JP2008169961A - Floating caliper type disc brake and its manufacturing method - Google Patents

Floating caliper type disc brake and its manufacturing method Download PDF

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JP2008169961A
JP2008169961A JP2007005371A JP2007005371A JP2008169961A JP 2008169961 A JP2008169961 A JP 2008169961A JP 2007005371 A JP2007005371 A JP 2007005371A JP 2007005371 A JP2007005371 A JP 2007005371A JP 2008169961 A JP2008169961 A JP 2008169961A
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torque receiving
torque
receiving members
rotor
disc brake
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Japanese (ja)
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Toshifumi Maehara
利史 前原
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Akebono Brake Industry Co Ltd
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Akebono Brake Industry Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure easily performing manufacturing of a floating caliper type disc brake, having excellent lay-out property with a wheel, and ensuring strength of a bonding part of both torque receiving members 31a and the mounting plate part 29 even if force is applied in a direction where the mounting plate part 29 is twisted. <P>SOLUTION: Both of the torque receiving members 31a and the mounting plate part 29 are formed separately. On both of the torque receiving members 31a, a guide hole for slidably fitting guide pins 5b, 5b for supporting a caliper 2a displaceably in an axial direction is provided. Both of the torque receiving members are connected to an extension plate part 43 of the mounting plate part 29 by screws 45, 45 in an axial direction, thereby solving the problem. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明の対象となるフローティングキャリパ型ディスクブレーキは、自動車の制動を行なう為に利用するもので、本発明は、この様なフローティングディスクブレーキの製造を、容易に行なえる構造に関する。   A floating caliper type disc brake which is an object of the present invention is used for braking an automobile, and the present invention relates to a structure which can easily manufacture such a floating disc brake.

自動車の制動を行なう為のディスクブレーキとして従来から、サポートに対しキャリパを一対の案内ピンにより変位自在に支持したフローティングキャリパ型のものが、特許文献１〜５に記載される等により、従来から広く知られ、実際に広く使用されている。図１４〜１５は、この様なフローティングキャリパ型ディスクブレーキのうちの特許文献１に記載されたものを示している。このフローティングキャリパ型のディスクブレーキは、制動時には、車輪（図示せず）と共に回転するロータ１に対しキャリパ２を変位させる。車両への組み付け状態では、このロータ１の一側に隣接させる状態で設けるサポート３を、取付孔４、４を介して車体（図示せず）に固定する。又、このサポート３に上記キャリパ２を、上記ロータ１の軸方向に変位可能に支持している。   Conventionally, as a disc brake for braking an automobile, a floating caliper type in which a caliper is supported by a pair of guide pins so as to be displaceable with respect to a support has been widely used. Known and widely used in practice. FIGS. 14 to 15 show the floating caliper type disc brake described in Patent Document 1 as described above. The floating caliper type disc brake displaces the caliper 2 with respect to the rotor 1 that rotates together with wheels (not shown) during braking. In the assembled state to the vehicle, the support 3 provided in a state of being adjacent to one side of the rotor 1 is fixed to the vehicle body (not shown) through the mounting holes 4 and 4. The caliper 2 is supported on the support 3 so as to be displaceable in the axial direction of the rotor 1.

この為に、上記ロータ１の回転方向に関して上記キャリパ２の両端部に一対の案内ピン５、５を、同じく上記サポート３の両端部に一対の案内孔６、６を、それぞれ上記ロータ１の中心軸に対し平行に設けている。そして、上記両案内ピン５、５を上記両案内孔６、６内に、軸方向の摺動自在に挿入している。これら両案内ピン５、５の基端部外周面と上記両案内孔６、６の開口部との間には、防塵用のブーツ７、７を設けている。尚、上記両案内孔６、６同士の内径は互いに異なる場合もあり、これに合わせて、上記両案内ピン５、５同士の外径も互いに異なる場合もある。   For this purpose, a pair of guide pins 5, 5 are provided at both ends of the caliper 2 with respect to the rotation direction of the rotor 1, and a pair of guide holes 6, 6 are provided at both ends of the support 3. It is provided parallel to the axis. The guide pins 5 and 5 are inserted into the guide holes 6 and 6 so as to be slidable in the axial direction. Dust-proof boots 7 and 7 are provided between the outer peripheral surfaces of the base end portions of the guide pins 5 and 5 and the openings of the guide holes 6 and 6. The inner diameters of the two guide holes 6 and 6 may be different from each other, and the outer diameters of the both guide pins 5 and 5 may be different from each other accordingly.

又、上記サポート３の両端部で、上記ロータ１の周方向に離隔した位置にそれぞれ、特許請求の範囲に記載したトルク受け部材に相当する、回入側、回出側両係合部８、９を設けている。これら両係合部８、９は、上記ロータ１の外周部を図１４の上下方向に跨ぐ様に、先端がＵ字形に屈曲しており、これら両係合部８、９にパッド１０ａ、１０ｂを構成するプレッシャプレート１１、１１の両端部を、上記ロータ１の軸方向に摺動可能に係合させている。又、上記パッド１０ａ、１０ｂを跨ぐブリッジ部で連結された、シリンダ部１２と爪部１３とを有する上記キャリパ２を配置している。このキャリパ２のうちの上記シリンダ部１２に、インナ側（車両の幅方向内側で図１４の下側）のパッド１０ａを上記ロータ１に対して押圧するピストン１４を、液密に嵌装している。   Further, at both ends of the support 3, at the positions spaced apart in the circumferential direction of the rotor 1, both the turn-in side and the turn-out side engaging portions 8 corresponding to the torque receiving members described in the claims, 9 is provided. These two engaging portions 8 and 9 are bent in a U shape at their tips so as to straddle the outer peripheral portion of the rotor 1 in the vertical direction of FIG. Both end portions of the pressure plates 11, 11 constituting the slidably engage in the axial direction of the rotor 1. The caliper 2 having a cylinder portion 12 and a claw portion 13 connected by a bridge portion straddling the pads 10a and 10b is disposed. A piston 14 that presses the pad 10a on the inner side (the inner side in the width direction of the vehicle in FIG. 14) against the rotor 1 is liquid-tightly fitted to the cylinder portion 12 of the caliper 2. Yes.

制動を行なう場合には、上記シリンダ部１２内に圧油を送り込み、上記ピストン１４により上記インナ側のパッド１０ａのライニング１５を、上記ロータ１の内側面に、図１４の下から上に押し付ける。すると、この押し付け力の反作用として上記キャリパ２が、上記両案内ピン５、５と上記両案内孔６、６との摺動に基づいて、図１４の下方に変位し、上記爪部１３がアウタ側（車両の幅方向外側で図１４の上側）のパッド１０ｂのライニング１５を、上記ロータ１の外側面に押し付ける。この結果、このロータ１が内外両側面側から強く挟持されて、制動が行なわれる。   When braking is performed, pressure oil is fed into the cylinder portion 12, and the lining 15 of the inner pad 10 a is pressed against the inner surface of the rotor 1 from the bottom of FIG. Then, as a reaction of this pressing force, the caliper 2 is displaced downward in FIG. 14 based on sliding between the guide pins 5 and 5 and the guide holes 6 and 6, and the claw portion 13 is moved to the outer side. The lining 15 of the pad 10 b on the side (the outer side in the width direction of the vehicle in FIG. 14) is pressed against the outer surface of the rotor 1. As a result, the rotor 1 is strongly clamped from both the inner and outer side surfaces, and braking is performed.

上述の図１４〜１５に記載した従来構造の第１例の場合、制動時に、両パッド１０ａ、１０ｂからロータ１の回転方向に作用するトルクを、回出側係合部９（回転方向が逆となった場合には、回入側係合部８）により支承している。上記従来構造の第１例の場合、これら回入側、回出側両係合部８、９を、所謂押しアンカ構造としている。即ち、これら両係合部８、９の内側面１６、１６（両パッド１０ａ、１０ｂ側の側面）を、これら両パッド１０ａ、１０ｂを構成するプレッシャプレート１１の上記ロータ１の回転方向両端縁部に近接対向させている。制動時に、上記両パッド１０ａ、１０ｂに、図１５の時計方向にトルクが作用した場合、上記プレッシャプレート１１の片端縁部（図１５の右端縁部）と、上記両係合部８、９のうちの回出側係合部９の内側面１６とが係合（当接）して、上記トルクを支承する。   In the case of the first example of the conventional structure shown in FIGS. 14 to 15 described above, the torque acting on the rotation direction of the rotor 1 from both pads 10a and 10b is applied to the delivery side engaging portion 9 (the rotation direction is reversed) during braking. In this case, it is supported by the turn-in side engaging portion 8). In the case of the first example of the conventional structure described above, the turn-in side and turn-out side engaging portions 8 and 9 have a so-called push anchor structure. That is, the inner side surfaces 16 and 16 (side surfaces on the side of both pads 10a and 10b) of the engaging portions 8 and 9 are connected to both end portions in the rotational direction of the rotor 1 of the pressure plate 11 constituting the pads 10a and 10b. Is in close proximity to each other. When a torque acts on both the pads 10a and 10b in the clockwise direction in FIG. 15 during braking, one end edge (the right end edge in FIG. 15) of the pressure plate 11 and the two engaging portions 8 and 9 The inner side surface 16 of the delivery side engaging portion 9 is engaged (contacted) to support the torque.

一方、特許文献２、３には、パッドからのトルクを支承する為に、所謂押しアンカと引きアンカとの両方を備えた構造が記載されている。このうちの特許文献３に記載された構造を図１６に示す。この図１６に記載した従来構造の第２例の場合も、サポート３ａの両端部で、ロータ１の周方向に離隔した位置に、回入側、回出側両係合部８ａ、９ａを、それぞれ設けている。これら両係合部８ａ、９ａは、それぞれ、上記ロータ１の回転方向に拘らず、トルクを支承可能である。   On the other hand, Patent Documents 2 and 3 describe a structure including both a so-called push anchor and a pull anchor in order to support torque from a pad. The structure described in Patent Document 3 is shown in FIG. Also in the case of the second example of the conventional structure shown in FIG. 16, the turn-in side and the turn-out side engaging portions 8a and 9a are located at positions separated from each other in the circumferential direction of the rotor 1 at both ends of the support 3a. Each is provided. Both the engaging portions 8a and 9a can support torque regardless of the rotational direction of the rotor 1.

即ち、上記両係合部８ａ、９ａの内側面にそれぞれ、突出腕部１７ａ、１７ｂを形成している。そして、これら両突出腕部１７ａ、１７ｂの先端部を、ロータの径方向外方（図１６の上方）に折り曲げる事により、これら両突出腕部１７ａ、１７ｂと上記両係合部８ａ、９ａの内側面とに囲まれる部分を、係合凹部１８ａ、１８ｂとしている。上記両係合部８ａ、９ａにパッド１０ａ、１０ｂを係合させる場合には、これら両パッド１０ａ、１０ｂのプレッシャプレート１１ａの両端部に形成した係合凸部１９ａ、１９ｂを、上記両係合凹部１８ａ、１８ｂに係合させる。   That is, projecting arm portions 17a and 17b are formed on the inner surfaces of the engaging portions 8a and 9a, respectively. And the front-end | tip part of these both projecting arm parts 17a and 17b is bent to the radial direction outer side (upper part of FIG. 16) of these rotors, and both these projecting arm parts 17a and 17b and said both engaging parts 8a and 9a The portions surrounded by the inner surface are the engaging recesses 18a and 18b. When the pads 10a and 10b are engaged with the engaging portions 8a and 9a, the engaging protrusions 19a and 19b formed at both ends of the pressure plate 11a of the pads 10a and 10b are Engage with the recesses 18a and 18b.

これにより、上記両パッド１０ａ、１０ｂに、ロータの回転方向に関して、例えば、図１６の時計方向のトルクが作用すると、このトルクが小さい場合には、上記プレッシャプレート１１ａの回入側（図１６の左側）の係合凸部１９ａのパッド１０ａ、１０ｂ側の側面２０ａと、上記両係合凹部１８ａ、１８ｂのうちの回入側の係合凹部１８ａの内側の側面２１ａとが係合し、上記トルクを支承する。一方、このトルクが大きい場合には、上記回入側の係合凹部１８ａと係合凸部１９との係合に加えて、上記プレッシャプレート１１ａの回出側（図１６の右側）の係合凸部１９ｂのパッド１０ａ、１０ｂと反対側の側面２０ｂと、回出側の係合凹部１８ｂの外側の側面２１ｂとが係合し、上記トルクを支承する。即ち、回入側の係合凹部１８ａと係合凸部１９ａとの係合部は引きアンカとなり、回出側の係合凹部１８ｂと係合凸部１９ｂとの係合部は押しアンカとなる。   Thereby, for example, when the clockwise torque in FIG. 16 acts on both the pads 10a and 10b in the rotational direction of the rotor, when this torque is small, the pressure plate 11a is turned in (see FIG. 16). The side surface 20a on the pad 10a, 10b side of the engagement convex portion 19a on the left side is engaged with the side surface 21a on the inner side of the engagement concave portion 18a on the turn-in side of the both engagement concave portions 18a, 18b. Support torque. On the other hand, when this torque is large, in addition to the engagement between the engagement recess 18a and the engagement protrusion 19 on the turn-in side, the engagement on the return side (right side in FIG. 16) of the pressure plate 11a. The side surface 20b opposite to the pads 10a and 10b of the convex portion 19b and the side surface 21b outside the engaging concave portion 18b on the delivery side are engaged to support the torque. That is, the engagement portion between the engagement recess 18a on the turn-in side and the engagement projection 19a serves as a pull anchor, and the engagement portion between the engagement recess 18b on the turn-out side and the engagement projection 19b serves as a push anchor. .

上述の特許文献１〜３に記載した従来構造の第１、２例の場合、何れも、パッド１０ａ、１０ｂから作用するトルクを支承する為の回入側、回出側両係合部８、８ａ、９、９ａと、案内ピン５、５を摺動自在に挿入する案内孔６、６（図１４、１５参照）と、車体への取付部分とを、サポート３、３ａとして、互いに一体に形成している。この様な構成に対応する為に、従来、このサポート３、３ａを鋳造により形成していた。従って、従来構造の場合、鋳造により形成した中間素材のうち、上記両係合部８、８ａ、９、９ａのパッド１０ａ、１０ｂから作用するトルクを支承する部分や、上記案内孔６、６、上記サポート３、３ａの車体への取付部分等、精度が要求される部分に切削加工等の機械加工を施す必要がある。従来構造の様に、サポートを構成する各部材を一体とした場合、この様に精度が要求される部分が複数に及ぶ為、機械加工を施しにくく、生産性が良好であるとは言えない。又、車体への取付部分は、組み付ける車種によって異なる場合があり、サポート３、３ａとして、それぞれに対応した構造が必要となる。   In the case of the first and second examples of the conventional structure described in Patent Documents 1 to 3 above, both the turn-in side and the turn-out side engaging portions 8 for supporting the torque acting from the pads 10a and 10b, 8a, 9, 9a, guide holes 6, 6 (see FIGS. 14 and 15) into which the guide pins 5, 5 are slidably inserted, and a mounting portion to the vehicle body are integrally formed as supports 3, 3a. Forming. In order to cope with such a configuration, the supports 3 and 3a are conventionally formed by casting. Therefore, in the case of the conventional structure, among the intermediate material formed by casting, the portions that support the torque acting from the pads 10a, 10b of the engaging portions 8, 8a, 9, 9a, and the guide holes 6, 6, It is necessary to perform machining such as cutting on a portion requiring accuracy, such as a portion where the support 3 or 3a is attached to the vehicle body. When the members constituting the support are integrated as in the conventional structure, since there are a plurality of parts that require high accuracy in this way, it is difficult to perform machining and it cannot be said that productivity is good. Moreover, the attachment part to a vehicle body may differ with the vehicle models to assemble | attach, and the structure corresponding to each is required as the support 3 and 3a.

これに対して、特許文献４には、図１７に示す様に、車体への取付板部２２と、案内ピン５ａを摺動自在に挿入する案内孔６ａとを別体に形成した構造が記載されている。即ち、上記図１７に示す従来構造の第３例の場合、板金製の上記取付部分２２の一部に貫通孔２３を形成し、この貫通孔２３に、上記案内孔６ａを有し、パッド１０ａ、１０ｂに作用するトルクの一部を支承可能なトルク受け部材２４を圧入している。そして、上記貫通孔２３の周辺部で上記取付部分２２の一部をかしめて、この貫通孔２３に上記トルク受け部材２４を固定している。この様に、従来構造の第３例の場合、取付部分２２と、案内孔６ａ及びトルクを支承する部分とを別体に形成している為、加工精度が要求される、これら取付部分２２と案内孔６ａ及びトルクを支承する部分とを別々に加工できる。   In contrast, as shown in FIG. 17, Patent Document 4 describes a structure in which a mounting plate portion 22 to a vehicle body and a guide hole 6a into which a guide pin 5a is slidably inserted are formed separately. Has been. That is, in the case of the third example of the conventional structure shown in FIG. 17, a through hole 23 is formed in a part of the mounting portion 22 made of sheet metal, the guide hole 6a is provided in the through hole 23, and the pad 10a. A torque receiving member 24 capable of supporting a part of the torque acting on 10b is press-fitted. Then, a part of the mounting portion 22 is caulked at the periphery of the through hole 23, and the torque receiving member 24 is fixed to the through hole 23. Thus, in the case of the third example of the conventional structure, since the attachment portion 22 and the guide hole 6a and the portion for supporting the torque are formed separately, these attachment portions 22 are required to have high processing accuracy. The guide hole 6a and the portion for supporting the torque can be processed separately.

但し、上述の従来構造の第３例の場合、トルク受け部材２４の貫通孔２３への取付精度を確保する事が難しいと考えられる。即ち、このトルク受け部材２４は、案内孔６ａが上記案内ピン５ａの摺動方向と平行になる様に配置する必要がある。これに対して、上記トルク受け部材２４は、上記貫通孔２３に圧入される事により位置決めされる為、これら貫通孔２３の内周面とトルク受け部材２４の外周面とを精度良く形成する必要がある。又、このトルク受け部材２４は、基端寄り部分を上記貫通孔２３に固定されるのみである為、圧入時の組み付け精度が高く要求される。更に、圧入した後、上記貫通孔２３の一部をかしめる為、この貫通孔２３への圧入時に上記案内ピン５ａの摺動方向と平行に配置できても、かしめ時に傾く可能性がある。   However, in the case of the above-described third example of the conventional structure, it is considered difficult to ensure the accuracy of attaching the torque receiving member 24 to the through hole 23. That is, the torque receiving member 24 needs to be arranged so that the guide hole 6a is parallel to the sliding direction of the guide pin 5a. On the other hand, since the torque receiving member 24 is positioned by being press-fitted into the through hole 23, it is necessary to accurately form the inner peripheral surface of the through hole 23 and the outer peripheral surface of the torque receiving member 24. There is. Further, since the torque receiving member 24 is only fixed at the proximal end portion to the through-hole 23, it is required to have high assembly accuracy during press-fitting. Further, since a part of the through hole 23 is caulked after the press-fitting, even if it can be arranged in parallel with the sliding direction of the guide pin 5a when the press-fitting into the through-hole 23, there is a possibility that the caulking may be inclined during caulking.

又、特許文献５には、図１８に示す様に、案内孔６ａを形成したトルク受け部材２４ａを、ナックル２５のロータの径方向に関して外側（外径側）の一部に固定した構造が記載されている。この図１８に示す従来構造の第４例の場合、ナックル２５の外径側の一部に切り欠き２６を形成し、この切り欠き２６に上記トルク受け部材２４ａを固定している。この為に、このトルク受け部材２４ａの上面に固定板２７を載置し、この固定板２７の一部を上記ナックル２５の一部にねじ２８により固定して、この固定板２７と上記切り欠き２６の底面との間に、上記トルク受け部材２４ａを支持している。   Further, Patent Document 5 describes a structure in which a torque receiving member 24a having a guide hole 6a is fixed to a part on the outer side (outer diameter side) in the radial direction of the rotor of the knuckle 25, as shown in FIG. Has been. In the case of the fourth example of the conventional structure shown in FIG. 18, a notch 26 is formed in a part on the outer diameter side of the knuckle 25, and the torque receiving member 24 a is fixed to the notch 26. For this purpose, a fixing plate 27 is placed on the upper surface of the torque receiving member 24a, and a part of the fixing plate 27 is fixed to a part of the knuckle 25 with a screw 28. The fixing plate 27 and the notch The torque receiving member 24a is supported between the bottom surface of the 26.

上述の様な従来構造の第４例の場合、トルク受け部材２４ａをナックル２５の径方向外方に配置している為、ディスクブレーキの径方向の寸法が大きくなる。この為、このディスクブレーキの径方向外側に配置されるホイールと干渉し易くなる。言い換えれば、ホイールとのレイアウト性が良くない。又、上記第４例の場合、上記ロータの径方向に関して、外径側から上記ねじ２８を螺合している。この為、上記ナックル２５が捩れる方向に力が作用した場合には、このナックル２５と上記トルク受け部材２４ａとの結合部の強度を十分に確保できない可能性がある。即ち、パッド１０ｃから作用するトルクは、アンカ側の上記トルク受け部材２４ａを介して上記ナックル２５の一部で支承される。このナックル２５が車体に固定されている部分と上記トルクが作用する部分とは、ロータの軸方向に関して離隔している為、このトルクに基づいて、上記ナックル２５の一部と上記トルク受け部材２４ａとの結合部に、このナックル２５が捩れる方向（図１８の表裏方向）の力が作用する。この結果、このナックル２５の一部と上記トルク受け部材２４ａとを結合する上記ねじ２８に、せん断方向に力が作用する為、上記結合部の強度を確保しにくくなる。尚、結合部の強度を確保する為に、上記ねじ２８としてサイズの大きいものを使用した場合、ディスクブレーキの大型化を招来する為、好ましくない。   In the case of the fourth example having the conventional structure as described above, since the torque receiving member 24a is disposed radially outward of the knuckle 25, the radial dimension of the disc brake increases. For this reason, it becomes easy to interfere with the wheel arrange | positioned on the radial direction outer side of this disc brake. In other words, the layout with the wheel is not good. In the case of the fourth example, the screw 28 is screwed from the outer diameter side in the radial direction of the rotor. For this reason, when a force acts in the direction in which the knuckle 25 is twisted, there is a possibility that the strength of the joint portion between the knuckle 25 and the torque receiving member 24a cannot be sufficiently secured. That is, the torque acting from the pad 10c is supported by a part of the knuckle 25 via the anchor side torque receiving member 24a. Since the portion where the knuckle 25 is fixed to the vehicle body and the portion where the torque acts are separated from each other in the axial direction of the rotor, a part of the knuckle 25 and the torque receiving member 24a are based on this torque. A force in the direction in which the knuckle 25 is twisted (the front and back direction in FIG. 18) acts on the joint portion. As a result, a force acts in the shear direction on the screw 28 that joins a part of the knuckle 25 and the torque receiving member 24a, so that it is difficult to ensure the strength of the joint. In order to secure the strength of the connecting portion, if a large screw 28 is used, it is not preferable because the disc brake is increased in size.

特開昭５５−１２３０２９号公報JP 55-123029 A 特表２００１−５０９２３３号公報Special table 2001-509233 gazette 特公昭６０−５６９３０号公報Japanese Patent Publication No. 60-56930 特開平８−２４０２３３号公報JP-A-8-240233 特許第２６７５０６１号公報Japanese Patent No. 2675061

本発明は、上述の様な事情に鑑みて、フローティングキャリパ型ディスクブレーキの製造を容易に行なえる構造で、ホイールとのレイアウト性を良好にでき、しかも、固定部材に捩れる方向に力が作用しても、トルク受け部材とこの固定部材との結合部の強度が確保できる構造を実現すべく発明したものである。   In view of the circumstances as described above, the present invention has a structure that allows easy manufacture of a floating caliper type disc brake, improves the layout with the wheel, and exerts a force in a direction twisting the fixing member. Even so, the present invention has been invented to realize a structure capable of ensuring the strength of the joint between the torque receiving member and the fixing member.

本発明のフローティングキャリパ型ディスクブレーキとその製造方法のうち、請求項１に記載したフローティングキャリパ型ディスクブレーキは、固定部材と、１対のパッドと、１対のトルク受け部材と、キャリパと、複数の案内ピンとを備える。
このうちの固定部材は、車体に固定される。
又、上記両パッドは、車輪と共に回転するロータの両側に配置される。
又、上記両トルク受け部材は、上記固定部材に支持され、上記両パッドをこのロータの軸方向に変位可能に支持すると共に、制動時にこれら両パッドから加わる、このロータの回転方向のトルクを受けるものである。
又、上記キャリパは、上記ロータを跨ぐ様に配置され、このロータに関して一方の側に爪部を、他方の側にピストンを嵌装する為のシリンダ部を、それぞれ備えるものである。
更に、上記各案内ピンは、上記キャリパを上記ロータの軸方向の変位可能に支持するものである。
そして、上記ピストンの押し出しに伴い、上記両パッドを上記ロータの両側面に押し付けて制動を行なう。
特に、本発明のフローティングキャリパ型ディスクブレーキに於いては、上記両トルク受け部材は、上記固定部材とは別体で、上記各案内ピンを摺動可能に嵌装する案内孔を有している。又、上記両トルク受け部材は、この固定部材の一部に上記ロータの軸方向に、例えば、ねじや、この固定部材とこれら両トルク受け部材との一方に形成された凸部を、他方に形成された貫通孔に嵌合して、この凸部の先端部をかしめる事等により、連結されている。 Of the floating caliper type disc brake and the manufacturing method thereof according to the present invention, the floating caliper type disc brake described in claim 1 includes a fixing member, a pair of pads, a pair of torque receiving members, a caliper, and a plurality of calipers. And a guide pin.
Of these, the fixing member is fixed to the vehicle body.
The two pads are arranged on both sides of the rotor that rotates with the wheels.
The two torque receiving members are supported by the fixing member, support the pads so that they can be displaced in the axial direction of the rotor, and receive torque in the rotational direction of the rotor applied from the pads during braking. Is.
The caliper is disposed so as to straddle the rotor, and includes a claw portion on one side of the rotor and a cylinder portion for fitting a piston on the other side.
Furthermore, each said guide pin supports the said caliper so that the displacement of the axial direction of the said rotor is possible.
As the piston is pushed out, the two pads are pressed against both side surfaces of the rotor to perform braking.
In particular, in the floating caliper type disc brake of the present invention, both the torque receiving members are separate from the fixing member and have guide holes for slidably fitting the respective guide pins. . Further, the both torque receiving members have, in part, the fixing member in the axial direction of the rotor, for example, a screw or a convex portion formed on one of the fixing member and the two torque receiving members on the other side. They are connected by fitting into the formed through-holes and caulking the tips of the convex portions.

上述の様な本発明を実施する場合に好ましくは、請求項２に記載した様に、上記固定部材に上記両トルク受け部材を連結した状態で、これら両トルク受け部材の一部にそれぞれ形成した側壁部と、上記固定部材の一部にそれぞれ形成した固定側壁部とを当接させる。尚、これら両側壁部は、上記ロータの回転方向に関して、上記両パッドを支持する側と反対側の一部にそれぞれ形成したものである。又、上記固定側壁部は、上記固定部材の一部で、上記両側壁部と対向する部分に、これら両側壁部と平行に形成したものである。
又、より好ましくは、請求項３に記載した様に、上記固定部材の一部で上記両トルク受け部材を連結する側を平坦面とし、この固定部材側の平坦面と、これら両トルク受け部材の端部の一部でこの固定部材側の平坦面と平行に形成された平坦面とが当接した状態で、これら両部材を連結する。
又、より好ましくは、請求項４に記載した様に、上記両トルク受け部材の上記両パッドからトルクを受ける部分のうち、少なくとも上記固定部材との連結部から遠い側であるアウタ側のパッドからトルクを受ける部分の回入側、回出側のそれぞれの構造を、上記ロータの回転方向に拘らずトルクを支承可能な構造である、所謂押しアンカと引きアンカとの両方を備えるものとする。
更に好ましくは、上記両トルク受け部材の上記両パッドからトルクを受ける部分の構造を、これら両パッドから加わる上記ロータの回転方向のトルクを支承する事に加えて、これら両パッドが上記ロータの径方向外方に変位する事を阻止可能とする。 Preferably, when the present invention as described above is carried out, as described in claim 2, the torque receiving members are connected to the fixing member and formed on a part of both torque receiving members. A side wall part and the fixed side wall part each formed in a part of said fixing member are made to contact | abut. These both side wall portions are formed on a part of the opposite side to the side supporting both the pads with respect to the rotation direction of the rotor. The fixed side wall portion is a part of the fixed member, and is formed in a portion facing the both side wall portions in parallel to the both side wall portions.
More preferably, as described in claim 3, a part of the fixed member that connects the two torque receiving members is a flat surface, the flat surface on the fixed member side, and the two torque receiving members. These members are connected in a state in which a flat surface formed in parallel with the flat surface on the fixing member side is in contact with a part of the end portion of the fixing member.
More preferably, as described in claim 4, at least a portion of the torque receiving member that receives torque from the two pads from an outer side pad that is at least far from the connecting portion with the fixing member. It is assumed that both the so-called push anchor and pull anchor, which are structures capable of supporting the torque regardless of the rotation direction of the rotor, are provided on each of the turn-in side and the turn-out side of the portion that receives the torque.
More preferably, in addition to supporting the torque in the rotational direction of the rotor applied from the two pads, the structure of the portion of the torque receiving member that receives the torque from the two pads is also used. It is possible to prevent displacement in the direction outward.

更に、本発明のうち、請求項６に記載したフローティングキャリパ型ディスクブレーキの製造方法は、上述の請求項１〜５のうちの何れか１項に記載したフローティングキャリパ型ディスクブレーキを製造する方法である。先ず、上記両トルク受け部材に、少なくとも、上記各案内ピンと、これら各案内ピンと各案内孔との摺動部を密封する密封部材（例えばブーツ）とを組み付けて中間組立体とする。その後、この中間組立体と、上記キャリパ及び上記固定部材とを組み合わせる。
尚、この際、請求項７に記載した様に、上記中間組立体とキャリパとを組み付けて第二の中間組立体とした後、この第二の中間組立体と上記固定部材とを締結する事もできる。 Furthermore, the manufacturing method of the floating caliper disc brake according to claim 6 of the present invention is a method of manufacturing the floating caliper disc brake according to any one of claims 1 to 5 described above. is there. First, at least the guide pins and a sealing member (for example, a boot) that seals the sliding portions of the guide pins and the guide holes are assembled to the torque receiving members to form an intermediate assembly. Thereafter, the intermediate assembly is combined with the caliper and the fixing member.
At this time, as described in claim 7, after the intermediate assembly and the caliper are assembled into a second intermediate assembly, the second intermediate assembly and the fixing member are fastened. You can also.

上述の様に構成する本発明によれば、フローティングキャリパ型ディスクブレーキの製造を容易に行なえる。
即ち、両トルク受け部材と固定部材とを別体に形成している為、精度が要求される部分の加工を別々に行なえると共に、それぞれ、単独の部材として管理できる。この為、ディスクブレーキの製造を容易に行なえると共に、部品管理を行ない易くなり、生産性を良好にできる。 According to the present invention configured as described above, the floating caliper type disc brake can be easily manufactured.
In other words, since both the torque receiving member and the fixing member are formed separately, the parts requiring high accuracy can be processed separately, and each can be managed as a single member. For this reason, the disc brake can be easily manufactured and the parts can be easily managed to improve the productivity.

又、本発明の場合、車体に組み付けた場合に、ホイールとのレイアウト性を良好にできる。即ち、上記両トルク受け部材は、上記固定部材と軸方向に連結されている為、径方向寸法を抑える事ができる。この為、ホイールと干渉しにくくなる。又、本発明の場合、上記固定部材に捩れる方向に力が作用しても、上記両トルク受け部材とこの固定部材との結合部の強度を確保できる。即ち、制動時に前記両パッドから作用するトルクが、上記両トルク受け部材から上記固定部材に作用する。この場合に、この固定部材と上記両トルク受け部材との結合部に、この固定部材が捩れる方向に力が作用し、この結合部に上記ロータの軸方向に力が作用する。但し、本発明の場合、上記固定部材と両トルク受け部材とは、軸方向に連結されている為、この様な力に対して十分な強度を確保できる。   In the case of the present invention, the layout with the wheel can be improved when assembled to the vehicle body. That is, since both the torque receiving members are connected to the fixed member in the axial direction, the radial dimension can be suppressed. For this reason, it becomes difficult to interfere with a wheel. In the case of the present invention, even if a force acts on the fixing member in a twisting direction, the strength of the joint portion between the torque receiving members and the fixing member can be ensured. That is, torque acting from both pads during braking acts on the fixed member from both torque receiving members. In this case, a force acts in the direction in which the fixing member is twisted on the joint between the fixing member and the torque receiving members, and a force acts in the axial direction of the rotor on the joint. However, in the case of the present invention, since the fixing member and both torque receiving members are connected in the axial direction, sufficient strength against such a force can be secured.

又、請求項２に記載した様に、上記固定部材に上記両トルク受け部材を固定した状態で、これら両トルク受け部材の一部にそれぞれ形成した側壁部と、上記固定部材の一部にそれぞれ形成した固定側壁部とを当接させれば、上記両トルク受け部材に作用するトルクを、上記固定部材により効果的に支承できる。そして、これら両トルク受け部材と固定部材との結合部に、ロータの回転方向に大きな力が作用する事を防止できる。   According to a second aspect of the present invention, in a state where both the torque receiving members are fixed to the fixing member, a side wall portion formed on each of the torque receiving members and a part of the fixing member, respectively. If the formed fixed side wall portion is brought into contact, the torque acting on both the torque receiving members can be effectively supported by the fixed member. And it can prevent that big force acts on the rotation direction of a rotor at the joint part of both these torque receiving members and a fixing member.

又、請求項３に記載した様に、上記固定部材の一部で上記両トルク受け部材を連結する側に設けた固定部材側の平坦面と、これら両トルク受け部材の端部の一部でこの固定部材側の平坦面と平行に形成された平坦面とが当接した状態で、これら両部材を連結すれば、上記両トルク受け部材の位置決めを図り易く、これら両トルク受け部材に形成した案内孔を、上記ロータの軸方向に精度良く配置し易くなる。   According to a third aspect of the present invention, there is a flat surface on the side of the fixing member provided on the side where the two torque receiving members are connected with a part of the fixing member, and a part of the end portions of these torque receiving members. If these two members are connected in a state where the flat surface formed in parallel with the flat surface on the side of the fixed member is in contact with each other, it is easy to position both the torque receiving members, and the two torque receiving members are formed. It becomes easy to arrange the guide holes with high accuracy in the axial direction of the rotor.

又、請求項４に記載した様に、上記両トルク受け部材を、所謂押しアンカと引きアンカとの両方を備えるものとすれば、制動時にこれら両トルク受け部材に作用するトルクを分散して、これら両トルク受け部材の強度を確保し易くなる。特に、上記両トルク受け部材の上記両パッドからトルクを受ける部分のうち、アウタ側のパッドからトルクを受ける部分は、通常インナ側に存在する、上記両トルク受け部材と上記固定部材との結合部からの距離が遠くなる。この為、制動時に、このトルクに基づきこの部分に作用する、この結合部を支点としたモーメントが、インナ側のパッドからトルクを受ける部分よりも大きくなる。従って、少なくともアウタ側のパッドからトルクを受ける部分を、所謂押しアンカと引きアンカとの両方を備えるもの（押し引きアンカ構造）とした場合、この部分に作用するトルクを分散して上記モーメントを小さくできる。この結果、上記結合部の強度を十分に確保できる。又、アウタ側とインナ側とのうちの何れか一方のみを押し引きアンカ構造とした場合、ダイスに対しパンチを一方向に押し込む事により形成する圧造加工が可能となる。例えば、インナ側のみを押し引きアンカ構造とした場合、アンカ側から型に押し込めば、切削加工等を施してトルク受け部材とする前の中間素材を、圧造加工により得る事ができる。   Further, as described in claim 4, if both the torque receiving members are provided with both a so-called pushing anchor and a pulling anchor, the torque acting on these torque receiving members during braking is dispersed, It becomes easy to ensure the strength of both torque receiving members. In particular, of the portions of the torque receiving members that receive torque from the pads, the portion that receives torque from the outer pad is normally located on the inner side, and is a joint between the torque receiving members and the fixing member. The distance from becomes far. For this reason, during braking, the moment acting on this portion based on this torque, with this connecting portion as a fulcrum, is greater than the portion receiving torque from the inner pad. Therefore, if at least the part that receives torque from the outer pad is provided with both a so-called push anchor and pull anchor (push / pull anchor structure), the torque acting on this part is dispersed to reduce the moment. it can. As a result, it is possible to sufficiently ensure the strength of the coupling portion. In addition, when only one of the outer side and the inner side is pushed and pulled to have an anchor structure, the forming process can be performed by pushing the punch in one direction with respect to the die. For example, when the anchor structure is pushed and pulled only on the inner side, the intermediate material before being used as a torque receiving member by cutting or the like can be obtained by forging if it is pushed into the mold from the anchor side.

更に、請求項５に記載した様に、上記両トルク受け部材を、パッドがロータの径方向外方に変位する事を阻止可能とすれば、このパッドが偶力により浮き上がるのを阻止できる。本発明の場合、上記両トルク受け部材を固定部材と別体としている為、この様な構造を得る為の加工が容易である。   Furthermore, as described in claim 5, if the two torque receiving members can prevent the pad from being displaced radially outward of the rotor, the pad can be prevented from being lifted by a couple of forces. In the case of the present invention, since both the torque receiving members are separated from the fixed member, processing for obtaining such a structure is easy.

又、本発明のフローティングキャリパ型ディスクブレーキは、上述した様に、両トルク受け部材と固定部材とを別体とし、更に、これら両トルク受け部材に案内孔を形成している為、請求項６に記載した様に、上記両トルク受け部材と、各案内ピンと、密封部材とを組み合わせて中間組立体とする事ができる。そして、この様な中間組立体を所定の部品ユニットとして管理すれば、複数種類のキャリパや固定部材と組み合わせる事ができ、フローティングキャリパ型ディスクブレーキの生産効率を向上させられる。
尚、本発明の場合、例えば、前述の図１４、１５に示した様なサポート３を配置する事なく、上記両トルク受け部材とキャリパとを直接組み付ける事が可能である。この為、これら両部材同士、及び、パッドと案内ピンと密封部材とを組み合わせた第二の中間組立体として管理すれば、複数種類の固定部材に対応可能である。例えば、請求項７に記載した様に、上記中間組立体とキャリパとを締結して、上記第二の中間組立体とする。 In the floating caliper type disc brake of the present invention, as described above, since both the torque receiving members and the fixing member are separated, and further, guide holes are formed in these torque receiving members. As described in the above, an intermediate assembly can be obtained by combining both the torque receiving members, the guide pins, and the sealing member. If such an intermediate assembly is managed as a predetermined component unit, it can be combined with a plurality of types of calipers and fixing members, and the production efficiency of the floating caliper type disc brake can be improved.
In the case of the present invention, for example, both the torque receiving member and the caliper can be directly assembled without disposing the support 3 as shown in FIGS. For this reason, if it manages as a 2nd intermediate assembly which combined these both members and the pad, the guide pin, and the sealing member, it can respond to a multiple types of fixing member. For example, as described in claim 7, the intermediate assembly and the caliper are fastened to form the second intermediate assembly.

［実施の形態の第１例］
図１〜１１は、本発明の実施の形態の第１例を示している。本例のフローティングキャリパ型ディスクブレーキは、固定部材である取付板部２９と、１対のパッド３０ａ、３０ｂと、１対のトルク受け部材３１ａ、３１ｂと、キャリパ２ａと、２本の案内ピン５ｂ、５ｂとを備える。このうちの取付板部２９は、車輪と共に回転する、図示しないロータに隣接して、車体に固定される。又、上記両パッド３０ａ、３０ｂは、このロータの両側に配置される。又、上記両トルク受け部材３１ａ、３１ｂは、これら両パッド３０ａ、３０ｂを上記ロータの軸方向（図１の上下方向、図２の左右方向、図３、４の表裏方向。尚、本明細書中、特に断らずに「軸方向」と言えば、「ロータの軸方向」を指す。）に変位可能に支持すると共に、制動時にこれら両パッド３０ａ、３０ｂから上記ロータの回転方向のトルクを受けるものである。又、上記キャリパ２ａは、このロータを跨ぐ様に配置され、このロータに関して一方の側に爪部１３ａを、他方の側にピストンを嵌装する為のシリンダ部１２ａを、それぞれ備えるものである。更に、上記各案内ピン５ｂ、５ｂは、上記キャリパ２ａを軸方向の変位可能に支持するものである。そして、上記ピストンの押し出しに伴い、上記両パッド３０ａ、３０ｂを上記ロータの両側面に押し付けて制動を行なう。尚、フローティングキャリパ型ディスクブレーキにより制動を行なう為の基本的な構成及び作用は、例えば、前述の図１４〜１５に示した様な従来構造と同様である。 [First example of embodiment]
1 to 11 show a first example of an embodiment of the present invention. The floating caliper type disc brake of this example includes a mounting plate portion 29 as a fixing member, a pair of pads 30a and 30b, a pair of torque receiving members 31a and 31b, a caliper 2a, and two guide pins 5b. 5b. Of these, the mounting plate portion 29 is fixed to the vehicle body adjacent to a rotor (not shown) that rotates with the wheel. The pads 30a and 30b are arranged on both sides of the rotor. Further, both the torque receiving members 31a and 31b are arranged so that these pads 30a and 30b are arranged in the axial direction of the rotor (the vertical direction in FIG. 1, the left and right direction in FIG. 2, the front and back directions in FIGS. 3 and 4. In particular, the term “axial direction” refers to “axial direction of the rotor” unless otherwise specified.) And supports the torque in the rotational direction of the rotor from both pads 30a and 30b during braking. Is. The caliper 2a is disposed so as to straddle the rotor, and includes a claw portion 13a on one side and a cylinder portion 12a for fitting a piston on the other side of the rotor. The guide pins 5b and 5b support the caliper 2a so as to be axially displaceable. As the piston is pushed out, the pads 30a and 30b are pressed against both side surfaces of the rotor to perform braking. The basic configuration and action for braking by the floating caliper type disc brake are the same as the conventional structure as shown in FIGS.

又、本例の場合、上記各案内ピン５ｂ、５ｂは、上記ロータの径方向（尚、本明細書中、特に断らずに「径方向」と言えば、「ロータの径方向」を指す。）外方にこのロータを跨ぐ様に配置される。これら各案内ピン５ｂ、５ｂを摺動可能に嵌装する案内孔６ｂ、６ｂ（図７、１０）は、次述する様に、上記両トルク受け部材３１ｂ、３１ｂに形成され、やはり、上記ロータの径方向外方にこのロータを跨ぐ様に配置される。従って、本例の場合、上記各案内孔６ｂ、６ｂと上記各案内ピン５ｂ、５ｂとの摺動部が、上記ロータの径方向外方に位置する。この結果、この摺動部を上記キャリパ２ａの重心位置に近く配置できる。一方、例えば、前述の特許文献２にも記載されている様に、案内孔と案内ピンとの摺動部がキャリパの重心位置からインナ側に大きく外れた部分に存在する構造が、従来から知られている。この構造の場合、キャリパの挙動が不安定になり易く、振動が生じる可能性がある。これに対して本例の様に、案内孔６ｂ、６ｂと案内ピン５ｂ、５ｂとの摺動部をキャリパ２ａの重心位置に近く配置できれば、このキャリパ２ａの安定性を高くして、振動を生じにくくできる。   In the case of this example, each of the guide pins 5b and 5b refers to the radial direction of the rotor (in the present specification, “radial direction” refers to “radial direction of the rotor” unless otherwise specified). ) It is arranged to straddle this rotor outward. Guide holes 6b and 6b (FIGS. 7 and 10) into which the guide pins 5b and 5b are slidably fitted are formed in the torque receiving members 31b and 31b as described below. It arrange | positions so that this rotor may be straddled on the radial direction outer side. Therefore, in the case of this example, the sliding portions between the guide holes 6b and 6b and the guide pins 5b and 5b are located radially outward of the rotor. As a result, the sliding portion can be disposed close to the position of the center of gravity of the caliper 2a. On the other hand, for example, as described in Patent Document 2 described above, a structure in which the sliding portion between the guide hole and the guide pin is present in a portion that is largely deviated from the center of gravity position of the caliper to the inner side has been known. ing. In the case of this structure, the caliper behavior tends to become unstable, and vibration may occur. On the other hand, if the sliding portion between the guide holes 6b and 6b and the guide pins 5b and 5b can be arranged close to the center of gravity of the caliper 2a as in this example, the stability of the caliper 2a is increased and vibration is generated. It can be difficult to occur.

又、本例の場合、上記両トルク受け部材３１ａ、３１ｂは、上記取付板部２９とは別体に形成されている。又、これら両トルク受け部材３１ａ、３１ｂは、上記各案内ピン５ｂ、５ｂを摺動可能に嵌装する上記各案内孔６ｂ、６ｂを有している。この様な両トルク受け部材３１ａ、３１ｂは、例えば図４、５、７〜１１に示す様に、径方向外側の面を、上記ロータの外周縁とほぼ同心の円弧状に傾斜させて、全体を略三角柱状に形成している。又、上記両トルク受け部材３１ａ、３１ｂを、フローティングキャリパ型ディスクブレーキに組み込んだ状態で、パッド３０ａ、３０ｂが存在する側となる内側に、上記案内孔６ｂ、６ｂを有する案内筒部３２を設けている。この為、フローティングキャリパ型ディスクブレーキを構成した状態で、上記両トルク受け部材３１ａ、３１ｂの径方向外方への突出量を抑えて、上記ディスクブレーキの小型化を図れる。   In the case of this example, both the torque receiving members 31 a and 31 b are formed separately from the mounting plate portion 29. The torque receiving members 31a and 31b have the guide holes 6b and 6b into which the guide pins 5b and 5b are slidably fitted. The two torque receiving members 31a and 31b, as shown in FIGS. 4, 5, and 7 to 11, for example, have a radially outer surface inclined in an arc shape substantially concentric with the outer peripheral edge of the rotor. Is formed in a substantially triangular prism shape. Further, a guide cylinder portion 32 having the guide holes 6b and 6b is provided on the inner side where the pads 30a and 30b are present in a state where both the torque receiving members 31a and 31b are incorporated in a floating caliper type disc brake. ing. For this reason, in the state where the floating caliper type disc brake is configured, it is possible to reduce the size of the disc brake by suppressing the projecting amount of the both torque receiving members 31a and 31b outward in the radial direction.

又、上記両トルク受け部材３１ａ、３１ｂの内側面で、上記案内筒部３２の径方向内方部分に、それぞれ係合凹部３４、３４を形成している。これら各係合凹部３４、３４は、上記両パッド３０ａ、３０ｂを構成するプレッシャプレート１１ｂの、上記ロータの回転方向両端部に形成した係合凸部３３、３３と係合する。又、上記案内筒部３２は、上記両トルク受け部材３１ａ、３１ｂの径方向外寄り部分に、上記ロータの軸方向と平行に配置している。そして、上記案内筒部３２に、軸方向に貫通した上記案内孔６ｂを形成している。この案内孔６ｂのアウタ側（図１の上側、図２の左側）の開口部は、案内ピン５ｂを嵌装後、盲栓（図示せず）等により塞ぐ。尚、この案内孔６ｂの具体的な形状は、例えば、前述の図１４に示した様な従来構造と同様である。   Engaging recesses 34 and 34 are formed on the inner side surfaces of the torque receiving members 31a and 31b in the radially inner portion of the guide tube portion 32, respectively. These engagement recesses 34 and 34 engage with engagement projections 33 and 33 formed at both ends in the rotational direction of the rotor of the pressure plate 11b constituting both the pads 30a and 30b. Further, the guide cylinder portion 32 is disposed parallel to the axial direction of the rotor at the radially outward portion of the torque receiving members 31a and 31b. And the said guide hole 6b penetrated to the axial direction in the said guide cylinder part 32 is formed. The opening on the outer side (upper side in FIG. 1, left side in FIG. 2) of the guide hole 6b is closed with a blind plug (not shown) after the guide pin 5b is fitted. The specific shape of the guide hole 6b is the same as that of the conventional structure as shown in FIG.

本例の場合、上記各係合凹部３４、３４を次の様に構成している。即ち、上記両トルク受け部３１ａ、３１ｂの内側で、上記案内筒部３２の径方向内方部分を、平坦な内側面３５、３５としている。又、これら各内側面３５、３５の径方向内端部から突出した突出腕部３６、３６の先端部を、径方向外方に折り曲げている。そして、これら各突出腕部３６、３６と、上記各内側面３５、３５と、上記案内筒部３２の径方向内方の側面とにより囲まれる部分を、上記各係合凹部３４、３４としている。   In the case of this example, each of the engaging recesses 34 is configured as follows. That is, the inner side in the radial direction of the guide tube portion 32 is formed as flat inner side surfaces 35 and 35 inside the torque receiving portions 31a and 31b. Moreover, the front-end | tip part of the protrusion arm parts 36 and 36 which protruded from the radial direction inner edge part of these each inner surface 35 and 35 is bent to radial direction outward. The portions surrounded by the projecting arm portions 36, 36, the inner side surfaces 35, 35, and the radially inner side surface of the guide tube portion 32 are the engagement recesses 34, 34. .

又、上記両トルク受け部材３１ａ、３１ｂの軸方向中間部で上記案内筒部３２よりも径方向内方部分に切り欠き３８を、上記ロータの回転方向に沿って形成している。そして、前記ディスクブレーキを車体に組み付けた状態で、上記両トルク受け部材３１ａ、３１ｂの切り欠き３８、３８内に、上記ロータが進入可能としている。従って、上記各係合凹部３４、３４は、上記両トルク受け部材３１ａ、３１ｂの内側に、上記各切り欠き３８、３８を挟んで、アウタ側とインナ側（図１の下側、図２の右側）とにそれぞれ形成されている。言い換えれば、上記両トルク受け部材３１ａ、３１ｂは、上記ロータを跨ぐ様に配置される。そして、インナ側とアウタ側とにそれぞれ存在する係合凹部３４、３４と前記プレッシャプレート１１ｂの係合凸部３３、３３との係合により、前記両パッド３０ａ、３０ｂをそれぞれ軸方向の変位自在に支持している。   Further, a notch 38 is formed along the rotational direction of the rotor at an axially intermediate portion between the torque receiving members 31a and 31b in a radially inner portion of the guide tube portion 32. The rotor can enter the notches 38 and 38 of the torque receiving members 31a and 31b with the disc brake assembled to the vehicle body. Accordingly, the engaging recesses 34, 34 are arranged on the outer side and the inner side (the lower side of FIG. 1, FIG. 2) with the notches 38, 38 sandwiched between the torque receiving members 31a, 31b. And the right side). In other words, the torque receiving members 31a and 31b are disposed so as to straddle the rotor. The pads 30a and 30b can be displaced in the axial direction by engaging the engaging recesses 34 and 34 existing on the inner side and the outer side, respectively, with the engaging projections 33 and 33 of the pressure plate 11b. I support it.

又、上記両トルク受け部材３１ａ、３１ｂのうちで、上記両パッド３０ａ、３０ｂとは反対側である外側のインナ側端部には、軸方向と平行に側壁部４０を形成している。この側壁部４０は、上記両トルク受け部材３１ａ、３１ｂを前記取付板部２９に固定した状態で、後述する、この取付板部２９の一部に形成した固定側壁部３９、３９と平行である（同一平面上に位置する）。又、上記両トルク受け部材３１ａ、３１ｂのインナ側端面で、上記側壁部４０よりも外側部分を、この側壁部４０とほぼ直角な平坦面４１としている。この平坦面４１は、上記両トルク受け部材３１ａ、３１ｂを上記取付板部２９に固定した状態で、後述する、この取付板部２９の延出板部４３、４３の上記インナ側端面と対向する側面と平行とし（同一平面上に位置させ）ている。この様に構成される両トルク受け部材３１ａ、３１ｂは、例えば、鍛造加工により中間素材を形成し、この中間素材に所定の切削加工等を施す事により形成する。   A side wall 40 is formed in parallel with the axial direction at the outer inner end of the both torque receiving members 31a, 31b opposite to the pads 30a, 30b. The side wall portion 40 is parallel to fixed side wall portions 39 and 39 formed on a part of the mounting plate portion 29, which will be described later, in a state where the torque receiving members 31a and 31b are fixed to the mounting plate portion 29. (Located on the same plane). Further, on the inner side end surfaces of the torque receiving members 31 a and 31 b, the outer portion of the side wall portion 40 is a flat surface 41 substantially perpendicular to the side wall portion 40. The flat surface 41 faces the inner side end surfaces of the extension plate portions 43 and 43 of the mounting plate portion 29, which will be described later, in a state where the torque receiving members 31a and 31b are fixed to the mounting plate portion 29. It is parallel to the side surface (located on the same plane). Both the torque receiving members 31a and 31b configured in this way are formed by, for example, forming an intermediate material by forging and performing predetermined cutting or the like on the intermediate material.

又、上記両トルク受け部材３１ａ、３１ｂには、前記案内ピン５ｂと、特許請求の範囲に記載した密封部材である防塵用のブーツ７ａと、パッドクリップ４８とをそれぞれ組み付けている。即ち、上記案内孔６ｂのインナ側開口部と、上記案内ピン５ｂの基端部との間に、この案内ピン５ｂを軸方向に変位可能に、且つ、この案内ピン５ｂと上記案内孔６ｂとの摺動部を密閉する、軸方向に伸縮自在な上記ブーツ７ａを設けている。又、ステンレス鋼板等の耐食性及び弾性を有する金属板により一体に形成した上記パッドクリップ４８を、上記両トルク受け部材３１ａ、３１ｂの係合凹部３４、３４内に組み付けている。   Further, the guide pin 5b, a dustproof boot 7a which is a sealing member described in claims, and a pad clip 48 are assembled to the torque receiving members 31a and 31b, respectively. That is, the guide pin 5b can be displaced in the axial direction between the inner side opening of the guide hole 6b and the base end of the guide pin 5b, and the guide pin 5b and the guide hole 6b The above-mentioned boot 7a is provided which seals the sliding portion and is freely expandable and contractable in the axial direction. Further, the pad clip 48 formed integrally with a metal plate having corrosion resistance and elasticity such as a stainless steel plate is assembled in the engaging recesses 34, 34 of the torque receiving members 31a, 31b.

又、前記取付板部２９は、必要とする剛性を確保する為に十分な厚さ寸法を有する１枚の金属板に、打抜き等の所定のプレス加工等を施して成るもので、例えば、図８に示す様に、上記ロータの径方向外方に開口した凹部４２を有する。この凹部４２の内面のうちで、このロータの回転方向両端部には、前記固定側壁部３９、３９をそれぞれ形成している。言い換えれば、上記取付板部２９の上記ロータの回転方向両端部を径方向外方に延出して前記延出板部４３、４３とし、これら両延出板部４３、４３の上記凹部４２の中央側の内側面を、上記固定側壁部３９、３９としている。又、この凹部４２の内面のうち、これら両固定側壁部３９、３９よりも中央寄りに、これら両固定側壁部３９、３９とほぼ直角に平面部４４、４４を形成している。又、上記取付板部２９の径方向内方部分で幅方向に離隔した部分に、それぞれ車体に取り付ける為の取付孔４、４を形成している。   The mounting plate 29 is formed by subjecting a single metal plate having a thickness dimension sufficient to ensure the required rigidity to a predetermined pressing process such as punching. As shown in FIG. 8, the rotor has a recess 42 that opens outward in the radial direction of the rotor. Of the inner surface of the recess 42, the fixed side wall portions 39, 39 are formed at both ends in the rotational direction of the rotor. In other words, both ends of the mounting plate 29 in the rotational direction of the rotor extend radially outward to form the extended plate portions 43, 43, and the center of the recessed portion 42 of both the extended plate portions 43, 43. The inner side surface on the side is the fixed side wall portions 39 and 39. Further, in the inner surface of the concave portion 42, flat portions 44 and 44 are formed at a position closer to the center than the both fixed side wall portions 39 and 39, substantially perpendicular to the both fixed side wall portions 39 and 39. Further, attachment holes 4 and 4 for attachment to the vehicle body are formed in the radially inward portion of the attachment plate portion 29 and spaced apart in the width direction.

この様な取付板部２９と、上述の様な両トルク受け部材３１ａ、３１ｂとを組み付ける場合には、上記固定側壁部３９、３９と上記側壁部４０、４０とを当接させると共に、上記平坦面４１、４１と上記取付板部２９の延出板部４３、４３のアウタ側の側面とを当接させる。この状態で、上記両トルク受け部材３１ａ、３１ｂは、上記凹部４２の平面部４４、４４上に載置される。そして、ねじ４５、４５を、上記ロータの軸方向に関し、インナ側からアウタ側に向けて、上記両延出板部４３、４３に形成した通孔４６、４６に挿通し、上記両トルク受け部材３１ａ、３１ｂの平坦面４１、４１にそれぞれ開口したねじ孔４７、４７に螺合緊締する。これにより、上記両トルク受け部材３１ａ、３１ｂと上記取付板部２９とが、上記ロータの軸方向に連結される。尚、この様なねじ４５、４５による結合に代えて、例えば、上記両延出板部４３、４３と上記両トルク受け部材３１ａ、３１ｂの平坦面４１、４１との一方に形成された凸部を、他方に形成された貫通孔に嵌合して、この凸部の先端部をかしめる事により連結する事もできる。   When assembling the mounting plate 29 and the torque receiving members 31a and 31b as described above, the fixed side wall 39 and 39 and the side walls 40 and 40 are brought into contact with each other and the flat side The surfaces 41, 41 are brought into contact with the outer side surfaces of the extension plate portions 43, 43 of the mounting plate portion 29. In this state, the torque receiving members 31 a and 31 b are placed on the flat portions 44 and 44 of the recess 42. Then, the screws 45, 45 are inserted into the through holes 46, 46 formed in the two extending plate portions 43, 43 from the inner side toward the outer side with respect to the axial direction of the rotor. The screw holes 47 and 47 opened in the flat surfaces 41 and 41 of the 31a and 31b are respectively screwed and tightened. Thereby, both the torque receiving members 31a and 31b and the mounting plate portion 29 are coupled in the axial direction of the rotor. Instead of such coupling by the screws 45, 45, for example, convex portions formed on one of the two extending plate portions 43, 43 and the flat surfaces 41, 41 of the torque receiving members 31a, 31b, for example. Can be connected to each other by fitting them into a through hole formed on the other side and caulking the tip of the convex portion.

又、本例の場合、上記両トルク受け部材３１ａ、３１ｂ同士の間に、前記両パッド３０ａ、３０ｂを配置している。この為に、前述した様に、これら両パッド３０ａ、３０ｂのプレッシャプレート１１ｂの両端部に形成した係合凸部３３、３３と、上記両トルク受け部材３１ａ、３１ｂに形成した係合凹部３４、３４とを係合させている。上記係合凸部３３、３３は、先端部を径方向内方に折り曲げて、この部分を、上記係合凹部３４、３４を構成する突出腕部３６、３６と内側面３５、３５とに囲まれる奥部に進入させている。又、この状態で、上記係合凹部３４と上記係合凸部３３との間で、前記パッドクリップ４８が弾性的に突っ張り、上記両パッド３０ａ、３０ｂが、非制動時にがたつく事を防止すると共に、上記プレッシャプレート１１ｂと上記両トルク受け部材３１ａ、３１ａとの摺動部が錆び付くのを防止する。   In the case of this example, the pads 30a and 30b are disposed between the torque receiving members 31a and 31b. For this reason, as described above, the engaging protrusions 33, 33 formed on both ends of the pressure plate 11b of both the pads 30a, 30b, and the engaging recess 34 formed on both the torque receiving members 31a, 31b, 34 is engaged. The engaging projections 33, 33 are bent at the tip end inward in the radial direction, and this portion is surrounded by protruding arm portions 36, 36 and inner side surfaces 35, 35 constituting the engaging recesses 34, 34. It is made to enter the back. Further, in this state, the pad clip 48 elastically stretches between the engagement recess 34 and the engagement protrusion 33, and both the pads 30a and 30b are prevented from rattling during non-braking. The sliding portions between the pressure plate 11b and the torque receiving members 31a and 31a are prevented from being rusted.

これにより、上記両パッド３０ａ、３０ｂを、上記各係合凹部３４、３４に沿って軸方向に摺動可能とすると共に、これら両パッド３０ａ、３０ｂに作用するトルクを、上記各係合凸部３３、３３と上記各係合凹部３４、３４との係合により支承可能としている。本例の場合、これら係合凸部３３、３３の先端部を上記各係合凹部３４、３４の奥部に進入させている為、それぞれの係合部で、上記ロータの回転方向に拘らずトルクを支承可能である。言い換えれば、押しアンカと引きアンカとの両方を備えた構成としている。即ち、上記両パッド３０ａ、３０ｂから、例えば、図３の時計方向にトルクが作用した場合、このトルクが小さい場合には、図３の左側の係合凸部３３の先端部内側面と、係合凹部３４の突出腕部３６の先端部外側面との係合により支承する、所謂引きアンカとなる。これに対して上記トルクが大きくなると、図３の右側の係合凸部３３の先端部外側面と、係合凹部３４の内側面３５との係合により支承する、所謂押しアンカともなる。又、本例の場合、案内筒部３２の径方向内方の側面と係合凸部３３の径方向外側面とが係合して、パッド３０ａ、３０ｂが偶力により浮き上がるのを阻止できる。即ち、制動時には、回入側と回出側との何れか一方の係合部を中心として、パッド３０ａ、３０ｂに偶力が作用する。この場合に、他方の係合部でパッド３０ａ、３０ｂが浮き上がる傾向となる。本例の場合、これらパッド３０ａ、３０ｂが浮き上がる傾向となっても、上記案内筒部３２の径方向内方の側面と係合して、この浮き上がりを阻止できる。   Thus, both the pads 30a and 30b can be slid in the axial direction along the respective engagement recesses 34 and 34, and the torque acting on both the pads 30a and 30b is transferred to the respective engagement projections. 33, 33 and the engagement recesses 34, 34 can be supported. In the case of this example, since the leading end portions of the engaging convex portions 33, 33 are inserted into the deep portions of the engaging concave portions 34, 34, the respective engaging portions do not depend on the rotation direction of the rotor. Torque can be supported. In other words, the structure includes both a push anchor and a pull anchor. That is, for example, when torque is applied from both the pads 30a and 30b in the clockwise direction in FIG. 3, when the torque is small, the inner side surface of the front end of the engaging protrusion 33 on the left side in FIG. This is a so-called pulling anchor that is supported by engagement with the outer surface of the distal end portion of the protruding arm portion 36 of the recess 34. On the other hand, when the torque increases, it becomes a so-called push anchor that is supported by the engagement between the outer surface of the front end of the engaging projection 33 on the right side of FIG. 3 and the inner surface 35 of the engaging recess 34. Further, in the case of this example, it is possible to prevent the pads 30a and 30b from being lifted by a couple due to the engagement of the radially inner side surface of the guide tube portion 32 and the radially outer side surface of the engagement convex portion 33. That is, at the time of braking, a couple acts on the pads 30a and 30b with the engaging portion on either the turn-in side or the turn-out side as the center. In this case, the pads 30a and 30b tend to float at the other engaging portion. In the case of this example, even if these pads 30a and 30b tend to float, they can be engaged with the radially inner side surface of the guide tube portion 32 to prevent the lift.

尚、本例の場合、インナ側とアウタ側との両方で、前記両パッド３０ａ、３０ｂから作用するトルクを支承する構造を、押しアンカと引きアンカとの両方を備えた構造（押し引きアンカ構造）としているが、この様な押し引きアンカ構造は、アウタ側のみとしても良い。即ち、前記両トルク受け部材３１ａ、３１ｂの上記両パッド３０ａ、３０ｂからトルクを受ける部分のうち、アウタ側のパッド３０ｂからトルクを受ける部分は、上記両トルク受け部材３１ａ、３１ｂと前記取付板部２９との結合部からの距離が遠くなる。この為、制動時に、このトルクに基づきこの部分に作用する、この結合部を支点としたモーメントが、インナ側のパッド３０ａからトルクを受ける部分よりも大きくなる。従って、上記アウタ側のパッド３０ｂからトルクを受ける部分を、上記押し引きアンカ構造とした場合、この部分に作用するトルクを分散して上記モーメントを小さくできる効果が大きい。この結果、上記結合部の強度を十分に確保できる。尚、アウタ側のみを押し引きアンカ構造とする（インナ側の引きアンカ構造を省略する）場合、両トルク受け部材３１ａ、３１ｂのインナ側のトルクを支承する部分の構造を押しアンカのみとすべく、このインナ側の突出腕部３６を省略できる。これにより、上記両トルク受け部材３１ａ、３１ｂの製造を、より容易に行なえる。   In the case of this example, the structure for supporting the torque acting from both the pads 30a and 30b on both the inner side and the outer side has a structure including both a push anchor and a pull anchor (push / pull anchor structure). However, such a push-pull anchor structure may be provided only on the outer side. That is, of the portions of the torque receiving members 31a and 31b that receive torque from the pads 30a and 30b, the portions that receive torque from the outer pad 30b are the torque receiving members 31a and 31b and the mounting plate portion. The distance from the coupling | bond part with 29 becomes long. For this reason, the moment which acts on this part based on this torque at the time of braking and which uses this joint as a fulcrum becomes larger than the part which receives torque from the inner pad 30a. Therefore, when the portion receiving torque from the outer pad 30b has the push-pull anchor structure, the effect of reducing the moment by dispersing the torque acting on this portion is great. As a result, it is possible to sufficiently ensure the strength of the coupling portion. When only the outer side is pushed and pulled into an anchor structure (the inner side pulling anchor structure is omitted), the structure of the portion that supports the torque on the inner side of both torque receiving members 31a and 31b should be the only push anchor. The projecting arm portion 36 on the inner side can be omitted. Thereby, both the torque receiving members 31a and 31b can be manufactured more easily.

更に、本例の場合、上記両トルク受け部材３１ａ、３１ｂと前記キャリパ２ａとを、次の様に組み合わせている。即ち、このキャリパ２ａのインナ寄りの上記ロータの回転方向両端部に、腕部４９、４９を幅方向（図１、３、４の左右方向）端部側に延出した状態で設ける。これら両腕部４９、４９の先端部には、通孔５０、５０（図９）を設けている。そして、これら両通孔５０、５０を挿通したボルト５１、５１を、上記案内ピン５ｂ、５ｂの基端面に形成したねじ孔５２、５２に螺合緊締して、これら案内ピン５ｂ、５ｂと上記キャリパ２ａとを結合している。これら案内ピン５ｂ、５ｂは、上記両トルク受け部材３１ａ、３１ｂに設けた案内孔６ｂ、６ｂに、それぞれ軸方向に摺動自在に嵌装されている為、上記キャリパ２ａは、上記両トルク受け部材３１ａ、３１ｂに、軸方向の変位自在に支持される。   Furthermore, in the case of this example, the torque receiving members 31a and 31b and the caliper 2a are combined as follows. That is, arm portions 49, 49 are provided at both ends in the rotational direction of the rotor close to the inner side of the caliper 2a so as to extend in the width direction (left-right direction in FIGS. 1, 3, and 4) end portions. Through holes 50 and 50 (FIG. 9) are provided at the tip portions of the both arm portions 49 and 49. Then, the bolts 51, 51 inserted through the both through holes 50, 50 are screwed and tightened into screw holes 52, 52 formed in the base end surfaces of the guide pins 5b, 5b, and the guide pins 5b, 5b and the above-mentioned The caliper 2a is coupled. Since these guide pins 5b and 5b are respectively fitted in the guide holes 6b and 6b provided in the torque receiving members 31a and 31b so as to be slidable in the axial direction, the caliper 2a The members 31a and 31b are supported so as to be axially displaceable.

上述の様に構成される本例のフローティングキャリパ型ディスクブレーキを組み立てる場合には、例えば次の様に行なう。先ず、図７に示す様に、上記両トルク受け部材３１ａ、３１ｂと、前記ブーツ７ａ、７ａと、上記各案内ピン５ｂ、５ｂと、前記パッドクリップ４８、４８（図７では省略）とを、互いに組み付けて、図８に示す様な中間組立体５３、５３とする。次に、この図８に示す様に、これら中間組立体５３、５３を、前記取付板部２９の延出板部４３、４３に前記ねじ４５、４５により固定する。そして、図９に示す様に、前記両パッド３０ａ、３０ｂと上記キャリパ２ａとを所定位置に組み付けて、上記フローティングキャリパ型ディスクブレーキとする。この様なフローティングキャリパ型ディスクブレーキは、前記取付板部２９に形成した取付孔４、４を介して車体に固定する。   When assembling the floating caliper type disc brake of this example configured as described above, for example, the following is performed. First, as shown in FIG. 7, the torque receiving members 31a and 31b, the boots 7a and 7a, the guide pins 5b and 5b, and the pad clips 48 and 48 (not shown in FIG. 7) These are assembled together to form intermediate assemblies 53, 53 as shown in FIG. Next, as shown in FIG. 8, these intermediate assemblies 53, 53 are fixed to the extension plate portions 43, 43 of the mounting plate portion 29 by the screws 45, 45. As shown in FIG. 9, the pads 30a and 30b and the caliper 2a are assembled at predetermined positions to form the floating caliper type disc brake. Such a floating caliper type disc brake is fixed to the vehicle body via mounting holes 4 and 4 formed in the mounting plate portion 29.

尚、上述の組立工程以外に、例えば、図１０の（Ａ）→（Ｂ）に示す様に、両トルク受け部材３１ａ、３１ｂと取付板部２９とを結合してから、ブーツ７ａ、７ａ、案内ピン５ｂ、５ｂ、パッドクリップ４８、４８、及び、パッド３０ａ、３０ｂを組み付けても良い。或は、図１１に示す様に、両トルク受け部材３１ａ（、３１ｂ）を取付板部２９に組み付ける以前に、ブーツ７ａ、７ａと、案内ピン５ｂ、５ｂと、パッドクリップ４８、４８と、更には、パッド３０ａ（、３０ｂ）と、キャリパ２ａと組み付けて、第二の中間組立体５４とし、この第二の中間組立体５４を上記取付板部２９に組み付ける事もできる。この場合に、例えば、前述の図８に示した中間組立体５３、５３とキャリパ２ａとを組み合わせて、上記第二の中間組立体５４を得る事ができる。   In addition to the assembly process described above, for example, as shown in FIG. 10 (A) → (B), both the torque receiving members 31a, 31b and the mounting plate portion 29 are coupled, and then the boots 7a, 7a, The guide pins 5b and 5b, the pad clips 48 and 48, and the pads 30a and 30b may be assembled. Alternatively, as shown in FIG. 11, before assembling both torque receiving members 31a (31b) to the mounting plate 29, boots 7a, 7a, guide pins 5b, 5b, pad clips 48, 48, The pad 30a (, 30b) and the caliper 2a can be assembled into the second intermediate assembly 54, and the second intermediate assembly 54 can be assembled to the mounting plate portion 29. In this case, for example, the second intermediate assembly 54 can be obtained by combining the intermediate assemblies 53 and 53 shown in FIG. 8 and the caliper 2a.

上述の様に構成する本例によれば、フローティングキャリパ型ディスクブレーキの製造を容易に行なえる。
即ち、上記両トルク受け部材３１ａ、３１ｂと上記取付板部２９とを別体に形成している為、精度が要求される部分の加工を別々に行なえると共に、それぞれ、単独の部材として管理できる。具体的には、上記両トルク受け部材３１ａ、３１ｂの場合、案内孔６ｂと係合凹部３４とを精度良く形成する必要がある。又、上記取付板部２９の場合、この取付板部２９を車体に固定する部分を精度良く形成する必要がある。本例の場合、この様に精度が要求される部分の加工をそれぞれ別に行なえる為、加工を行ない易い。又、上記両トルク受け部材３１ａ、３１ｂと上記取付板部２９とを別々に管理できる為、これら両部材の組み合わせを変える事等により、複数種類のディスクブレーキを容易に得る事ができると共に、部品管理も行ない易くなる。この結果、ディスクブレーキの製造を容易に行なえ、生産性を良好にできる。例えば、上記両トルク受け部材３１ａ、３１ｂのロータが進入する部分である切り欠き３８の幅を、このロータの厚さに合わせて調節するだけで、複数種類のディスクブレーキを容易に得る事ができる。又、この場合、両トルク受け部材３１ａ、３１ｂの切り欠き３８を形成する前の中間素材の段階では、この中間素材を共通とする事ができ、この中間素材を部品として標準化する事により、生産効率を向上させられる。 According to the present example configured as described above, the floating caliper type disc brake can be easily manufactured.
That is, since both the torque receiving members 31a and 31b and the mounting plate portion 29 are formed separately, it is possible to separately process parts requiring high accuracy and to manage each as a single member. . Specifically, in the case of both the torque receiving members 31a and 31b, it is necessary to form the guide hole 6b and the engaging recess 34 with high accuracy. In the case of the mounting plate portion 29, it is necessary to accurately form a portion for fixing the mounting plate portion 29 to the vehicle body. In the case of this example, it is easy to perform the processing because it is possible to perform processing of parts that require accuracy as described above. Further, since both the torque receiving members 31a and 31b and the mounting plate portion 29 can be managed separately, a plurality of types of disc brakes can be easily obtained by changing the combination of these two members. Management is also easier. As a result, the disc brake can be easily manufactured and the productivity can be improved. For example, a plurality of types of disc brakes can be easily obtained simply by adjusting the width of the notch 38, which is the portion into which the rotor of both the torque receiving members 31a and 31b enters, according to the thickness of the rotor. . In this case, the intermediate material can be made common in the intermediate material stage before the notches 38 of the torque receiving members 31a and 31b are formed. By standardizing the intermediate material as a part, production is possible. Efficiency can be improved.

又、本例の場合、各案内ピン５ｂ、５ｂを嵌装する為の案内孔６ｂ、６ｂを、上記両トルク受け部材３１ａ、３１ｂに形成すると共に、これら両トルク受け部材３１ａ、３１ｂを上記取付板部２９と別体としている為、この取付板部２９を、加工が容易な板金製とする事ができる。この結果、製造コストの低減を図れる。   In the case of this example, the guide holes 6b and 6b for fitting the guide pins 5b and 5b are formed in the torque receiving members 31a and 31b, and the torque receiving members 31a and 31b are attached to the mounting holes. Since the plate portion 29 is a separate body, the mounting plate portion 29 can be made of a sheet metal that can be easily processed. As a result, the manufacturing cost can be reduced.

又、本例の場合、車体に組み付けた場合に、ホイールとのレイアウト性を良好にできる。即ち、上記両トルク受け部材３１ａ、３１ｂは、上記取付板部２９と軸方向に連結されている為、ディスクブレーキの径方向寸法を、例えば、前述の図１８に示した従来構造の第４例の場合と比べて抑えられる。この為、内径が小さいホイールと組み合わせても、このホイールと干渉しにくく、様々な大きさのホイールと組み合わせ易い。   In the case of this example, the layout with the wheel can be improved when assembled to the vehicle body. That is, since both the torque receiving members 31a and 31b are connected to the mounting plate portion 29 in the axial direction, the radial dimension of the disc brake is, for example, the fourth example of the conventional structure shown in FIG. Compared to the case of. For this reason, even when combined with a wheel having a small inner diameter, it is difficult to interfere with this wheel, and it is easy to combine with wheels of various sizes.

又、本例の場合、制動時に、上記取付板部２９に捩れる方向に力が作用しても、上記両トルク受け部材３１ａ、３１ｂとこの取付板部２９との結合部の強度を、十分に確保できる。例えば、制動時に前記両パッド３０ａ、３０ｂから作用するトルクが、図１の矢印イ方向に作用した場合、このトルクが、上記両トルク受け部材３１ａ、３１ｂのうち、回出側（図１の右側）のトルク受け部材３１ｂから上記取付板部２９に作用する。ディスクブレーキを車体に組み付けた状態では、このディスクブレーキと車体との取付部分は、上記トルクが作用する部分に対しインナ側に存在する。従って、上記回出側のトルク受け部材３１ｂから上記取付板部２９にトルクが作用した場合、この取付板部２９とこれら両トルク受け部材３１ａ、３１ｂとの結合部に、この取付板部２９が、図１の矢印ロ方向に捩れる力が作用する。この為、この結合部に上記ロータの軸方向に力が作用する。本例の場合、上記取付板部２９と両トルク受け部材３１ａ、３１ｂとは、軸方向に連結されている為、この様な力に対して十分な強度を確保できる。   Further, in the case of this example, even when a force acts in the twisting direction on the mounting plate portion 29 during braking, the strength of the joint portion between the torque receiving members 31a and 31b and the mounting plate portion 29 is sufficiently increased. Can be secured. For example, when the torque applied from the pads 30a and 30b during braking is applied in the direction of the arrow A in FIG. 1, this torque is applied to the output side (the right side in FIG. 1) of the torque receiving members 31a and 31b. ) Acts on the mounting plate portion 29 from the torque receiving member 31b. In a state where the disc brake is assembled to the vehicle body, the mounting portion between the disc brake and the vehicle body is on the inner side with respect to the portion where the torque acts. Therefore, when a torque acts on the mounting plate portion 29 from the torque receiving member 31b on the delivery side, the mounting plate portion 29 is connected to a connecting portion between the mounting plate portion 29 and the torque receiving members 31a and 31b. A force that twists in the direction of arrow B in FIG. 1 acts. For this reason, a force acts on the coupling portion in the axial direction of the rotor. In the case of this example, the mounting plate portion 29 and the torque receiving members 31a and 31b are connected in the axial direction, so that sufficient strength can be secured against such a force.

特に、大きな力が作用する上記回出側の結合部には圧縮方向の力が作用する為、この結合部の強度をより確保し易く、この結合部のねじ４５、４５が緩みにくくなる。尚、上述の例の場合、回入側（図１の左側）のトルク受け部材３１ａは、引きアンカとなるが、トルクが一定以上大きくなると、トルクを支承する部分が弾性変形して、それ以上大きなトルクを支承する事はなくなる（主として、回出側のトルク受け部材３１ｂによりトルクを支承する）。この為、回入側のトルク受け部材３１ａから上記取付板部２９に作用する力は小さく、これらトルク受け部材３１ａと取付板部２９との結合部に軸方向に作用する力は小さい。   In particular, since the force in the compression direction acts on the connecting portion on the delivery side where a large force is applied, the strength of the connecting portion is more easily secured, and the screws 45 and 45 of the connecting portion are less likely to loosen. In the case of the above example, the torque receiving member 31a on the turn-in side (left side in FIG. 1) serves as a pulling anchor, but when the torque becomes larger than a certain level, the portion that supports the torque is elastically deformed, and more Large torque is not supported (mainly, torque is supported by the torque receiving member 31b on the delivery side). For this reason, the force acting on the mounting plate portion 29 from the torque receiving member 31a on the turn-in side is small, and the force acting in the axial direction on the connecting portion between the torque receiving member 31a and the mounting plate portion 29 is small.

又、本例の場合、上記取付板部２９に上記両トルク受け部材３１ａ、３１ｂを固定した状態で、これら両トルク受け部材３１ａ、３１ｂの一部にそれぞれ形成した側壁部４０、４０と、上記取付板部２９の一部にそれぞれ形成した固定側壁部３９、３９とを当接させている。この為、前記両パッド３０ａ、３０ｂから上記両トルク受け部材３１ａ、３１ｂに作用するトルクを、上記取付板部２９により効果的に支承できる。即ち、これら両トルク受け部材３１ａ、３１ｂからこの取付板部２９に作用するトルクの殆どは、上記側壁部４０と固定側壁部３９との当接部で支承される。従って、上記両トルク受け部材３１ａ、３１ｂと取付板部２９とを結合するねじ４５、４５に作用するトルクは小さい。この結果、これら各ねじ４５、４５の強度を十分に確保できる。   Further, in the case of this example, in a state where both the torque receiving members 31a and 31b are fixed to the mounting plate portion 29, the side wall portions 40 and 40 respectively formed on a part of both the torque receiving members 31a and 31b, Fixed side wall portions 39 and 39 respectively formed on a part of the mounting plate portion 29 are brought into contact with each other. Therefore, the torque acting on the torque receiving members 31 a and 31 b from the pads 30 a and 30 b can be effectively supported by the mounting plate portion 29. That is, most of the torque acting on the mounting plate portion 29 from these torque receiving members 31 a and 31 b is supported by the contact portion between the side wall portion 40 and the fixed side wall portion 39. Accordingly, the torque acting on the screws 45 and 45 that couple the torque receiving members 31a and 31b and the mounting plate 29 is small. As a result, the strength of each of the screws 45, 45 can be sufficiently secured.

又、本例の場合、上記取付板部２９と上記両トルク受け部材３１ａ、３１ｂとを連結する際に、この取付板部２９の延出板部４３、４３のこれら両トルク受け部材３１ａ、３１ｂを連結する側の側面と、これら両トルク受け部材３１ａ、３１ｂの平坦面４１、４１とを当接させている。この為、これら両トルク受け部材３１ａ、３１ｂの位置決めを図り易く、これら両トルク受け部材３１ａ、３１ｂに形成した案内孔６ｂ、６ｂを軸方向に精度良く配置し易くなる。即ち、上記両延出板部４３、４３の側面と上記平坦面４１、４１とを互いに平行に形成している為、これら両面同士を精度良く加工すれば、上記両トルク受け部材３１ａ、３１ｂを、上記取付板部２９に対し軸方向に連結する事を容易に行なえる。尚、本例の場合、前記固定側壁部３９、３９と側壁部４０、４０とは、上記両延出板部４３、４３の側面及び平坦面４１、４１に対しほぼ直角に形成されている。従って、上記両側壁部３９、４０同士が当接する事によっても、上記両トルク受け部材３１ａ、３１ｂの上記取付板部２９に対する位置決めを行なえる。何れにしても、上記各案内孔６ｂ、６ｂを軸方向に精度良く配置できれば、これら各案内孔６ｂ、６ｂに嵌装される、前記案内ピン５ｂ、５ｂの軸方向の摺動を円滑に行なえる。   Further, in the case of this example, when the mounting plate portion 29 and the torque receiving members 31a and 31b are connected, the torque receiving members 31a and 31b of the extension plate portions 43 and 43 of the mounting plate portion 29 are connected. And the flat surfaces 41 and 41 of the torque receiving members 31a and 31b are brought into contact with each other. Therefore, it is easy to position the torque receiving members 31a and 31b, and the guide holes 6b and 6b formed in the torque receiving members 31a and 31b can be easily arranged in the axial direction. That is, since the side surfaces of both the extension plate portions 43 and 43 and the flat surfaces 41 and 41 are formed in parallel to each other, the two torque receiving members 31a and 31b can be formed by accurately processing both surfaces. Further, it is possible to easily connect the mounting plate portion 29 in the axial direction. In the case of this example, the fixed side wall portions 39, 39 and the side wall portions 40, 40 are formed substantially at right angles to the side surfaces of the extension plate portions 43, 43 and the flat surfaces 41, 41. Therefore, positioning of the torque receiving members 31a and 31b with respect to the mounting plate 29 can also be performed by the side walls 39 and 40 coming into contact with each other. In any case, if the guide holes 6b and 6b can be accurately arranged in the axial direction, the guide pins 5b and 5b fitted in the guide holes 6b and 6b can be smoothly slid in the axial direction. The

又、本例の場合、上記両トルク受け部材３１ａ、３１ｂを、所謂押しアンカと引きアンカとの両方を備えるものとしている。この為、制動時にこれら両トルク受け部材３１ａ、３１ｂに作用するトルクを分散して、これら両トルク受け部材３１ａ、３１ｂの強度を確保し易くなる。即ち、本例の場合、制動時に作用するトルクが図１の矢印イ方向に作用した場合で、このトルクが小さい場合には、回入側のトルク受け部材３１ａでこのトルクを支承し、トルクが大きい場合には、この回入側のトルク受け部材３１ａに加えて、回出側のトルク受け部材３１ｂでもこのトルクを支承する。この結果、一方のトルク受け部材にのみトルクが繰り返し作用して、このトルク受け部材にへたり等の損傷を生じにくくできる。   In the case of this example, both the torque receiving members 31a and 31b are provided with both a so-called push anchor and pull anchor. For this reason, it is easy to secure the strength of both the torque receiving members 31a and 31b by dispersing the torque acting on both the torque receiving members 31a and 31b during braking. That is, in the case of this example, when the torque acting at the time of braking acts in the direction of arrow A in FIG. 1 and this torque is small, this torque is supported by the torque receiving member 31a on the turning-in side, If it is larger, in addition to the torque receiving member 31a on the turn-in side, the torque is also supported on the torque receiving member 31b on the turn-out side. As a result, the torque acts repeatedly only on one of the torque receiving members, and it is difficult to cause damage such as sag on the torque receiving member.

又、本例のフローティングキャリパ型ディスクブレーキは、上記両トルク受け部材３１ａ、３１ｂと取付板部２９とを別体とし、更に、これら両トルク受け部材３１ａ、３１ｂに案内孔６ｂ、６ｂを形成している為、これら両トルク受け部材３１ａ、３１ｂと、各案内ピン５ｂ、５ｂと、ブーツ７ａ、７ａと、パッドクリップ４８、４８とを組み合わせて、前記中間組立体５３、５３とする事ができる。そして、この様な中間組立体５３、５３を所定の部品ユニットとして管理すれば、複数種類のキャリパ２ａや取付板部２９と組み合わせる事ができ、フローティングキャリパ型ディスクブレーキの生産効率を向上させられる。更に、本例の場合、上記両トルク受け部材３１ａ、３１ｂを上記取付板部２９と別体としている為、これら両トルク受け部材３１ａ、３１ｂとキャリパ２ａとを直接組み付ける事が可能である。この為、前述の図１１に示した様に、これら両部材及び所定の部材を組み合わせた第二の中間組立体５４として管理する事ができる。この結果、この第二の中間組立体５４と取付板部２９との組み合わせにより、複数種類のフローティングキャリパ型ディスクブレーキを得られる。   In the floating caliper type disc brake of this example, the torque receiving members 31a and 31b and the mounting plate 29 are separated from each other, and guide holes 6b and 6b are formed in the torque receiving members 31a and 31b. Therefore, the intermediate assemblies 53 and 53 can be formed by combining the torque receiving members 31a and 31b, the guide pins 5b and 5b, the boots 7a and 7a, and the pad clips 48 and 48. . If such intermediate assemblies 53, 53 are managed as predetermined component units, they can be combined with a plurality of types of calipers 2a and mounting plate portions 29, and the production efficiency of the floating caliper type disc brake can be improved. Further, in the case of this example, since both the torque receiving members 31a and 31b are separated from the mounting plate portion 29, it is possible to directly assemble both the torque receiving members 31a and 31b and the caliper 2a. Therefore, as shown in FIG. 11 described above, the second intermediate assembly 54 can be managed by combining these two members and a predetermined member. As a result, a combination of the second intermediate assembly 54 and the mounting plate portion 29 can provide a plurality of types of floating caliper type disc brakes.

［実施の形態の第２例］
図１２、１３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、フローティングキャリパ型ディスクブレーキを、車体側に設けたナックル５５に直接固定している。この為に、このナックル５５には、車輪を支持するハブを固定する主部５６から径方向外方に延出した、１対の延出腕部５７、５７を設けている。又、これら両延出腕部５７、５７の内側面に固定側壁部３９を形成すると共に、これら両延出腕部５７、５７のアウタ側（図１２の奥側、図１３の手前側）の側面を、トルク受け部材３１ａ、３１ｂの平坦面４１と平行に形成している。そして、この様に構成されるナックル５５の両延出板部５７、５７に、前述の図１１に示した様に、キャリパ２ａと、パッド３０ａ、３０ｂと、トルク受け部材３１ａ、３１ｂと、案内ピン５ｂ、５ｂと、ブーツ７ａ、７ａと、パッドクリップ４８とを組み付けた第二の中間組立体５４を固定する。これにより、上述の実施の形態の第１例の構造の様な、取付板部２９が不要となり、部品の削減と組み付け工程の削減によるコストの低減を図れる。又、この取付板部２９が不要となる分、ディスクブレーキの軽量化を図れ、車体に組み付けた場合に、ばね下荷重を小さくできる。これにより、自動車の乗り心地や走行安定性等の走行性能の向上に貢献できる。その他の構造及び作用は、上記第１例と同様である。 [Second Example of Embodiment]
12 and 13 show a second example of the embodiment of the present invention. In the case of this example, the floating caliper type disc brake is directly fixed to the knuckle 55 provided on the vehicle body side. For this purpose, the knuckle 55 is provided with a pair of extending arm portions 57 and 57 that extend radially outward from a main portion 56 that fixes a hub that supports the wheel. Further, a fixed side wall portion 39 is formed on the inner side surfaces of both the extended arm portions 57, 57, and on the outer side (the back side in FIG. 12, the near side in FIG. 13) of both the extended arm portions 57, 57. The side surface is formed in parallel with the flat surface 41 of the torque receiving members 31a and 31b. As shown in FIG. 11, the caliper 2a, the pads 30a and 30b, the torque receiving members 31a and 31b, and the guides are provided on the two extending plate portions 57 and 57 of the knuckle 55 configured as described above. The second intermediate assembly 54 assembled with the pins 5b and 5b, the boots 7a and 7a, and the pad clip 48 is fixed. This eliminates the need for the mounting plate 29 as in the structure of the first example of the above-described embodiment, and can reduce the cost by reducing the number of parts and the assembly process. Further, since the mounting plate portion 29 is not required, the weight of the disc brake can be reduced, and the unsprung load can be reduced when assembled to the vehicle body. Thereby, it can contribute to the improvement of driving performance, such as riding comfort and driving stability of a car. Other structures and operations are the same as those in the first example.

上述した各例では、密封部材としてブーツを使用した構造に就いて説明したが、ブーツ以外にもワイパーシールと呼ばれるシールリングを使用する事もできる。即ち、案内孔の内周面開口寄り部分に全周に亙って凹溝を形成し、この凹溝内にシールリングを嵌装し、上記案内孔内に挿通した案内ピンの基端部外周面にこのシールリングを摺接させる。これにより、これら案内孔と案内ピンとの摺動部を密封できる。
又、上述した各例では、案内ピンとキャリパとの結合をボルトにより行なっているが、これら案内ピンとボルトとを一体とする事もできる。即ち、案内ピンの基端部外周面に雄ねじ部を設け、この雄ねじ部を上記キャリパに設けた雌ねじ部に螺合し、この案内ピンの中間部乃至先端部を、トルク受け部材の案内孔に挿通する。これにより、案内ピンのみにより、上記キャリパとトルク受け部材とを結合できる。 In each of the above-described examples, the structure using the boot as the sealing member has been described. However, a seal ring called a wiper seal can be used in addition to the boot. That is, a groove is formed over the entire circumference of the guide hole near the inner peripheral surface opening, a seal ring is fitted in the groove, and the outer periphery of the base end of the guide pin inserted into the guide hole The seal ring is brought into sliding contact with the surface. Thereby, the sliding part of these guide holes and guide pins can be sealed.
In each of the above-described examples, the guide pin and the caliper are coupled by a bolt. However, the guide pin and the bolt can be integrated. That is, a male screw portion is provided on the outer peripheral surface of the base end portion of the guide pin, this male screw portion is screwed into a female screw portion provided on the caliper, and the middle portion or the tip portion of the guide pin is inserted into the guide hole of the torque receiving member. Insert. Thereby, the caliper and the torque receiving member can be coupled only by the guide pin.

本発明の実施の形態の第１例を示す、フローティングキャリパ型ディスクブレーキを外径側から見た図。The figure which looked at the floating caliper type disc brake from the outer diameter side which shows the 1st example of embodiment of this invention. 図１の左側から見た図。The figure seen from the left side of FIG. 図１の下側であるインナ側から見た図。The figure seen from the inner side which is the lower side of FIG. 図１の上側であるアウタ側から見た図。The figure seen from the outer side which is the upper side of FIG. 第１例のフローティングキャリパ型ディスクブレーキを、インナ側から見た斜視図。The perspective view which looked at the floating caliper type disc brake of the 1st example from the inner side. 同じくアウタ側から見た斜視図。The perspective view similarly seen from the outer side. トルク受け部材とブーツと案内ピンとを組み付ける前の状態を示す斜視図。The perspective view which shows the state before attaching a torque receiving member, boots, and a guide pin. 中間組立体と取付板部とを組み付ける前の状態を示す斜視図。The perspective view which shows the state before attaching an intermediate assembly and an attachment board part. 第１例のフローティングキャリパ型ディスクブレーキの分解斜視図。The exploded perspective view of the floating caliper type disc brake of the 1st example. トルク受け部材と取付板部とを組み付けた状態（Ａ）と、これにブーツ及び案内ピンを組み付けた状態（Ｂ）とを、それぞれ示す斜視図。The perspective view which shows the state (A) which assembled | attached the torque receiving member and the attachment board part, and the state (B) which assembled | attached the boot and the guide pin to this, respectively. 第二の中間組立体をインナ側から見た状態で示す斜視図。The perspective view which shows the state which looked at the 2nd intermediate assembly from the inner side. 本発明の実施の形態の第２例を、インナ側から見た状態で示す斜視図。The perspective view which shows the 2nd example of embodiment of this invention in the state seen from the inner side. 同じく、アウタ側から見た状態で示す斜視図。Similarly, the perspective view shown in the state seen from the outer side. 従来構造の第１例を、一部を切断して図１と同方向から見た状態で示す部分切断面図。The fragmentary sectional view which shows the 1st example of conventional structure in the state which cut | disconnected a part and looked from the same direction as FIG. 図１４のＡ−Ａ断面図。AA sectional drawing of FIG. 従来構造の第２例を、右半部を切断してインナ側から見た図。The figure which cut | disconnected the right half part and saw the 2nd example of the conventional structure from the inner side. 同第３例を、一部を切断して図１と同方向から見た状態で示す部分切断面図。The partial cutaway view which shows the 3rd example in the state which cut | disconnected a part and was seen from the same direction as FIG. 同第４例示す部分断面図。The fragmentary sectional view which shows the same 4th example.

符号の説明Explanation of symbols

１ ロータ
２、２ａ キャリパ
３、３ａ サポート
４ 取付孔
５、５ａ、５ｂ 案内ピン
６、６ａ、６ｂ 案内孔
７、７ａ ブーツ
８、８ａ 回入側係合部
９、９ａ 回出側係合部
１０ａ、１０ｂ、１０ｃ パッド
１１、１１ａ、１１ｂ プレッシャプレート
１２、１２ａ シリンダ部
１３、１３ａ 爪部
１４ ピストン
１５ ライニング
１６ 内側面
１７ａ、１７ｂ 突出腕部
１８ａ、１８ｂ 係合凹部
１９ａ、１９ｂ 係合凸部
２０ａ、２０ｂ 側面
２１ａ、２１ｂ 側面
２２ 取付板部
２３ 貫通孔
２４、２４ａ トルク受け部材
２５ ナックル
２６ 切り欠き
２７ 固定板
２８ ねじ
２９ 取付板部
３０ａ、３０ｂ パッド
３１ａ、３１ｂ トルク受け部材
３２ 案内筒部
３３ 係合凸部
３４ 係合凹部
３５ 内側面
３６ 突出腕部
３８ 切り欠き
３９ 固定側壁部
４０ 側壁部
４１ 平坦面
４２ 凹部
４３ 延出板部
４４ 平面部
４５ ねじ
４６ 通孔
４７ ねじ孔
４８ パッドクリップ
４９ 腕部
５０ 通孔
５１ ボルト
５２ ねじ孔
５３ 中間組立体
５４ 第二の中間組立体
５５ ナックル
５６ 主部
５７ 延出腕部 DESCRIPTION OF SYMBOLS 1 Rotor 2, 2a Caliper 3, 3a Support 4 Mounting hole 5, 5a, 5b Guide pin 6, 6a, 6b Guide hole 7, 7a Boot 8, 8a Entry side engagement part 9, 9a Delivery side engagement part 10a 10b, 10c Pad 11, 11a, 11b Pressure plate 12, 12a Cylinder part 13, 13a Claw part 14 Piston 15 Lining 16 Inner side face 17a, 17b Projecting arm part 18a, 18b Engaging recess part 19a, 19b Engaging convex part 20a, 20b side surface 21a, 21b side surface 22 mounting plate portion 23 through hole 24, 24a torque receiving member 25 knuckle 26 notch 27 fixing plate 28 screw 29 mounting plate portion 30a, 30b pad 31a, 31b torque receiving member 32 guide tube portion 33 engagement Convex part 34 Engaging concave part 35 Inner surface 36 Protruding arm part 38 Notch 39 Fixed side Part 40 Side wall part 41 Flat surface 42 Recess 43 Extension plate part 44 Flat part 45 Screw 46 Through hole 47 Screw hole 48 Pad clip 49 Arm part 50 Through hole 51 Bolt 52 Screw hole 53 Intermediate assembly 54 Second intermediate assembly 55 Knuckle 56 Main part 57 Extension arm

Claims (7)

車体に固定される固定部材と、車輪と共に回転するロータの両側に配置される１対のパッドと、この固定部材に支持され、これら両パッドをこのロータの軸方向に変位可能に支持すると共に、制動時にこれら両パッドから加わる、このロータの回転方向のトルクを受ける１対のトルク受け部材と、このロータを跨ぐ様に配置され、このロータに関して一方の側に爪部を、他方の側にピストンを嵌装する為のシリンダ部を、それぞれ備えたキャリパと、このキャリパを上記ロータの軸方向の変位可能に支持する複数の案内ピンとを備え、上記ピストンの押し出しに伴い、上記両パッドを上記ロータの両側面に押し付けて制動を行なうフローティングキャリパ型ディスクブレーキに於いて、上記両トルク受け部材は、上記固定部材とは別体で、上記各案内ピンを摺動可能に嵌装する案内孔を有しており、この固定部材の一部に上記ロータの軸方向に連結されている事を特徴とするフローティングキャリパ型ディスクブレーキ。   A fixing member fixed to the vehicle body, a pair of pads disposed on both sides of the rotor rotating together with the wheel, supported by the fixing member, and supporting both the pads displaceably in the axial direction of the rotor; A pair of torque receiving members for receiving torque in the rotational direction of the rotor, which is applied from these pads during braking, are arranged so as to straddle the rotor, with the claw portion on one side of the rotor and the piston on the other side. And calipers each having a cylinder portion for fitting the caliper, and a plurality of guide pins that support the calipers so as to be displaceable in the axial direction of the rotor. In the floating caliper type disc brake that presses against both side surfaces of the disc to perform braking, both the torque receiving members are separate from the fixed member, Each guide pin has a slidably fitted to the guide hole, a floating caliper type disc brake, characterized in that is connected to the shaft direction of the rotor to a part of the fixing member. 上記固定部材に上記両トルク受け部材を連結した状態で、これら両トルク受け部材の、上記ロータの回転方向に関して、上記両パッドを支持する側と反対側の一部にそれぞれ形成した側壁部と、上記固定部材の一部で、これら両側壁部と対向する部分に、これら両側壁部と平行にそれぞれ形成した固定側壁部とが当接する、請求項１に記載したフローティングキャリパ型ディスクブレーキ。   In the state where the both torque receiving members are connected to the fixing member, side walls formed on a part of each of the torque receiving members on the side opposite to the side supporting the pads with respect to the rotation direction of the rotor, The floating caliper type disc brake according to claim 1, wherein a fixed side wall portion formed in parallel with both side wall portions is in contact with a portion of the fixed member facing the both side wall portions. 上記固定部材の一部で上記両トルク受け部材を連結する側を平坦面とし、この固定部材側の平坦面と、これら両トルク受け部材の端部の一部でこの固定部材側の平坦面と平行に形成された平坦面とが当接した状態で、これら両部材が連結される、請求項１又は請求項２に記載したフローティングキャリパ型ディスクブレーキ。   The side where the torque receiving members are connected to a part of the fixing member is a flat surface, the flat surface on the side of the fixing member, and the flat surface on the side of the fixing member at a part of the ends of the torque receiving members. The floating caliper type disc brake according to claim 1 or 2, wherein the two members are connected in a state in which the flat surface formed in parallel is in contact therewith. 上記両トルク受け部材の上記両パッドからトルクを受ける部分のうち、少なくとも上記固定部材との連結部から遠い側であるアウタ側のパッドからトルクを受ける部分の回入側、回出側のそれぞれの構造を、押しアンカと引きアンカとの両方を備えるものとしている、請求項１〜３のうちの何れか１項に記載したフローティングキャリパ型ディスクブレーキ。   Of the portions of the torque receiving members that receive torque from the pads, at least the portion that receives torque from the outer pad that is far from the connecting portion with the fixing member, respectively, The floating caliper type disc brake according to any one of claims 1 to 3, wherein the structure includes both a push anchor and a pull anchor. 上記両トルク受け部材の上記両パッドからトルクを受ける部分の構造を、これら両パッドから加わる上記ロータの回転方向のトルクを支承する事に加えて、これら両パッドが上記ロータの径方向外方に変位する事を阻止可能としている、請求項１〜４のうちの何れか１項に記載したフローティングキャリパ型ディスクブレーキ。   In addition to supporting the torque in the rotational direction of the rotor applied from the two pads, the structure of the portion of the torque receiving member that receives torque from the two pads is also used. The floating caliper type disc brake according to any one of claims 1 to 4, wherein the disc brake can be prevented from being displaced. 請求項１〜５のうちの何れか１項に記載したフローティングキャリパ型ディスクブレーキの製造方法であって、上記両トルク受け部材に、少なくとも、上記各案内ピンと、これら各案内ピンと各案内孔との摺動部を密封する密封部材とを組み付けて中間組立体とした後、この中間組立体と、上記キャリパ及び上記固定部材とを組み合わせる、フローティングキャリパ型ディスクブレーキの製造方法。   It is a manufacturing method of the floating caliper type disc brake given in any 1 paragraph of Claims 1-5, Comprising: At least both said guide pin, each of these guide pins, and each guide hole to said both torque receiving members. A manufacturing method of a floating caliper type disc brake, wherein a sealing member for sealing a sliding portion is assembled to form an intermediate assembly, and then the intermediate assembly is combined with the caliper and the fixing member. 上記中間組立体とキャリパとを組み付けて第二の中間組立体とした後、この第二の中間組立体と上記固定部材とを締結する、請求項６に記載したフローティングキャリパ型ディスクブレーキの製造方法。   7. The method of manufacturing a floating caliper type disc brake according to claim 6, wherein the intermediate assembly and the caliper are assembled to form a second intermediate assembly, and then the second intermediate assembly and the fixing member are fastened. .
JP2007005371A 2007-01-15 2007-01-15 Floating caliper type disc brake and its manufacturing method Pending JP2008169961A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
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