WO2023084934A1 - Floating-type brake disc, and wheel for straddle-type vehicle - Google Patents

Floating-type brake disc, and wheel for straddle-type vehicle Download PDF

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Publication number
WO2023084934A1
WO2023084934A1 PCT/JP2022/035659 JP2022035659W WO2023084934A1 WO 2023084934 A1 WO2023084934 A1 WO 2023084934A1 JP 2022035659 W JP2022035659 W JP 2022035659W WO 2023084934 A1 WO2023084934 A1 WO 2023084934A1
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Prior art keywords
hub
curved beam
circumferential direction
brake disc
spoke
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PCT/JP2022/035659
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French (fr)
Japanese (ja)
Inventor
裕美子 渡辺
直樹 冨沢
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株式会社ユタカ技研
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Priority claimed from JP2021184187A external-priority patent/JP7478125B2/en
Application filed by 株式会社ユタカ技研 filed Critical 株式会社ユタカ技研
Publication of WO2023084934A1 publication Critical patent/WO2023084934A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62L—BRAKES SPECIALLY ADAPTED FOR CYCLES
    • B62L1/00—Brakes; Arrangements thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes

Definitions

  • the present invention is a floating type brake system mainly used for a saddle-ride type vehicle such as a motorcycle, which includes an annular rotor and a hub arranged concentrically with a predetermined gap inside the rotor.
  • the present invention relates to a brake disc and a wheel for a saddle type vehicle provided with a floating type brake disc.
  • this type of floating type brake disc is known, for example, from Japanese Unexamined Patent Application Publication No. 2002-200012.
  • the rotor and hub are connected by a plurality of connecting portions provided at regular intervals in the circumferential direction, and an annular mounting portion is provided at the center of the hub to be fastened to the wheel.
  • the spokes which are composed of two beams branching from each of the connecting portions toward the mounting portion, are arranged at regular intervals in the circumferential direction.
  • the hub is lightened without providing an annular beam that connects the joints.
  • the present invention provides a floating type brake disc capable of reducing the weight of the hub while having sufficient strength to withstand shearing force during braking, and a saddle type vehicle equipped with this floating type brake disc.
  • the object is to provide a wheel of
  • the floating type brake disc of the present invention comprises an annular rotor and a hub arranged concentrically with a predetermined gap inside the rotor.
  • the hub is joined by a plurality of joints provided at equal intervals in the circumferential direction, and has an annular mounting portion at the center of the hub that is fastened to the wheel. It has a spoke portion formed by two curved beam portions extending in a branched manner so as to gradually widen and curved in the circumferential direction with a predetermined curvature, and the spoke portions are arranged at equal intervals in the circumferential direction. characterized by
  • the two curved beam portions that are curved in the circumferential direction and that constitute each spoke portion act like springs, and when a load is applied in the circumferential direction, the straight beams as in the conventional example are formed.
  • the portion by elastically deforming, it is possible to elastically absorb the shear force acting on the hub during braking.
  • the width of the curved beam portion is 20% or more and 50% or less of the width of the tip portion of the spoke portion on the joint portion side. If the width of the curved beam portion is larger than 50% of the width of the tip portion of the spoke portion on the connecting portion side, the weight of the hub becomes heavier than that of a conventional hub, making it difficult to reduce the weight of the hub. On the other hand, if the width of the curved beam portion is less than 20% of the width of the tip portion of the spoke portion on the connecting portion side, the curved beam portions will warp due to heat generated during machining of the hub.
  • the curved beam portion on one side in the circumferential direction of the spoke portion is the first curved beam portion
  • the curved beam portion on the other side in the circumferential direction is the second curved beam portion
  • the first curved beam portion extends in the circumferential direction.
  • the tip portion of the first curved beam portion on the mounting portion side is the first curved beam portion of the spoke portion that is further adjacent to the adjacent spoke portion on the one side in the circumferential direction. 2
  • the spokes arranged at equal intervals in the circumferential direction between the connecting portion and the mounting portion form a truss structure, so that all the load applied to the hub is distributed to each curved beam portion. Therefore, even if a large load acts on the hub, deformation of the hub can be prevented.
  • the weight of the hub can be further reduced as compared with the case where the joint portion is directly connected to the mounting portion without providing the connecting protrusion.
  • the connecting protrusion is provided on a line connecting the center of the hub and the connecting portion, and the connecting portion, the two curved beam portions of the spoke portion and It is preferable that the shape of each of the connecting protrusions is symmetrical. According to this, the load applied from the connecting portion to the hub is divided equally between the curved beam portions and the connecting protrusions of the spoke portions, and the same load acts on the curved beam portions and the connecting protrusions. As a result, the strength of the entire hub can be improved, and the braking performance and durability of the brake disc can be improved.
  • the wheel of the saddle-riding type vehicle having the wheel and the floating type brake disc mounted on the wheel of the present invention uses the floating type brake disc of the present invention as the floating type brake disc.
  • FIG. 1 is a side view of a front wheel of a saddle-ride type vehicle equipped with a floating type brake disc according to a first embodiment of the present invention
  • FIG. 1 is a side view of a floating type brake disc according to a first embodiment of the present invention, viewed from one axial direction
  • FIG. 2 is an exploded perspective view of the coupling portion between the rotor and hub of the floating brake disc according to the first embodiment of the present invention
  • FIG. 11 is a side view of a floating type brake disc according to a second embodiment of the present invention, viewed from one axial direction
  • FIG. 11 is a side view of a floating type brake disc according to a third embodiment of the present invention, viewed from one axial direction
  • FIG. 11 is a side view of a floating type brake disc according to a fourth embodiment of the present invention, viewed from one axial direction;
  • FIG. 11 is a side view of a floating type brake disc according to a fifth embodiment of the present invention, viewed from one axial direction;
  • FW is the front wheel of a saddle type vehicle such as a motorcycle.
  • the front wheel FW has a wheel We rotatably supported via a bearing (not shown) on an axle Fs suspended from a front fork Ff, and a tire Tr mounted on the outer peripheral portion of the wheel We.
  • Cp is a caliper as a component of the braking device.
  • the brake disc BD1 of the first embodiment of the present invention is attached with fixing bolts Vt.
  • the brake device, and the fixing bolt Vt well-known ones can be used, so further explanation will be omitted.
  • the brake disc BD 1 comprises an annular rotor 1 and a hub 2 arranged concentrically inside the rotor 1 with a predetermined gap.
  • the rotor 1 is made of stainless steel plate, for example.
  • the rotor 1 is clamped by the brake pads of the caliper Cp and transmits braking force to the axle Fs via the hub 2 .
  • the rotor 1 is provided with a plurality of circular through-holes 11 penetrating in the plate thickness direction for weight reduction and the like.
  • a plurality of substantially rectangular tongue-like protruding pieces 12 extending radially inward are formed on the inner peripheral edge portion of the rotor 1 at predetermined intervals in the circumferential direction.
  • the hub 2 is made of aluminum alloy, for example.
  • Receiving recesses 21 are formed on the outer periphery of the hub 2 so as to correspond to the projecting pieces 12 and are recessed radially inward to receive the projecting pieces 12 .
  • a slip-off prevention means 3 is provided to prevent the projecting piece 12 from slipping out of the receiving recess 21 in the axial direction.
  • a connecting portion 4 for connecting the rotor 1 and the hub 2 is constituted by the projecting piece 12, the receiving recess 21, and the retaining means 3.
  • an annular mounting portion 22 having a shaft hole 22a is provided at the center of the hub 2.
  • a fixing bolt Vt is inserted through a mounting hole 22b formed around the shaft hole 22a to fasten the mounting portion 22 to the wheel We.
  • the receiving recess 21 has receiving surfaces substantially parallel to both radial side surfaces of the projecting piece 12 , and the width between the receiving surfaces is slightly larger than the circumferential width of the projecting piece 12 . Further, the receiving recess 21 is provided so that only one axial direction is open, and the other axial direction is closed by a wall 211 integral with the hub 2 . Further, one radially inner end portion 21a of the receiving recess 21 in the axial direction is formed in a substantially circular shape larger than the other portion of the receiving recess 21, and the inner wall surface of this end portion 21a has a A groove 212 is formed along the .
  • the retaining means 3 is provided so as to face one of the surfaces in the axial direction of the protruding piece 12, and is, for example, a disk-shaped holding plate 31 made of an aluminum alloy, and engages with the groove 212 to hold the holding plate 31 in the axial direction. It is composed of a retaining ring 32 that prevents it from slipping out on one side. Since a known C-shaped snap ring can be used as the snap ring 32, detailed description thereof will be omitted.
  • a U-shaped plate member 5 along the inner wall surface of the receiving recess 21 is inserted into the gap between the projecting piece 12 and the receiving recess 21, and between the projecting piece 12 and the pressing plate 31, A disc spring 6 is interposed as a biasing means.
  • the strength of the hub 2 can be increased.
  • the method of connecting the rotor 1 and the hub 2 is not limited to the one described above, and other known methods can be used.
  • the hub 2 is formed with a receiving recess penetrating from one surface to the other in the axial direction, and a connecting pin having a flange portion formed at one end of a cylindrical body portion is used to protrude the connecting pin.
  • the rotor 1 and the hub 2 can also be connected by inserting the connecting pin through a pin hole formed in the piece and crimping the other end of the connecting pin.
  • a plurality of (12 in the present embodiment) spoke portions 23 are formed between the connecting portions 4 and the mounting portions 22 of the hub 2 at equal intervals in the circumferential direction.
  • the spokes 23 branch from each connecting portion 4 toward the mounting portion 22 (that is, radially inwardly) so as to gradually widen the interval in the circumferential direction, and have a predetermined curvature (R150 ) (hereinafter, the curved beam portion 231 on one side in the circumferential direction of each spoke portion 23 will be referred to as a first curved beam portion 231 1 , and the curved beam portion 231 on the other side in the circumferential direction will be referred to as a first curved beam portion 231 1 . is also called the second curved beam portion 2312 ).
  • the width W1 of the curved beam portion 231 is 3 mm, and the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 13 mm.
  • the width W1 of each curved beam portion 231, 231 is uniform from the radially outer side to the radially inner side, but is not limited to this. The width W1 may not be uniform from the radially outer side to the radially inner side.
  • each first curved beam portion 231-1 intersects the second curved beam portion 231-2 of the spoke portion 23 adjacent to one side in the circumferential direction. Further, each tip portion of the first curved beam portion 231-1 on the mounting portion 22 side is located on the mounting portion side of the second curved beam portion 231-2 of the spoke portion 23 further adjacent to the adjacent spoke portion 23 on one side in the circumferential direction. 23 to form each joint 232 .
  • each connecting portion 4 a connecting projection 221 projecting radially outward from the outer periphery of the mounting portion 23 and connected to each connecting portion 232 is provided. , are formed at regular intervals in the circumferential direction.
  • the shapes of each connecting portion 4, the two curved beam portions 231, 231 of each spoke portion 23, and the connecting protrusion 221 are symmetrical with respect to the line L. As shown in FIG.
  • the two curved beam portions 231, 231, which are curved in the circumferential direction and constitute each spoke portion 23, act like springs, and when a load is applied in the circumferential direction, the Unlike such a straight beam portion, the elastic deformation can absorb the shearing force acting on the hub 2 which acts as an impact during braking.
  • the width W1 of each curved beam portion 231, 231 of each spoke portion 23 can be reduced while maintaining sufficient strength to withstand shearing force during braking, and the weight of the hub 2 can be reduced.
  • the curvature of each curved beam portion 231, 231 of each spoke portion 23 can be set within the range of R35 to R150 depending on the number of spoke portions 23 (second embodiment to fifth embodiment described later). See also morphology).
  • the width W1 of the curved beam portion 231 is preferably 20% or more and 50% or less of the width W2 of the tip portion 23a of the spoke portion 23 on the coupling portion 4 side. If the width W1 of the curved beam portion 231 is larger than 50% of the width W2 of the tip portion 23a of the spoke portion 23 on the coupling portion 4 side, the hub 2 becomes heavier than the conventional hub 2, and it is difficult to reduce the weight of the hub 2. . On the other hand, if the width W1 of the curved beam portion 231 is smaller than 20% of the width W2 of the tip portion 23a of the spoke portion 23 on the coupling portion 4 side, the curved beam portion 231 will warp due to heat generated during machining of the hub 2. occurs.
  • the first curved beam portion 231-1 of the spoke portion 23 intersects the second curved beam portion 231-2 of the spoke portion 23 adjacent to the one side in the circumferential direction, and the first curved beam portion 231-1 on the mounting portion 22 side
  • the tip portion has a joint portion 232 that joins the tip portion of the second curved beam portion 2312 of the spoke portion 23 that is further adjacent to the adjacent spoke portion 23 on one side in the circumferential direction on the mounting portion 22 side.
  • the spoke portions 23 arranged at equal intervals in the circumferential direction between the connecting portion 4 and the mounting portion 22 form a truss structure, so that all the load applied to the hub 2 is transferred to each curved beam portion 231. , 231, and even if a large load acts on the hub 2, the deformation of the hub 2 can be prevented.
  • a connecting protrusion 221 that protrudes radially outward from the outer periphery of the mounting portion 22 and connects with the joint portion 232 . According to this, the weight of the hub 2 can be further reduced as compared with the case where the joint portion 232 is directly connected to the mounting portion 22 without providing the connecting protrusion 221 .
  • the connecting protrusion 221 is provided on a line L connecting the center O of the hub 2 and the coupling portion 4. It is preferable that each shape of the connecting protrusions 221 is symmetrical. According to this, the load applied from the coupling portion 4 to the hub 2 is evenly distributed to the curved beam portions 231, 231 and the connecting protrusion 221 of the spoke portion 23, and the curved beam portions 231, 231 and the connecting protrusion By applying an equivalent load to 221, the strength of the hub 2 as a whole can be improved, and the braking performance and durability of the brake disc BD1 are improved.
  • floating type brake discs BD 2 to BD 5 for motorcycles according to second to fifth embodiments shown in FIGS. 4 to 7 will be described.
  • the same members and portions as those of the first embodiment are denoted by the same reference numerals.
  • the second embodiment shown in FIG. 4 has 12 spoke portions 23 as in the first embodiment.
  • Each spoke portion 23 branches from each connecting portion 4 toward the mounting portion 22 so that the interval in the circumferential direction gradually widens, and each curved beam portion 231 curves in the circumferential direction with a predetermined curvature (R70). 231.
  • the width W1 of the curved beam portion 231 is 3 mm
  • the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 13 mm.
  • the width W1 of each curved beam portion 231, 231 and the width of each connecting protrusion 221 are uniform from the radially outer side to the radially inner side.
  • the width W1 of each curved beam portion 231, 231 and the width of each connecting protrusion 221 may not be uniform from the radially outer side to the radially inner side.
  • the third embodiment shown in FIG. 5 also has four spokes 23 .
  • Each spoke portion 23 branches from each connecting portion 4 toward the mounting portion 22 so as to gradually widen the interval in the circumferential direction. 231.
  • the width W1 of the curved beam portion 231 is 4.5 mm
  • the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 13 mm.
  • the joints to which the ends of the curved beams 231 and 231 on the side of the mounting portion 22 are joined and the connecting protrusions connected thereto are not provided.
  • the tip portion is joined to the mounting portion 22 .
  • each spoke portion 23 branches from each connecting portion 4 toward the mounting portion 22 so as to gradually widen the interval in the circumferential direction. 231.
  • the width W1 of the curved beam portion 231 is 3.5 mm
  • the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 12 mm.
  • the joints to which the ends of the curved beams 231 and 231 on the side of the mounting portion 22 are joined and the connecting projections to be connected to the joints are not provided.
  • Each tip of the curved beam portions 231 , 231 is joined to the mounting portion 22 .
  • each spoke portion 23 branches from each connecting portion 4 toward the mounting portion 22 so as to gradually widen the interval in the circumferential direction. 231.
  • the width W1 of the curved beam portion 231 is 3 mm
  • the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 12 mm.
  • this embodiment also does not provide joints where the ends of the curved beams 231 and 231 on the side of the mounting portion 22 are joined and connecting projections connected thereto.
  • Each tip of each curved beam portion 231 , 231 is joined to the mounting portion 22 .
  • a hole 22c having a different hole diameter is formed between the mounting holes 22b and 22b.
  • the present invention is not limited to the above.
  • the curved beam portions 231, 231 of the spoke portion 23 are symmetrical with respect to the line L connecting the center O of the hub 2 and the coupling portions 4.
  • the shape of 231 can also be asymmetrical.
  • the curvature of each of the curved beam portions 231, 231 can be in the range of R35 to R150 depending on the number of spoke portions 23 and the like.
  • the number of the spoke portions 23 and the curved beam portions 231, 231 The hub 2 can be designed without changing the diameter of the annular mounting portion 22 by changing the width W1 and the curvature of the ring.
  • FIG. 1 an example in which the brake disc BD 1 of the first embodiment is mounted on the wheel We of the front wheel FW for a saddle type vehicle has been described, but the brake discs of the second to fifth embodiments are described. BD 2 to BD 5 can also be attached.
  • the wheels shown in FIG . 1 are front wheels FW for a saddle-ride type vehicle . can be worn.
  • BD 1 to BD 5 floating type brake disc
  • FW front wheel of motorcycle (wheel for saddle type vehicle)
  • L line connecting center of hub and connecting portion
  • R curvature
  • W1 curve of curved beam Width
  • W2 Width of the tip portion of the spoke portion on the joint side

Abstract

Provided is a floating-type brake disc that is equipped with an annular rotor and a hub disposed concentrically with a prescribed gap with respect to the inner side of the rotor, and that enables reduction in hub weight while achieving a strength adequate to withstand shearing force during braking.　A rotor 1 and a hub 2 are joined at a plurality of joints 4 that are disposed at an equal interval in the circumferential direction. An annular attaching portion 22 to be fastened to a wheel We is provided at the center of the hub 2. The hub 2 has spoke portions 23 each comprising two curved beams 231, 231 which extend and branch out such that a circumferential gap therebetween gradually increases from the corresponding joint 4 toward the attaching portion 22 and which are curved at a prescribed curvature R in the circumferential direction. The spoke portions 23 are arranged at an equal interval in the circumferential direction.

Description

フローティング型ブレーキディスク並びに鞍乗り型車両用の車輪Wheels for floating type brake discs and saddle type vehicles

　本発明は、主として自動二輪車等の鞍乗り型車両用の制動装置に用いられる、環状のロータと、このロータの内側に所定の隙間を存して、同心に配置されるハブとを備えるフローティング型ブレーキディスク並びにフローティング型ブレーキディスクを備える鞍乗り型車両用の車輪に関する。
The present invention is a floating type brake system mainly used for a saddle-ride type vehicle such as a motorcycle, which includes an annular rotor and a hub arranged concentrically with a predetermined gap inside the rotor. The present invention relates to a brake disc and a wheel for a saddle type vehicle provided with a floating type brake disc.

　従来、この種のフローティング型ブレーキディスクは例えば特許文献１で知られている。このものは、ロータとハブとが、周方向に等間隔で設けられた複数の結合部で結合され、ハブの中心に、ホイールに締結される環状の取付部を備える。
Conventionally, this type of floating type brake disc is known, for example, from Japanese Unexamined Patent Application Publication No. 2002-200012. The rotor and hub are connected by a plurality of connecting portions provided at regular intervals in the circumferential direction, and an annular mounting portion is provided at the center of the hub to be fastened to the wheel.

　ところで、制動時には、ハブの回転する力とロータの止まろうとする力とによって、各結合部からハブに対して大きな荷重、即ち、剪断力が作用する。このため、この剪断力に耐え得るだけの強度を有しつつ、ハブ（即ち、ブレーキディスク）の軽量化を図ることが求められる。
By the way, during braking, a large load, that is, a shear force acts on the hub from each coupling portion due to the rotating force of the hub and the stopping force of the rotor. Therefore, it is required to reduce the weight of the hub (that is, the brake disc) while having enough strength to withstand this shearing force.

　そこで、上記従来のものは、上記各結合部から上記取付部に向けて周方向間隔が次第に広がるように分岐してのびる２本の梁部で構成されるスポーク部を、周方向に等間隔で配列させたトラス構造とすることで、各結合部同士を連結する環状梁部を設けず、ハブを軽量化している。
Therefore, in the above-described conventional device, the spokes, which are composed of two beams branching from each of the connecting portions toward the mounting portion, are arranged at regular intervals in the circumferential direction. By adopting an arrayed truss structure, the hub is lightened without providing an annular beam that connects the joints.

　ここで、ハブの更なる軽量化を図るには、各梁部の幅を細くすることが考えられるが、ハブの強度が低下する虞があり、ハブの強度を確保しながら、ハブの軽量化を図ることが難しかった。
Here, in order to further reduce the weight of the hub, it is conceivable to narrow the width of each beam, but there is a risk that the strength of the hub will decrease. was difficult to achieve.

特許第４４８１０７４号Patent No. 4481074

　本発明は、以上の点に鑑み、制動時の剪断力に耐え得る十分な強度を有しつつ、ハブの軽量化を実現できるフローティング型ブレーキディスク並びにこのフローティング型ブレーキディスクを備える鞍乗り型車両用の車輪を提供することをその課題とするものである。
In view of the above points, the present invention provides a floating type brake disc capable of reducing the weight of the hub while having sufficient strength to withstand shearing force during braking, and a saddle type vehicle equipped with this floating type brake disc. The object is to provide a wheel of

　上記課題を解決するために、環状のロータと、このロータの内側に所定の隙間を存して、同心に配置されるハブとを備える本発明のフローティング型ブレーキディスクは、ロータとハブとが、周方向に等間隔で設けられた複数の結合部で結合され、ハブの中心に、ホイールに締結される環状の取付部を備え、ハブは、各結合部から取付部に向けて周方向間隔が次第に広がるように分岐してのび、且つ、所定の曲率で周方向に湾曲した２本の湾曲梁部で構成されるスポーク部を有し、このスポーク部が周方向に等間隔で配列されることを特徴とする。
In order to solve the above problems, the floating type brake disc of the present invention comprises an annular rotor and a hub arranged concentrically with a predetermined gap inside the rotor. The hub is joined by a plurality of joints provided at equal intervals in the circumferential direction, and has an annular mounting portion at the center of the hub that is fastened to the wheel. It has a spoke portion formed by two curved beam portions extending in a branched manner so as to gradually widen and curved in the circumferential direction with a predetermined curvature, and the spoke portions are arranged at equal intervals in the circumferential direction. characterized by

　本発明によれば、各スポーク部を構成する周方向に湾曲した２本の湾曲梁部が、バネの様に作用して、周方向荷重を加えたときに、従来例の如き直線状の梁部と異なり、弾性的に変形することで、制動時にハブに衝撃的に作用する剪断力を弾性的に吸収することができる。その結果、制動時の剪断力に耐え得る十分な強度を維持しつつ、各スポーク部の各湾曲梁部の幅を細くすることができ、ハブの軽量化を実現できる。
According to the present invention, the two curved beam portions that are curved in the circumferential direction and that constitute each spoke portion act like springs, and when a load is applied in the circumferential direction, the straight beams as in the conventional example are formed. Unlike the portion, by elastically deforming, it is possible to elastically absorb the shear force acting on the hub during braking. As a result, it is possible to reduce the width of each curved beam portion of each spoke portion while maintaining sufficient strength to withstand shearing force during braking, thereby realizing weight reduction of the hub.

　また、本発明においては、前記湾曲梁部の幅は、前記スポーク部の結合部側の先端部の幅の２０％以上５０％以下であることが好ましい。前記湾曲梁部の幅が、前記スポーク部の結合部側の先端部の幅の５０％より大きいと、従来のハブよりも重くなるため、ハブの軽量化を図ることが難しい。一方、前記湾曲梁部の幅が、前記スポーク部の結合部側の先端部の幅の２０％より小さいと、ハブのマシニング加工時に発生する熱によって、各湾曲梁部に反りが生じてしまう。
Further, in the present invention, it is preferable that the width of the curved beam portion is 20% or more and 50% or less of the width of the tip portion of the spoke portion on the joint portion side. If the width of the curved beam portion is larger than 50% of the width of the tip portion of the spoke portion on the connecting portion side, the weight of the hub becomes heavier than that of a conventional hub, making it difficult to reduce the weight of the hub. On the other hand, if the width of the curved beam portion is less than 20% of the width of the tip portion of the spoke portion on the connecting portion side, the curved beam portions will warp due to heat generated during machining of the hub.

　また、本発明においては、前記スポーク部の周方向一方側の湾曲梁部を第１湾曲梁部、周方向他方側の湾曲梁部を第２湾曲梁部とし、第１湾曲梁部が周方向一方側に隣接するスポーク部の第２湾曲梁部と交差して、第１湾曲梁部の取付部側の先端部が、この隣接するスポーク部と周方向一方側で更に隣接するスポーク部の第２湾曲梁部の取付部側の先端部と接合する接合部を有することが好ましい。これによれば、上記結合部と上記取付部との間で周方向に等間隔で配列されるスポーク部同士がトラス構造となることで、ハブにかかる荷重は、すべて各湾曲梁部に分力される圧縮力と引張力のみになり、ハブに大きな荷重が作用しても、ハブが変形するのを防ぐことができる。
Further, in the present invention, the curved beam portion on one side in the circumferential direction of the spoke portion is the first curved beam portion, the curved beam portion on the other side in the circumferential direction is the second curved beam portion, and the first curved beam portion extends in the circumferential direction. Intersecting with the second curved beam portion of the spoke portion adjacent on one side, the tip portion of the first curved beam portion on the mounting portion side is the first curved beam portion of the spoke portion that is further adjacent to the adjacent spoke portion on the one side in the circumferential direction. 2 It is preferable to have a joint portion that joins with the tip portion of the mounting portion side of the curved beam portion. According to this structure, the spokes arranged at equal intervals in the circumferential direction between the connecting portion and the mounting portion form a truss structure, so that all the load applied to the hub is distributed to each curved beam portion. Therefore, even if a large load acts on the hub, deformation of the hub can be prevented.

　また、本発明においては、前記取付部の外周から径方向外方に向かって突出して、前記接合部と連結する連結突部を有することが好ましい。これによれば、連結突部を設けずに、前記接合部を前記取付部に直接連結する場合に比べて、更にハブの軽量化を図ることができる。
Further, in the present invention, it is preferable to have a connecting protrusion that protrudes radially outward from the outer circumference of the mounting portion and connects with the joint portion. According to this, the weight of the hub can be further reduced as compared with the case where the joint portion is directly connected to the mounting portion without providing the connecting protrusion.

　また、本発明においては、前記連結突部は、前記ハブの中心と前記結合部とを結ぶ線上に設けられ、この線に対して、前記結合部、前記スポーク部の２本の湾曲梁部及び前記連結突部の夫々の形状が対称であることが好ましい。これによれば、前記結合部からハブにかかる荷重は、前記スポーク部の各湾曲梁部及び前記連結突部に均等に分力され、各湾曲梁部及び連結突部に同等の荷重が作用することで、ハブ全体の強度を向上させることができ、ブレーキディスクの制動性能や耐久性が向上する。
Further, in the present invention, the connecting protrusion is provided on a line connecting the center of the hub and the connecting portion, and the connecting portion, the two curved beam portions of the spoke portion and It is preferable that the shape of each of the connecting protrusions is symmetrical. According to this, the load applied from the connecting portion to the hub is divided equally between the curved beam portions and the connecting protrusions of the spoke portions, and the same load acts on the curved beam portions and the connecting protrusions. As a result, the strength of the entire hub can be improved, and the braking performance and durability of the brake disc can be improved.

　また、ホイールと、ホイールに装着したフローティング型ブレーキディスクとを備える本発明の鞍乗り型車両用の車輪は、フローティング型ブレーキディスクとして、上述した本発明のフローティング型ブレーキディスクが用いられる。
Further, the wheel of the saddle-riding type vehicle having the wheel and the floating type brake disc mounted on the wheel of the present invention uses the floating type brake disc of the present invention as the floating type brake disc.

本発明の第１実施形態のフローティング型ブレーキディスクが装着された鞍乗り型車両の前輪の側面図。1 is a side view of a front wheel of a saddle-ride type vehicle equipped with a floating type brake disc according to a first embodiment of the present invention; FIG. 本発明の第１実施形態のフローティング型ブレーキディスクの軸方向一方から見た側面図。1 is a side view of a floating type brake disc according to a first embodiment of the present invention, viewed from one axial direction; FIG. 本発明の第１実施形態のフローティング型ブレーキディスクのロータとハブとの結合部の分解斜視図。FIG. 2 is an exploded perspective view of the coupling portion between the rotor and hub of the floating brake disc according to the first embodiment of the present invention; 本発明の第２実施形態のフローティング型ブレーキディスクの軸方向一方から見た側面図。FIG. 11 is a side view of a floating type brake disc according to a second embodiment of the present invention, viewed from one axial direction; 本発明の第３実施形態のフローティング型ブレーキディスクの軸方向一方から見た側面図。FIG. 11 is a side view of a floating type brake disc according to a third embodiment of the present invention, viewed from one axial direction; 本発明の第４実施形態のフローティング型ブレーキディスクの軸方向一方から見た側面図。FIG. 11 is a side view of a floating type brake disc according to a fourth embodiment of the present invention, viewed from one axial direction; 本発明の第５実施形態のフローティング型ブレーキディスクの軸方向一方から見た側面図。FIG. 11 is a side view of a floating type brake disc according to a fifth embodiment of the present invention, viewed from one axial direction;

　図１を参照して、ＦＷは、自動二輪車等の鞍乗り型車両の前輪である。この前輪ＦＷは、フロントフォークＦｆに懸架した車軸Ｆｓに軸受（図示せず）を介して回転自在に支持されるホイールＷｅと、ホイールＷｅの外周部に装着されるタイヤＴｒとを有する。図１中、Ｃｐは、ブレーキ装置の構成要素としてのキャリパである。そして、ホイールＷｅの軸方向片側の所定位置には、本発明の第１実施形態のブレーキディスクＢＤ１が固定用ボルトＶｔにより取り付けられている。尚、ホイールＷｅ、ブレーキ装置及び固定用ボルトＶｔとしては、公知のものが利用できるため、これ以上の説明は省略する。
Referring to FIG. 1, FW is the front wheel of a saddle type vehicle such as a motorcycle. The front wheel FW has a wheel We rotatably supported via a bearing (not shown) on an axle Fs suspended from a front fork Ff, and a tire Tr mounted on the outer peripheral portion of the wheel We. In FIG. 1, Cp is a caliper as a component of the braking device. At a predetermined position on one side of the wheel We in the axial direction, the brake disc BD1 of the first embodiment of the present invention is attached with fixing bolts Vt. As the wheel We, the brake device, and the fixing bolt Vt, well-known ones can be used, so further explanation will be omitted.

　図２及び図３も参照して、ブレーキディスクＢＤ１は、環状のロータ１と、ロータ１の内側に所定の隙間を存して、同心に配置されるハブ２とを備える。ロータ１は、例えばステンレス鋼板製である。ブレーキ操作時、ロータ１は、キャリパＣｐのブレーキパットで挟持され、ハブ２を介して車軸Ｆｓに制動力を伝達する。ロータ１には、軽量化等のため、板厚方向に貫通する円形の貫通孔１１が複数開設されている。また、ロータ１の内周縁部には、径方向内方にのびるほぼ矩形の舌片状の突片１２が周方向に所定間隔で複数形成されている。
2 and 3, the brake disc BD 1 comprises an annular rotor 1 and a hub 2 arranged concentrically inside the rotor 1 with a predetermined gap. The rotor 1 is made of stainless steel plate, for example. During braking, the rotor 1 is clamped by the brake pads of the caliper Cp and transmits braking force to the axle Fs via the hub 2 . The rotor 1 is provided with a plurality of circular through-holes 11 penetrating in the plate thickness direction for weight reduction and the like. In addition, a plurality of substantially rectangular tongue-like protruding pieces 12 extending radially inward are formed on the inner peripheral edge portion of the rotor 1 at predetermined intervals in the circumferential direction.

　ハブ２は、例えばアルミニウム合金製である。ハブ２の外周には、各突片１２に夫々対応させて、径方向内方に凹入して、各突片１２を受け入れる受入凹部２１が形成される。また、突片１２が受入凹部２１から軸方向に抜け出ないようにする抜け止め手段３を備える。これら突片１２、受入凹部２１及び抜け止め手段３により、ロータ１とハブ２とを結合する結合部４が構成される。また、ハブ２の中心には、軸孔２２ａが形成される環状の取付部２２が設けられている。そして、軸孔２２ａの周囲に形成した取付孔２２ｂに、固定用ボルトＶｔを挿通して、取付部２２をホイールＷｅに締結する。
The hub 2 is made of aluminum alloy, for example. Receiving recesses 21 are formed on the outer periphery of the hub 2 so as to correspond to the projecting pieces 12 and are recessed radially inward to receive the projecting pieces 12 . In addition, a slip-off prevention means 3 is provided to prevent the projecting piece 12 from slipping out of the receiving recess 21 in the axial direction. A connecting portion 4 for connecting the rotor 1 and the hub 2 is constituted by the projecting piece 12, the receiving recess 21, and the retaining means 3. As shown in FIG. Further, at the center of the hub 2, an annular mounting portion 22 having a shaft hole 22a is provided. A fixing bolt Vt is inserted through a mounting hole 22b formed around the shaft hole 22a to fasten the mounting portion 22 to the wheel We.

　受入凹部２１は、突片１２の径方向に沿う両側面に略平行な受入面を有し、両受入面間の幅は、突片１２の周方向の幅よりわずかに大きく形成されている。また、受入凹部２１は、軸方向一方のみが開放されるように設けられており、軸方向他方はハブ２と一体の壁２１１で閉塞されている。更に、受入凹部２１の軸方向一方の径方向内方の端部２１ａは、受入凹部２１の他の部分よりも大きな略円形状に形成され、この端部２１ａの内壁面には、その周方向に沿って溝２１２が形成されている。
The receiving recess 21 has receiving surfaces substantially parallel to both radial side surfaces of the projecting piece 12 , and the width between the receiving surfaces is slightly larger than the circumferential width of the projecting piece 12 . Further, the receiving recess 21 is provided so that only one axial direction is open, and the other axial direction is closed by a wall 211 integral with the hub 2 . Further, one radially inner end portion 21a of the receiving recess 21 in the axial direction is formed in a substantially circular shape larger than the other portion of the receiving recess 21, and the inner wall surface of this end portion 21a has a A groove 212 is formed along the .

　抜け止め手段３は、突片１２の軸方向一方の面に対向するように設けられ、例えばアルミニウム合金製の円板状の押え板３１と、溝２１２に係合して押え板３１を軸方向一方に抜け止めする止め輪３２とで構成される。止め輪３２としては、公知のＣ型スナップリングを用いることができるため、詳細な説明は省略する。また、突片１２と受入凹部２１との間の隙間には、受入凹部２１の内壁面に沿うコの字形状の板部材５が挿入され、突片１２と押え板３１との間には、付勢手段としての皿バネ６が介設されている。
The retaining means 3 is provided so as to face one of the surfaces in the axial direction of the protruding piece 12, and is, for example, a disk-shaped holding plate 31 made of an aluminum alloy, and engages with the groove 212 to hold the holding plate 31 in the axial direction. It is composed of a retaining ring 32 that prevents it from slipping out on one side. Since a known C-shaped snap ring can be used as the snap ring 32, detailed description thereof will be omitted. In addition, a U-shaped plate member 5 along the inner wall surface of the receiving recess 21 is inserted into the gap between the projecting piece 12 and the receiving recess 21, and between the projecting piece 12 and the pressing plate 31, A disc spring 6 is interposed as a biasing means.

　上記の如く、受入凹部２１の軸方向他方側がハブ２に一体の壁２１１で閉塞されていれば、即ち、受入凹部２１がハブ２の板厚方向に貫通していなければ、ハブ２の強度（剛性）を高めることができる。尚、ロータ１とハブ２との結合方式は、上記のものに限定されず、他の公知のものを用いることができる。例えば、ハブ２に、軸方向一方の面から他方の面まで貫通させた受入凹部を形成するともに、筒状の胴部の一端にフランジ部が形成された連結ピンを用いて、連結ピンを突片に形成されたピン孔に挿通して、連結ピンの他端をかしめることで、ロータ１とハブ２とを連結することもできる。
As described above, if the other side of the receiving recess 21 in the axial direction is closed by the wall 211 integral with the hub 2, that is, if the receiving recess 21 does not penetrate the hub 2 in the plate thickness direction, the strength of the hub 2 ( stiffness) can be increased. Incidentally, the method of connecting the rotor 1 and the hub 2 is not limited to the one described above, and other known methods can be used. For example, the hub 2 is formed with a receiving recess penetrating from one surface to the other in the axial direction, and a connecting pin having a flange portion formed at one end of a cylindrical body portion is used to protrude the connecting pin. The rotor 1 and the hub 2 can also be connected by inserting the connecting pin through a pin hole formed in the piece and crimping the other end of the connecting pin.

　また、ハブ２の各結合部４と取付部２２との間には、周方向に等間隔で配置されるスポーク部２３が複数（本実施形態では１２個）形成されている。スポーク部２３は、各結合部４から取付部２２に向かって（即ち、径方向内方に向かって）、周方向間隔が次第に広がるように分岐してのびるとともに、周方向に所定の曲率（Ｒ１５０）で湾曲した２本の湾曲梁部２３１，２３１を有する（以後、各スポーク部２３の周方向一方側の湾曲梁部２３１を第１湾曲梁部２３１１、周方向他方側の湾曲梁部２３１を第２湾曲梁部２３１２とも呼ぶ）。また、本実施形態では、湾曲梁部２３１の幅Ｗ１は３ｍｍ、スポーク部２３の結合部４側の先端部２３ａの幅Ｗ２は１３ｍｍである。尚、本実施形態では、各湾曲梁部２３１，２３１の幅Ｗ１は、径方向外方側から径方向内方側まで均一であるが、これに限定されず、各湾曲梁部２３１，２３１の幅Ｗ１は、径方向外方側から径方向内方側まで均一でなくてもよい。
A plurality of (12 in the present embodiment) spoke portions 23 are formed between the connecting portions 4 and the mounting portions 22 of the hub 2 at equal intervals in the circumferential direction. The spokes 23 branch from each connecting portion 4 toward the mounting portion 22 (that is, radially inwardly) so as to gradually widen the interval in the circumferential direction, and have a predetermined curvature (R150 ) (hereinafter, the curved beam portion 231 on one side in the circumferential direction of each spoke portion 23 will be referred to as a first curved beam portion 231 1 , and the curved beam portion 231 on the other side in the circumferential direction will be referred to as a first curved beam portion 231 1 . is also called the second curved beam portion 2312 ). In this embodiment, the width W1 of the curved beam portion 231 is 3 mm, and the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 13 mm. In this embodiment, the width W1 of each curved beam portion 231, 231 is uniform from the radially outer side to the radially inner side, but is not limited to this. The width W1 may not be uniform from the radially outer side to the radially inner side.

　ここで、各第１湾曲梁部２３１１は、周方向一方側に隣接するスポーク部２３の第２湾曲梁部２３１２と交差している。更に、第１湾曲梁部２３１１の取付部２２側の各先端部は、この隣接するスポーク部２３と周方向一方側で更に隣接するスポーク部２３の第２湾曲梁部２３１２の取付部側２３の各先端部と接合し、各接合部２３２を形成する。
Here, each first curved beam portion 231-1 intersects the second curved beam portion 231-2 of the spoke portion 23 adjacent to one side in the circumferential direction. Further, each tip portion of the first curved beam portion 231-1 on the mounting portion 22 side is located on the mounting portion side of the second curved beam portion 231-2 of the spoke portion 23 further adjacent to the adjacent spoke portion 23 on one side in the circumferential direction. 23 to form each joint 232 .

　また、ハブ２の中心Ｏと各結合部４とを結ぶ線Ｌ上には、取付部２３の外周から径方向外方に向かって突出して、各接合部２３２と連結される連結突部２２１が、周方向に等間隔で形成されている。本実施形態では、各結合部４、各スポーク部２３の２本の湾曲梁部２３１，２３１及び連結突部２２１の夫々の形状は、線Ｌに対して対称である。
Further, on the line L connecting the center O of the hub 2 and each connecting portion 4, a connecting projection 221 projecting radially outward from the outer periphery of the mounting portion 23 and connected to each connecting portion 232 is provided. , are formed at regular intervals in the circumferential direction. In the present embodiment, the shapes of each connecting portion 4, the two curved beam portions 231, 231 of each spoke portion 23, and the connecting protrusion 221 are symmetrical with respect to the line L. As shown in FIG.
本実施形態によれば、各スポーク部２３を構成する周方向に湾曲した２本の湾曲梁部２３１，２３１が、バネの様に作用して、周方向荷重を加えたときに、従来例の如き直線状の梁部と異なり、弾性的に変形することで、制動時に衝撃的に作用するハブ２に作用する剪断力を吸収することができる。その結果、制動時の剪断力に耐え得る十分な強度を維持しつつ、各スポーク部２３の各湾曲梁部２３１，２３１の幅Ｗ１を細くすることができ、ハブ２の軽量化を実現できる。この場合、各スポーク部２３の各湾曲梁部２３１，２３１の曲率は、スポーク部２３の個数等に応じて、Ｒ３５～Ｒ１５０の範囲とすることができる（後述する第２実施形態乃至第５実施形態も参照）。
According to the present embodiment, the two curved beam portions 231, 231, which are curved in the circumferential direction and constitute each spoke portion 23, act like springs, and when a load is applied in the circumferential direction, the Unlike such a straight beam portion, the elastic deformation can absorb the shearing force acting on the hub 2 which acts as an impact during braking. As a result, the width W1 of each curved beam portion 231, 231 of each spoke portion 23 can be reduced while maintaining sufficient strength to withstand shearing force during braking, and the weight of the hub 2 can be reduced. In this case, the curvature of each curved beam portion 231, 231 of each spoke portion 23 can be set within the range of R35 to R150 depending on the number of spoke portions 23 (second embodiment to fifth embodiment described later). See also morphology).

　また、湾曲梁部２３１の幅Ｗ１は、スポーク部２３の結合部４側の先端部２３ａの幅Ｗ２の２０％以上５０％以下であることが好ましい。湾曲梁部２３１の幅Ｗ１が、スポーク部２３の結合部４側の先端部２３ａの幅Ｗ２の５０％より大きいと、従来のハブ２よりも重くなり、ハブ２の軽量化を図ることが難しい。一方、湾曲梁部２３１の幅Ｗ１が、スポーク部２３の結合部４側の先端部２３ａの幅Ｗ２の２０％より小さいと、ハブ２のマシニング加工時に発生する熱によって、湾曲梁部２３１に反りが生じてしまう。
Further, the width W1 of the curved beam portion 231 is preferably 20% or more and 50% or less of the width W2 of the tip portion 23a of the spoke portion 23 on the coupling portion 4 side. If the width W1 of the curved beam portion 231 is larger than 50% of the width W2 of the tip portion 23a of the spoke portion 23 on the coupling portion 4 side, the hub 2 becomes heavier than the conventional hub 2, and it is difficult to reduce the weight of the hub 2. . On the other hand, if the width W1 of the curved beam portion 231 is smaller than 20% of the width W2 of the tip portion 23a of the spoke portion 23 on the coupling portion 4 side, the curved beam portion 231 will warp due to heat generated during machining of the hub 2. occurs.

　また、スポーク部２３の第１湾曲梁部２３１１が周方向一方側に隣接するスポーク部２３の第２湾曲梁部２３１２と交差して、第１湾曲梁部２３１１の取付部２２側の先端部が、この隣接するスポーク部２３と周方向一方側で更に隣接するスポーク部２３の第２湾曲梁部２３１２の取付部２２側の先端部と接合する接合部２３２を有することが好ましい。これによれば、結合部４と取付部２２との間で周方向に等間隔で配列されるスポーク部２３同士がトラス構造となることで、ハブ２にかかる荷重は、すべて各湾曲梁部２３１，２３１に分力される径圧縮力と引張力のみになり、ハブ２に大きな荷重が作用しても、ハブ２が変形するのを防ぐことができる。
In addition, the first curved beam portion 231-1 of the spoke portion 23 intersects the second curved beam portion 231-2 of the spoke portion 23 adjacent to the one side in the circumferential direction, and the first curved beam portion 231-1 on the mounting portion 22 side It is preferable that the tip portion has a joint portion 232 that joins the tip portion of the second curved beam portion 2312 of the spoke portion 23 that is further adjacent to the adjacent spoke portion 23 on one side in the circumferential direction on the mounting portion 22 side. According to this configuration, the spoke portions 23 arranged at equal intervals in the circumferential direction between the connecting portion 4 and the mounting portion 22 form a truss structure, so that all the load applied to the hub 2 is transferred to each curved beam portion 231. , 231, and even if a large load acts on the hub 2, the deformation of the hub 2 can be prevented.

　また、取付部２２の外周から径方向外方に向かって突出して、接合部２３２と連結する連結突部２２１を有することが好ましい。これによれば、連結突部２２１を設けずに、接合部２３２を取付部２２に直接連結する場合に比べて、更にハブ２の軽量化を図ることができる。
Moreover, it is preferable to have a connecting protrusion 221 that protrudes radially outward from the outer periphery of the mounting portion 22 and connects with the joint portion 232 . According to this, the weight of the hub 2 can be further reduced as compared with the case where the joint portion 232 is directly connected to the mounting portion 22 without providing the connecting protrusion 221 .

　更に、連結突部２２１は、ハブ２の中心Ｏと結合部４とを結ぶ線Ｌ上に設けられ、この線Ｌに対して、結合部４、スポーク部２３の各湾曲梁部２３１，２３１及び連結突部２２１の夫々の形状が対称であることが好ましい。これによれば、結合部４からハブ２にかかる荷重は、スポーク部２３の各湾曲梁部２３１，２３１及び連結突部２２１に均等に分力され、各湾曲梁部２３１，２３１及び連結突部２２１に同等の荷重が作用することで、ハブ２全体の強度を向上させることができ、ブレーキディスクＢＤ１の制動性能や耐久性が向上する。
Furthermore, the connecting protrusion 221 is provided on a line L connecting the center O of the hub 2 and the coupling portion 4. It is preferable that each shape of the connecting protrusions 221 is symmetrical. According to this, the load applied from the coupling portion 4 to the hub 2 is evenly distributed to the curved beam portions 231, 231 and the connecting protrusion 221 of the spoke portion 23, and the curved beam portions 231, 231 and the connecting protrusion By applying an equivalent load to 221, the strength of the hub 2 as a whole can be improved, and the braking performance and durability of the brake disc BD1 are improved.
次に、図４乃至図７に示す第２実施形態乃至第５実施形態の自動二輪車用フローティング型ブレーキディスクＢＤ２～ＢＤ５ついて説明する。なお、上記第１実施形態と同様の部材、部位には上記と同一の符号を付している。
Next, floating type brake discs BD 2 to BD 5 for motorcycles according to second to fifth embodiments shown in FIGS. 4 to 7 will be described. The same members and portions as those of the first embodiment are denoted by the same reference numerals.

　図４に示す第２実施形態は、上記第１実施形態と同様、１２個のスポーク部２３を備える。各スポーク部２３は、各結合部４から取付部２２に向かって、周方向間隔が次第に広がるように分岐してのびるとともに、周方向に所定の曲率（Ｒ７０）で湾曲する各湾曲梁部２３１，２３１を有する。また、本実施形態は、湾曲梁部２３１の幅Ｗ１が３ｍｍ、スポーク部２３の結合部４側の先端部２３ａの幅Ｗ２が１３ｍｍである。尚、本実施形態では、各湾曲梁部２３１，２３１の幅Ｗ１及び各連結突部２２１の幅は、径方向外方側から径方向内方側まで均一であるが、これに限定されず、各湾曲梁部２３１，２３１の幅Ｗ１や各連結突部２２１の幅は、径方向外方側から径方向内方側まで均一でなくてもよい。
The second embodiment shown in FIG. 4 has 12 spoke portions 23 as in the first embodiment. Each spoke portion 23 branches from each connecting portion 4 toward the mounting portion 22 so that the interval in the circumferential direction gradually widens, and each curved beam portion 231 curves in the circumferential direction with a predetermined curvature (R70). 231. Further, in this embodiment, the width W1 of the curved beam portion 231 is 3 mm, and the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 13 mm. In this embodiment, the width W1 of each curved beam portion 231, 231 and the width of each connecting protrusion 221 are uniform from the radially outer side to the radially inner side. The width W1 of each curved beam portion 231, 231 and the width of each connecting protrusion 221 may not be uniform from the radially outer side to the radially inner side.

　また、図５に示す第３実施形態は、４個のスポーク部２３を備える。各スポーク部２３は、各結合部４から取付部２２に向かって、周方向間隔が次第に広がるように分岐してのびるとともに、周方向に所定の曲率（Ｒ１００）で湾曲する各湾曲梁部２３１，２３１を有する。本実施形態は、湾曲梁部２３１の幅Ｗ１が４．５ｍｍ、スポーク部２３の結合部４側の先端部２３ａの幅Ｗ２が１３ｍｍである。また、本実施形態は、各湾曲梁部２３１，２３１の取付部２２側の各先端部が夫々接合する接合部及びこれに連結する連結突部を設けず、各湾曲梁部２３１，２３１の各先端部は取付部２２に接合される。
The third embodiment shown in FIG. 5 also has four spokes 23 . Each spoke portion 23 branches from each connecting portion 4 toward the mounting portion 22 so as to gradually widen the interval in the circumferential direction. 231. In this embodiment, the width W1 of the curved beam portion 231 is 4.5 mm, and the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 13 mm. In addition, in the present embodiment, the joints to which the ends of the curved beams 231 and 231 on the side of the mounting portion 22 are joined and the connecting protrusions connected thereto are not provided. The tip portion is joined to the mounting portion 22 .

　また、図６に示す第４実施形態では、３個のスポーク部２３を備える。各スポーク部２３は、各結合部４から取付部２２に向かって、周方向間隔が次第に広がるように分岐してのびるとともに、周方向に所定の曲率（Ｒ９０）で湾曲する各湾曲梁部２３１，２３１を有する。本実施形態は、湾曲梁部２３１の幅Ｗ１が３．５ｍｍ、スポーク部２３の結合部４側の先端部２３ａの幅Ｗ２は１２ｍｍである。また、本実施形態も、上記第３実施形態と同様、各湾曲梁部２３１，２３１の取付部２２側の各先端部が夫々接合する接合部及びこれに連結する連結突部を設けず、各湾曲梁部２３１，２３１の各先端部は取付部２２に接合される。
Further, in the fourth embodiment shown in FIG. 6, three spoke portions 23 are provided. Each spoke portion 23 branches from each connecting portion 4 toward the mounting portion 22 so as to gradually widen the interval in the circumferential direction. 231. In this embodiment, the width W1 of the curved beam portion 231 is 3.5 mm, and the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 12 mm. In addition, in the present embodiment, as in the third embodiment, the joints to which the ends of the curved beams 231 and 231 on the side of the mounting portion 22 are joined and the connecting projections to be connected to the joints are not provided. Each tip of the curved beam portions 231 , 231 is joined to the mounting portion 22 .

　また、図７に示す第５実施形態では、１０個のスポーク部２３を備える。各スポーク部２３は、各結合部４から取付部２２に向かって、周方向間隔が次第に広がるように分岐してのびるとともに、周方向に所定の曲率（Ｒ３５）で湾曲する各湾曲梁部２３１，２３１を有する。本実施形態は、湾曲梁部２３１の幅Ｗ１は３ｍｍ、スポーク部２３の結合部４側の先端部２３ａの幅Ｗ２は１２ｍｍである。本実施形態も、上記第３及び第４実施形態と同様、各湾曲梁部２３１，２３１の取付部２２側の各先端部が夫々接合する接合部及びこれに連結する連結突部を設けず、各湾曲梁部２３１，２３１の各先端部は取付部２２に接合される。また、本実施形態の取付部２２には、取付孔２２ｂと取付孔２２ｂとの間に、孔径の異なる孔２２ｃが形成されている。
Further, in the fifth embodiment shown in FIG. 7, ten spoke portions 23 are provided. Each spoke portion 23 branches from each connecting portion 4 toward the mounting portion 22 so as to gradually widen the interval in the circumferential direction. 231. In this embodiment, the width W1 of the curved beam portion 231 is 3 mm, and the width W2 of the tip portion 23a of the spoke portion 23 on the joint portion 4 side is 12 mm. As in the third and fourth embodiments, this embodiment also does not provide joints where the ends of the curved beams 231 and 231 on the side of the mounting portion 22 are joined and connecting projections connected thereto. Each tip of each curved beam portion 231 , 231 is joined to the mounting portion 22 . Further, in the mounting portion 22 of the present embodiment, a hole 22c having a different hole diameter is formed between the mounting holes 22b and 22b.

　以上、本発明の実施形態について説明したが、本発明は上記のものに限定されるものではない。例えば上記実施形態では、ハブ２の中心Ｏと各結合部４とを結ぶ線Ｌに対して、スポーク部２３の各湾曲梁部２３１，２３１の形状を対称としたが、各湾曲梁部２３１，２３１の形状を非対称とすることもできる。また、上述したように、各湾曲梁部２３１，２３１の曲率は、スポーク部２３の個数等に応じて、Ｒ３５～Ｒ１５０の範囲とすることができる。この場合、ロータ１の径の変更に伴って、ロータ１の摺動幅を確保するため、ハブ２の形状を小さくする必要が生じても、スポーク部２３の個数、各湾曲梁部２３１，２３１の幅Ｗ１や曲率を変更することで、環状の取付部２２の径を変えることなく、ハブ２を設計することができる。　
Although the embodiments of the present invention have been described above, the present invention is not limited to the above. For example, in the above embodiment, the curved beam portions 231, 231 of the spoke portion 23 are symmetrical with respect to the line L connecting the center O of the hub 2 and the coupling portions 4. The shape of 231 can also be asymmetrical. Further, as described above, the curvature of each of the curved beam portions 231, 231 can be in the range of R35 to R150 depending on the number of spoke portions 23 and the like. In this case, even if it becomes necessary to reduce the shape of the hub 2 in order to secure the sliding width of the rotor 1 as the diameter of the rotor 1 is changed, the number of the spoke portions 23 and the curved beam portions 231, 231 The hub 2 can be designed without changing the diameter of the annular mounting portion 22 by changing the width W1 and the curvature of the ring.

　また、図１では、鞍乗り型車両用の前輪ＦＷのホイールＷｅに、第１実施形態のブレーキディスクＢＤ１を装着したものを例に説明したが、上記第２乃至第５実施形態のブレーキディスクＢＤ２～ＢＤ５を装着することもできる。尚、図１に示す車輪は、鞍乗り型車両用の前輪ＦＷであるが、鞍乗り型車両用の後輪のホイールにも、上記第１乃至第５実施形態のブレーキディスクＢＤ１～ＢＤ５を装着することができる。
Further, in FIG. 1, an example in which the brake disc BD 1 of the first embodiment is mounted on the wheel We of the front wheel FW for a saddle type vehicle has been described, but the brake discs of the second to fifth embodiments are described. BD 2 to BD 5 can also be attached. The wheels shown in FIG . 1 are front wheels FW for a saddle-ride type vehicle . can be worn.

　ＢＤ１～ＢＤ５…フローティング型ブレーキディスク、ＦＷ…自動二輪車の前輪（鞍乗り型車両用の車輪）、Ｌ…ハブの中心と結合部とを結ぶ線、Ｒ…曲率、Ｗ１…湾曲梁部の幅、Ｗ２…スポーク部の結合部側の先端部の幅、Ｗｅ…ホイール、１…ロータ、１２…突片（結合部）、２…ハブ、２１…受入凹部（結合部）、２２…取付部、２２１…連結突部、２３…スポーク部、２３１…湾曲梁部、２３１１…第１湾曲梁部、２３１２…第２湾曲梁部、２３２…接合部、３…抜け止め手段（結合部）、４…結合部。
BD 1 to BD 5 : floating type brake disc, FW: front wheel of motorcycle (wheel for saddle type vehicle), L: line connecting center of hub and connecting portion, R: curvature, W1: curve of curved beam Width, W2... Width of the tip portion of the spoke portion on the joint side, We... Wheel, 1... Rotor, 12... Protruding piece (joint part), 2... Hub, 21... Receiving recess (joint part), 22... Mounting part , 221... Connecting protrusion 23... Spoke part 231... Curved beam part 231 1 ... First curved beam part 231 2 ... Second curved beam part 232... Joint part 3... Retaining means (coupling part) , 4 . . .

Claims (6)


  1. 　環状のロータと、このロータの内側に所定の隙間を存して、同心に配置されるハブとを備えるフローティング型ブレーキディスクであって、

    　ロータとハブとが、周方向に等間隔で設けられた複数の結合部で結合され、ハブの中心に、ホイールに締結される環状の取付部を備えるものにおいて、

    　ハブは、各結合部から取付部に向けて周方向間隔が次第に広がるように分岐してのび、且つ、所定の曲率で周方向に湾曲した２本の湾曲梁部で構成されるスポーク部を有し、このスポーク部が周方向に等間隔で配列されることを特徴とするフローティング型ブレーキディスク。
    A floating type brake disc comprising an annular rotor and a hub concentrically arranged with a predetermined gap inside the rotor,

    The rotor and the hub are joined by a plurality of joints provided at equal intervals in the circumferential direction, and an annular mounting portion that is fastened to the wheel is provided at the center of the hub,

    The hub has a spoke portion extending from each connecting portion toward the mounting portion so as to gradually widen the interval in the circumferential direction, and composed of two curved beam portions that are curved in the circumferential direction with a predetermined curvature. and the spoke portions are arranged at regular intervals in the circumferential direction.

  2. 　前記湾曲梁部の幅は、前記スポーク部の結合部側の先端部の幅の２０％以上５０％以下であることを特徴とする請求項１記載のフローティング型ブレーキディスク。
    2. The floating type brake disc according to claim 1, wherein the width of the curved beam portion is 20% or more and 50% or less of the width of the tip portion of the spoke portion on the connecting portion side.

  3. 　前記スポーク部の周方向一方側の湾曲梁部を第１湾曲梁部、周方向他方側の湾曲梁部を第２湾曲梁部とし、

    　第１湾曲梁部が周方向一方側に隣接するスポーク部の第２湾曲梁部と交差して、第１湾曲梁部の取付部側の先端部が、この隣接するスポーク部と周方向一方側で更に隣接するスポーク部の第２湾曲梁部の取付部側の先端部と接合する接合部を有することを特徴とする請求項１又は２記載のフローティング型ブレーキディスク。
    The curved beam portion on one side in the circumferential direction of the spoke portion is a first curved beam portion, and the curved beam portion on the other side in the circumferential direction is a second curved beam portion,

    The first curved beam portion intersects the second curved beam portion of the spoke portion adjacent to the one side in the circumferential direction, and the tip portion of the first curved beam portion on the mounting portion side is aligned with the adjacent spoke portion on the one side in the circumferential direction. 3. The floating type brake disc according to claim 1, further comprising a joint portion that joins with the tip portion of the second curved beam portion of the adjacent spoke portion on the mounting portion side.

  4. 　前記取付部の外周から径方向外方に向かって突出して、前記接合部と連結する連結突部を有することを特徴とする請求項３記載のフローティング型ブレーキディスク。
    4. The floating type brake disc according to claim 3, further comprising a connecting protrusion projecting radially outward from an outer periphery of said mounting portion and connecting with said joint portion.

  5. 　前記連結突部は、前記ハブの中心と前記結合部とを結ぶ線上に設けられ、この線に対して、前記結合部、前記スポーク部の２本の湾曲梁部及び前記連結突部の夫々の形状が対称であることを特徴とする請求項４記載のフローティング型ブレーキディスク。
    The connecting projection is provided on a line connecting the center of the hub and the connecting portion, and the connecting portion, the two curved beams of the spoke portion, and the connecting projection are arranged with respect to this line. 5. The floating brake disc of claim 4, wherein the shape is symmetrical.

  6. 　ホイールと、ホイールに装着したフローティング型ブレーキディスクとを備える鞍乗り型車両用の車輪であって、

    　フローティング型ブレーキディスクとして、請求項１～５の何れか１項記載のフローティング型ブレーキディスクを用いることを特徴とする鞍乗り型車両用の車輪。
    A wheel for a straddle-type vehicle comprising a wheel and a floating brake disc mounted on the wheel,

    A wheel for a straddle-type vehicle, wherein the floating type brake disc according to any one of claims 1 to 5 is used as the floating type brake disc.
PCT/JP2022/035659 2021-11-11 2022-09-26 Floating-type brake disc, and wheel for straddle-type vehicle WO2023084934A1 (en)

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JP2021-184187 2021-11-11

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130092485A1 (en) * 2011-10-13 2013-04-18 Wayne-Ian Moore Brake disk assembly
JP2015169264A (en) * 2014-03-06 2015-09-28 株式会社ユタカ技研 brake disk
JP2018144796A (en) * 2017-02-09 2018-09-20 カンパニョーロ・ソシエタ・ア・レスポンサビリタ・リミタータＣａｍｐａｇｎｏｌｏ Ｓｏｃｉｅｔａ Ａ Ｒｅｓｐｏｎｓａｂｉｌｉｔａ Ｌｉｍｉｔａｔａ Brake disc for bicycle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130092485A1 (en) * 2011-10-13 2013-04-18 Wayne-Ian Moore Brake disk assembly
JP2015169264A (en) * 2014-03-06 2015-09-28 株式会社ユタカ技研 brake disk
JP2018144796A (en) * 2017-02-09 2018-09-20 カンパニョーロ・ソシエタ・ア・レスポンサビリタ・リミタータＣａｍｐａｇｎｏｌｏ Ｓｏｃｉｅｔａ Ａ Ｒｅｓｐｏｎｓａｂｉｌｉｔａ Ｌｉｍｉｔａｔａ Brake disc for bicycle

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