JP2006144856A

JP2006144856A - Brake disk

Info

Publication number: JP2006144856A
Application number: JP2004333478A
Authority: JP
Inventors: Mitsutaka Yuki; 光貴結城
Original assignee: Aisin Takaoka Co Ltd
Current assignee: Aisin Takaoka Co Ltd
Priority date: 2004-11-17
Filing date: 2004-11-17
Publication date: 2006-06-08

Abstract

<P>PROBLEM TO BE SOLVED: To provide a brake disk capable of minimizing the thermal fall of a sliding body in braking. <P>SOLUTION: This brake disk comprises a hub 1 having a body part 10 for axle installation and an outer peripheral flange part 20 formed on the periphery thereof and an annular sliding body 3 fixed to the outer periphery flange part 20 of the hub with tightening bolts 4. The outer peripheral flange part 20 of the hub comprises an annular outer ring part 22 having a plurality of outer ring connection parts 26 and a plurality of tightening holes 25 and a plurality of connection arms 23 and 24 for connecting the outer ring connection parts 26 to the body part 10 of the hub. The two outer ring connection parts 26 adjacent to each other are connected to each other by installing a part of the outer ring part 22 (circular arc-shaped bridging part) across the outer ring connection parts. Also, the tightening hole 25 is formed between these two outer ring connection parts 26. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、ディスクブレーキ用のブレーキディスクに関するものである。 The present invention relates to a brake disc for a disc brake.

一般にブレーキディスクは、車軸への取付部であるハブと、ブレーキキャリパの制輪子（ブレーキシューやブレーキライニング）と摩擦接触させるべく前記ハブの周囲に設けられた環状円盤形の摺動部（制動部）とから構成されている。従来、ハブと摺動部とを一体鋳造したブレーキディスクが知られている。一体型のディスクでは図６に示すように、摺動部の内周側根元部がハブに強固に固定されているために、制動時の摩擦熱で摺動部が熱膨張した際、ディスクの中心軸線Ｃと平行な方向へのモーメントが生じ、摺動部が車軸方向に傾くように変形する現象（この現象を「熱倒れ」と呼ぶ）が知られている。熱倒れは、それ単独で又はディスクの取付精度の低さに起因した摺動面振れと相俟ってディスクの偏摩耗を生じさせ、ひいては制動時における制動トルクの不安定化や不快なブレーキ振動の原因となる。このため、熱倒れを極力防止するための対策が種々提案されている。 Generally, a brake disc is a ring-shaped sliding part (braking part) provided around the hub to be brought into frictional contact with a hub that is an attachment part to an axle and a brake caliper control (brake shoe or brake lining). ). Conventionally, a brake disk in which a hub and a sliding portion are integrally cast is known. As shown in FIG. 6, in the integrated disc, the inner peripheral side root portion of the sliding portion is firmly fixed to the hub, so that when the sliding portion is thermally expanded by frictional heat during braking, There is known a phenomenon in which a moment in a direction parallel to the central axis C is generated and the sliding portion is deformed so as to be inclined in the axle direction (this phenomenon is referred to as “heat collapse”). The thermal collapse alone or in combination with the sliding surface run-out caused by the low mounting accuracy of the disk causes uneven wear of the disk, resulting in unstable braking torque and unpleasant brake vibration during braking. Cause. For this reason, various measures for preventing thermal collapse as much as possible have been proposed.

特許文献１のディスクブレーキ用ディスクプレートは、「円環状の制動部材の内周部に、制動部材と別体にされた取付部材の端部が重ねられ、前記両部材がそれらを貫通する連結ピンで連結されたものにおいて、連結ピンを挿通する両部材の孔の一方または両方が径方向に長い長孔になっている」ものである。つまり、連結ピン用の孔を径方向に長孔化することで、制動部材の熱膨張時における取付部材（ハブ）による拘束を緩和し、制動部材がディスクの半径方向外向きに熱膨張することを容易にして、制動部材の熱倒れを極力防止せんとするものである。しかしながら、特許文献１のように連結ピン用の孔を長孔化すると、取付部材（ハブ）に対する制動部材の姿勢保持力が低下し、摺動面の振れ精度を高精度に保つことが難しくなる。このため、特許文献１の技術も、総合的な評価としてはディスク偏摩耗の回避につながらない。 The disk plate for a disk brake disclosed in Patent Document 1 is “a connecting pin through which an end portion of a mounting member separated from a braking member is superimposed on an inner peripheral portion of an annular braking member, and the both members pass through them. In which one or both of the holes of the two members through which the connecting pin is inserted is a long hole that is long in the radial direction. That is, by making the connecting pin hole long in the radial direction, the restraint by the mounting member (hub) during thermal expansion of the braking member is relaxed, and the braking member thermally expands outward in the radial direction of the disk. This makes it easy to prevent the braking member from falling over as much as possible. However, if the connecting pin hole is elongated as in Patent Document 1, the holding force of the braking member with respect to the mounting member (hub) is reduced, and it is difficult to maintain the sliding surface with high accuracy. . For this reason, the technique of Patent Document 1 does not lead to avoiding uneven disk wear as a comprehensive evaluation.

特許文献２のディスクブレーキ用ベンチレーテッドディスクは、摺動部たる摩擦トラックが支持ディスクハブに対して、その支持ディスクハブの周囲に放射状に配設された複数のピンを介して連結されたものであって、各ピンの外端部が摩擦トラック内に埋設・固定される一方で、各ピンの内端部が支持ディスクハブ内に半径方向に摺動可能なインサートとして収容されているものである。つまり、摩擦トラックの内周側に固定されたピンを、支持ディスクハブに対して半径方向に摺動可能としておくことにより、摩擦トラックの熱膨張時における支持ディスクハブによる拘束を緩和し、摩擦トラックがディスクの半径方向外向きに熱膨張することを容易にして、摩擦トラックの熱倒れを極力防止せんとするものである。この構造によれば、支持ディスクハブによる複数のピンを介した摩擦トラックの姿勢保持性も悪くなく、摺動面の振れ精度を高精度に保つことも可能である。 In the ventilated disc for disc brake of Patent Document 2, a friction track as a sliding portion is connected to a support disc hub via a plurality of pins arranged radially around the support disc hub. The outer end portion of each pin is embedded and fixed in the friction track, while the inner end portion of each pin is accommodated in the support disk hub as a radially slidable insert. is there. In other words, the pin fixed to the inner peripheral side of the friction track is slidable in the radial direction with respect to the support disc hub, so that the restraint by the support disc hub during thermal expansion of the friction track is alleviated, and the friction track This facilitates thermal expansion of the disk outward in the radial direction of the disk, and prevents the friction track from falling over as much as possible. According to this structure, the posture retention of the friction track via the plurality of pins by the support disk hub is not bad, and it is possible to keep the deflection accuracy of the sliding surface with high accuracy.

しかしながら、特許文献２のディスクを製造するためには、複数のピンを砂型（中子）内に収めた状態で摩擦トラック及び支持ディスクハブを一体鋳造し、その後に機械加工によって摩擦トラックと支持ディスクハブとを切り離し、両者間に残された一群のピンによって両者を連結した状態に導くという複雑な工程を経る必要がある。この製造方法には、ピンを中子内に仮保持する際の位置決め精度をいかに確保するかという問題や、型内にピンを含んだ状態で鋳造することに起因してピンと他の肉部との界面に生じた酸化物が、ピンの固定強度を低下させたりピンの摺動性を悪化させたりするおそれがあるなど製造上多くの問題がある。このため、特許文献２のディスクは、製造コストが高くつく一方で、そのコストに見合うだけの品質や性能を確保することが難しいという欠点がある。 However, in order to manufacture the disc of Patent Document 2, the friction track and the support disc hub are integrally cast with a plurality of pins contained in a sand mold (core), and then the friction track and the support disc are machined. It is necessary to go through a complicated process of separating the hub and guiding it to a connected state by a group of pins left between them. In this manufacturing method, there is a problem of how to ensure positioning accuracy when temporarily holding the pin in the core, and due to casting with the pin included in the mold, the pin and other meat parts There are many problems in production, such as that the oxide generated at the interface may reduce the fixing strength of the pin or deteriorate the sliding property of the pin. For this reason, the disk of Patent Document 2 has a drawback that it is difficult to ensure quality and performance sufficient to meet the cost while the manufacturing cost is high.

実開昭６１−１０４８４２号の全文明細書及び図面Full text and drawings of Japanese Utility Model Publication No. 61-104842 特表２００３−５２６０５８号Special table 2003-526058

本発明の目的は、従来の技術とは異なる解決手法により、制動時における摺動体の熱倒れを極力防止することができるブレーキディスクを提供することにある。 An object of the present invention is to provide a brake disk that can prevent the sliding body from falling over during braking by using a solution different from that of the prior art.

請求項１の発明は、車軸に取り付けられる本体部及びその本体部の周囲に設けられた外周フランジ部を具備してなるハブと、当該ハブの外周フランジ部に対して複数の締結具により固着される環状の摺動体とから構成されるブレーキディスクにおいて、前記ハブの外周フランジ部は、複数の外輪連結部及び前記各締結具を装着するための複数の締結部を有する環状の外輪部と、前記各外輪連結部をハブの本体部に連結するための複数の連結アームとを備え、前記外輪部において、隣り合う二つの外輪連結部が当該外輪部の一部によって連結されると共に、それら二つの外輪連結部間には前記締結部が設けられていることを特徴とするブレーキディスクである。 According to the first aspect of the present invention, there is provided a hub having a main body portion attached to an axle and an outer peripheral flange portion provided around the main body portion, and a plurality of fasteners to the outer peripheral flange portion of the hub. The outer peripheral flange portion of the hub includes an annular outer ring portion having a plurality of outer ring connecting portions and a plurality of fastening portions for mounting the fasteners; A plurality of connecting arms for connecting each outer ring connecting portion to the main body portion of the hub, and in the outer ring portion, two adjacent outer ring connecting portions are connected by a part of the outer ring portion, and the two The brake disc is characterized in that the fastening portion is provided between the outer ring connecting portions.

請求項２の発明は、請求項１に記載のブレーキディスクにおいて、前記外輪部において、前記複数の外輪連結部がハブの中心軸線（Ｃ）を中心として等角度間隔で設けられていると共に、外輪連結部と同数の締結部の各々が、隣り合う二つの外輪連結部の丁度中間に位置するように設けられていることを特徴とする。 According to a second aspect of the present invention, in the brake disc according to the first aspect, in the outer ring portion, the plurality of outer ring connecting portions are provided at equiangular intervals around the central axis (C) of the hub. Each of the same number of fastening portions as the connecting portions is provided so as to be positioned exactly in the middle between two adjacent outer ring connecting portions.

請求項３の発明は、請求項１又は２に記載のブレーキディスクにおいて、前記外輪部における複数の外輪連結部は、隣り合う二つの外輪連結部間の外輪部に沿った離間長（Ｌ）が、外輪部の幅（ｈ）の５倍の長さ（５ｈ）よりも大きくなるように設定されていることを特徴とする。 According to a third aspect of the present invention, in the brake disc according to the first or second aspect, the plurality of outer ring connecting portions in the outer ring portion have a separation length (L) along the outer ring portion between two adjacent outer ring connecting portions. The outer ring portion is set to be larger than the length (5h) five times the width (h) of the outer ring portion.

請求項４の発明は、車軸に取り付けられる本体部及びその本体部の周囲に設けられた外周フランジ部を具備してなるハブと、当該ハブの外周フランジ部に対して複数の締結具により固着される環状の摺動体とから構成されるブレーキディスクにおいて、前記ハブの外周フランジ部は、ハブの中心軸線（Ｃ）を中心として等角度間隔で設けられた複数の外輪連結部、及び、その外輪連結部と同数で且つそれぞれが前記隣り合う二つの外輪連結部の丁度中間に位置するように設けられた前記各締結具を装着するための締結部を有する環状の外輪部と、前記各外輪連結部をハブの本体部に連結するための外輪連結部の２倍の数の連結アームとを備え、前記各外輪連結部が、当該外輪連結部とハブの中心軸線（Ｃ）とを結ぶ半径方向仮想線に対し線対称となるように傾斜させた２本の連結アームを介してハブの本体部に連結されると共に、当該外輪連結部の両隣に位置する締結部の各々とハブの中心軸線（Ｃ）とを結ぶ半径方向仮想線に対する各連結アームの傾斜角度（θ２）が３０°以上６０°以下であることを特徴とするブレーキディスクである。 According to a fourth aspect of the present invention, there is provided a hub comprising a main body portion attached to an axle and an outer peripheral flange portion provided around the main body portion, and a plurality of fasteners fixed to the outer peripheral flange portion of the hub. The outer peripheral flange portion of the hub includes a plurality of outer ring connecting portions provided at equiangular intervals around the center axis (C) of the hub, and the outer ring connecting portion. An annular outer ring portion having a fastening portion for mounting the fasteners provided so as to be located at the middle of the two adjacent outer ring connecting portions, and the same number of the outer ring connecting portions. A number of connecting arms which are twice as many as the outer ring connecting portions for connecting the outer ring connecting portions to the main body portion of the hub, and each outer ring connecting portion connects the outer ring connecting portion and the central axis (C) of the hub in the radial direction. Line pair to line Are connected to the main body of the hub via two connecting arms inclined so as to become a radius connecting each of the fastening portions located on both sides of the outer ring connecting portion and the central axis (C) of the hub. The brake disk is characterized in that an inclination angle (θ2) of each connecting arm with respect to a direction imaginary line is 30 ° or more and 60 ° or less.

請求項５の発明は、請求項４に記載のブレーキディスクにおいて、前記外輪部における複数の外輪連結部は、隣り合う二つの外輪連結部間の外輪部に沿った離間長（Ｌ）が、外輪部の幅（ｈ）の５倍の長さ（５ｈ）よりも大きくなるように設定されていることを特徴とする。 According to a fifth aspect of the present invention, in the brake disc according to the fourth aspect, the plurality of outer ring connecting portions in the outer ring portion have a separation length (L) along the outer ring portion between two adjacent outer ring connecting portions. It is characterized by being set to be larger than the length (5h) which is five times the width (h) of the part.

［作用］
制動時の摩擦熱でディスクの摺動体の全体が半径方向外向き（拡径方向）に熱膨張すると、各締結具を介して、ハブの外周フランジ部を構成する環状の外輪部が各締結部の位置で拡径方向に引っ張られる。その際、図５に示すように、締結部（２５）の周方向両側に位置する各外輪連結部（２６）は、連結アーム（２３，２４）を介してハブ本体部に連結されているため、拡径方向への引っ張りに対しては頑強に抵抗してハブ本体部との距離を維持しようとするのに対し、二つの外輪連結部間に位置する締結部（２５）は、締結具を介して熱膨張する摺動体に追従しようとする。このため、二つの外輪連結部（２６）を架橋的に連結している外輪部の一部（図５では円弧状架橋部）が、摺動体の熱膨張に追従して締結部位置にて拡径方向に膨出するように変形する。この膨出変形によって摺動体の内周部とハブ本体部との間隔が微増調整され、摺動体の熱膨張に起因する拡径方向への引っ張り力がハブ本体部に及ぶことが緩和される。その後、一旦膨張した摺動体が半径方向内向き（縮径方向）に収縮するときには、前記二つの外輪連結部を架橋的に連結している外輪部の一部が元の状態に復帰することで、摺動体の内周部とハブ本体部との間隔が膨張前の状態に戻される。 [Action]
When the entire disc sliding body is thermally expanded radially outward (in the direction of expansion) due to frictional heat during braking, the annular outer ring portion constituting the outer peripheral flange portion of the hub is connected to each fastening portion via each fastener. It is pulled in the diameter expansion direction at the position of. At that time, as shown in FIG. 5, each outer ring connecting portion (26) located on both sides in the circumferential direction of the fastening portion (25) is connected to the hub body portion via the connecting arms (23, 24). The fastening part (25) located between the two outer ring connecting parts is intended to maintain the distance from the hub body part by strongly resisting the pulling in the diameter expanding direction. It tries to follow the sliding body which thermally expands through. For this reason, a part of the outer ring portion (the arc-shaped bridge portion in FIG. 5) that connects the two outer ring connecting portions (26) in a bridging manner follows the thermal expansion of the sliding body and expands at the fastening portion position. Deforms to bulge in the radial direction. By this bulging deformation, the distance between the inner peripheral portion of the sliding body and the hub main body portion is slightly increased and adjusted so that the pulling force in the diameter expanding direction due to the thermal expansion of the sliding body is applied to the hub main body portion. After that, when the sliding body once expanded contracts radially inwardly (in the direction of diameter reduction), a part of the outer ring part connecting the two outer ring connecting parts in a bridging manner returns to the original state. The interval between the inner peripheral portion of the sliding body and the hub main body is returned to the state before expansion.

このように、ハブの外周フランジ部を構成する外輪部において、隣り合う二つの外輪連結部を当該外輪部の一部によって連結すると共に、それら二つの外輪連結部間に締結部を設けるという構成を採用することで、摺動体はハブ本体部に過度に拘束されることなく拡径方向又は縮径方向への変形自由度をある程度確保されている。それ故、制動時の摩擦熱で摺動体が熱膨張する場合でも、ハブ本体部が摺動体の内周部（つまり根元部）を過度に拘束することがないため、摺動体の熱倒れが効果的に防止又は抑制される。 As described above, in the outer ring portion constituting the outer peripheral flange portion of the hub, the two adjacent outer ring connecting portions are connected by a part of the outer ring portion, and a fastening portion is provided between the two outer ring connecting portions. By adopting the sliding body, the degree of freedom of deformation in the diameter expansion direction or the diameter reduction direction is secured to some extent without being excessively constrained by the hub body. Therefore, even when the sliding body thermally expands due to frictional heat at the time of braking, the hub body does not excessively restrain the inner peripheral portion (that is, the root portion) of the sliding body. Is prevented or suppressed.

なお、請求項２のように、複数の外輪連結部が等角度間隔で設けられると共に、各締結部が隣り合う二つの外輪連結部の丁度中間に位置することは好ましい。この構成によれば、摺動体が膨張又は収縮する際に、ハブの外周フランジ部の外輪部に作用する応力が全ての半径方向に対して均等化するため、外輪部に局部的な歪みを生ずるおそれがない。また、各締結部からその左側の外輪連結部までの距離と、その右側の外輪連結部までの距離とが等しいことで、摺動体の熱膨張時における締結部位置での外輪部の半径方向変位量を確保することが容易になる。 As in claim 2, it is preferable that the plurality of outer ring connecting portions are provided at equiangular intervals, and that each fastening portion is located exactly in the middle of two adjacent outer ring connecting portions. According to this configuration, when the sliding body expands or contracts, stress acting on the outer ring portion of the outer peripheral flange portion of the hub is equalized in all radial directions, so that local distortion occurs in the outer ring portion. There is no fear. Further, since the distance from each fastening portion to the left outer ring connecting portion is equal to the distance from the right outer ring connecting portion, the radial displacement of the outer ring portion at the fastening portion position during thermal expansion of the sliding body It becomes easy to secure the amount.

また、請求項３のように、５ｈ＜Ｌの関係を満たすことは好ましい。隣り合う二つの外輪連結部間の外輪部に沿った離間長（Ｌ）が、外輪部の幅（ｈ）の５倍の長さ（５ｈ）以下になると、二つの外輪連結部を架橋的に連結している外輪部の一部が、摺動体の熱膨張に追従して締結部位置にて拡径方向に膨出変形することが難しくなり、摺動体がハブ本体部に拘束される度合いが強くなって所期の作用効果を得られないおそれがある。 Further, as in claim 3, it is preferable to satisfy the relationship of 5h <L. When the separation length (L) along the outer ring portion between two adjacent outer ring connecting portions becomes equal to or less than five times the length (5h) of the width (h) of the outer ring portion, the two outer ring connecting portions can be bridged. It becomes difficult for a part of the connected outer ring portion to bulge and deform in the diameter increasing direction at the fastening portion position following the thermal expansion of the sliding body, and the degree to which the sliding body is restrained by the hub body portion There is a risk that the intended action and effect may not be obtained.

更に、請求項４のように、各外輪連結部を線対称に傾斜した２本の連結アームを介してハブ本体部に連結すると共に、各連結アームの傾斜角度（θ２）を３０°以上６０°以下とすることは好ましい。このように、各外輪連結部を線対称に傾斜した２本の連結アームを介してハブ本体部に連結することで、各外輪連結部において外輪部をハブ本体部に対して確実に保持することができる。また、各連結アームをディスクの放射方向（半径方向）に沿って設けるのではなく、放射方向に対して上記範囲の角度で傾斜させることにより、制動トルクに対するせん断強度を高めて、ブレーキディスク全体の剛性を高めることができる。なお、請求項５の技術的意義は、請求項３と同じである。 Further, as in claim 4, each outer ring connecting portion is connected to the hub body through two connecting arms inclined in line symmetry, and the inclination angle (θ2) of each connecting arm is 30 ° or more and 60 °. The following is preferable. Thus, by connecting each outer ring connecting portion to the hub main body via two connecting arms inclined in line symmetry, the outer ring portion is reliably held with respect to the hub main body at each outer ring connecting portion. Can do. In addition, each connecting arm is not provided along the radial direction (radial direction) of the disk, but is inclined at an angle in the above range with respect to the radial direction, thereby increasing the shear strength against the braking torque, and the entire brake disk. Stiffness can be increased. The technical significance of claim 5 is the same as that of claim 3.

［付記］本発明の更に好ましい態様や追加的構成要件を以下に列挙する。
イ．請求項１〜５にて、前記ハブがアルミニウム又はその合金で作られていること。
ロ．請求項１〜５にて、前記摺動体が鉄系の金属で作られていること。
ハ．請求項１〜５にて、前記外輪部の一部が弾性変形可能であること。 [Additional remarks] Further preferable aspects and additional constituent elements of the present invention are listed below.
I. 6. The hub according to claim 1, wherein the hub is made of aluminum or an alloy thereof.
B. 6. The sliding body according to claim 1, wherein the sliding body is made of an iron-based metal.
C. In Claims 1-5, a part of said outer ring part is elastically deformable.

［用語の定義］この明細書及び特許請求の範囲において、「環状の外輪部」には、円環状の外輪部のみならず、多角形環状の外輪部も含まれる。多角形環状の外輪部としては、例えば各外輪連結部を多角形の各頂点とすると共に、隣り合う頂点を結ぶ辺の中間位置に締結部を配設してなる外輪部をあげることができる。 [Definition of Terms] In this specification and claims, the “annular outer ring portion” includes not only an annular outer ring portion but also a polygonal annular outer ring portion. As the polygonal annular outer ring portion, for example, an outer ring portion in which each outer ring connecting portion is set as each vertex of the polygon and a fastening portion is disposed at an intermediate position between adjacent vertexes can be exemplified.

請求項１〜５に記載のブレーキディスクによれば、摺動体の内周部（根元部）がハブ本体部によって過度に拘束されることがなく、摺動体の熱倒れを効果的に防止又は抑制することができる。 According to the brake disk of Claims 1-5, the inner peripheral part (root part) of a sliding body is not restrained excessively by a hub main-body part, and prevents or suppresses the thermal collapse of a sliding body effectively. can do.

また、一群の連結アームによってディスクの摺動体がハブ本体部に対し確実に姿勢保持されるので、本発明を採用することで摺動体における摺動面の振れ精度を高精度に保つことが困難になるということはない。 In addition, since the disc slide body is reliably held in the posture with respect to the hub main body by the group of connecting arms, it is difficult to maintain the high accuracy of the sliding surface of the slide body by adopting the present invention. There is no such thing as

本発明をベンチレーテッド型ブレーキディスクに具体化した一実施形態を図面を参照しつつ説明する。図１〜図４に示すように、ブレーキディスクは、ハブ１と、その周囲に設けられた環状の摺動体３とから構成されている。 An embodiment in which the present invention is embodied in a ventilated brake disc will be described with reference to the drawings. As shown in FIGS. 1-4, the brake disc is comprised from the hub 1 and the cyclic | annular sliding body 3 provided in the circumference | surroundings.

図２及び図３に示すように、ハブ１は、鋳造によりアルミニウム合金を一体成形したものであり、車軸に取り付けられる本体部１０と、その本体部１０の周囲に設けられた外周フランジ部２０とを具備する。 As shown in FIGS. 2 and 3, the hub 1 is formed by integrally molding an aluminum alloy by casting, and includes a main body portion 10 attached to an axle, and an outer peripheral flange portion 20 provided around the main body portion 10. It comprises.

ハブの本体部１０は、円板状の車軸取付け用フランジ１２を主体とし、そのフランジ１２の外周縁部に短円筒状の円筒壁１３を設けたものである。車軸取付け用フランジ１２はハブの中心軸線Ｃに対し直交する方向（半径方向）に展開する。円筒壁１３は、その長さは短いものの、車軸取付け用フランジ１２の外周縁から中心軸線Ｃと平行に後方向に向けて突設されている。車軸取付け用フランジ１２には、その中心位置において車軸を通すための中央大穴１４が形成されると共に、その中央大穴１４を取り囲む位置において複数のボルト挿通穴１５（本例では５個）が等角度間隔（本例では７２°間隔）にて配列・形成されている。 The main body 10 of the hub has a disk-shaped axle mounting flange 12 as a main body, and a short cylindrical cylindrical wall 13 is provided on the outer peripheral edge of the flange 12. The axle mounting flange 12 extends in a direction (radial direction) orthogonal to the central axis C of the hub. Although the length of the cylindrical wall 13 is short, the cylindrical wall 13 protrudes rearward from the outer peripheral edge of the axle mounting flange 12 in parallel with the central axis C. The axle mounting flange 12 is formed with a central large hole 14 for passing the axle at its center position, and a plurality of bolt insertion holes 15 (5 in this example) are equiangular at positions surrounding the central large hole 14. They are arranged and formed at intervals (72 ° intervals in this example).

ハブの外周フランジ部２０は、ハブ本体部１０の円筒壁１３の後端縁からハブの半径方向外向きに当該円筒壁１３の全周にわたって突設されている。具体的には図３に示すように、外周フランジ部２０は、前記円筒壁１３の後端縁から半径方向外向きに突設された円環状の内輪部２１と、その内輪部２１を取り囲むと共に内輪部２１よりも大径な円環状の外輪部２２と、内輪部２１と外輪部２２との間の円環状帯領域にあって内外両輪部２１，２２を連結するための複数本の連結アーム２３，２４（合計２０本）とを備えている。これら２０本の連結アームのうち、半数の連結アーム２３は、ディスク又はハブの半径方向に対してディスク又はハブの一周方向たる時計回り方向に傾斜しており、残る半数の連結アーム２４は、ディスク又はハブの半径方向に対してディスク又はハブの他の周方向たる反時計回り方向に傾斜している。 The outer peripheral flange portion 20 of the hub projects from the rear end edge of the cylindrical wall 13 of the hub main body portion 10 outward in the radial direction of the hub over the entire circumference of the cylindrical wall 13. Specifically, as shown in FIG. 3, the outer peripheral flange portion 20 surrounds an annular inner ring portion 21 projecting radially outward from the rear end edge of the cylindrical wall 13, and the inner ring portion 21. An annular outer ring portion 22 having a larger diameter than the inner ring portion 21 and a plurality of connecting arms in the annular band region between the inner ring portion 21 and the outer ring portion 22 for connecting the inner and outer ring portions 21 and 22 23, 24 (20 in total). Of these 20 connecting arms, half of the connecting arms 23 are inclined in the clockwise direction, which is the circumference of the disk or hub, with respect to the radial direction of the disk or hub, and the remaining half of the connecting arms 24 are the disk. Alternatively, the disk or the hub is inclined in the counterclockwise direction that is the other circumferential direction with respect to the radial direction of the hub.

外周フランジ部２０の外輪部２２には、複数の締結部としての締結孔２５（本例では１０個）がハブの中心軸線Ｃを中心として等角度間隔（本例では３６°間隔）にて配列・形成されている。各締結孔２５は、単なるボルト通し孔であってその内側にネジ溝は形成されていない。この外輪部２２において、隣り合う二つの締結孔２５の丁度中間位置には、２本の連結アーム２３，２４の結合部位である「外輪連結部２６」がそれぞれ設定されている。つまり外輪部２２には、締結孔２５と同数（１０個）の外輪連結部２６が、ハブの中心軸線Ｃを中心として等角度間隔（３６°間隔）にて配列されると共に、隣り合う二つの外輪連結部２６は、外輪部２２の一部である円弧状部分によって相互連結されている。そして、隣り合う二つの外輪連結部２６の丁度中間位置に締結孔２５がそれぞれ設けられている。 In the outer ring portion 22 of the outer peripheral flange portion 20, a plurality of fastening holes 25 (10 in this example) are arranged at equal angular intervals (36 ° intervals in this example) about the center axis C of the hub.・ It is formed. Each fastening hole 25 is a mere bolt through hole, and no thread groove is formed therein. In the outer ring portion 22, an “outer ring connecting portion 26” that is a connecting portion of the two connecting arms 23 and 24 is set just at an intermediate position between two adjacent fastening holes 25. That is, in the outer ring portion 22, the same number (10) of outer ring connecting portions 26 as the fastening holes 25 are arranged at equiangular intervals (36 ° intervals) around the central axis C of the hub, and two adjacent two are arranged. The outer ring connecting portion 26 is interconnected by an arcuate portion that is a part of the outer ring portion 22. And the fastening hole 25 is each provided in the intermediate position of the two adjacent outer ring | wheel connection parts 26 adjacently.

外周フランジ部２０の外輪部２２は、各締結孔２５の周辺部位が他部位よりも幅広になっており、外輪部２２の幅は全周にわたって必ずしも一様ではないが、各締結孔２５の周辺部位を除いた部位の幅ｈ（即ち、隣り合う二つの外輪連結部２６を実質的に連結している部位の幅ｈ）は、約８ｍｍに設定されている。また、外輪部２２の厚さｔは、約５ｍｍに設定されている。そして、隣り合う二つの外輪連結部２６間の外輪部２２の円弧に沿った離間長Ｌ（この離間長Ｌは隣り合う二つの締結孔２５間の外輪部２２の円弧に沿った離間長でもある）は、約６７ｍｍとなっている。つまり本実施形態では、ハブの外周フランジ部２０の直径及び締結孔２５の数を考慮しつつ、５×ｈ＝４０＜Ｌ＝６７の関係を満たすように、外輪部２２の幅ｈが設定されている。また、外輪部２２の厚さｔは幅ｈ未満となるように設定されている。 In the outer ring portion 22 of the outer peripheral flange portion 20, the peripheral portion of each fastening hole 25 is wider than the other portions, and the width of the outer ring portion 22 is not necessarily uniform over the entire circumference. The width h of the portion excluding the portion (that is, the width h of the portion that substantially connects the two adjacent outer ring connecting portions 26) is set to about 8 mm. Further, the thickness t of the outer ring portion 22 is set to about 5 mm. Then, the separation length L along the arc of the outer ring portion 22 between the two adjacent outer ring connecting portions 26 (this separation length L is also the separation length along the arc of the outer ring portion 22 between the two adjacent fastening holes 25. ) Is about 67 mm. That is, in the present embodiment, the width h of the outer ring portion 22 is set so as to satisfy the relationship of 5 × h = 40 <L = 67, taking into account the diameter of the outer peripheral flange portion 20 of the hub and the number of fastening holes 25. ing. Further, the thickness t of the outer ring portion 22 is set to be less than the width h.

外輪部２２の各外輪連結部２６は、時計回り方向に傾斜した連結アーム２３及び反時計回り方向に傾斜した連結アーム２４の２本の連結アームによって内輪部２１に連結されている。これら２本の連結アーム２３，２４の傾斜状態は、その外輪連結部２６とハブの中心軸線Ｃとを結ぶ半径方向仮想線に対し線対称となっている。つまり、連結アーム２３と２４とは、ハブの半径方向に対して傾斜の向きが互いに反対向きであるが、ハブの半径方向に対する傾斜角度は等しくなっている。二種類の連結アーム２３，２４の各傾斜角度については、図３に示すように、各連結アーム２３，２４に対応する当該外輪連結部２６の左右両隣に位置する締結孔２５の各々とハブの中心軸線Ｃとを結ぶ半径方向仮想線に対する各連結アーム２３，２４の傾斜角度θ２が、約６０°に設定されている。 Each outer ring connecting portion 26 of the outer ring portion 22 is connected to the inner ring portion 21 by two connecting arms, a connecting arm 23 inclined in the clockwise direction and a connecting arm 24 inclined in the counterclockwise direction. The inclined states of the two connecting arms 23 and 24 are symmetrical with respect to a virtual imaginary line connecting the outer ring connecting portion 26 and the central axis C of the hub. That is, the connecting arms 23 and 24 are inclined in directions opposite to each other with respect to the radial direction of the hub, but the inclination angles with respect to the radial direction of the hub are equal. As shown in FIG. 3, the inclination angles of the two types of connection arms 23 and 24, as shown in FIG. 3, each of the fastening holes 25 located on the left and right sides of the outer ring connection portion 26 corresponding to each connection arm 23 and 24 and the hub. The inclination angle θ2 of each of the connecting arms 23 and 24 with respect to the imaginary radial line connecting the central axis C is set to about 60 °.

その結果、時計回り方向に傾斜した各連結アーム２３の内端は、その連結アーム２３に対応する外輪連結部２６の左隣（反時計回り方向での隣）に位置する締結孔２５とハブの中心軸線Ｃとを結ぶ半径方向仮想線が内輪部２１と交わる位置にある内輪連結部２７に連結されている。同様に、反時計回り方向に傾斜した各連結アーム２４の内端は、その連結アーム２４に対応する外輪連結部２６の右隣（時計回り方向での隣）に位置する締結孔２５とハブの中心軸線Ｃとを結ぶ半径方向仮想線が内輪部２１と交わる位置にある内輪連結部２７に連結されている。これにより外輪部２２は内輪部２１に対し、総じて周方向に沿いジグザグに配列された合計２０本の連結アーム２３，２４によって連結されている。 As a result, the inner end of each connecting arm 23 inclined in the clockwise direction is connected to the fastening hole 25 and the hub located on the left side of the outer ring connecting portion 26 corresponding to the connecting arm 23 (adjacent in the counterclockwise direction). A radial imaginary line connecting the central axis C is connected to an inner ring connecting portion 27 at a position where the inner ring portion 21 intersects. Similarly, the inner end of each connecting arm 24 inclined in the counterclockwise direction is connected to the fastening hole 25 and the hub located on the right side (next to the clockwise direction) of the outer ring connecting portion 26 corresponding to the connecting arm 24. A radial imaginary line connecting the central axis C is connected to an inner ring connecting portion 27 at a position where the inner ring portion 21 intersects. As a result, the outer ring portion 22 is connected to the inner ring portion 21 by a total of 20 connecting arms 23 and 24 arranged in a zigzag manner along the circumferential direction.

図２及び図４に示すように、環状の摺動体３は、鋳造により片状黒鉛鋳鉄を一体成形したものである。この摺動体３は、第１の環状円板部３１と第２の環状円板部３２とを、両環状円板部３１，３２間にあって放射方向に延びる複数の連結リブ３３で相互に連結したものであり、隣り合う連結リブ３３間に放射方向に延びる通気路３４が確保されたベンチレート構造を有するものである。第１及び第２の環状円板部３１，３２における各外側面が、ブレーキキャリパの制輪子と摩擦接触する摺動面となる。 As shown in FIGS. 2 and 4, the annular sliding body 3 is obtained by integrally molding flake graphite cast iron by casting. In the sliding body 3, the first annular disc portion 31 and the second annular disc portion 32 are connected to each other by a plurality of connecting ribs 33 extending between the annular disc portions 31 and 32 and extending in the radial direction. It has a ventilating structure in which an air passage 34 extending in the radial direction is secured between adjacent connecting ribs 33. The outer side surfaces of the first and second annular disk portions 31 and 32 become sliding surfaces that come into frictional contact with the brake caliper control wheel.

第１の環状円板部３１の内周側には、幅ｈ２の内周フランジ部３５が、第１の環状円板部３１の全内周にわたって突設されている。この内周フランジ部３５には、複数の締結ネジ孔３６（本例では１０個）が摺動体３の中心軸線Ｃを中心として等角度間隔（本例では３６°間隔）にて配列・形成されている。各締結ネジ孔３６の内側には、締結ボルト４の雄ネジに対応する雌ネジが形成されている。なお、摺動体３の中心軸線Ｃから内周フランジ部３５の各締結ネジ孔３６までの距離は、前記ハブ１の中心軸線Ｃから外周フランジ部２０の各締結孔２５までの距離に一致しており、締結ネジ孔３６と締結孔２５とを一致させつつ、摺動体３の内周フランジ部３５とハブ１の外周フランジ部２０とを相互に接合可能となっている（図２参照）。 On the inner peripheral side of the first annular disc portion 31, an inner peripheral flange portion 35 having a width h <b> 2 projects from the entire inner periphery of the first annular disc portion 31. A plurality of fastening screw holes 36 (10 in this example) are arranged and formed in the inner peripheral flange portion 35 at equiangular intervals (36 ° intervals in this example) around the central axis C of the sliding body 3. ing. A female screw corresponding to the male screw of the fastening bolt 4 is formed inside each fastening screw hole 36. The distance from the central axis C of the sliding body 3 to each fastening screw hole 36 of the inner peripheral flange portion 35 matches the distance from the central axis C of the hub 1 to each fastening hole 25 of the outer peripheral flange portion 20. Thus, the inner peripheral flange portion 35 of the sliding body 3 and the outer peripheral flange portion 20 of the hub 1 can be joined to each other while the fastening screw hole 36 and the fastening hole 25 are matched (see FIG. 2).

図１及び図２に示すように、締結具としての締結ボルト４を用いて、ハブ１の外周フランジ部２０に対して環状の摺動体３を固着することにより、ブレーキディスクが組み立てられる。即ち、ハブの外周フランジ部２０における１０個の締結孔２５と、摺動体の内周フランジ部３５における１０個の締結ネジ孔３６とを一致させながらハブ１の周囲に環状摺動体３を位置合わせすると共に、各締結孔２５及び締結ネジ孔３６に対し、ハブの車軸取付け用フランジ１２側から締結ボルト４をワッシャー５とともに螺合する。すると、合計１０本の締結ボルト４の締付力により、ハブ１と摺動体３とが一体結合される。なお、締結ボルト４を取り付ける際に、締結ボルト４の螺子目にボルト緩み防止剤を予め塗布しておくことは好ましい。 As shown in FIGS. 1 and 2, the brake disc is assembled by fixing the annular sliding body 3 to the outer peripheral flange portion 20 of the hub 1 using a fastening bolt 4 as a fastener. That is, the annular sliding member 3 is aligned around the hub 1 while the ten fastening holes 25 in the outer peripheral flange portion 20 of the hub and the ten fastening screw holes 36 in the inner peripheral flange portion 35 of the sliding member are aligned. At the same time, the fastening bolts 4 and the washers 5 are screwed into the fastening holes 25 and the fastening screw holes 36 from the axle mounting flange 12 side of the hub. Then, the hub 1 and the sliding body 3 are integrally coupled by the tightening force of a total of ten fastening bolts 4. In addition, when attaching the fastening bolt 4, it is preferable to apply a bolt loosening prevention agent to the screw of the fastening bolt 4 in advance.

ブレーキディスクの組み立て完了後に、ハブ１の車軸取付け用フランジ１２や摺動体３の各摺動面に対して、精度向上のための追加加工（例えば表面切削や研磨加工）を適宜施してもよい。 After the assembly of the brake disk is completed, additional processing (for example, surface cutting or polishing) for improving accuracy may be appropriately performed on the axle mounting flange 12 of the hub 1 and each sliding surface of the sliding body 3.

次に、本実施形態のディスクを車輌に取り付けた場合の作用及び効果を説明する。 Next, operations and effects when the disk of this embodiment is attached to a vehicle will be described.

制動時の摩擦熱で環状の摺動体３の全体が半径方向外向き（拡径方向）に熱膨張した場合、各締結ボルト４を介して、ハブの外周フランジ部２０を構成する円環状の外輪部２２が各締結孔２５の位置で拡径方向に引っ張られる。その際、図５に示すように、締結孔２５の周方向両側に位置する各外輪連結部２６は、２本の連結アーム２３，２４を介して内輪部２１の内輪連結部２７に、ひいてはハブ本体部１０に連結されているため、拡径方向への引っ張りに対しては頑強に抵抗してハブ本体部１０との距離を維持しようとする。これに対し、隣り合う二つの外輪連結部２６間に位置する締結孔２５は、締結ボルト４を介して熱膨張する摺動体３に追従しようとする。このため、隣り合う二つの外輪連結部２６を架橋的に連結している外輪部の一部（円弧状の架橋部）が、摺動体３の熱膨張に追従して締結孔位置にて拡径方向に膨出するように変形する。この円弧状の架橋部の変形は、好ましくは弾性変形である。この膨出変形によって摺動体３の内周部とハブ本体部１０の円筒壁１３との間隔が微増調整されるため、摺動体３の熱膨張に起因する拡径方向への引っ張り力が、ハブ本体部１０の円筒壁１３（つまり外周フランジ部２０の根元）に及ぶことが緩和される。従って、環状の摺動体３を中心軸線Ｃの方向に熱倒れさせるようなモーメントをほとんど生じない。 When the entire annular sliding body 3 thermally expands radially outward (in the direction of expansion) due to frictional heat at the time of braking, an annular outer ring constituting the outer peripheral flange portion 20 of the hub via each fastening bolt 4 The part 22 is pulled in the diameter increasing direction at the position of each fastening hole 25. At that time, as shown in FIG. 5, the outer ring connecting portions 26 located on both sides in the circumferential direction of the fastening hole 25 are connected to the inner ring connecting portion 27 of the inner ring portion 21 via the two connecting arms 23 and 24 and eventually to the hub. Since it is connected to the main body 10, it tries to maintain the distance from the hub main body 10 by strongly resisting the pulling in the diameter expanding direction. On the other hand, the fastening hole 25 located between two adjacent outer ring connecting portions 26 tends to follow the sliding body 3 that thermally expands via the fastening bolt 4. For this reason, a part of the outer ring portion (the arc-shaped bridging portion) that bridges the two adjacent outer ring coupling portions 26 in a cross-linked manner follows the thermal expansion of the sliding body 3 and expands in diameter at the fastening hole position. Deforms to bulge in the direction. The deformation of the arcuate bridging portion is preferably elastic deformation. Since the space between the inner peripheral part of the sliding body 3 and the cylindrical wall 13 of the hub main body 10 is slightly increased and adjusted by this bulging deformation, the pulling force in the diameter expansion direction caused by the thermal expansion of the sliding body 3 is caused by the hub. Covering the cylindrical wall 13 of the main body portion 10 (that is, the root of the outer peripheral flange portion 20) is alleviated. Therefore, a moment that causes the annular sliding body 3 to heat down in the direction of the central axis C hardly occurs.

その後、ブレーキキャリパの制輪子によるディスクの押圧が解除されて、一旦膨張した摺動体３が放熱することで半径方向内向き（縮径方向）に収縮するときには、前記二つの外輪連結部２６を架橋的に連結している外輪部の一部が元の状態に復帰する方向に変形する。そして、各締結ボルト４又は締結孔２５とハブ本体部１０の円筒壁１３との間隔が熱膨張前の状態に戻される。 After that, when the disc is released from the brake caliper by the brake caliper and the expanded sliding body 3 radiates heat and contracts inward in the radial direction (reducing direction), the two outer ring connecting portions 26 are bridged. The part of the outer ring part that is connected in general is deformed in a direction to return to the original state. And the space | interval of each fastening bolt 4 or the fastening hole 25 and the cylindrical wall 13 of the hub main-body part 10 is returned to the state before thermal expansion.

このように本実施形態によれば、環状の摺動体３は、隣り合う二つの外輪連結部２６を架橋的に連結している外輪部２２の一部（円弧状の架橋部）の膨出的変形可能性のために、ハブ本体部１０に過度に拘束されることなく拡径方向又は縮径方向への変形自由度をある程度確保されている。つまり、制動時の摩擦熱で摺動体３が熱膨張する場合でも、ハブ本体部１０が、実質的に摺動体３の内周側根元に相当する部分（本例では外周フランジ部２０と円筒壁１３との結合部分）を過度に拘束しない。このため、摺動体３の熱倒れを効果的に防止又は抑制することができる。そして、摺動体３の熱倒れをほとんど生じないことで、ディスクの偏摩耗を極力回避でき、制動時における制動トルクの不安定化や不快なブレーキ振動を低減することができる。 Thus, according to the present embodiment, the annular sliding body 3 is a bulging part of the outer ring portion 22 (arc-shaped bridging portion) that bridges two adjacent outer ring coupling portions 26 in a bridging manner. Because of the possibility of deformation, the degree of freedom of deformation in the diameter expansion direction or the diameter reduction direction is ensured to some extent without being excessively constrained by the hub body 10. That is, even when the sliding body 3 thermally expands due to frictional heat at the time of braking, the hub body portion 10 is a portion substantially corresponding to the inner peripheral side base of the sliding body 3 (in this example, the outer peripheral flange portion 20 and the cylindrical wall). 13 is not excessively restrained. For this reason, the thermal collapse of the sliding body 3 can be prevented or suppressed effectively. Further, since the thermal collapse of the sliding body 3 hardly occurs, uneven wear of the disk can be avoided as much as possible, and instability of braking torque and unpleasant brake vibration during braking can be reduced.

本実施形態によれば、外輪部２２には、複数の外輪連結部２６が等角度間隔で配列されると共に、各締結孔２５が隣り合う二つの外輪連結部２６の丁度中間に位置するように配列されているため、摺動体３が膨張又は収縮する際に、外輪部２２に作用する応力が全ての半径方向に対して均等化し、外輪部２２に局部的な歪みを生ずるおそれがない。また、各締結孔２５からその左側の外輪連結部２６までの距離と、その右側の外輪連結部２６までの距離とが等しいことで、摺動体３の熱膨張時における締結孔位置での外輪部２２の半径方向変位量を確保し易い。 According to the present embodiment, the outer ring portion 22 has a plurality of outer ring connecting portions 26 arranged at equiangular intervals, and each fastening hole 25 is positioned exactly in the middle of two adjacent outer ring connecting portions 26. Since they are arranged, when the sliding body 3 expands or contracts, the stress acting on the outer ring portion 22 is equalized in all radial directions, and there is no possibility of causing local distortion in the outer ring portion 22. Further, since the distance from each fastening hole 25 to the left outer ring connecting portion 26 is equal to the distance from the right outer ring connecting portion 26, the outer ring portion at the fastening hole position at the time of thermal expansion of the sliding body 3 is achieved. It is easy to secure a radial displacement amount of 22.

本実施形態によれば、合計２０本の連結アーム２３，２４を用いると共に、各外輪連結部２６を線対称に傾斜した２本の連結アーム２３，２４を介してハブ本体部１０に連結することにより、各外輪連結部２６において外輪部２２ひいては摺動体３がハブ本体部１０に対し確実に支持される。そして、連結アーム群による摺動体３の姿勢保持力も非常に高い。それ故、本実施形態のブレーキディスクには、摺動体３における各摺動面の振れ精度を長期間にわたり高精度に保つことを困難にするような事情は存在しない。また、各連結アーム２３，２４をディスクの放射方向（半径方向）に沿って設けるのではなく、放射方向に対して傾斜角度θ２＝６０°で傾斜させたことで、制動トルクに対するせん断強度を高めて、ブレーキディスク全体の剛性を高めることができる。 According to the present embodiment, a total of 20 connecting arms 23 and 24 are used, and each outer ring connecting portion 26 is connected to the hub main body 10 via two connecting arms 23 and 24 that are inclined in line symmetry. Thus, the outer ring portion 22 and the sliding body 3 are reliably supported with respect to the hub main body portion 10 in each outer ring connecting portion 26. And the attitude | position holding force of the sliding body 3 by a connection arm group is also very high. Therefore, there is no circumstance that makes it difficult to keep the deflection accuracy of each sliding surface of the sliding body 3 high for a long period of time in the brake disk of this embodiment. Further, the connecting arms 23 and 24 are not provided along the radial direction (radial direction) of the disk, but are inclined at an inclination angle θ2 = 60 ° with respect to the radial direction, thereby increasing the shear strength against the braking torque. Thus, the rigidity of the entire brake disc can be increased.

本実施形態によれば、ハブ１の外周フランジ部２０には、連結アーム２３，２４間において略三角形状の開口が２０区画ほど存在しており、これらの開口の分だけハブ１の減肉による軽量化を図ることができる。また、ハブ１と摺動体３とを別体としているので、摺動体３が摩耗又は破損した場合でも摺動体３のみを交換することができ、保守管理性に優れている。 According to the present embodiment, the outer peripheral flange portion 20 of the hub 1 includes approximately 20 triangular openings between the connecting arms 23 and 24, and the hub 1 is thinned by the amount of these openings. Weight reduction can be achieved. Further, since the hub 1 and the sliding body 3 are separated, only the sliding body 3 can be replaced even when the sliding body 3 is worn or damaged, and the maintenance management is excellent.

［変更例］本発明における締結具は、締結ボルト４に限定されるものではなく、リベット等のピン状の機械要素であってもよい。また、締結具の全部又は一部が、ハブ１又は摺動体３のいずれかに予め一体化されていてもよい。 [Modification] The fastener in the present invention is not limited to the fastening bolt 4 but may be a pin-like mechanical element such as a rivet. Further, all or part of the fasteners may be integrated in advance with either the hub 1 or the sliding body 3.

［変更例］ハブ１の外輪部２２は、弾性変形可能な素材で構成されてもよい。 [Modification] The outer ring portion 22 of the hub 1 may be made of an elastically deformable material.

ブレーキディスクの一例を示す正面図。The front view which shows an example of a brake disc. 図１のＣ−Ａ線での半径方向断面図。FIG. 2 is a radial cross-sectional view taken along line C-A in FIG. 1. 図１のブレーキディスクの一構成部品であるハブの正面図。The front view of the hub which is one component of the brake disc of FIG. 図１のブレーキディスクの一構成部品である摺動体の正面図。The front view of the sliding body which is one component of the brake disc of FIG. 本発明の作用を説明するための概念図。The conceptual diagram for demonstrating the effect | action of this invention. 従来のブレーキディスクの半径方向断面図。FIG. 3 is a radial cross-sectional view of a conventional brake disc.

Explanation of symbols

１…ハブ、３…摺動体、４…締結ボルト（締結具）、１０…ハブの本体部、２０…ハブの外周フランジ部、２１…内輪部、２２…外輪部、２３，２４…連結アーム、２５…外輪部の締結孔（締結部）、２６…外輪連結部、２７…内輪連結部、Ｃ…中心軸線、ｈ…外輪部の幅、Ｌ…外輪連結部間の離間長、θ２…連結アームの傾斜角度。 DESCRIPTION OF SYMBOLS 1 ... Hub, 3 ... Sliding body, 4 ... Fastening bolt (fastener), 10 ... Main part of hub, 20 ... Outer peripheral flange part of hub, 21 ... Inner ring part, 22 ... Outer ring part, 23, 24 ... Connection arm, 25 ... fastening hole (fastening part) of outer ring part, 26 ... outer ring connecting part, 27 ... inner ring connecting part, C ... central axis, h ... width of outer ring part, L ... separation distance between outer ring connecting parts, θ2 ... connecting arm Angle of inclination.

Claims

A hub having a main body portion attached to an axle and an outer peripheral flange portion provided around the main body portion, and an annular slide body fixed to the outer peripheral flange portion of the hub by a plurality of fasteners In the configured brake disc,
The outer peripheral flange portion of the hub includes a plurality of outer ring connecting portions and an annular outer ring portion having a plurality of fastening portions for mounting the fasteners, and the outer ring connecting portion for connecting the outer ring connecting portions to the main body portion of the hub. A plurality of connecting arms,
In the outer ring portion, two adjacent outer ring connecting portions are connected by a part of the outer ring portion, and the fastening portion is provided between the two outer ring connecting portions.

In the outer ring portion, the plurality of outer ring connecting portions are provided at equiangular intervals with the center axis (C) of the hub as the center, and each of the same number of fastening portions as the outer ring connecting portions is adjacent to the two outer ring connecting portions. The brake disc according to claim 1, wherein the brake disc is provided so as to be located exactly in the middle of the portion.

The plurality of outer ring connecting portions in the outer ring portion have a separation length (L) along the outer ring portion between two adjacent outer ring connecting portions that is five times longer than the width (h) of the outer ring portion (5h). The brake disk according to claim 1, wherein the brake disk is set to be large.

A hub having a main body portion attached to an axle and an outer peripheral flange portion provided around the main body portion, and an annular slide body fixed to the outer peripheral flange portion of the hub by a plurality of fasteners In the configured brake disc,
The outer peripheral flange portion of the hub is
A plurality of outer ring connecting portions provided at equiangular intervals around the center axis (C) of the hub, and the same number as the outer ring connecting portions, and each being positioned between the two adjacent outer ring connecting portions. An annular outer ring portion having a fastening portion for mounting each of the fasteners provided on,
A number of connecting arms twice as many as the outer ring connecting portions for connecting the outer ring connecting portions to the main body of the hub,
Each outer ring connecting portion is connected to the main body portion of the hub via two connecting arms inclined so as to be symmetrical with respect to a virtual imaginary line connecting the outer ring connecting portion and the central axis (C) of the hub. In addition, the inclination angle (θ2) of each connecting arm with respect to a virtual imaginary line connecting each of the fastening portions located on both sides of the outer ring connecting portion and the central axis (C) of the hub is 30 ° or more and 60 ° or less. Brake disc characterized by being.

The plurality of outer ring connecting portions in the outer ring portion have a separation length (L) along the outer ring portion between two adjacent outer ring connecting portions that is five times longer than the width (h) of the outer ring portion (5h). The brake disc according to claim 4, wherein the brake disc is set to be large.