake Download PDF

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JP2007211806A
JP2007211806A JP2006029571A JP2006029571A JP2007211806A JP 2007211806 A JP2007211806 A JP 2007211806A JP 2006029571 A JP2006029571 A JP 2006029571A JP 2006029571 A JP2006029571 A JP 2006029571A JP 2007211806 A JP2007211806 A JP 2007211806A
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support
rotor
portions
pad
outer pad
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JP2006029571A
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Japanese (ja)
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Haruo Yagi
晴雄 八木
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Akebono Brake Industry Co Ltd
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Akebono Brake Industry Co Ltd
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Priority to JP2006029571A priority Critical patent/JP2007211806A/en
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Abstract

<P>PROBLEM TO BE SOLVED: To effectively prevent damage and deformation of a support 19a and an outer pad 5a in a structure capable of effectively preventing the outer pad 5a from coming off from the support 19a. <P>SOLUTION: Each pair of folding sections 44a and 44b are arranged circumferentially on both ends of the outer pad 5a so that each pair of folding sections 44a and 44b are mutually approached in a radial direction of a rotor 1. Respective outer diameter-side and inner diameter-side locking grooves 15 and 16 respectively recessed in its radial direction are arranged radially on both sides of the rotor 1 at front end portions of a pair of extended plate sections 23 and 23 extended in a direction mutually approached to an outer-side end of the support 19a. Pointed heads of respective folding sections 44a and 44b are inserted into the locking grooves 15 and 16. <P>COPYRIGHT: (C)2007,JPO&INPIT

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、特に、キャリパの、ロータを挟んだ両側部分のうち、片側のみにシリンダ及びピストンを設けた、所謂フローティングキャリパ型のディスクブレーキの改良に関する。   The present invention relates to an improvement of a so-called floating caliper type disc brake in which a cylinder and a piston are provided only on one side of both sides of a caliper sandwiching a rotor among disc brakes used for braking an automobile.

自動車の制動に使用する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、サポートに対しキャリパを軸方向の変位を自在に支持すると共に、このキャリパの、ロータを挟んだ両側部分のうち、片側のみにシリンダ及びピストンを設けたフローティングキャリパ型のものが、従来から広く知られ、実際に広く使用されている。   Various types of disc brakes have been known for use in automobile braking, but the caliper is supported by the support so that it can freely move in the axial direction. Among them, a floating caliper type in which a cylinder and a piston are provided only on one side has been widely known and widely used in practice.

又、この様なフローティングキャリパ型のディスクブレーキのうち、厚肉鋼板等の金属板に曲げ加工を施して成る金属板製サポートを使用するものも、コスト並びに重量の低減を図る面から研究が進められている。図２２〜２５は、この様な金属板製サポートを組み込んだフローティングキャリパ型ディスクブレーキの１例として、特許文献１に記載された従来構造の第１例を示している。先ず、この従来構造の第１例に就いて簡単に説明する。   Among these floating caliper-type disc brakes, those that use metal plate supports made by bending metal plates such as thick steel plates are also being studied from the viewpoint of reducing cost and weight. It has been. 22 to 25 show a first example of a conventional structure described in Patent Document 1 as an example of a floating caliper disc brake incorporating such a metal plate support. First, the first example of this conventional structure will be briefly described.

この従来構造の第１例のディスクブレーキは、車輪と共に回転するロータ１に隣接した状態で懸架装置に対し固定されるサポート２にキャリパ３を、１対のガイドピン４ａ、４ｂにより、上記ロータ１の軸方向（図２２の上下方向、図２３の左右方向）の変位自在に支持している。上記サポート２には、上記ロータ１を挟んでアウタ側（車両の幅方向に関して外側）のアウタパッド５ａ及びインナ側（車両の幅方向に関して中央側）のインナパッド５ｂを、上記ロータ１の軸方向の変位自在に支持している。又、上記キャリパ３のシリンダ部６に嵌装したピストン７の先端面（図２３の左端面）を、上記インナパッド５ｂを構成するプレッシャプレート８ｂに突き当て、上記キャリパ３のアウタ側端部に形成したキャリパ爪９の内側面を、アウタパッド５ａを構成するプレッシャプレート８ａに当接させている。   In the first example of the disc brake of the conventional structure, the caliper 3 is attached to the support 2 fixed to the suspension device in a state adjacent to the rotor 1 that rotates together with the wheel, and the rotor 1 is constituted by a pair of guide pins 4a and 4b. Is supported so as to be freely displaceable in the axial direction (vertical direction in FIG. 22, horizontal direction in FIG. 23). The support 2 includes an outer pad 5a on the outer side (outer side in the vehicle width direction) and an inner pad 5b on the inner side (center side in the vehicle width direction) across the rotor 1 in the axial direction of the rotor 1. Supports displaceability. Further, the tip end surface (left end surface in FIG. 23) of the piston 7 fitted in the cylinder portion 6 of the caliper 3 is abutted against the pressure plate 8b constituting the inner pad 5b, and is brought into contact with the outer side end portion of the caliper 3. The inner side surface of the formed caliper claw 9 is brought into contact with the pressure plate 8a constituting the outer pad 5a.

制動を行なう場合には、上記シリンダ部６内への圧油の送り込みにより、上記ピストン７が上記インナパッド５ｂを上記ロータ１の側面に押し付ける。この押し付けの反作用として、上記キャリパ３がインナ側に変位するので、上記キャリパ爪９が上記アウタパッド５ａを上記ロータ１の側面に押し付ける。この結果、このロータ１が１対のパッド５ａ、５ｂのライニング１０ａ、１０ｂにより両側から強く挟持されて、制動が行なわれる。この制動の際、これら各ライニング１０ａ、１０ｂとロータ１との摩擦に伴って上記各パッド５ａ、５ｂに加わる制動トルクは、これら各パッド５ａ、５ｂのプレッシャプレート８ａ、８ｂを支持した、上記サポート２により支承される。   When braking is performed, the piston 7 presses the inner pad 5 b against the side surface of the rotor 1 by feeding pressure oil into the cylinder portion 6. As a reaction of the pressing, the caliper 3 is displaced toward the inner side, so that the caliper claw 9 presses the outer pad 5 a against the side surface of the rotor 1. As a result, the rotor 1 is strongly held from both sides by the linings 10a and 10b of the pair of pads 5a and 5b, and braking is performed. The braking torque applied to the pads 5a and 5b due to the friction between the linings 10a and 10b and the rotor 1 during the braking is supported by the pressure plates 8a and 8b of the pads 5a and 5b. 2 is supported.

上述の様に構成し作用する従来構造の第１例の場合には、上記各パッド５ａ、５ｂに伝わる制動トルクの全部を、上記サポート２のうちで上記ロータ１の回出側（ロータ１の回転方向前方で、例えばロータ１が図２２の矢印α方向に回転する場合に、同図の右側）部分で支承する。従って、この回出側部分の強度及び剛性を確保すべく、上記サポート２のアウタ側端部に、回入側（ロータ１の回転方向後方で、例えばロータ１が図２２の矢印α方向に回転する場合に、同図の左側）、回出側両端部同士を結ぶ連結部１１を設けている。   In the case of the first example of the conventional structure configured and operated as described above, all of the braking torque transmitted to each of the pads 5a and 5b is taken out of the support 2 on the delivery side of the rotor 1 (of the rotor 1). For example, when the rotor 1 rotates in the direction of the arrow α in FIG. Accordingly, in order to ensure the strength and rigidity of the delivery side portion, the outer side end of the support 2 is connected to the entry side (the rotor 1 rotates in the direction of arrow α in FIG. In this case, a connecting portion 11 is provided to connect the both ends on the delivery side.

上述の様な従来構造の第１例に対して、サポート２のアウタ側端部の、ロータ１の径方向外側面に、アウタパッド５ａの両端部を、このロータ１の軸方向の変位自在に係止する為の係止溝を設ける事も考えられている。この様な係止溝を設けた構造の場合には、アウタパッド５ａのサポート２からの脱落をより有効に防止できる。図２６〜２７は、この様な事情に鑑みて発明された、特許文献２に記載された従来構造の第２例のディスクブレーキを、キャリパ３（図２２〜２３参照）等、一部を省略した状態で示している。   Compared to the first example of the conventional structure as described above, both ends of the outer pad 5a are freely displaceable in the axial direction of the rotor 1 on the radially outer surface of the rotor 1 at the outer side end of the support 2. It is also considered to provide a locking groove for stopping. In the case of the structure provided with such a locking groove, it is possible to more effectively prevent the outer pad 5a from falling off the support 2. FIGS. 26 to 27 show a second example of the disc brake having the conventional structure described in Patent Document 2 invented in view of such circumstances, and a part of the caliper 3 (see FIGS. 22 to 23) is omitted. Shown in the state.

このディスクブレーキは、厚肉鋼板等の金属板を曲げ加工する等により一体に造った金属板製のサポート１９と、このサポート１９に支持されたキャリパ３と、アウタパッド５ａ及びインナパッド５ｂ（図２２〜２３参照）とを備える。このうちのサポート１９は、基板部１３と、それぞれ１対ずつの、インナパッド支持部２４、２４と、連結板部２２、２２と、突出板部２３、２３とを備える。このうちの基板部１３に、車体に固定する為のボルト取り付け用の第一のねじ孔１７、１７を形成している。   The disc brake includes a metal plate support 19 integrally formed by bending a metal plate such as a thick steel plate, the caliper 3 supported by the support 19, an outer pad 5a and an inner pad 5b (FIG. 22). To 23). Of these, the support 19 includes a base plate portion 13, a pair of inner pad support portions 24, 24, connecting plate portions 22, 22, and protruding plate portions 23, 23. Of these, the board portion 13 is formed with first screw holes 17 for mounting bolts for fixing to the vehicle body.

又、上記１対のインナパッド支持部２４、２４は、上記基板部１３の周方向中間部２個所位置に、この基板部１３の外周縁側が開口する状態で、それぞれ形成している。これらインナパッド支持部２４、２４には、互いに対称形の係止切り欠き２５、２５を形成している。これら各係止切り欠き２５、２５には、インナパッド５ｂを構成するプレッシャプレート８ｂの両端部に形成した係止鉤部２６、２６を進入させる。この構成により、上記インナパッド５ｂを、サポート１９に対し、ロータ１の軸方向の変位自在に、且つ、制動時にこのインナパッド５ｂに加わる制動トルクを支承自在に支持する。   The pair of inner pad support portions 24, 24 are formed at two positions in the circumferential middle portion of the substrate portion 13 so that the outer peripheral edge side of the substrate portion 13 is open. The inner pad support portions 24, 24 are formed with locking notches 25, 25 symmetrical to each other. The locking notches 25 and 25 formed at both ends of the pressure plate 8b constituting the inner pad 5b are inserted into the locking notches 25 and 25, respectively. With this configuration, the inner pad 5b is supported with respect to the support 19 so as to be displaceable in the axial direction of the rotor 1 and to support a braking torque applied to the inner pad 5b during braking.

又、上記各連結板部２２、２２は、上記基板部１３の周方向両端部の外周縁部からアウタ側（図２６の表側）に折れ曲がったもので、車体への取付状態では、上記各連結板部２２、２２の内周面と上記ロータ１の外周縁とが対向する。そして、これら各連結板部２２、２２の先端部から上記各突出板部２３、２３が、互いに近づき合う方向に延出している。更に、これら各突出板部２３、２３の先端部の、ロータ１の径方向外側面に係止溝２７、２７を、それぞれ形成している。これら各係止溝２７、２７に、アウタパッド５ａを構成するプレッシャプレート８ａの両端部に設けた鉤部２８、２８を係止する事で、このアウタパッド５ａを、ロータ１の軸方向の変位自在に、且つ、制動時にこのアウタパッド５ａに加わる制動トルクを支承自在に支持する。   Further, each of the connecting plate portions 22 and 22 is bent from the outer peripheral edge portion of both end portions in the circumferential direction of the substrate portion 13 to the outer side (the front side of FIG. 26). The inner peripheral surfaces of the plate portions 22 and 22 are opposed to the outer peripheral edge of the rotor 1. And each said protrusion board part 23, 23 is extended in the direction which mutually approaches from the front-end | tip part of these each connection board part 22 and 22. As shown in FIG. Furthermore, locking grooves 27 and 27 are formed on the radially outer side surfaces of the rotor 1 at the tips of the protruding plate portions 23 and 23, respectively. The outer pad 5a can be displaced in the axial direction of the rotor 1 by engaging the hooks 28, 28 provided at both ends of the pressure plate 8a constituting the outer pad 5a. Moreover, the braking torque applied to the outer pad 5a during braking is supported in a freely supporting manner.

上記サポート１９には、前記キャリパ３を、ロータ１の軸方向の変位自在に支持する。この為に、上記サポート１９のロータ１回入側、回出側両端部に形成した第二のねじ孔１８、１８に、１対のガイドピン４ａ、４ｂ（図２２、２４、２５参照）の基端部を螺合・固定する。そして、これら両ガイドピン４ａ、４ｂに、キャリパ３の一部に設けたガイドシリンダ部を、ロータ１の軸方向の変位自在に外嵌する。   The caliper 3 is supported on the support 19 so as to be freely displaceable in the axial direction of the rotor 1. For this purpose, a pair of guide pins 4a, 4b (see FIGS. 22, 24, 25) are formed in the second screw holes 18, 18 formed on both ends of the support 19 on the rotor entrance and exit sides. Screw and fix the base end. And the guide cylinder part provided in a part of caliper 3 is externally fitted to these guide pins 4a and 4b so that the displacement of the rotor 1 in the axial direction is possible.

上述の図２６〜２７に示した従来構造の第２例のディスクブレーキの場合、サポート１９のアウタ側端部に１対の突出板部２３、２３を設けると共に、これら各突出板部２３、２３の先端部の径方向外側面に形成した係止溝２７、２７に、アウタパッド５ａを構成するプレッシャプレート８ａに設けた鉤部２８、２８を係止している。この為、上記サポート１９に対しアウタパッド５ａが外れる事を、より有効に防止し易くできる。しかも、上記サポート１９のアウタ側端部の強度を或る程度有効に確保し易くできる。即ち、ロータ１が図２６、２７の矢印イで示す方向に回転する場合の制動時に、アウタパッド５ａに比較的大きな制動トルクが加わる場合には、図２７に示す様に、１対の突出板部２３、２３のうち、ロータ１の回出側（図２７の右側）の突出板部２３の先端面に、上記アウタパッド５ａを構成するプレッシャプレート８ａの本体部の周方向片面（図２７の右側面）が接触する。これと共に、上記１対の突出板部２３、２３のうち、ロータ１の回入側（図２７の左側）の突出板部２３に形成した係止溝２７の周方向片側（図２７の右側）の側面に、上記プレッシャプレート８ａの回入側端部に設けた鉤部２８の周方向片面（図２７の右側面）が接触する。この場合には、回入側、回出側の突出板部２３、２３の両方で、アウタパッド５ａに加わる制動トルクがサポート１９に支承される為、これら各突出板部２３、２３の強度を過度に高くする必要がない。この為、サポート１９のアウタ側端部の強度を或る程度有効に確保し易くできる。   In the case of the disc brake of the second example of the conventional structure shown in FIGS. 26 to 27 described above, a pair of protruding plate portions 23, 23 are provided at the outer side end portion of the support 19, and these protruding plate portions 23, 23 are provided. The flanges 28, 28 provided on the pressure plate 8a constituting the outer pad 5a are locked in the locking grooves 27, 27 formed on the radially outer side surface of the tip end portion. For this reason, it is possible to more effectively prevent the outer pad 5a from being detached from the support 19. In addition, the strength of the outer end portion of the support 19 can be easily secured to some extent. That is, when a relatively large braking torque is applied to the outer pad 5a during braking when the rotor 1 rotates in the direction indicated by the arrow A in FIGS. 26 and 27, as shown in FIG. 23, 23, the circumferential surface of the main body of the pressure plate 8a constituting the outer pad 5a (the right side surface in FIG. 27) is formed on the tip surface of the protruding plate portion 23 on the outlet side (right side in FIG. 27) of the rotor 1. ) Come into contact. At the same time, of the pair of projecting plate portions 23, 23, one side in the circumferential direction (right side in FIG. 27) of the locking groove 27 formed in the projecting plate portion 23 on the turn-in side of the rotor 1 (left side in FIG. 27). The circumferential side surface (the right side surface in FIG. 27) of the flange portion 28 provided at the end of the pressure plate 8a is brought into contact with the side surface of the pressure plate 8a. In this case, since the braking torque applied to the outer pad 5a is supported by the support 19 at both of the projecting plate portions 23 and 23 on the entrance side and the exit side, the strength of each of the projecting plate portions 23 and 23 is excessively increased. There is no need to make it too high. For this reason, the strength of the outer side end portion of the support 19 can be easily ensured to some extent effectively.

但し、この様な従来構造の第２例の場合、アウタパッド５ａ及びサポート１９の損傷及び変形を抑える面からは未だ改良の余地がある。即ち、制動時には、アウタパッド５ａがロータ１により回転方向に移動するが、この場合、このアウタパッド５ａが、このロータ１の回転方向に対し、回入側端部（図２６、２７の左端部）が図２６、２７の上方にずれ易くなる。例えば、ロータが図２６、２７の矢印イで示す方向に回転している場合の制動時で、アウタパッド５ａに比較的大きな制動トルクが加わる場合には、図２７に示す様に、アウタパッド５ａの回入側の鉤部２８の周方向片面が回入側の係止溝２７の周方向片面に突き当てられ、この係止溝２７の片面部分でアウタパッド５ａに加わった制動トルクが支承される。この図２７に示した状態では、アウタパッド５ａの回出側の鉤部２８の周方向片面（図２７の左側面）は、回出側の係止溝２７の周方向片側（図２７の左側）の側面から離れた状態となる。   However, in the case of the second example having such a conventional structure, there is still room for improvement in terms of suppressing damage and deformation of the outer pad 5a and the support 19. That is, during braking, the outer pad 5a is moved in the rotational direction by the rotor 1. In this case, the outer pad 5a has a turn-in side end (left end in FIGS. 26 and 27) with respect to the rotational direction of the rotor 1. It becomes easy to shift | deviate upwards of FIG. For example, when a relatively large braking torque is applied to the outer pad 5a during braking when the rotor rotates in the direction indicated by the arrow A in FIGS. 26 and 27, the rotation of the outer pad 5a is performed as shown in FIG. One circumferential surface of the inlet flange 28 is abutted against one circumferential surface of the engagement groove 27 on the turn-in side, and the braking torque applied to the outer pad 5a is supported by one surface portion of the engagement groove 27. In the state shown in FIG. 27, the circumferential one side surface (left side surface in FIG. 27) of the outer flange portion 28 of the outer pad 5a is one circumferential side side (left side in FIG. 27) of the locking groove 27 on the delivery side. It will be in the state away from the side.

又、アウタパッド５ａを構成するライニング１０ａの回入側、回出側両端部とロータ１との接触部での摩擦力の作用方向の違いに基づき、上記アウタパッド５ａのプレッシャプレート８ａの回入側端部（図２７の左端部）が回出側端部（図２７の右端部）よりもロータ１の回転方向に対して、図２７の上方に変位する様に挙動して、傾斜する傾向となる。即ち、上記プレッシャプレート８ａの同図の左端部が同図で上方に浮き上がる様に変位し、逆に、同図の右端部は、同図で下方に沈み込む様に変位する。この状態では、同図に示す様に、アウタパッド５ａの回出側端部に設けた鉤部２８の径方向側面（図２７の下側面）が回出側の係止溝２７の底面に、アウタパッド５ａを構成するプレッシャプレート８ａの本体部の周方向片面（図２７の右面）が回出側の突出板部２３の先端面に、それぞれ十分に大きな面積を有する部分で押し付けられる。一方、上記アウタパッド５ａの回入側端部に設けた鉤部２８は、図２７の上方に変位する為、この鉤部２８と回入側の係止溝２７の周方向片面（図２７の右面）との引っ掛かり代（接触面積）が極く小さくなる可能性がある。この様に、回入側の鉤部２８と回入側の係止溝２７との引っ掛かり代が極く小さくなってしまうと、これら回入側の鉤部２８と係止溝２７との間に作用する面圧が著しく上昇し、これら鉤部２８と係止溝２７とに摩耗等の損傷を生じる可能性がある。又、この回入側の鉤部２８と回入側の突出板部２３とが大きく変形し易くなってしまう。又、この変形により、アウタパッド５ａがロータ１の回転方向に対し、より傾斜し易くなってしまう。   Further, based on the difference in the acting direction of the friction force at the contact portion between the rotor 1 and the both ends of the lining 10a constituting the outer pad 5a and the rotor 1, the end of the pressure plate 8a of the outer pad 5a. 27 (left end portion in FIG. 27) behaves so as to be displaced upward in FIG. 27 with respect to the rotation direction of the rotor 1 relative to the outlet side end portion (right end portion in FIG. 27), and tends to be inclined. . That is, the left end portion of the pressure plate 8a is displaced so as to be lifted upward in the drawing, and the right end portion of the pressure plate 8a is displaced so as to sink downward in the drawing. In this state, as shown in the figure, the radial side surface (the lower side surface in FIG. 27) of the flange portion 28 provided at the outlet side end portion of the outer pad 5a is connected to the bottom surface of the locking groove 27 on the outlet side. One circumferential surface (the right surface in FIG. 27) of the main body portion of the pressure plate 8a constituting 5a is pressed against the distal end surface of the projecting plate portion 23 on the outlet side at a portion having a sufficiently large area. On the other hand, since the flange 28 provided at the end of the outer pad 5a on the turn-in side is displaced upward in FIG. 27, one circumferential direction of the hook 28 and the engagement groove 27 on the turn-in side (the right side of FIG. 27). There is a possibility that the catching amount (contact area) with) will be extremely small. In this way, when the catching margin between the turn-in side flange 28 and the turn-in side locking groove 27 becomes extremely small, the gap between the turn-in side hook 28 and the lock groove 27 is reduced. The acting surface pressure is remarkably increased, and there is a possibility that damage such as abrasion occurs in the flange portion 28 and the locking groove 27. In addition, the hook portion 28 on the turn-in side and the protruding plate portion 23 on the turn-in side are easily deformed greatly. Further, due to this deformation, the outer pad 5 a is more easily inclined with respect to the rotation direction of the rotor 1.

尚、図２６〜２７に示した構造の場合には、アウタパッド５ａの周方向両端部で、ロータ１の径方向外側（図２６、２７の上側）に、先端部が径方向内側に折れ曲がった１対の鉤部２８、２８を設けると共に、アウタパッド５ａの、ロータ１の径方向内側（図２６、２７の下側）に、周方向両側に伸びる１対の突部２１、２１を、それぞれ設けている。但し、上述の図２６〜２７に示した構造の場合とは逆に、アウタパッド５ａの周方向両端部で、ロータの径方向内側（図２６、２７の下側）に、先端部が径方向外側に折れ曲がった１対の鉤部を設けると共に、アウタパッド５ａの、ロータ１の径方向外側（図２６、２７の上側）に、周方向両側に伸びる１対の突部を、それぞれ設ける事もできる。この際、サポート１９の周方向両端部に設ける１対の突出板部２３、２３の先端部の径方向内側面（図２６、２７の下側面）に、係止溝を形成する。そして、これら各係止溝内に、上記各鉤部を進入させる（係止自在とする）。   In addition, in the case of the structure shown in FIGS. 26-27, the front-end | tip part was bent in the radial direction inner side (upper side of FIG. 26, 27) at the radial direction both ends of the outer pad 5a at the radial direction inner side. A pair of flanges 28 and 28 are provided, and a pair of protrusions 21 and 21 extending on both sides in the circumferential direction are provided on the inner side of the outer pad 5a in the radial direction of the rotor 1 (lower side in FIGS. 26 and 27). Yes. However, contrary to the case of the structure shown in FIGS. 26 to 27 described above, at the both ends in the circumferential direction of the outer pad 5a, the tip is radially outward on the inner side in the radial direction of the rotor (lower side in FIGS. 26 and 27). In addition to providing a pair of flanges that are bent to each other, a pair of protrusions extending on both sides in the circumferential direction can also be provided on the outer side of the outer pad 5a in the radial direction of the rotor 1 (the upper side in FIGS. 26 and 27). At this time, a locking groove is formed on the radially inner side surface (the lower side surface of FIGS. 26 and 27) of the distal end portions of the pair of protruding plate portions 23 and 23 provided at both circumferential ends of the support 19. And each said collar part is made to approach in each of these latching groove | channels (it makes it latchable).

この様にアウタパッド５ａの鉤部と突部とのロータ１の径方向に関する内外を、図２６〜２７に示した構造の場合とは逆にした場合で、ロータ１が図２６〜２７の矢印イで示す方向に回転する場合の制動時でも、やはりアウタパッド５ａの回入側端部が回出側端部に対して、図２６、２７の上方に変位する様に、ロータ１の回転方向に対して傾斜する傾向となる。但し、この構造の場合には、アウタパッド５ａの回入側端部に設けた内径側の鉤部が回入側の係止溝に、十分に広い面積を有する部分で押し付けられるのに対して、アウタパッド５ａの回出側端部に設けた内径側の鉤部と、回出側の係止溝との引っ掛かり代が極く小さくなる可能性がある。この様に、回出側の鉤部と回出側の係止溝との引っ掛かり代が極く小さくなってしまう場合には、これら回出側の鉤部と係止溝との間に作用する面圧が著しく上昇する事により、これら鉤部と係止溝とに摩耗等の損傷を生じる可能性がある。又、この回出側の鉤部と回出側の係止溝とが大きく変形し易くなってしまう。又、この場合も、アウタパッド５ａがロータ１の回転方向に対し、より傾斜し易くなってしまう。   In this way, the inner and outer portions of the outer pad 5a with respect to the radial direction of the rotor 1 are reversed from the case of the structure shown in FIGS. 26, even when braking is performed in the direction indicated by the arrow, the rotation direction of the rotor 1 is such that the turn-in side end of the outer pad 5a is displaced upward in FIGS. Tend to tilt. However, in the case of this structure, the flange on the inner diameter side provided at the end of the outer pad 5a is pressed against the engagement groove on the inlet side with a portion having a sufficiently large area, There is a possibility that the catching margin between the inner diameter side flange portion provided at the outlet side end portion of the outer pad 5a and the locking groove on the outlet side is extremely small. In this manner, when the catching margin between the feeding side hook and the feeding side locking groove becomes extremely small, it acts between the feeding side hook and the locking groove. When the surface pressure is significantly increased, there is a possibility that damage such as wear may occur in the flange and the locking groove. In addition, the hook part on the outlet side and the locking groove on the outlet side are easily deformed greatly. Also in this case, the outer pad 5a is more easily inclined with respect to the rotation direction of the rotor 1.

又、この様な不都合は、金属板製のサポート１９を使用する場合だけでなく、鋳物製のサポートで、切削加工により各係止溝を形成したものを使用する場合も同様に生じる。即ち、この様な鋳物製のサポートを使用する場合でも、上述の図２６〜２７に示した従来構造の第２例と同様に、各サポートのアウタ側端部に設けた１対の突出板部の先端部の径方向片側面のみに上記各係止溝を形成した場合には、やはり制動時にアウタパッドの端部と係止溝とに摩耗等の損傷を生じたり、アウタパッドの端部とサポートの一部とが大きく変形する可能性がある。   Such inconvenience occurs not only when the metal plate support 19 is used, but also when a cast support having each locking groove formed by cutting is used. That is, even when such a cast support is used, a pair of projecting plate portions provided at the outer side end portion of each support, as in the second example of the conventional structure shown in FIGS. If each of the locking grooves is formed only on one side surface in the radial direction of the tip of the outer pad, the end of the outer pad and the locking groove are also damaged during braking, or the end of the outer pad and the support Some may be greatly deformed.

尚、上述の図２６〜２７に示した従来構造の第２例の場合、サポート１９のアウタ側端部で、回入側、回出側両端部同士を連結する連結部を省略している。但し、前述の図２２〜２５に示した従来構造の第１例の様に、サポート２のアウタ側端部で、回入側、回出側両端部同士を連結部１１により連結した構造で、この連結部１１よりもロータ１側に位置する部分に、互いに近づく方向に延出した１対の突出板部２３、２３（図２２）を形成し、これら各突出板部２３、２３の先端部の径方向片側面に係止溝を形成した構造も、従来から考えられている。但し、この様な構造の場合も、上記従来構造の第２例と同様に、やはり制動時にアウタパッド５ａの端部と係止溝とに摩耗等の損傷が生じたり、アウタパッド５ａの端部とサポート２の一部とが大きく変形する可能性がある。
尚、本発明に関連する先行技術文献として、特許文献１、２の他に、特許文献３がある。 In the case of the second example of the conventional structure shown in FIGS. 26 to 27 described above, the connecting portion that connects the both ends on the turn-in side and the turn-out side is omitted at the outer side end of the support 19. However, as in the first example of the conventional structure shown in FIGS. 22 to 25 described above, the outer side end portion of the support 2 is connected to the turn-in side and the turn-out side both ends by the connecting portion 11, A pair of protruding plate portions 23, 23 (FIG. 22) extending in a direction approaching each other is formed in a portion located on the rotor 1 side with respect to the connecting portion 11, and tip portions of these protruding plate portions 23, 23. A structure in which a locking groove is formed on one side surface in the radial direction has been conventionally considered. However, in the case of such a structure as well, as in the second example of the conventional structure described above, the end of the outer pad 5a and the engaging groove are damaged during braking, or the end of the outer pad 5a and the support are supported. 2 may be greatly deformed.
In addition to Patent Documents 1 and 2, Patent Document 3 is a prior art document related to the present invention.

実開昭５２−８０３８９号公報Japanese Utility Model Publication No. 52-80389 特開２００２−２９５５３８号公報JP 2002-295538 A 実開平１−１１６２２９号公報Japanese Utility Model Publication No. 1-116229

本発明のディスクブレーキは、この様な事情に鑑みて、サポートからアウタパッドが外れるのを有効に防止できる構造で、このアウタパッド及びサポートの損傷及び変形を有効に抑えるべく発明したものである。   In view of such circumstances, the disc brake of the present invention has a structure that can effectively prevent the outer pad from being detached from the support, and has been invented to effectively suppress damage and deformation of the outer pad and the support.

本発明のディスクブレーキは、前述の図２６〜２７に示した従来構造の第２例のディスクブレーキと同様に、車輪と共に回転するロータに隣接して車体に固定されるサポートと、このロータの軸方向両側に配置されると共に、このサポートによりこのロータの軸方向への移動可能に案内されたアウタパッド及びインナパッドと、キャリパとを備える。
又、このキャリパは、爪部と、ピストンが嵌装されるシリンダ部とを有するものであり、このピストンの押し出しに伴い、上記１対のパッドを上記ロータの側面に押圧して制動を行なう。
又、上記サポートは、上記キャリパをロータの軸方向に変位自在に支持し、車体に取り付ける為にこのロータの一方の側に隣接して設けた基板部と、この基板部に上記インナパッドを支持する為に形成されたインナパッド支持部と、この基板部の周方向両端部から上記ロータの外周縁部を越えて他方の側に伸びた１対の連結板部と、これら両連結板部の先端部から互いに近づき合う方向に延出された１対の突出板部とを備えたものである。 The disc brake of the present invention includes a support fixed to a vehicle body adjacent to a rotor rotating together with a wheel, and a shaft of the rotor, like the disc brake of the second example of the conventional structure shown in FIGS. An outer pad and an inner pad which are arranged on both sides in the direction and are guided by the support so as to be movable in the axial direction of the rotor, and a caliper.
The caliper has a claw portion and a cylinder portion into which the piston is fitted. As the piston is pushed out, the pair of pads are pressed against the side surface of the rotor to perform braking.
Further, the support supports the caliper so as to be displaceable in the axial direction of the rotor, a board part provided adjacent to one side of the rotor for mounting on the vehicle body, and the inner pad on the board part. An inner pad support portion formed for this purpose, a pair of connecting plate portions extending from the circumferential ends of the substrate portion to the other side beyond the outer peripheral edge portion of the rotor, and And a pair of projecting plate portions extending in a direction approaching each other from the tip portion.

特に、本発明のディスクブレーキに於いては、上記アウタパッドの周方向両端部にこの周方向に凹んだ１対の凹部が形成されており、上記アウタパッドの周方向両端部でこれら各凹部の開口両端部となる部分に、それぞれ１対ずつの折れ曲がり部を、これら１対の折れ曲がり部同士でロータの径方向に近づき合う様に設けている。又、上記サポートに設けられた１対の突出板部の先端部の径方向に関する両側面に、それぞれこの径方向に凹んだ外径側、内径側係止溝を設けており、これら外径側、内径側各係止溝に上記各折れ曲がり部の先端部を進入させている。
尚、本明細書及び特許請求の範囲で、「周方向」とは、特に断らない限りロータの周方向を言い、同じく「軸方向」とは、特に断らない限りロータの軸方向を言い、同じく「径方向」とは、特に断らない限りロータの径方向を言う。 In particular, in the disc brake of the present invention, a pair of recesses recessed in the circumferential direction are formed at both ends in the circumferential direction of the outer pad, and both ends of the openings of the respective recesses are formed at both ends in the circumferential direction of the outer pad. Each pair of bent portions is provided in the portion to be a portion so that the pair of bent portions approach each other in the radial direction of the rotor. Further, on both side surfaces in the radial direction of the distal end portions of the pair of protruding plate portions provided on the support, there are provided an outer diameter side and an inner diameter side locking groove which are recessed in the radial direction, respectively. The tip end portions of the respective bent portions are made to enter the respective engagement grooves on the inner diameter side.
In the present specification and claims, “circumferential direction” refers to the circumferential direction of the rotor unless otherwise specified, and “axial direction” refers to the axial direction of the rotor unless otherwise specified. The “radial direction” refers to the radial direction of the rotor unless otherwise specified.

又、より好ましくは、請求項２に記載した様に、上記アウタパッドがロータの径方向に移動する場合での、このアウタパッドが上記サポートの各突出板部に、上記径方向に接触する部分を、これら各突出板部の先端部の、上記各係止溝の底面から先端側に外れた径方向側面のみとする。   More preferably, as described in claim 2, in the case where the outer pad moves in the radial direction of the rotor, a portion where the outer pad comes into contact with the protruding plate portion of the support in the radial direction, Only the radial side surfaces of the distal end portions of these protruding plate portions are removed from the bottom surfaces of the respective locking grooves toward the distal end side.

又、より好ましくは、請求項３に記載した様に、上記サポートを金属板製とすると共に、このサポートの各突出板部の先端部に径方向両側から押圧加工を施す事により上記各係止溝を形成する。   More preferably, as described in claim 3, the support is made of a metal plate, and the locking portions are formed by pressing the tips of the protruding plate portions of the support from both sides in the radial direction. Grooves are formed.

上述の様に構成する本発明のディスクブレーキの場合、サポートのアウタ側端部に１対の突出板部を設けると共に、これら各突出板部の先端部の径方向両側面に形成した外径側、内径側各係止溝に、アウタパッドを構成するプレッシャプレートの両端部に設けた１対の折れ曲がり部を進入させている。この為、このサポートに対しアウタパッドが外れる事を、より有効に防止し易くできる。   In the case of the disc brake of the present invention configured as described above, a pair of projecting plate portions are provided at the outer side end portion of the support, and the outer diameter side formed on both radial side surfaces of the tip portions of these projecting plate portions. A pair of bent portions provided at both end portions of the pressure plate constituting the outer pad are made to enter each inner-side locking groove. For this reason, it is possible to more effectively prevent the outer pad from coming off from the support.

特に、本発明の場合、制動時にアウタパッドがロータの回転方向に対し傾斜する様に挙動する傾向となった場合でも、このアウタパッド及びサポートの損傷及び変形を有効に抑える事ができる。即ち、本発明の場合には、サポートの１対の突出板部に設けた外径側、内径側各係止溝に、アウタパッドの周方向両端部に設けた折れ曲がり部を進入させている。この為、制動時にアウタパッドの回入側の折れ曲がり部の周方向片面が回入側の外径側、内径側各係止溝の周方向片面に押し付けられつつ、アウタパッドが上記回転方向に対し、回入側端部がロータの外径側にずれる様に挙動して傾斜しようとした場合で、アウタパッドの回入側端部に設けた１対の折れ曲がり部のうち、径方向外側の折れ曲がり部と外径側係止溝との引っ掛かり代が減少しても、回入側の径方向内側の折れ曲がり部と内径側係止溝との引っ掛かり代を増大させる事ができる。この為、回入側の各折れ曲がり部と各係止溝との接触部に作用する面圧が上昇するのを抑える事ができる。又、車両が後進する際の制動時には、アウタパッドの回入側、回出側、及び、サポートの突出板部の回入側、回出側が、車両の前進時の場合とは逆になる。この場合、アウタパッドがロータの回転方向に対し傾斜する方向も、車両の前進時とは逆になる。そして、この場合にも、車両の前進時とは回入側、回出側が逆になった状態での、回入側の各折れ曲がり部と回入側の各係止溝との接触部に作用する面圧が上昇するのを抑える事ができる。この結果、車両の前進、後進に拘らず、制動時のアウタパッド及びサポートの損傷及び変形を有効に抑える事ができる。又、このアウタパッドがロータの回転方向に対し傾斜するのを有効に抑える事ができる。   In particular, in the case of the present invention, even when the outer pad tends to behave so as to be inclined with respect to the rotation direction of the rotor during braking, damage and deformation of the outer pad and the support can be effectively suppressed. That is, in the case of the present invention, the bent portions provided at both ends in the circumferential direction of the outer pad are inserted into the outer-diameter side and inner-diameter side engaging grooves provided in the pair of protruding plate portions of the support. For this reason, during braking, the outer pad is rotated with respect to the rotational direction while the circumferential one side of the bent portion of the outer pad on the feeding side is pressed against the outer circumferential side of each of the locking grooves on the outer diameter side and the inner diameter side. Of the pair of bent portions provided at the end of the outer pad on the turn-in side of the outer pad, when the inlet-side end portion behaves so as to shift toward the outer diameter side of the rotor, the outer-side bent portion and the outer Even if the hooking allowance with the diameter side locking groove is reduced, the hooking allowance between the bent portion on the radially inward side and the inner diameter side locking groove can be increased. For this reason, it can suppress that the surface pressure which acts on the contact part of each bending part and each latching groove on the turning-in side rises. Further, at the time of braking when the vehicle moves backward, the turn-in side and the turn-out side of the outer pad and the turn-in side and the turn-out side of the protruding plate portion of the support are opposite to those when the vehicle is moving forward. In this case, the direction in which the outer pad is inclined with respect to the rotational direction of the rotor is also opposite to that when the vehicle is moving forward. In this case as well, it acts on the contact portion between each bent portion on the turn-in side and each locking groove on the turn-in side in a state where the turn-in side and the turn-out side are reversed from when the vehicle moves forward. It is possible to suppress the surface pressure from increasing. As a result, damage and deformation of the outer pad and the support during braking can be effectively suppressed regardless of whether the vehicle is moving forward or backward. Further, it is possible to effectively suppress the outer pad from being inclined with respect to the rotation direction of the rotor.

又、請求項２に記載した構成によれば、制動時にアウタパッドがロータの回転方向に対し傾斜しようとする際に、このアウタパッドのサポートと接触する部分を、ロータから制動トルクを受けるライニングに近い部分とし易くできる。この為、上記アウタパッドの強度をより有効に確保し易くできる。   According to the second aspect of the present invention, when the outer pad is inclined with respect to the rotation direction of the rotor during braking, the portion that contacts the support of the outer pad is the portion close to the lining that receives the braking torque from the rotor. And easy to do. For this reason, it is possible to easily ensure the strength of the outer pad more effectively.

又、請求項３に記載した構成によれば、サポートのアウタ側端部に外径側、内径側各係止溝を形成する作業を短時間で行なえ、しかも、これら各係止溝の形状精度を高くする事を容易に行なえる。   Further, according to the configuration described in claim 3, the operation of forming the outer diameter side and inner diameter side locking grooves on the outer side end of the support can be performed in a short time, and the shape accuracy of each locking groove is also improved. Can be easily increased.

［本発明の実施の形態の第１例］
図１〜１０は、本発明のディスクブレーキの実施の形態の第１例を示している。尚、本例のディスクブレーキの特徴は、アウタパッド５ａの周方向両端部とサポート１９ａのアウタ側端部との係止部の構造を工夫した点にある。その他の部分の構造、例えば、キャリパ３（図２２、２３参照）の構造等は、前述の図２２〜２５に示した従来構造の第１例の場合と同様である。この為、この従来構造の第１例と同等部分には同一符号を付して、重複する説明を省略若しくは簡略にし、以下、本例の特徴部分並びに上記従来構造の第１例と異なる部分を中心に説明する。 [First example of embodiment of the present invention]
FIGS. 1-10 has shown the 1st example of embodiment of the disc brake of this invention. The disc brake of this example is characterized in that the structure of the engaging portion between the circumferential direction both ends of the outer pad 5a and the outer side end of the support 19a is devised. The structure of other parts, for example, the structure of the caliper 3 (see FIGS. 22 and 23) is the same as that of the first example of the conventional structure shown in FIGS. For this reason, the same parts as those in the first example of the conventional structure are denoted by the same reference numerals, and redundant description is omitted or simplified. Hereinafter, the characteristic parts of the present example and the parts different from the first example of the conventional structure are described. The explanation is centered.

本例のディスクブレーキは、前述の図２２〜２５に示した従来構造の第１例のディスクブレーキと同様に、サポート１９ａと、このサポート１９ａによりロータ１の軸方向への移動可能に案内されたアウタパッド５ａ（図１）及びインナパッド５ｂ（図２）と、キャリパ３とを備える。このうちのサポート１９ａは、前述の図２６〜２７に示した従来構造の第２例のサポート１９と同様に、厚肉鋼板等の金属板を曲げ加工する等により一体に造ったもので、ロータ１に関してインナ側（図１の裏側、図２の表側）に設けた略コ字形の基板部１３ａと、それぞれ１対ずつの連結板部２２、２２及び突出板部２３、２３とを備える。又、上記基板部１３ａの周方向両端寄り部分に、インナパッド５ｂを構成するプレッシャプレート８ｂの両端部に設けた係止突部８１、８１（図２）を係止自在なインナパッド支持部２４ａ、２４ａを設けている。これらインナパッド支持部２４ａ、２４ａは、上記基板部１３ａの周方向両端寄り部分の内側面に、互いに向き合う様に開口する状態で形成した断面コ字形の係止溝８０、８０（図２）を備える。制動時にロータ１からインナパッド５ｂに加わる制動トルクは、上記各係止溝８０、８０の周方向に向いた内側面でサポート１９ａに支承される。即ち、上記各インナパッド支持部２４ａ、２４ａは、インナパッド５ｂの係止突部８１、８１の周方向側面がロータ１の回転方向と同方向に押し付けられる、所謂押しアンカとなる。   The disc brake of this example was guided so as to be movable in the axial direction of the rotor 1 by the support 19a and the support 19a in the same manner as the disc brake of the first example of the conventional structure shown in FIGS. The outer pad 5a (FIG. 1), the inner pad 5b (FIG. 2), and the caliper 3 are provided. Of these, the support 19a is integrally formed by bending a metal plate such as a thick steel plate as in the case of the support 19 of the second example of the conventional structure shown in FIGS. 1 is provided with a substantially U-shaped substrate portion 13a provided on the inner side (the back side in FIG. 1, the front side in FIG. 2), and a pair of connecting plate portions 22 and 22 and protruding plate portions 23 and 23, respectively. Further, inner pad support portions 24a that can freely lock the locking protrusions 81 and 81 (FIG. 2) provided at both ends of the pressure plate 8b that constitutes the inner pad 5b at both ends in the circumferential direction of the substrate portion 13a. , 24a are provided. The inner pad support portions 24a and 24a have U-shaped locking grooves 80 and 80 (FIG. 2) formed on the inner side surfaces of the substrate portion 13a near the both ends in the circumferential direction so as to open to face each other. Prepare. The braking torque applied from the rotor 1 to the inner pad 5b during braking is supported by the support 19a on the inner surface of each of the locking grooves 80, 80 facing in the circumferential direction. That is, the inner pad support portions 24 a and 24 a are so-called push anchors in which the circumferential side surfaces of the locking protrusions 81 and 81 of the inner pad 5 b are pressed in the same direction as the rotation direction of the rotor 1.

特に、本例の場合には、サポートのアウタ側（図１の表側、図２の裏側）に設けた上記各突出板部２３、２３の先端部の、ロータ１の径方向に関する外側面（図１、９、１０の上側面）に外径側係止溝１５、１５を、同じくロータ１の径方向に関する内側面（図１、９、１０の下側面）に内径側係止溝１６、１６を、それぞれ形成している。そして、これら各外径側係止溝１５、１５と各内径側係止溝１６、１６とに、アウタパッド５ａの周方向両端部にそれぞれ１対ずつ設けた折れ曲がり部４４ａ、４４ｂの先端部を係止自在としている。即ち、このアウタパッド５ａを構成するプレッシャプレート８ａの周方向両端部に、この周方向に凹んだ断面コ字形の１対の凹部４５、４５を形成している。又、上記プレッシャプレート８ａの周方向両端部で、これら各凹部４５、４５の開口両端部となる部分に、それぞれ１対ずつの折れ曲がり部４４ａ、４４ｂを、互いにロータ１の径方向に近づき合う様に設けている。そして、これら各折れ曲がり部４４ａ、４４ｂの先端部を、上記外径側、内径側各係止溝４４ａ、４４ｂに進入させている（係止自在としている）。又、本例の場合には、サポート１９ａとアウタパッド５ａとを、図１、３に示す様な位置関係に配置した状態で、このアウタパッド５ａの周方向両端部に形成した各凹部４５、４５の奥部の内面を構成する第一〜第五の側面４６〜５０（図３、１０）のうち、径方向内側に向いた第二の側面４７を除く、第一、第三〜第五の側面４６、４８〜５０と、上記サポート１９ａに設けた各突出板部２３、２３の先端部の周方向に向いた側面及び径方向内側面６０、及び、外径側、内径側各係止溝１５、１６の周方向片面との間に、周方向又は径方向の隙間をそれぞれ設けている。尚、本例の場合、非制動時には、図３に示す様に、各突出板部２３の先端部の径方向外側面８３を上記第二の側面４７に突き当てている。但し、非制動時に、これら両面８３、４７間に隙間をあけて、各突出板部２３の先端部の径方向内側面６０を上記第四の側面４９に突き当てる様にしても良い。この場合、各突出板部２３の内径側係止溝１６の底面と、アウタパッド５ａの内径側折れ曲がり部４４ｂの径方向外側面との間に隙間を設ける。   In particular, in the case of this example, the outer side surface in the radial direction of the rotor 1 (see FIG. 1) at the tip of each of the protruding plate portions 23, 23 provided on the outer side of the support (the front side in FIG. 1 and the back side in FIG. 2). Outer diameter side locking grooves 15 and 15 on the upper side surface of 1, 9, 10 and inner diameter side locking grooves 16 and 16 on the inner side surface (the lower side surface of FIGS. Are formed respectively. Then, the outer end side locking grooves 15 and 15 and the inner diameter side locking grooves 16 and 16 are respectively engaged with the distal end portions of the bent portions 44a and 44b provided in pairs at both circumferential ends of the outer pad 5a. It can be stopped. That is, a pair of recesses 45, 45 having a U-shaped cross section recessed in the circumferential direction are formed at both ends in the circumferential direction of the pressure plate 8a constituting the outer pad 5a. In addition, a pair of bent portions 44a and 44b are brought close to each other in the radial direction of the rotor 1 at both ends of the pressure plate 8a in the circumferential direction at the opening end portions of the recesses 45 and 45, respectively. Provided. And the front-end | tip part of each these bending parts 44a and 44b is made to enter into each said outer diameter side and inner diameter side locking groove 44a, 44b (it can be locked). Further, in the case of this example, the support 19a and the outer pad 5a are arranged in the positional relationship as shown in FIGS. 1 and 3, and the recesses 45, 45 formed at both ends in the circumferential direction of the outer pad 5a. Of the first to fifth side surfaces 46 to 50 (FIGS. 3 and 10) constituting the inner surface of the inner portion, the first and third to fifth side surfaces excluding the second side surface 47 facing inward in the radial direction. 46, 48 to 50, side surfaces facing the circumferential direction of the distal end portions of the projecting plate portions 23, 23 provided on the support 19a and the radially inner side surface 60, and the outer diameter side and inner diameter side locking grooves 15 , 16 circumferential circumferential or radial gaps are provided respectively. In the case of this example, at the time of non-braking, as shown in FIG. 3, the radially outer side surface 83 of the tip portion of each protruding plate portion 23 abuts against the second side surface 47. However, at the time of non-braking, a gap may be provided between the both surfaces 83 and 47 so that the radially inner side surface 60 of the tip portion of each protruding plate portion 23 abuts against the fourth side surface 49. In this case, a gap is provided between the bottom surface of the inner diameter side locking groove 16 of each protruding plate portion 23 and the radially outer side surface of the inner diameter side bent portion 44b of the outer pad 5a.

又、本例の場合、上記サポート１９ａを次の様にして造っている。先ず、厚肉鋼板等の金属板を打ち抜き成形する事により、図４に示す様な素板２０を造る。この素板２０は、前記基板部１３ａ及びインナパッド支持部２４ａ、２４ａに対応する形状を加工している。又、上記素板２０の周方向両端部に、それぞれが前記各連結板部２２、２２及び各突出板部２３、２３（図１参照）を構成する、１対の腕部１４、１４を、互いに同方向に延出させている。又、上記基板部１３ａの周方向両端部に１対のインナパッド支持部２４ａ、２４ａを設けている。   In the case of this example, the support 19a is manufactured as follows. First, a base plate 20 as shown in FIG. 4 is made by stamping and forming a metal plate such as a thick steel plate. The base plate 20 has a shape corresponding to the substrate portion 13a and the inner pad support portions 24a and 24a. In addition, a pair of arm portions 14, 14, each constituting the connecting plate portions 22, 22 and the protruding plate portions 23, 23 (see FIG. 1), are provided at both ends in the circumferential direction of the base plate 20. They extend in the same direction. A pair of inner pad support portions 24a and 24a are provided at both ends in the circumferential direction of the substrate portion 13a.

次いで、上記素板２０を構成する１対の腕部１４、１４に曲げ加工を施す事により、図８に示す様な、全体をＬ字形に構成した中間素材５１を造る。即ち、この曲げ加工により、上記基板部１３ａに対応する部分の両端部外周縁からほぼ直角に折れ曲がった、１対の連結板部２２、２２と、これら各連結板部２２、２２の先端部に互いに近づく方向に延出した、１対の突出板部２３、２３とを有する、中間素材５１を得る。この為に、本例の場合には、図４〜８に示す様な曲げ加工装置２９を使用する。この曲げ加工装置２９は、互いに上下方向に対向する第一の上型３０及び第一の下型３１と、互いに上下方向に対向する第二の上型３２及び第二の下型３３とを備える。このうちの第一の上型３０及び第一の下型３１は、上記素板２０の基板部１３ａ寄り部分を挟持する機能を有する。又、上記第一の上型３０は、上方に設けた支持部分３７（図８）と共に昇降自在となっている。これに対して、第一の下型３１は、基台３４の上面に、上下方向に伸縮自在な弾性部材３５を介して、昇降自在に支持している。この弾性部材３５は、スプリングを備えたもので、曲げ加工の力に対応する為にスプリング力が高く設定されている。又、上記弾性部材３５の下端部は、上記基台３４の上面に設けられた溝部５８に固定されている。   Next, by bending the pair of arm portions 14 and 14 constituting the base plate 20, an intermediate material 51 having an overall L shape as shown in FIG. 8 is produced. That is, by this bending process, a pair of connecting plate portions 22 and 22 bent substantially at right angles from the outer peripheral edges of both ends of the portion corresponding to the substrate portion 13a, and the tip portions of these connecting plate portions 22 and 22 are formed. An intermediate material 51 having a pair of protruding plate portions 23 and 23 extending in a direction approaching each other is obtained. For this reason, in this example, a bending apparatus 29 as shown in FIGS. 4 to 8 is used. The bending apparatus 29 includes a first upper mold 30 and a first lower mold 31 that face each other in the vertical direction, and a second upper mold 32 and a second lower mold 33 that face each other in the vertical direction. . Among these, the first upper mold 30 and the first lower mold 31 have a function of sandwiching a portion of the base plate 20 close to the substrate portion 13a. The first upper mold 30 can be raised and lowered together with a support portion 37 (FIG. 8) provided above. On the other hand, the first lower mold 31 is supported on the upper surface of the base 34 so as to be movable up and down via an elastic member 35 that can expand and contract in the vertical direction. The elastic member 35 includes a spring, and the spring force is set high in order to cope with the bending force. The lower end of the elastic member 35 is fixed to a groove 58 provided on the upper surface of the base 34.

又、上記第一の下型３１の上面は、上記素板２０の基板部１３ａ寄り部分を、がたつきなく設置可能な形状としている。即ち、上記第一の下型３１の上面の一端部（図４〜６、８の右端部）に第一の壁部５３を、他端部（図４〜６、８の左端部）の長さ方向（図４、６の上下方向、図５、８の表裏方向）中央部に第二の壁部５４を、それぞれ形成している。又、上記第一の壁部５３の片面（図４〜６、８の左側面）に、上記素板２０の基端部に設けた１対の突部５５、５５を進入自在な凹部５６、５６を形成している。上記第一の下型３１の上面のうち、上記第一、第二の壁部５３、５４から外れた部分を、上記基板部１３ａ寄り部分を載置自在な載置面４１としている。上記基板部１３ａに設けた凹部５７内に上記第二の壁部５４を進入させつつ、上記載置面４１に上記基板部１３ａ寄り部分を設置した状態で、上記素板２０の第一の下型３１に対するずれを、上記第一、第二の壁部５３、５４により規制する。   Further, the upper surface of the first lower mold 31 has a shape in which a portion near the substrate portion 13a of the base plate 20 can be installed without rattling. That is, the first wall 53 is placed on one end (the right end in FIGS. 4 to 6 and 8) of the upper surface of the first lower mold 31, and the length of the other end (the left end in FIGS. 4 to 6 and 8). A second wall portion 54 is formed at the center in the vertical direction (the vertical direction in FIGS. 4 and 6 and the front and back direction in FIGS. 5 and 8). Further, on one side of the first wall portion 53 (the left side surface in FIGS. 4 to 6 and 8), a pair of protrusions 55, 55 provided at the base end portion of the base plate 20 are allowed to enter a recess 56. 56 is formed. Of the upper surface of the first lower mold 31, the portion that is removed from the first and second wall portions 53, 54 is a mounting surface 41 on which the portion closer to the substrate portion 13 a can be mounted. While the second wall portion 54 is inserted into the recess 57 provided in the substrate portion 13a, the first lower surface of the base plate 20 is placed with the portion close to the substrate portion 13a installed on the placement surface 41. The displacement with respect to the mold 31 is restricted by the first and second wall portions 53 and 54.

一方、上記第二の上型３２は、下方に突出する１対の脚部３６、３６を有するもので、前記支持部分３７（図８）と共に昇降自在となっている。これら各脚部３６、３６の下面は、水平方向に対し、先端に向かう程第一の上型３０及び第一の下型３１から離れる方向に傾斜した、第一の傾斜面３８、３８としている。又、上記第二の下型３３は、上記基台３４の上面に、上記第一の下型３１に対する水平方向の遠近動を可能に支持しており、片側（図４〜６、８の左側）上面に、それぞれが上記各第一の傾斜面３８、３８と平行な、水平方向に対し傾斜した１対の第二の傾斜面３９、３９を形成している。この様な構成により、上記第二の上型３２が下降するのに伴って、上記各第一の傾斜面３８、３８と各第二の傾斜面３９、３９とが係合すると、これら両傾斜面３８、３９同士の押し付け合いにより、上記第二の下型３３が上記第一の下型３１に近づく方向（図４〜６、８の右方）に移動する。即ち、上記各第一、第二の傾斜面３８、３９がカム面としての役目を果たす。又、上記第二の下型３３の他側（図４〜６、８の右側）上面に、下方に向かう程第一の下型３１に近づく方向に傾斜した傾斜面４０を形成している。この傾斜面４０は、上記第一の下型３１の上面に設けた、上記素板２０を設置可能な載置面４１を含む仮想平面に対し、ほぼ直交している。   On the other hand, the second upper mold 32 has a pair of leg portions 36, 36 projecting downward, and is movable up and down together with the support portion 37 (FIG. 8). The lower surfaces of these leg portions 36 and 36 are first inclined surfaces 38 and 38 that are inclined in a direction away from the first upper mold 30 and the first lower mold 31 toward the tip with respect to the horizontal direction. . The second lower mold 33 is supported on the upper surface of the base 34 so as to be able to move in the horizontal direction with respect to the first lower mold 31, and is on one side (the left side of FIGS. 4 to 6 and 8). ) A pair of second inclined surfaces 39, 39 are formed on the upper surface, each of which is parallel to the first inclined surfaces 38, 38 and inclined with respect to the horizontal direction. With such a configuration, when the first inclined surfaces 38, 38 and the second inclined surfaces 39, 39 are engaged with each other as the second upper mold 32 is lowered, both the inclined surfaces are engaged. By pressing the surfaces 38 and 39 together, the second lower mold 33 moves in a direction approaching the first lower mold 31 (rightward in FIGS. 4 to 6 and 8). That is, the first and second inclined surfaces 38 and 39 function as cam surfaces. Further, an inclined surface 40 is formed on the upper surface of the other side of the second lower mold 33 (the right side in FIGS. 4 to 6 and 8) so as to be closer to the first lower mold 31 as it goes downward. The inclined surface 40 is substantially orthogonal to a virtual plane provided on the upper surface of the first lower mold 31 and including the mounting surface 41 on which the base plate 20 can be installed.

又、本例の場合には、上記第二の下型３３の他側上面で、傾斜面４０を形成した部分の幅方向（図４、６の上下方向、図５、８の裏表方向）中央部に、受け部となる受け部材４２を結合固定している。この受け部材４２は、直方体状で、ボルト等の締結部材により、上記第二の下型３３に一体に結合固定している。そして、この受け部材４２の幅方向（図４、６の上下方向、図５、８の裏表方向）両側面を、互いに平行な平坦面４３、４３としている。例えば、締結部材としてボルトを使用する場合には、上記受け部材４２の厚さ方向に貫通する図示しない通孔に挿通させたボルトの先端部を、上記第二の下型３３に形成した図示しないねじ孔に螺合・緊締する事で、上記受け部材４２をこの第二の下型３３に一体に結合固定する。   Further, in the case of this example, the width direction (vertical direction in FIGS. 4 and 6, the front and back direction in FIGS. 5 and 8) of the portion where the inclined surface 40 is formed on the other upper surface of the second lower mold 33. A receiving member 42 serving as a receiving portion is coupled and fixed to the portion. The receiving member 42 has a rectangular parallelepiped shape, and is integrally coupled and fixed to the second lower mold 33 by a fastening member such as a bolt. Then, both side surfaces of the receiving member 42 in the width direction (the vertical direction in FIGS. 4 and 6 and the back and front direction in FIGS. 5 and 8) are flat surfaces 43 and 43 parallel to each other. For example, when a bolt is used as the fastening member, the tip of the bolt inserted into a through hole (not shown) that penetrates the receiving member 42 in the thickness direction is formed on the second lower mold 33 (not shown). The receiving member 42 is integrally coupled and fixed to the second lower mold 33 by screwing and tightening into the screw hole.

更に、上記受け部材４２の各平坦面４３、４３同士の間隔（幅方向の全長）Ｌ42（図４）を、上記素板２０の１対の腕部１４、１４の先端部内側面同士の間隔Ｌ14（図４）よりも僅かに小さくしている（Ｌ42＜Ｌ14）。例えば、上記第一の下型３１の上面に設けた載置面４１に上記素板２０の基板部１３ａ寄り部分を設置し、この素板２０の１対の腕部１４、１４の先端部内側面同士の間に上記受け部材４２を位置させた状態で、これら内側面とこの受け部材４２の各平坦面４３、４３とを、それぞれ０．１mm以下の隙間を介して対向させる。 Further, the distance (total length in the width direction) L 42 (FIG. 4) between the flat surfaces 43, 43 of the receiving member 42 is the distance between the inner surfaces of the tip end portions of the pair of arm portions 14, 14 of the base plate 20. It is slightly smaller than L 14 (FIG. 4) (L 42 <L 14 ). For example, a portion closer to the substrate portion 13 a of the base plate 20 is installed on the mounting surface 41 provided on the top surface of the first lower mold 31, and the inner side surfaces of the tip portions of the pair of arm portions 14 and 14 of the base plate 20. With the receiving member 42 positioned between them, these inner side surfaces and the flat surfaces 43, 43 of the receiving member 42 are opposed to each other with a gap of 0.1 mm or less.

上述の様に構成する曲げ加工装置２９により、上記素板２０を曲げ加工する作業は、次の様にして行なう。先ず、上記第一の上型３０と第一の下型３１とを上下方向に離隔させた状態で、この第一の下型３１の載置面４１に、素材２０の基板部１３ａ寄り部分を設置する。又、この素材２０の１対の腕部１４、１４の先端部同士の間に、上記第二の下型３３に結合固定した受け部材４２を位置させる。この状態で、第一の上型３０を下降させ、上記素材２０を、この第一の上型３０と上記第一の下型３１との間で挟持し、加圧する。又、これに伴って、この第一の下型３１を下降させる。そして、上記第一の上型３０が第一の下型３１との間で素材２０を挟持するのよりも少し遅れて、前記第二の上型３２の下降により、第一、第二の各傾斜面３８、３９同士の押し付け合いを行なわせ、前記第二の下型３３を上記第一の下型３１に向け移動させる。この結果、上記素板２０の１対の腕部１４、１４の先半部を上記第二の下型３３の上面に押し付けつつ、上記素板２０の基板部１３ａ寄り部分が上記第一の上型３０及び第一の下型３１により下方に押し下げられる。そして、上記１対の腕部１４、１４が、図４の鎖線イ、イ部分に沿って（鎖線イ、イ部分を起点として）略Ｌ字形に曲げられ、図８に示す様に、１対ずつの連結板部２２と突出板部２３とを備えた中間素材５１となる。   The bending process of the base plate 20 by the bending apparatus 29 configured as described above is performed as follows. First, in a state where the first upper mold 30 and the first lower mold 31 are separated in the vertical direction, a portion closer to the substrate portion 13a of the material 20 is placed on the placement surface 41 of the first lower mold 31. Install. A receiving member 42 coupled and fixed to the second lower mold 33 is positioned between the tip portions of the pair of arm portions 14, 14 of the material 20. In this state, the first upper mold 30 is lowered, and the material 20 is sandwiched between the first upper mold 30 and the first lower mold 31 and pressed. Along with this, the first lower mold 31 is lowered. The first upper mold 30 and the first lower mold 31 sandwich the material 20 with a slight delay, and the second upper mold 32 descends to cause each of the first and second molds The inclined surfaces 38 and 39 are pressed against each other, and the second lower mold 33 is moved toward the first lower mold 31. As a result, while the first half of the pair of arm portions 14, 14 of the base plate 20 is pressed against the upper surface of the second lower mold 33, the portion close to the substrate portion 13a of the base plate 20 is the first upper portion. It is pushed down by the mold 30 and the first lower mold 31. Then, the pair of arms 14 and 14 are bent into a substantially L shape along the chain lines i and i in FIG. 4 (starting from the chain lines i and i), as shown in FIG. The intermediate material 51 includes the connecting plate portion 22 and the protruding plate portion 23.

又、この様な曲げ加工に伴って、鎖線イ、イ部分に沿って直角に曲げられるので、上記１対の腕部１４、１４の先端部内側面が互いに近づく方向に力が加わる。そして、これら内側面が上記受け部材４２の各平坦面４３、４３に対し、直線方向又は曲線方向に、又はこれらを組み合わせながら相対移動しつつ摺接する。これにより、上記各腕部１４、１４の先端部の変形が、上記受け部材４２により規制される。更に、上記第一、第二の上型３０、３２がストロークの最下点（下死点）に達した状態で、図８に示す様に、この第一の上型３０の下面と、第二の下型３３の上面との間で上記突出板部２３の先端部を含む上記素板２０が押圧されて、これら各突出板部２３の先端部が所望の形状に矯正される。又、上述の様に、曲げ加工時に上記各腕部１４、１４の先端部が変形しようとして、これら各先端部の内側面が受け部材４２の各平坦面４３、４３に摺接し、そのまま上記各突出板部２３の先端部内側面が互いの平行度を高精度に維持する。   In addition, along with such bending, bending is performed at right angles along the chain line a and b, so that a force is applied in a direction in which the inner side surfaces of the tip portions of the pair of arm portions 14 and 14 approach each other. Then, these inner side surfaces are in sliding contact with the respective flat surfaces 43, 43 of the receiving member 42 while moving relative to each other in a linear direction or a curved direction, or a combination thereof. As a result, the deformation of the tip portions of the arm portions 14 and 14 is restricted by the receiving member 42. Further, with the first and second upper molds 30 and 32 reaching the lowest point (bottom dead center) of the stroke, as shown in FIG. The base plate 20 including the tip portion of the protruding plate portion 23 is pressed between the upper surfaces of the two lower molds 33, and the tip portions of the protruding plate portions 23 are corrected to a desired shape. Further, as described above, the inner end surfaces of the respective arm portions 14 and 14 are slidably contacted with the respective flat surfaces 43 and 43 of the receiving member 42 so that the distal end portions of the respective arm portions 14 and 14 are deformed at the time of bending. The inner side surface of the tip end portion of the protruding plate portion 23 maintains the parallelism of each other with high accuracy.

この様に上記素材２０は、曲げ加工装置２９により周方向両端部を曲げられて、１対ずつの連結板部２２と突出板部２３とを備えた中間素材５１（図８）となる。曲げ加工後、第一の上型３０と第二の上型３２とは元の位置に上昇し、第二の下型３３も第一の下型３１から離れる方向に移動するので、上記中間素材５１を上記曲げ加工装置２９から容易に取り外せる。尚、第二の上型３２の上昇後は、第二の下型３３が、引っ張りばね又は圧縮ばねを備えた図示しない移動機構により図８の左方に移動する。この様に、本例の場合には、素板２０に曲げ加工を施す際に、１対の腕部１４、１４の先端部同士の間に配置した受け部材４２によりこれら腕部１４、１４の先端部の変形を規制している。この為、上記中間素材５１により構成するサポート１９ａで、これら各腕部１４、１４の先端部の所望形状からのずれを僅少にでき、このサポート１９ａを、能率良く、且つ精度良く造れる。   In this way, the material 20 is bent at both ends in the circumferential direction by the bending device 29 to become an intermediate material 51 (FIG. 8) having a pair of connecting plate portions 22 and protruding plate portions 23. After bending, the first upper mold 30 and the second upper mold 32 are raised to their original positions, and the second lower mold 33 is also moved away from the first lower mold 31. 51 can be easily removed from the bending apparatus 29. Note that after the second upper mold 32 is raised, the second lower mold 33 is moved to the left in FIG. 8 by a moving mechanism (not shown) provided with a tension spring or a compression spring. Thus, in the case of this example, when bending the base plate 20, the arm portions 14, 14 are arranged by the receiving member 42 disposed between the tip portions of the pair of arm portions 14, 14. The deformation of the tip is restricted. For this reason, the support 19a constituted by the intermediate material 51 can minimize the deviation of the tip portions of the arm portions 14 and 14 from the desired shape, and the support 19a can be manufactured efficiently and accurately.

又、上記中間素材５１は、次工程で、各突出板部２３、２３に外径側、内径側各係止溝１５、１６（図１、３、９、１０）を形成するプレス加工を施して、第二中間素材（図示せず）とする。このプレス加工は、上述の様にして造った中間素材５１の各突出板部２３、２３を、径方向両側から図示しない押型と受型とにより挟持して、これら各突出板部２３、２３を押圧する事により行なう。又、このプレス加工の際、これら各突出板部２３、２３の互いに対向する先端面を、押型と一体に動作するガイド型（図示せず）により抑える。尚、このガイド型を静止型として、上記受型と一体に構成する事もできる。   Further, the intermediate material 51 is subjected to a pressing process for forming the outer diameter side and inner diameter side locking grooves 15 and 16 (FIGS. 1, 3, 9, and 10) in the protruding plate portions 23 and 23 in the next step. The second intermediate material (not shown). In this pressing, the protruding plate portions 23 and 23 of the intermediate material 51 made as described above are sandwiched between a pressing die and a receiving die (not shown) from both sides in the radial direction, and each of the protruding plate portions 23 and 23 is held. This is done by pressing. Further, at the time of the press working, the front end surfaces of the protruding plate portions 23 and 23 facing each other are suppressed by a guide die (not shown) that operates integrally with the pressing die. Note that the guide mold can be a stationary mold and can be configured integrally with the receiving mold.

この様にして、各突出板部２３、２３に外径側、内径側各係止溝１５、１６を形成した第二中間素材は、次の工程で、基板部１３ａに第一、第二のねじ孔１７、１８（図１、２）を形成する事により、前述の図１〜３に示したサポート１９ａの完成品とする。この様なサポート１９ａは、前記アウタパッド５ａを構成するプレッシャプレート８ａの両端部にそれぞれ１対ずつ形成した折れ曲がり部４４ａ、４４ｂを、上記各突出板部２３、２３の外径側、内径側各係止溝１５、１６内に進入させ、ロータ１の軸方向の変位自在に係止自在とする。   In this way, the second intermediate material in which the outer diameter side and inner diameter side locking grooves 15 and 16 are formed in the projecting plate portions 23 and 23 is the first and second in the substrate portion 13a in the next step. By forming the screw holes 17 and 18 (FIGS. 1 and 2), the support 19a shown in FIGS. Such a support 19a has bent portions 44a and 44b formed in pairs at both end portions of the pressure plate 8a constituting the outer pad 5a, respectively, on the outer diameter side and inner diameter side of the projecting plate portions 23 and 23, respectively. It is made to enter into the stop grooves 15 and 16 so that the rotor 1 is displaceable in the axial direction.

次に、前記各インナパッド支持部２４ａ、２４ａ（図１、２、９）に、前記インナパッド５ｂを構成するプレッシャプレート８ｂの両端部を、ロータ１の軸方向の変位自在に係止する。又、上記サポート１９ａの基板部１３ａに形成した第一のねじ孔１７、１７に螺合、緊締したボルトにより、上記基板部１３ａを車体に結合固定すると共に、上記第二のねじ孔１８、１８に、キャリパ３を支持する為のガイドピン４ａ、４ｂ（図２２、２３参照）の基端部を結合固定する。この部分の構成及び作用に就いては、前述の図２２〜２３に示した構造を含め、従来から広く知られているものであるから、詳しい図示並びに説明は省略する。   Next, both end portions of the pressure plate 8b constituting the inner pad 5b are locked to the inner pad support portions 24a and 24a (FIGS. 1, 2 and 9) so as to be displaceable in the axial direction of the rotor 1. The board portion 13a is coupled and fixed to the vehicle body by bolts that are screwed and tightened into the first screw holes 17 and 17 formed in the board portion 13a of the support 19a, and the second screw holes 18 and 18 are fixed. Further, the base end portions of the guide pins 4a and 4b (see FIGS. 22 and 23) for supporting the caliper 3 are coupled and fixed. Since the structure and operation of this part are well known in the art including the structures shown in FIGS. 22 to 23, detailed illustration and description thereof will be omitted.

更に、本例の場合には、上記アウタパッド５ａがロータ１の径方向外方に移動する場合での、このアウタパッド５ａが上記サポート１９ａの各突出板部２３、２３に、上記径方向に接触する部分を、これら各突出板部２３、２３の先端部の、上記各内径側係止溝１６、１６の底面から先端側（図３の右側）に外れた径方向内側面６０及び径方向外側面８３（図３、１０）のみとしている。この為に、例えば、上記アウタパッド５ａに設けた１対の折れ曲がり部４４ａ、４４ｂのうちの内径側（図１、３、９、１０の下側）の折れ曲がり部４４ｂの径方向外側面と、各内径側係止溝１６、１６の底面との間の径方向の隙間ｄ1 （図３）を、アウタパッド５ａの周方向両端部に設けた凹部４５、４５の径方向外方に向いた第四の側面４９と、各突出板部２３、２３の先端部の、内径側係止溝１６、１６の底面から先端側に外れた径方向内側面６０との間の径方向の隙間ｄ2 （図３）よりも大きくしている（ｄ1 ＞ｄ2 ）。 Further, in the case of this example, the outer pad 5a contacts the protruding plate portions 23, 23 of the support 19a in the radial direction when the outer pad 5a moves radially outward of the rotor 1. The radially inner side surface 60 and the radially outer side surface of the projecting plate portions 23, 23 are separated from the bottom surface of the inner diameter side locking grooves 16, 16 to the distal end side (right side in FIG. 3). Only 83 (FIGS. 3 and 10). For this purpose, for example, the radially outer surface of the bent portion 44b on the inner diameter side (the lower side of FIGS. 1, 3, 9, and 10) of the pair of bent portions 44a and 44b provided on the outer pad 5a, A radial gap d 1 (FIG. 3) between the inner surface side locking grooves 16 and 16 and the bottom surface of the inner side locking grooves 16, 16 is directed to the outer side in the circumferential direction of the outer pad 5 a. Radial gap d 2 between the side surface 49 and the radially inner side surface 60 of the distal end portion of each of the protruding plate portions 23, 23, which deviates from the bottom surface of the inner diameter side locking grooves 16, 16 toward the distal end side (see FIG. 3) (d 1 > d 2 ).

制動時には、アウタパッド５ａ及びインナパッド５ｂに加わる制動トルクが、上記各突出板部２３、２３のうちの少なくとも一方の突出板部２３と、上記各インナパッド支持部２４ａ、２４ａのうちの一方のインナパッド支持部２４ａとで、サポート１９ａに支承さ
れる。特に、アウタパッド５ａに加わる制動トルクは、次の様にしてサポート１９ａに支承される。
例えば、ロータ１が図１、２、９に矢印イで示す方向に回転する場合での、軽制動時の様に、アウタパッド５ａに加わる制動トルクが小さい場合には、サポート１９ａの前記各突出板部２３、２３のうち、ロータ１の回転方向前側である、回出側（図１、９の右側）の突出板部２３の先端面５９部分のみに、アウタパッド５ａを構成するプレッシャプレート８ａの周方向片側（図１、９の右側）に設けた凹部４５の周方向側面が接触する。そして、上記回出側の突出板部２３の先端面５９部分のみで、上記制動トルクを支承する。これに対して、急制動時の様に上記制動トルクが大きい場合には、上記サポート１９ａの回出側の突出板部２３がロータ１の回出側（両突出板部２３、２３同士を引き離す方向）に弾性変形する。そして、図９、１０に示す様に、上記回出側の突出板部２３が回出側に変形する事を主原因として、上記各突出板部２３、２３のうち、回入側（図９の左側）の突出板部２３に形成した外径側、内径側各係止溝１５、１６の周方向片側（図９、１０の右側）の側面に、アウタパッド５ａを構成するプレッシャプレート８ａの周方向他側（回入側）に設けた１対の折れ曲がり部４４ａ、４４ｂの周方向片面（図９、１０の右側面）が接触し、上記回入側の突出板部２３の外径側、内径側各係止溝１５、１６部分と、上記回出側の突出板部２３の先端面５９部分との両方で、上記制動トルクを支承する。この場合には、上記回入側の各係止溝１５、１６部分が所謂引きアンカの役目を果たし、上記回出側の突出板部２３の先端面５９部分が所謂押しアンカの役目を果たし、これら引きアンカと押しアンカとの両方で上記制動トルクを支承する。これにより、本例の場合には、上記制動トルクが大きい場合でも、サポート１９ａの制動時の変形を効率良く小さく抑える事ができる。 During braking, the braking torque applied to the outer pad 5a and the inner pad 5b is caused by at least one of the protruding plate portions 23, 23 and one of the inner pad support portions 24a, 24a. It is supported by the support 19a with the pad support 24a. In particular, the braking torque applied to the outer pad 5a is supported by the support 19a as follows.
For example, when the braking torque applied to the outer pad 5a is small as in the case of light braking when the rotor 1 rotates in the direction indicated by the arrow A in FIGS. Of the portions 23 and 23, only the front end surface 59 of the protruding plate portion 23 on the delivery side (right side in FIGS. 1 and 9), which is the front side in the rotation direction of the rotor 1, is the circumference of the pressure plate 8a constituting the outer pad 5a. The circumferential side surface of the recess 45 provided on one side of the direction (the right side of FIGS. 1 and 9) comes into contact. The braking torque is supported only by the front end surface 59 portion of the projecting plate portion 23 on the delivery side. On the other hand, when the braking torque is large as in the case of sudden braking, the projecting plate part 23 on the delivery side of the support 19a separates the projecting side of the rotor 1 (both projecting plate parts 23, 23 from each other). Direction). Then, as shown in FIGS. 9 and 10, the main reason is that the protruding plate portion 23 on the outlet side is deformed to the outlet side. On the side surface on one side in the circumferential direction (right side in FIGS. 9 and 10) of the outer diameter side and inner diameter side locking grooves 15 and 16 formed in the protruding plate portion 23 on the left side) of the pressure plate 8 a constituting the outer pad 5 a. One side in a circumferential direction (the right side surface in FIGS. 9 and 10) of a pair of bent portions 44a and 44b provided on the other side of the direction (turn-in side) is in contact, The braking torque is supported by both the inner diameter side locking grooves 15 and 16 and the tip end surface 59 of the projecting plate 23 on the outlet side. In this case, the engaging grooves 15 and 16 on the turn-in side serve as so-called pull anchors, and the front end surface 59 part of the projecting plate 23 on the turn-out side serves as a so-called push anchor. The braking torque is supported by both the pull anchor and the push anchor. Thereby, in the case of this example, even when the braking torque is large, the deformation of the support 19a during braking can be efficiently suppressed to a small level.

但し、上記回出側の突出板部２３の先端面５９とアウタパッド５ａの回出側の凹部４５の周方向側面との周方向の隙間、並びに、上記回入側の外径側、内径側各係止溝１５、１６の周方向片面とアウタパッド５ａの回入側の各折れ曲がり部４４ａ、４４ｂの周方向片面との周方向の隙間の関係を調整する事により、上記制動トルクが小さい場合に、上記回入側の外径側、内径側各係止溝１５、１６の周方向片面に回入側の各折れ曲がり部４４ａ、４４ｂを接触させ、これら回入側の外径側、内径側各係止溝１５、１６部分のみで上記制動トルクを支承し、制動トルクが大きい場合に、上記回出側の突出板部２３の先端面５９部分と上記回入側の外径側、内径側各係止溝１５、１６部分との両方で上記制動トルクを支承する様にする事もできる。   However, the circumferential clearance between the distal end surface 59 of the projecting plate portion 23 on the delivery side and the circumferential side surface of the recess 45 on the delivery side of the outer pad 5a, and the outer diameter side and inner diameter side of the delivery side When the braking torque is small by adjusting the relationship between the circumferential gaps between the circumferential one side of the locking grooves 15 and 16 and the respective bent parts 44a and 44b on the turning-around side of the outer pad 5a, The bent portions 44a and 44b on the turn-in side are brought into contact with one circumferential surface of the engaging grooves 15 and 16 on the outer diameter side and the inner diameter side of the turn-in side, and the outer diameter side and the inner diameter side of the turn-in side are respectively engaged. When the braking torque is supported only by the stop grooves 15 and 16 and the braking torque is large, the front end surface 59 portion of the projecting plate portion 23 on the delivery side and the outer diameter side and inner diameter side of the delivery side are respectively connected. The braking torque can be supported by both the stop grooves 15 and 16.

上述の様に構成する本例のディスクブレーキの場合には、サポート１９ａのアウタ側端部に１対の突出板部２３、２３を設けると共に、これら各突出板部２３、２３の先端部に形成した外径側、内径側各係止溝１５、１６に、アウタパッド５ａを構成するプレッシャプレート８ａの周方向両端部に設けた各折れ曲がり部４４ａ、４４ｂの先端部を進入させている。この為、上記サポート１９ａに対しアウタパッド５ａが外れる事を、より有効に防止し易くできる。しかも、本例の場合には、前述の図２６〜２７に示した従来構造の第２例と同様に、サポート１９ａのアウタ側端部の強度を或る程度有効に確保し易くできる。又、サポート１９ａのアウタ側端部（図１の表側端部、図２の裏側端部）で、ロータ１回入側（ロータ１の回転方向後側）とロータ１回出側（ロータ１の回転方向前側）とを連結する連結部を省略している為、この連結部を省略できる分、サポート１９ａを備えたディスクブレーキのコストを低減できると共に、設置スペースの有効利用を図れる。   In the case of the disc brake of this example configured as described above, a pair of protruding plate portions 23, 23 are provided at the outer side end portion of the support 19a, and are formed at the distal end portions of these protruding plate portions 23, 23. The distal end portions of the bent portions 44a and 44b provided at both end portions in the circumferential direction of the pressure plate 8a constituting the outer pad 5a are made to enter the outer diameter side and inner diameter side locking grooves 15 and 16, respectively. For this reason, it is possible to more effectively prevent the outer pad 5a from being detached from the support 19a. Moreover, in the case of this example, as in the second example of the conventional structure shown in FIGS. 26 to 27 described above, the strength of the outer side end portion of the support 19a can be easily secured to some extent. Further, at the outer end of the support 19a (the front end of FIG. 1, the back end of FIG. 2), the rotor 1 entry side (rotation direction rear side of the rotor 1) and the rotor 1 exit side (of the rotor 1) Since the connecting portion for connecting to the front side in the rotational direction is omitted, the cost of the disc brake provided with the support 19a can be reduced and the installation space can be effectively used as much as this connecting portion can be omitted.

しかも、本例の場合には、制動時にアウタパッド５ａがロータ１の回転方向に対し傾斜する様に挙動する傾向となった場合でも、このアウタパッド５ａ及びサポート１９ａの損傷及び変形を有効に抑える事ができる。即ち、本例の場合には、サポート１９ａの１対の突出板部２３、２３に設けた外径側、内径側各係止溝１５、１６に、アウタパッド５ａの周方向両端部に設けた折れ曲がり部４４ａ、４４ｂの先端部を進入させている。この為、例えば、図９、１０に示す様に、急制動時に、アウタパッド５ａの回入側（図９の左側）の折れ曲がり部４４ａ、４４ｂの周方向片面が回入側の外径側、内径側各係止溝１５、１６の周方向片面に押し付けられつつ、上記アウタパッド５ａが上記回転方向に対し、回入側端部（図９の左端部）がロータ１の外径側（図９、１０の上側）にずれる様に挙動して傾斜しようとした場合で、アウタパッド５ａの回入側端部に設けた１対の折れ曲がり部４４ａ、４４ｂのうち、回入側の径方向外側の折れ曲がり部４４ａと外径側係止溝１５との引っ掛かり代が減少しても、径方向内側の折れ曲がり部４４ｂと内径側係止溝１６との引っ掛かり代を増大させる事ができる。この為、回入側の各折れ曲がり部４４ａ、４４ｂと各係止溝１５、１６との接触部に作用する面圧が上昇するのを抑える事ができる。   Moreover, in the case of this example, even when the outer pad 5a tends to be inclined with respect to the rotation direction of the rotor 1 during braking, damage and deformation of the outer pad 5a and the support 19a can be effectively suppressed. it can. That is, in the case of this example, the outer side and inner side locking grooves 15 and 16 provided in the pair of protruding plate parts 23 and 23 of the support 19a are bent at the circumferential ends of the outer pad 5a. The tip portions of the portions 44a and 44b are advanced. For this reason, for example, as shown in FIGS. 9 and 10, during sudden braking, one circumferential direction of the bent portions 44 a and 44 b on the turn-in side (the left side in FIG. 9) of the outer pad 5 a is the outer diameter side and inner diameter on the turn-in side. The outer pad 5a is pressed against the one side in the circumferential direction of each of the side locking grooves 15 and 16, and the turn-in side end (left end in FIG. 9) is on the outer diameter side of the rotor 1 (FIG. 9, Of the pair of bent portions 44a and 44b provided at the end of the turn-in side of the outer pad 5a. Even if the catching allowance between 44a and the outer diameter side engaging groove 15 decreases, the catching allowance between the radially inner bent portion 44b and the inner diameter side engaging groove 16 can be increased. For this reason, it can suppress that the surface pressure which acts on the contact part of each bending part 44a, 44b and each locking groove 15 and 16 by the side of entrance is raised.

又、車両が後進する際の制動時には、アウタパッド５ａの回入側、回出側、及び、サポート１９ａの突出板部２３、２３の回入側、回出側が、それぞれ車両の前進時の場合とは逆になる。この場合、アウタパッド５ａがロータ１の回転方向に対し傾斜する方向も、車両の前進時の場合とは逆になる。   Further, when braking when the vehicle is moving backward, the turning-in side and the turning-out side of the outer pad 5a and the turning-in side and the drawing-out side of the protruding plate portions 23 and 23 of the support 19a are respectively when the vehicle is moving forward. Is reversed. In this case, the direction in which the outer pad 5a is inclined with respect to the rotational direction of the rotor 1 is also opposite to that when the vehicle is moving forward.

例えば、車両の前進時には、ロータ１が図９に矢印イで示す方向に回転し、急制動時に回入側（図９の左側）の各係止溝１５、１６の周方向側面に、アウタパッド５ａの回入側端部の各折れ曲がり部４４ａ、４４ｂの周方向側面が押し付けられる。これに対して、車両の後進時には、ロータ１が、図９の矢印イで示す方向とは逆方向に回転し、急制動時に、同図の右側に存在する、回入側の各係止溝１５、１６の周方向側面に、やはり同図の右側に存在する、アウタパッド５ａの回入側端部の各折れ曲がり部４４ａ、４４ｂの周方向側面が押し付けられる。又、この場合には、アウタパッド５ａのライニング１０ａの周方向端部とロータ１とに作用する摩擦力の作用方向の違いに基づき、アウタパッド５ａの、図９の右端部に存在する回入側端部がロータ１の回転方向に対し外径側（同図の上側）にずれる様に挙動して傾斜する。そして、この場合には、図９の右側に存在するアウタパッド５ａの回入側端部に設けた各折れ曲がり部４４ａ、４４ｂのうち、外径側の折れ曲がり部４４ａと外径側係止溝１５の周方向側面との引っ掛かり代が減少するのに対して、回入側の内径側の折れ曲がり部４４ｂと内径側係止溝１６の周方向側面との引っ掛かり代を増大できる。この為、車両の前進時の場合とは回入側、回出側が逆になった状態での、回入側の各折れ曲がり部４４ａ、４４ｂと回入側の各係止溝１５、１６との接触部に作用する面圧が上昇するのを抑える事ができる。この結果、車両の前進、後進に拘らず、制動時のアウタパッド５ａ及びサポート１９ａの損傷及び変形を有効に抑える事ができる。又、この変形を抑える事ができる為、このアウタパッド５ａがロータ１の回転方向に対し傾斜するのを有効に抑える事ができる。   For example, when the vehicle moves forward, the rotor 1 rotates in the direction indicated by the arrow A in FIG. 9, and the outer pad 5a is placed on the circumferential side surface of each of the locking grooves 15 and 16 on the turn-in side (left side in FIG. 9) during sudden braking. The circumferential side surfaces of the bent portions 44a and 44b at the end portion on the turn-in side are pressed. On the other hand, when the vehicle moves backward, the rotor 1 rotates in the direction opposite to the direction indicated by the arrow A in FIG. The circumferential side surfaces of the bent portions 44a and 44b at the end of the outer pad 5a that are also present on the right side of FIG. Further, in this case, based on the difference in the acting direction of the frictional force acting on the circumferential end of the lining 10a of the outer pad 5a and the rotor 1, the turn-in side end of the outer pad 5a present at the right end of FIG. The part behaves and tilts so as to shift to the outer diameter side (upper side in the figure) with respect to the rotation direction of the rotor 1. In this case, of the bent portions 44a and 44b provided at the end of the outer pad 5a existing on the right side of FIG. 9, the outer bent portion 44a and the outer diameter locking groove 15 are formed. While the hook margin with the circumferential side surface decreases, the hook margin between the bent portion 44b on the inner diameter side on the turn-in side and the circumferential side surface of the inner diameter side locking groove 16 can be increased. For this reason, when the vehicle is moving forward, the turn-in side and the turn-out side are reversed, and the bent portions 44a and 44b on the turn-in side and the locking grooves 15 and 16 on the turn-in side are formed. An increase in the surface pressure acting on the contact portion can be suppressed. As a result, it is possible to effectively suppress damage and deformation of the outer pad 5a and the support 19a during braking regardless of whether the vehicle is moving forward or backward. Further, since this deformation can be suppressed, it is possible to effectively suppress the outer pad 5a from being inclined with respect to the rotation direction of the rotor 1.

又、本例の場合には、上記アウタパッド５ａがロータ１の径方向外側に移動する場合での、このアウタパッド５ａが上記サポート１９ａの各突出板部２３、２３に、上記径方向に接触する部分を、これら各突出板部２３、２３の先端部の、上記各内径側係止溝１６、１６の底面から先端側に外れた、径方向内側面６０及び径方向外側面８３のみとしている。この為、制動時にアウタパッド５ａがロータ１の回転方向に対し傾斜しようとする際に、このアウタパッド５ａのサポート１９ａと接触する部分を、ロータ１から制動トルクを受けるライニング１０ａ、１０ａ（図１、９）に近い部分とし易くできる。この為、上記アウタパッド５ａの強度をより有効に確保し易くできる。   In the case of this example, when the outer pad 5a moves outward in the radial direction of the rotor 1, the outer pad 5a is in contact with the protruding plate portions 23, 23 of the support 19a in the radial direction. These are only the radially inner side surface 60 and the radially outer side surface 83 of the distal end portions of the projecting plate portions 23, 23 that are detached from the bottom surface of the inner diameter side locking grooves 16, 16 toward the distal end side. For this reason, when the outer pad 5a is inclined with respect to the rotation direction of the rotor 1 during braking, the portions of the outer pad 5a that come into contact with the support 19a are linings 10a and 10a that receive braking torque from the rotor 1 (FIGS. 1 and 9). ) Can be made close to the part. For this reason, it is possible to easily ensure the strength of the outer pad 5a more effectively.

又、本例の場合には、上記サポート１９ａを金属板製とすると共に、このサポート１９ａの各突出板部２３、２３の先端部を径方向両側から押圧加工を施す事により前記外径側、内径側各係止溝１５、１６を形成している。この為、サポート１９ａのアウタ側端部にこれら各係止溝１５、１６を形成する作業を短時間で行なえ、しかも、これら各係止溝１５、１６の形状精度を高くする事を容易に行なえる。   Further, in the case of this example, the support 19a is made of a metal plate, and the distal end portions of the projecting plate portions 23, 23 of the support 19a are pressed from both sides in the radial direction, whereby the outer diameter side, Inner diameter side locking grooves 15 and 16 are formed. Therefore, the operation of forming the locking grooves 15 and 16 at the outer end of the support 19a can be performed in a short time, and the shape accuracy of the locking grooves 15 and 16 can be easily increased. The

尚、本例の場合には、車両の走行時（非制動時）に、図３に示した様に、各突出板部２３の先端部の径方向外側面８３を、アウタパッド５ａの周方向両端部に形成した各凹部４５の奥部の内面を構成する第二の側面４７に突き当てている。但し、本発明は、非制動時に、各突出板部２３の径方向内側面６０を、アウタパッド５ａの各凹部４５の奥部の内面を構成する第四の側面４９に突き当てた状態とする事もできる。この様な場合でも制動時には、上述の図９、１０に示したのと同様に、回入側の折れ曲がり部４４ａ、４４ｂと回入側の係止溝１５、１６との接触部に作用する面圧の上昇を抑える事ができる。この為、アウタパッド５ａ及びサポート１９ａの損傷及び変形を有効に抑える事ができ、アウタパッド５ａがロータ１の回転方向に対し傾斜するのを有効に抑える事ができる。   In the case of this example, when the vehicle is running (during non-braking), as shown in FIG. 3, the radially outer surface 83 at the tip of each protruding plate 23 is connected to both ends in the circumferential direction of the outer pad 5a. It abuts against the second side surface 47 that constitutes the inner surface of the back of each recess 45 formed in the portion. However, in the present invention, the non-braking state is such that the radially inner side surface 60 of each protruding plate portion 23 abuts against the fourth side surface 49 constituting the inner surface of the inner portion of each recess 45 of the outer pad 5a. You can also. Even in such a case, at the time of braking, as shown in FIGS. 9 and 10 described above, the surface acting on the contact portion between the bent portions 44a and 44b on the turn-in side and the locking grooves 15 and 16 on the turn-on side. The rise in pressure can be suppressed. For this reason, damage and deformation of the outer pad 5a and the support 19a can be effectively suppressed, and the inclination of the outer pad 5a with respect to the rotation direction of the rotor 1 can be effectively suppressed.

又、本例の場合、アウタパッド５ａがロータ１の周方向に移動する際に、各凹部４５の内面の第一、第五の側面４６、５０（図３、１０）が係止溝１５、１６の周方向片面（図３、１０の右側面）に突き当たる事はあっても、各係止溝１５、１６の周方向他面（図３、１０の左側面）に、各折れ曲がり部４４ａ、４４ｂの周方向側面が接触する事はない。即ち、この接触は、アウタパッド５ａの凹部４５の第三の側面４８が突出板部２３の先端面（図３、１０の右端面）に突き当たる事で阻止される。又、上記各係止溝１５、１６の底面に各折れ曲がり部４４ａ、４４ｂの径方向側面は殆ど接触しない。但し、制動時にロータ１からアウタパッド５ａに加わる制動トルクが大きくなった場合には、各突出板部２３、２３の先端部と各折れ曲がり部４４ａ、４４ｂとのうちの少なくとも何れかが変形し、各折れ曲がり部４４ａ、４４ｂの径方向側面の何れかが各係止溝１５、１６の底面の何れかに接触する可能性はある。   In the case of this example, when the outer pad 5 a moves in the circumferential direction of the rotor 1, the first and fifth side surfaces 46 and 50 (FIGS. 3 and 10) of the inner surface of each recess 45 are the locking grooves 15 and 16. 4a, 44b, 44b on the other circumferential surface (left side surface in FIGS. 3 and 10) of each locking groove 15, 16 There is no contact between the circumferential side surfaces. That is, this contact is prevented by the third side surface 48 of the concave portion 45 of the outer pad 5a abutting against the front end surface of the protruding plate portion 23 (the right end surface in FIGS. 3 and 10). Further, the radial side surfaces of the bent portions 44a and 44b hardly contact the bottom surfaces of the locking grooves 15 and 16, respectively. However, when the braking torque applied to the outer pad 5a from the rotor 1 during braking increases, at least one of the tip portions of the protruding plate portions 23 and 23 and the bent portions 44a and 44b is deformed, There is a possibility that any one of the side surfaces in the radial direction of the bent portions 44a and 44b may contact one of the bottom surfaces of the respective locking grooves 15 and 16.

又、本例の場合、非制動時に、アウタパッド５ａの各折れ曲がり部４４ａ、４４ｂの径方向側面の何れもが、各突出板部２３、２３の各係止溝１５、１６の底面に接触しない様にしている。但し、非制動時に、外径側の折れ曲がり部４４ａ（又は内径側の折れ曲がり部４４ｂ）の径方向側面が外径側係止溝１５（又は内径側係止溝１６）の底面に突き当たる様にして、その代わりに、アウタパッド５ａの各凹部４５の第二の側面４７（又は第四の側面４９）と各突出板部２３、２３の先端部の径方向外側面８３（又は径方向内側面６０）との間に径方向の隙間が形成される様にしても良い。   Further, in the case of this example, at the time of non-braking, none of the radial side surfaces of the bent portions 44a and 44b of the outer pad 5a is in contact with the bottom surfaces of the locking grooves 15 and 16 of the protruding plate portions 23 and 23. I have to. However, during non-braking, the radial side surface of the outer diameter side bent portion 44a (or inner diameter side bent portion 44b) abuts against the bottom surface of the outer diameter side locking groove 15 (or inner diameter side locking groove 16). Instead, the second side surface 47 (or the fourth side surface 49) of each recess 45 of the outer pad 5a and the radially outer side surface 83 (or the radially inner side surface 60) of the tip of each protruding plate portion 23, 23 are used. A gap in the radial direction may be formed between the two.

［本発明の実施の形態の第２例］
次に、図１１〜２０は、本発明の実施の形態の第２例を示している。本例の場合には、図１２、１３、２０に詳示する様に、サポート１９ａのアウタ側端部に設けた各突出板部２３ａの先端部の、径方向（図１２、１３、２０の上下方向）両側面に設けた外径側、内径側各係止溝１５ａ、１６ａの底面を、各突出板部２３ａの先端（図１２、１３、２０の右端）に向かう程深くなる方向に傾斜させている。又、本例の場合には、各突出板部２３ａの先端部を、その先端面を後述するガイド型６１（図１４、１７、１８参照）により規制しつつ径方向両側から押圧する事により、上記外径側、内径側各係止溝１５ａ、１６ａを形成している。又、これと共に、サポート１９ａを構成する素板２０（図４、５参照）を得る為の金属板の打ち抜き加工に伴って、上記各突出板部２３ａの先端面に形成された剪断面６２及び破断面６３（図１２、１６）のうち、少なくとも破断面６３を矯正し、この先端面のほぼ全体を平坦面としている。この為に、本例の場合には、図１４〜１５、１７〜１８に示す様な押圧加工装置６４を使用する。この押圧加工装置６４は、固定の部分に対し昇降自在な上型６５と、この上型６５と対向する固定の下型６６とを備える。このうちの上型６５は、互いに上下方向に相対変位自在な第一の上型６７及び第二の上型６８を備える。これら第一の上型６７の下面と第二の上型６８の上面との間に、ばね７２を設けて、互いに離れる方向に弾力を付与している。又、上記第一の上型６７は、上記各突出板部２３ａに外径側係止溝１５を形成する為の第一の押圧部６９を下面に有する押圧部材７０と、前記ガイド型６１とを、一体に固定している。又、上記下型６６の上面に、上記各突出板部２３ａに内径側係止溝１６を形成する為の第二の押圧部７１を設けている。上記各突出板部２３ａに各係止溝１５、１６を形成する押圧加工を行なう際には、図１４〜１５に示す様に、上記上型６５と下型６６との間に上記各突出板部２３ａを位置させる様に、中間素材５１を設置する。この中間素材５１は、図示しないコイルばね、空気ばね等を有する弾性支持部材により、固定の部分に対し上下方向の移動可能に支持する。 [Second example of the embodiment of the present invention]
Next, FIGS. 11 to 20 show a second example of the embodiment of the present invention. In the case of this example, as shown in detail in FIGS. 12, 13, and 20, the radial direction (of FIGS. 12, 13, and 20) of the tip of each protruding plate portion 23a provided at the outer side end of the support 19a. (Vertical direction) The bottom surface of each of the outer and inner diameter side locking grooves 15a and 16a provided on both side surfaces is inclined so as to become deeper toward the tip of each projecting plate portion 23a (the right end in FIGS. 12, 13, and 20). I am letting. Further, in the case of this example, by pressing the distal end portion of each protruding plate portion 23a from both sides in the radial direction while restricting the distal end surface by a guide die 61 (see FIGS. 14, 17, and 18) described later, The outer diameter side and inner diameter side locking grooves 15a and 16a are formed. Along with this, along with the punching process of the metal plate for obtaining the base plate 20 (see FIGS. 4 and 5) constituting the support 19a, the shearing surface 62 formed on the front end surface of each protruding plate portion 23a and Of the fracture surface 63 (FIGS. 12 and 16), at least the fracture surface 63 is corrected, and almost the entire tip surface is a flat surface. For this reason, in the case of this example, a pressing device 64 as shown in FIGS. 14 to 15 and 17 to 18 is used. The pressing device 64 includes an upper mold 65 that can be raised and lowered with respect to a fixed portion, and a fixed lower mold 66 that faces the upper mold 65. Of these, the upper die 65 includes a first upper die 67 and a second upper die 68 that are relatively displaceable in the vertical direction. A spring 72 is provided between the lower surface of the first upper die 67 and the upper surface of the second upper die 68 to provide elasticity in a direction away from each other. The first upper die 67 includes a pressing member 70 having a first pressing portion 69 on the lower surface for forming the outer diameter side locking groove 15 in each protruding plate portion 23a, the guide die 61, Are fixed together. Further, on the upper surface of the lower mold 66, a second pressing portion 71 for forming the inner diameter side locking groove 16 in each protruding plate portion 23a is provided. When the pressing process for forming the locking grooves 15 and 16 in the protruding plate portions 23a is performed, the protruding plates are interposed between the upper mold 65 and the lower mold 66 as shown in FIGS. The intermediate material 51 is installed so that the part 23a is positioned. The intermediate material 51 is supported by an elastic support member having a coil spring, an air spring, etc. (not shown) so as to be movable in the vertical direction with respect to a fixed portion.

この状態で、上記各突出板部２３ａの先端面には、図１６に詳示する様に、上記素板２０を得る為の金属板の打ち抜き加工に伴って形成された剪断面６２及び破断面６３が存在する。尚、図１６に梨地で示す部分は、打ち抜き加工により各突出板部２３ａの、得るべき正規の先端部の形状から欠落した部分（欠肉部）である。又、上記ガイド型６１は、上記上型６５を下降させた状態で、その幅方向（図１４、１５、１７、１８の左右方向）両側面が上記各突出板部２３ａの先端面と接触するか、又はこれと僅かな隙間を介して対向する様に規制する。押圧加工時には、図１７〜１８に示す様に、上記上型６５を下降させ、上記第一の上型６７を上記第二の上型６８に対し下方に変位させた状態で、この第二の上型６８の下面及び上記第一の上型６７の押圧部材７０の下面を、上記各突出板部２３ａに押し付ける。又、これに伴って、これら各突出板部２３ａを有する中間素材５１を下降させ、これら各突出板部２３ａの下面を上記下型６６の上面に押し付ける。この結果、これら各突出板部２３ａが、上記第二の上型６８及び押圧部材７０と下型６６との間で、ロータ１（図１等参照）の径方向に対応する、上下方向両側から挟持する様に押圧される。又、各突出板部２３ａの先端面がガイド型６１の幅方向両側面に対向する。そして、上記押圧部材７０の下面に設けた第一の押圧部６９と、上記下型６６の上面に設けた第二の押圧部７１とにより、上記各突出板部２３ａの上下方向両側面に外径側、内径側各係止溝１５ａ、１６ａが形成される。   In this state, as shown in detail in FIG. 16, the front end surface of each protruding plate portion 23a has a shearing surface 62 and a fracture surface formed by punching a metal plate for obtaining the base plate 20. 63 exists. In addition, the part shown with a satin surface in FIG. 16 is a part (missing part) missing from the shape of the regular front-end | tip part which should be obtained of each protrusion board part 23a by punching. In addition, the guide die 61 has both sides in the width direction (left and right directions in FIGS. 14, 15, 17, and 18) in contact with the tip end surfaces of the protruding plate portions 23a in a state where the upper die 65 is lowered. Or it is regulated so as to face this with a slight gap. At the time of pressing, as shown in FIGS. 17 to 18, the upper die 65 is lowered and the second upper die 68 is displaced downward with respect to the second upper die 68. The lower surface of the upper die 68 and the lower surface of the pressing member 70 of the first upper die 67 are pressed against the protruding plate portions 23a. Along with this, the intermediate material 51 having the protruding plate portions 23 a is lowered, and the lower surface of the protruding plate portions 23 a is pressed against the upper surface of the lower mold 66. As a result, the protruding plate portions 23a are located between the second upper die 68 and the pressing member 70 and the lower die 66 from both sides in the vertical direction corresponding to the radial direction of the rotor 1 (see FIG. 1 and the like). It is pressed to pinch. Further, the front end surface of each protruding plate portion 23 a faces both side surfaces of the guide die 61 in the width direction. Then, the first pressing portion 69 provided on the lower surface of the pressing member 70 and the second pressing portion 71 provided on the upper surface of the lower mold 66 are externally attached to both side surfaces in the vertical direction of the protruding plate portions 23a. Diameter side and inner diameter side locking grooves 15a, 16a are formed.

又、上記押圧部材７０の下面の、第一の押圧部６９の形状は、外径側係止溝１５ａに対応する形状としている。又、上記下型６６の上面の、第二の押圧部７１の形状は、内径側係止溝１６ａに対応する形状としている。この結果、上記各突出板部２３ａの先端部の材料が、上記各係止溝１５ａ、１６ａよりも先端側に外れた部分の先端面部分に流動して、先端面の剪断面６２（図１６）及び破断面６３のうち、少なくとも破断面６３（通常は両方の面６２、６３）が矯正されて、この先端面のほぼ全体が平坦面となる。尚、図１２に梨地で示す部分は、前記中間素材５１の状態から、押圧加工装置６４による押圧加工に伴って材料が増えた部分である。   The shape of the first pressing portion 69 on the lower surface of the pressing member 70 is a shape corresponding to the outer diameter side locking groove 15a. The shape of the second pressing portion 71 on the upper surface of the lower mold 66 is a shape corresponding to the inner diameter side locking groove 16a. As a result, the material of the tip portion of each protruding plate portion 23a flows to the tip surface portion of the portion disengaged from the respective locking grooves 15a, 16a toward the tip side, and the shear surface 62 (FIG. 16) of the tip surface. ) And the fractured surface 63, at least the fractured surface 63 (usually both surfaces 62, 63) is corrected, and almost the entire tip surface becomes a flat surface. 12 is a portion where the material has increased from the state of the intermediate material 51 in accordance with the press processing by the press processing device 64.

この様にして上記各突出板部２３ａに外径側、内径側各係止溝１５ａ、１６ａが形成されると共に、これら各突出板部２３ａの先端面に平坦面が形成される事により、第二中間素材７３が得られたならば、この第二中間素材７３を押圧加工装置６４から取り出して、第一、第二のねじ孔１７、１８（図１、２）を形成する事により、サポート１９ａの完成品とする。
この様にしてサポート１９ａを造る本例の場合には、素板２０（図４、５）の打ち抜き成形により、各突出板部２３ａの先端面に剪断面６２及び破断面６３が形成されるのにも拘らず、この先端面を平坦面に矯正できる為、後工程でシェービング加工等の機械加工をこの先端面に施す必要がなくなり、高い形状精度を有する高品質なサポート１９ａを容易に得られる。
その他の構成及び作用に就いては、上述した第１例と同様である為、同等部分には同一符号を付して重複する図示並びに説明を省略する。 In this way, each of the protruding plate portions 23a is formed with the outer diameter side and inner diameter side locking grooves 15a, 16a, and a flat surface is formed on the front end surface of each of the protruding plate portions 23a. If the second intermediate material 73 is obtained, the second intermediate material 73 is taken out from the pressing device 64 to form the first and second screw holes 17 and 18 (FIGS. 1 and 2), thereby supporting the second intermediate material 73. The finished product 19a.
In the case of this example in which the support 19a is manufactured in this manner, the shear surface 62 and the fracture surface 63 are formed on the tip surface of each protruding plate portion 23a by punching the base plate 20 (FIGS. 4 and 5). Nevertheless, since the tip surface can be corrected to a flat surface, it is not necessary to perform machining such as shaving processing on the tip surface in a later process, and a high-quality support 19a having high shape accuracy can be easily obtained. .
Since other configurations and operations are the same as those in the first example described above, the same parts are denoted by the same reference numerals, and overlapping illustrations and descriptions are omitted.

［本発明の実施の形態の第３例］
次に、図２１は、本発明の実施の形態の第３例を示している。本例の場合には、サポート１９ａの各突出板部２３ｂに設けた外径側、内径側各係止溝１５ｂ、１６ｂの周方向両側面を、断面円弧形の曲面部７４、７４とし、これら曲面部７４、７４と平面状の底面部７５とを滑らかに連続させている。又、アウタパッド５ａを構成するプレッシャプレート８ａの周方向両端部に設けた１対の折れ曲がり部７６ａ、７６ｂの、先端部の周方向片側面を断面円弧形の曲面部７７、７７とし、径方向片側面を平坦面部７８、７８としている。そして、上記外径側、内径側各係止溝１５ｂ、１６ｂに、上記アウタパッド５ａの各折れ曲がり部７６ａ、７６ｂの先端部を進入させている（係止自在としている）。 [Third example of the embodiment of the present invention]
Next, FIG. 21 shows a third example of the embodiment of the present invention. In the case of this example, the circumferential side both side surfaces of the outer diameter side and inner diameter side locking grooves 15b, 16b provided on the protruding plate portions 23b of the support 19a are curved surface portions 74, 74 having arcuate cross sections, The curved surface portions 74 and 74 and the planar bottom surface portion 75 are smoothly continued. Moreover, the circumferential direction one side surface of the pair of bent portions 76a and 76b provided at both ends in the circumferential direction of the pressure plate 8a constituting the outer pad 5a is formed into curved surface portions 77 and 77 having a circular arc shape in the radial direction. One side is set as flat surface portions 78 and 78. And the front-end | tip part of each bending part 76a, 76b of the said outer pad 5a is made to approach into each said outer diameter side and inner diameter side locking groove 15b, 16b (it can be locked).

この様な本例の場合には、制動時に、サポート１９ａの各突出板部２３ｂの各係止溝１５ｂ、１６ｂにアウタパッド５ａの各折れ曲がり部７６ａ、７６ｂの先端部が押し付けられるのにも拘らず、上記各突出板部２３ｂの各係止溝１５ｂ、１６ｂを形成した部分に存在する薄肉部７９と、これら各係止溝１５ｂ、１６ｂから周方向両側に外れた厚肉の部分との連続部に過度に応力が集中する事を防止できる。この為、上記サポート１９ａの強度をより有効に確保できる。
その他の構成及び作用に就いては、前述の図１〜１０に示した第１例と同様である為、同等部分には同一符号を付して重複する図示並びに説明を省略する。 In the case of this example, the front end portions of the bent portions 76a and 76b of the outer pad 5a are pressed against the engaging grooves 15b and 16b of the protruding plate portions 23b of the support 19a during braking. The continuous portion of the thin-walled portion 79 present in the portions where the respective locking grooves 15b, 16b of the protruding plate portions 23b are formed, and the thick-walled portions deviated from the respective locking grooves 15b, 16b on both sides in the circumferential direction. It is possible to prevent stress from being concentrated excessively. For this reason, the strength of the support 19a can be secured more effectively.
Since other configurations and operations are the same as those in the first example shown in FIGS. 1 to 10 described above, the same parts are denoted by the same reference numerals, and overlapping illustrations and descriptions are omitted.

尚、上述した各例では、サポート１９ａの各突出板部２３、２３ａ、２３ｂに設ける外径側、内径側各係止溝１５、１５ａ、１５ｂ、１６、１６ａ、１６ｂを、押圧加工により形成する場合に就いて説明した。但し、本発明は、この様な構造に限定するものではなく、例えば、上記外径側、内径側各係止溝１５、１５ａ、１５ｂ、１６、１６ａ、１６ｂを切削加工等により形成する事もできる。又、上述した各例では、サポート１９ａのアウタ側端部同士を連結する連結部を省略した場合に就いて説明したが、本発明は、この連結部を設けた構造でも実施できる。この様に連結部を設けた場合には、サポートの更なる強度向上を図れる。更に、本発明は、サポート１９ａを金属板製とする構造に限定するものではなく、例えば、このサポートを鋳物製とする事もできる。   In each of the above-described examples, the outer diameter side and inner diameter side locking grooves 15, 15a, 15b, 16, 16a, and 16b provided on the protruding plate portions 23, 23a, and 23b of the support 19a are formed by pressing. I explained about the case. However, the present invention is not limited to such a structure. For example, the outer diameter side and inner diameter side locking grooves 15, 15a, 15b, 16, 16a, and 16b may be formed by cutting or the like. it can. In each of the above-described examples, the case where the connecting portion that connects the outer end portions of the support 19a is omitted has been described. However, the present invention can also be implemented in a structure provided with this connecting portion. When the connecting portion is provided in this manner, the strength of the support can be further improved. Further, the present invention is not limited to the structure in which the support 19a is made of a metal plate. For example, the support can be made of a casting.

本発明の実施の形態の第１例のディスクブレーキを、一部を省略した状態でアウタ側から見た図。The figure which looked at the disc brake of the 1st example of an embodiment of the invention from the outer side in the state where a part was omitted. 図１をインナ側から見た図。The figure which looked at FIG. 1 from the inner side. 図１のＡ部拡大図。The A section enlarged view of FIG. サポートを構成する素板から中間素材を得る為の曲げ加工装置の下型部分を、この素板を設置した状態で示す略平面図。The schematic plan view which shows the lower mold | type part of the bending apparatus for obtaining an intermediate material from the base plate which comprises a support in the state which installed this base plate. 図４のＢ−Ｂ断面図。BB sectional drawing of FIG. 上記曲げ加工装置の下型部分の一部を、上方から見た斜視図。The perspective view which looked at a part of lower mold part of the above-mentioned bending device from the upper part. 同じく第二の上型及び第二の下型の一部を、図６の左方から見た斜視図。The perspective view which looked at a part of 2nd upper mold | type and 2nd lower mold | type from the left of FIG. 6 similarly. 上記曲げ加工装置により素板に曲げ加工を施す場合の曲げ加工の最終段階を示す、図５と同様の図。The figure similar to FIG. 5 which shows the last stage of the bending process in the case of bending a base plate with the said bending apparatus. 急制動時にアウタパッドにロータから大きな制動トルクが加わる状態を示す、図１と同様の図。The figure similar to FIG. 1 which shows the state which a big braking torque is added to an outer pad from a rotor at the time of sudden braking. 図９のＣ部拡大図。The C section enlarged view of FIG. 本発明の実施の形態の第２例のディスクブレーキを、一部を省略した状態でアウタ側から見た図。The figure which looked at the disc brake of the 2nd example of an embodiment of the invention from the outer side in the state where a part was omitted. 図１１のサポートの、１対の突出板部のうちの一方の突出板部部分のみを拡大して示す図。The figure which expands and shows only one protrusion board part part of a pair of protrusion board parts of the support of FIG. 図１１のＤ部拡大図。The D section enlarged view of FIG. 図１１のサポートを構成する中間素材から外径側、内径側各係止溝を形成した第二中間素材を得る為の押圧加工装置を、上記中間素材を設置した状態で示す半部断面図。FIG. 12 is a half cross-sectional view showing a pressing device for obtaining a second intermediate material having outer and inner diameter side locking grooves formed from the intermediate material constituting the support of FIG. 11 in a state where the intermediate material is installed. 図１４の下半部の拡大断面図。The expanded sectional view of the lower half part of FIG. 上記押圧加工装置に設置する中間素材の一方の突出板部部分のみを示す拡大断面図。The expanded sectional view which shows only one protrusion board part part of the intermediate material installed in the said press processing apparatus. この押圧加工装置により中間素材に外径側、内径側各係止溝を形成すべく押圧加工を施す際の最終段階を示す、図１４と同様の図。The same figure as FIG. 14 which shows the last stage at the time of performing a press process in order to form each outer diameter side and inner diameter side latching groove | channel on an intermediate material with this press processing apparatus. 一部を省略して示す、図１７の部分拡大断面図。The partial expanded sectional view of FIG. 17 which abbreviate | omits and shows a part. 急制動時にアウタパッドにロータから大きな制動トルクが加わる状態を示す、図１１と同様の図。FIG. 12 is a view similar to FIG. 11 showing a state in which a large braking torque is applied from the rotor to the outer pad during sudden braking. 図１９のＥ部拡大図。The E section enlarged view of FIG. 本発明の実施の形態の第３例を示す、図３と同様の図。The figure similar to FIG. 3 which shows the 3rd example of embodiment of this invention. ディスクブレーキの従来構造の第１例を、一部を切断して外径側から見た図。The figure which cut | disconnected a 1st example of the conventional structure of a disc brake, and was seen from the outer-diameter side. 図２２のＦ−Ｆ断面図。FF sectional drawing of FIG. 図２２からサポートのみを取り出して外径側から見た図。The figure which took out only the support from FIG. 22 and was seen from the outer diameter side. 図２４の下方に相当するインナ側から見た図。The figure seen from the inner side equivalent to the downward direction of FIG. ディスクブレーキの従来構造の第２例を、一部を省略した状態でアウタ側から見た図。The figure which looked at the 2nd example of the conventional structure of a disc brake from the outer side in the state which omitted a part. 同第２例の制動時にアウタパッドが回転方向に対し傾斜した状態を説明する為の、図２６と同様の図。The figure similar to FIG. 26 for demonstrating the state which the outer pad inclined with respect to the rotation direction at the time of the braking of the said 2nd example.

符号の説明Explanation of symbols

１ ロータ
２ サポート
３ キャリパ
４ａ、４ｂ ガイドピン
５ａ アウタパッド
５ｂ インナパッド
６ シリンダ部
７ ピストン
８ａ、８ｂ プレッシャプレート
９ キャリパ爪
１０ａ、１０ｂ ライニング
１１ 連結部
１３、１３ａ 基板部
１４ 腕部
１５、１５ａ、１５ｂ 外径側係止溝
１６、１６ａ、１６ｂ 内径側係止溝
１７ 第一のねじ孔
１８ 第二のねじ孔
１９、１９ａ サポート
２０ 素板
２１ 突部
２２ 連結板部
２３、２３ａ、２３ｂ 突出板部
２４、２４ａ インナパッド支持部
２５ 係止切り欠き
２６ 係止鉤部
２７ 係止溝
２８ 鉤部
２９ 曲げ加工装置
３０ 第一の上型
３１ 第一の下型
３２ 第二の上型
３３ 第二の下型
３４ 基台
３５ 弾性部材
３６ 脚部
３７ 支持部分
３８ 第一の傾斜面
３９ 第二の傾斜面
４０ 傾斜面
４１ 載置面
４２ 受け部材
４３ 平坦面
４４ａ、４４ｂ 折れ曲がり部
４５ 凹部
４６ 第一の側面
４７ 第二の側面
４８ 第三の側面
４９ 第四の側面
５０ 第五の側面
５１ 中間素材
５２ 第二中間素材
５３ 第一の壁部
５４ 第二の壁部
５５ 突部
５６ 凹部
５７ 凹部
５８ 溝部
５９ 先端面
６０ 径方向内側面
６１ ガイド型
６２ 剪断面
６３ 破断面
６４ 押圧加工装置
６５ 上型
６６ 下型
６７ 第一の上型
６８ 第二の上型
６９ 第一の押圧部
７０ 押圧部材
７１ 第二の押圧部
７２ ばね
７３ 第二中間素材
７４ 曲面部
７５ 底面部
７６ａ、７６ｂ 折れ曲がり部
７７ 曲面部
７８ 平坦面部
７９ 薄肉部
８０ 係止溝
８１ 係止突部
８２ａ、８２ｂ 折れ曲がり部
８３ 径方向外側面 DESCRIPTION OF SYMBOLS 1 Rotor 2 Support 3 Caliper 4a, 4b Guide pin 5a Outer pad 5b Inner pad 6 Cylinder part 7 Piston 8a, 8b Pressure plate 9 Caliper claw 10a, 10b Lining 11 Connection part 13, 13a Substrate part 14 Arm part 15, 15a, 15b Outside Diameter side locking groove 16, 16a, 16b Inner diameter side locking groove 17 First screw hole 18 Second screw hole 19, 19a Support 20 Base plate 21 Projection portion 22 Connecting plate portion 23, 23a, 23b Projection plate portion 24 24a Inner pad support part 25 Locking notch 26 Locking hook part 27 Locking groove 28 Hook part 29 Bending device 30 First upper mold 31 First lower mold 32 Second upper mold 33 Second lower Mold 34 Base 35 Elastic member 36 Leg 37 Support portion 38 First inclined surface 39 Second inclined surface 40 Inclined surface 41 Mounted 42 receiving member 43 flat surface 44a, 44b bent portion 45 recessed portion 46 first side surface 47 second side surface 48 third side surface 49 fourth side surface 50 fifth side surface 51 intermediate material 52 second intermediate material 53 first Wall part 54 Second wall part 55 Projection part 56 Concave part 57 Concave part 58 Groove part 59 End face 60 Radial inner side face 61 Guide mold 62 Shear surface 63 Fracture surface 64 Pressing device 65 Upper mold 66 Lower mold 67 First upper mold 68 Second upper mold 69 First pressing portion 70 Pressing member 71 Second pressing portion 72 Spring 73 Second intermediate material 74 Curved surface portion 75 Bottom surface portion 76a, 76b Bent portion 77 Curved portion 78 Flat surface portion 79 Thin portion 80 Engagement Stop groove 81 Locking protrusion 82a, 82b Bent portion 83 Radial outer surface

Claims (3)

車輪と共に回転するロータに隣接して車体に固定されるサポートと、このロータの軸方向両側に配置されると共に、このサポートによりこのロータの軸方向への移動可能に案内されたアウタパッド及びインナパッドと、キャリパとを備え、このキャリパは、爪部と、ピストンが嵌装されるシリンダ部とを有するものであり、このピストンの押し出しに伴い、上記１対のパッドを上記ロータの側面に押圧して制動を行なうディスクブレーキであって、
上記サポートが、上記キャリパをロータの軸方向に変位自在に支持し、車体に取り付ける為にこのロータの一方の側に隣接して設けた基板部と、この基板部に上記インナパッドを支持する為に形成されたインナパッド支持部と、この基板部の周方向両端部から上記ロータの外周縁部を越えて他方の側に伸びた１対の連結板部と、これら両連結板部の先端部から互いに近づき合う方向に延出された１対の突出板部とを備えたものであるディスクブレーキに於いて、
上記アウタパッドの周方向両端部にこの周方向に凹んだ１対の凹部が形成されており、上記アウタパッドの周方向両端部でこれら各凹部の開口両端部となる部分に、それぞれ１対ずつの折れ曲がり部を、これら１対の折れ曲がり部同士でロータの径方向に近づき合う様に設けており、上記サポートに設けられた１対の突出板部の先端部の径方向に関する両側面に、それぞれこの径方向に凹んだ外径側、内径側係止溝を設けており、これら外径側、内径側各係止溝に上記各折れ曲がり部の先端部を進入させている事を特徴とするディスクブレーキ。 A support fixed to the vehicle body adjacent to a rotor that rotates together with the wheels, and an outer pad and an inner pad that are arranged on both sides in the axial direction of the rotor and guided by the support so as to be movable in the axial direction of the rotor; The caliper has a claw portion and a cylinder portion into which the piston is fitted, and the pair of pads are pressed against the side surface of the rotor as the piston is pushed out. A disc brake for braking,
The support supports the caliper so as to be displaceable in the axial direction of the rotor, a board part provided adjacent to one side of the rotor for mounting on the vehicle body, and the inner pad to support the inner pad. An inner pad support portion formed on the substrate portion, a pair of connecting plate portions extending from the circumferential end portions of the substrate portion to the other side beyond the outer peripheral edge portion of the rotor, and tip portions of both connecting plate portions A disc brake having a pair of projecting plate portions extending in a direction approaching each other,
A pair of recesses recessed in the circumferential direction are formed at both ends in the circumferential direction of the outer pad, and a pair of bent portions are formed at both ends of the outer pad in the circumferential direction at the ends of the openings of the respective recesses. Are provided so that the pair of bent portions come close to each other in the radial direction of the rotor. A disc brake characterized in that an outer diameter side and an inner diameter side engaging groove recessed in a direction is provided, and a distal end portion of each bent portion is inserted into the outer diameter side and inner diameter side engaging grooves. 上記アウタパッドがロータの径方向に移動する場合での、このアウタパッドが上記サポートの各突出板部に、上記径方向に接触する部分を、これら各突出板部の先端部の、上記各係止溝の底面から先端側に外れた径方向側面のみとしている、請求項１に記載したディスクブレーキ。   In the case where the outer pad moves in the radial direction of the rotor, the portion where the outer pad comes into contact with the protruding plate portion of the support in the radial direction is defined as the locking groove at the tip of each protruding plate portion. The disc brake according to claim 1, wherein only the radial side surface deviated from the bottom surface to the front end side is used. 上記サポートが金属板製であり、このサポートの各突出板部の先端部に径方向両側から押圧加工を施す事により上記各係止溝を形成している、請求項１又は請求項２に記載したディスクブレーキ。   3. The support according to claim 1, wherein the support is made of a metal plate, and the locking grooves are formed by pressing the distal ends of the protruding plate portions of the support from both sides in the radial direction. Disc brake.
JP2006029571A 2006-02-07 2006-02-07 Disk brake Pending JP2007211806A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2006029571A JP2007211806A (en) 2006-02-07 2006-02-07 Disk brake

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006029571A JP2007211806A (en) 2006-02-07 2006-02-07 Disk brake

Publications (1)

Publication Number Publication Date
JP2007211806A true JP2007211806A (en) 2007-08-23

Family

ID=38490446

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2006029571A Pending JP2007211806A (en) 2006-02-07 2006-02-07 Disk brake

Country Status (1)

Country Link
JP (1) JP2007211806A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018105347A (en) * 2016-12-22 2018-07-05 トヨタ自動車株式会社 Brake module

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018105347A (en) * 2016-12-22 2018-07-05 トヨタ自動車株式会社 Brake module

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