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JP3663894B2 - Disc brake disc rotor - Google Patents
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JP3663894B2 - Disc brake disc rotor - Google Patents

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Publication number
JP3663894B2
JP3663894B2 JP06346998A JP6346998A JP3663894B2 JP 3663894 B2 JP3663894 B2 JP 3663894B2 JP 06346998 A JP06346998 A JP 06346998A JP 6346998 A JP6346998 A JP 6346998A JP 3663894 B2 JP3663894 B2 JP 3663894B2
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Prior art keywords
flow path
air flow
brake
circumferential
disc
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JPH11257388A (en
Inventor
修一 中川
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Nissan Motor Co Ltd
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Nissan Motor Co Ltd
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    • 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
    • F16D65/0006—Noise or vibration control
    • 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
    • F16D65/128—Discs; Drums for disc brakes characterised by means for cooling

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、ヘンチレーテッドデイスクブレーキのディスクロータに関する。
【０００２】
【従来の技術】
従来のこの種のディスクロータとしては、例えば特開昭５８−２４６２９号公報に図３に示すものが記載されている。
【０００３】
図３は、このディスクロータ１０１の外周を展開して示したものであり、上下の圧接面１０１ａ，１０１ｂ間に等ピッチＰ1 にリブ１０３，１０３，１０３……が配設され、リブ１０３同士の間に冷却のための空気流路１０５ａ，１０５ｂが形成されている。一方、ロータ厚さ方向の空気流路１０５ａ，１０５ｂの幅Ｗ1 ，Ｗ2 は一律ではなく、広幅の空気流路１０５ｂと狭幅の空気流路１０５ａとがディスクロータ１０１の全周に亘って適宜配設され、周方向における重量分布が不均一になるように構成されている。これにより、ディスクロータ１０１に等分割共振波形が発生するのを抑えてブレーキの鳴き現象の発生を防止している。
【０００４】
【発明が解決しようとする課題】
ところが、周方向の剛性が不均一にされているため、圧接面１０１ａ，１０１ｂの、加工時の変形や制動中の熱変形などが不均一になって、ディスクロータ１０１に周期的なトルク変動が発生し、ウーというような異音が発生する場合がある。
【０００５】
そこで，本発明は、ブレーキの鳴き防止と共に異音の発生を防止することを目的とする。
【０００６】
【課題を解決するための手段】
上記課題を解決するために、請求項１に記載の発明は、ブレーキパッドが圧接される両側のブレーキディスクと、前記両ブレーキディスク間に放射状に周方向等分に配置される複数のリブと、前記各リブ間に形成される空気流路とを備え、前記空気流路として、第１の空気流路及び第２の空気流路を設け、該第２の空気流路は、周方向等分の複数箇所で各々１本のリブをリブ抜きすることにより形成され、前記第２の空気流路の両ブレーキディスク間の厚さ方向の流路幅を第１の空気流路の同流路幅よりも小さく設定したデイスクブレーキのディスクロータであって、前記第２の空気流路の周方向の両側に設けられた各リブの周方向の中心同士の間に配置された第２の周方向範囲と、該第２の周方向範囲と同一の周方向長さを有し、２つの第１の空気流路を含む第１の周方向範囲とにおける、ディスクロータの厚さの中心軸に対する断面２次モーメントがほぼ等しくなるように設定したことを特徴とする。
【０００９】
請求項２に記載の発明は、請求項１記載のデイスクブレーキのディスクロータであって、前記リブの周方向の厚さをａとし、前記第１と第２の空気流路のブレーキディスク外周部における周方向の幅をそれぞれｂ1 ，ｂ2 としたとき、第１と第２の空気流路の両ブレーキディスク間の各流路幅ｈ1 ，ｈ2 の比をｈ2 ／ｈ1 ＝｛２ｂ1 ／（２ｂ1 ＋ａ）｝1/3 に設定することを特徴とする。
【００１０】
【発明の効果】
請求項１に記載の発明によれば、周方向の幅の小さい第１の空気流路の間に、リブ抜きにより同幅が大きく形成される第２の空気流路が配置されることにより、ディスクロータの周方向の重量分布が不均一になるので、ディスクロータに発生する等分割共振波形が抑えられブレーキの鳴きが防止される。
【００１２】
請求項１に記載の発明によれば、ブレーキディスク間の全周に等分配置されたリブを間引くことにより周方向の幅が拡大された第２の空気流路が形成されるので、ディスクロータの鋳型の形成や鋳造が容易になりコストを低減することができる。
【００１３】
請求項１に記載の発明によれば、第１の周方向範囲と、第２の周方向範囲とにおける、ディスクロータの厚さの中心軸に対する断面２次モーメントがほぼ等しくなるように設定しているので、ブレーキディスクの剛性が周方向に均一化される。
【００１４】
請求項２に記載の発明によれば、例えば第１の空気流路のブレーキディスク外周部における周方向幅ｂ1 をリブの厚さａと等しく設定すると、第１と第２の空気流路の周方向所定の同一範囲の各断面２次モーメントを等しくするための各流路幅の比ｈ2 ／ｈ1 は、
ｈ2 ／ｈ1 ＝｛２ｂ1 ／（２ｂ1 ＋ａ）｝1/3
＝（２／３）1/3
＝０．８７４
として求められ、ｈ2 を製造条件から適宜設定するとｈ1 が導かれる。
【００１５】
こうして、リブおよび第１と第２の空気流路の諸元が容易に計算可能となり、請求項１の発明と同等の効果が得られる。
【００１６】
【発明の実施の形態】
本発明の一実施形態を図１、図２により説明する。図１は本実施形態のディスクロータのリブの配置状態を模式的に示し、図２はディスクロータの外周を展開して示す。
【００１７】
図１、図２に示すように、ディスクロータ１の両側のブレーキディスク圧接面１ａ，１ｂ間には放射状に３０本のリブ３が配設されている。これは全周等分に３６本のリブを配設した状態から周方向等分の６箇所で各１本づつ、合計６本のリブ（図１の矢印部）を削除してリブ抜きした状態のものである。
【００１８】
リブ３を削除していない部分のリブ３，３間に第１の空気流路１５が形成され、削除した箇所において第２の空気流路１７が形成されている。こうして、周方向６箇所の各第２の空気流路１７の、ディスクロータ１の外周における周方向の幅ｂ2 は第１の空気流路１５の幅ｂ1 よりも大きく形成されている。空気がディスクロータ１の中心側から外方へ向って両空気流路１５，１７内を流れ、ディスクロータ１を冷却する。
【００１９】
なお、リブ３の削除本数は上記の６本に限るものではなく、等分に２，３，４，５本…などであってもよい。
【００２０】
ディスクロータ１のブレーキディスク圧接面１ａ，１ｂは、硬い表面を有するローラを圧接面１ａ，１ｂに押し付けつつ周方向に転動させてローラーバニッシュ仕上げされる。このとき、ブレーキディスク圧接面１ａ，１ｂの、周方向幅の大きい第２の空気流路１７部が押圧荷重により撓んで、塑性変形を生じないように、この部の肉厚は第１の空気流路１５部の肉厚よりも大きく設定されている。すなわち、第２の空気流路１７の両ブレーキディスク間の流路幅ｈ2 は第１の空気流路１５部の同流路幅ｈ1 よりも小さく（ｈ2 ＜ｈ1 ）設定されている。
【００２１】
リブ３および第１、第２の空気流路１５，１７の寸法設定方法の詳細をつぎに説明する。
【００２２】
図２に示すように、第２の空気流路１７の周方向所定範囲としてのＡ2 範囲（第２の周方向範囲）の断面の、ディスクロータ１の厚さＴの中心軸に対する断面２次モーメントＩ2 と、隣接する第１の空気流路１５の同範囲としてのＡ1 範囲（第１の周方向範囲）の断面の同断面２次モーメントＩ1 とがほぼ等しくなるように、リブ３および第１と第２の空気流路１５，１７の各諸元が設定されている。
【００２３】
Ａ1 ，Ａ2 範囲の各断面２次モーメントＩ1 ，Ｉ2 は次式で表される。
【００２４】
Ｉ1 ＝｛２（ｂ1 ＋ａ）Ｔ3 −２ｂ 1 ・ｈ 1 3 ｝／１２……………（１）
Ｉ2 ＝｛２（ｂ1 ＋ａ）Ｔ3 −（２ｂ 1 ＋ａ）ｈ 2 3 ｝／１２……（２）
ここに、
Ｉ1 ：第１の空気流路１５のＡ1 範囲断面の断面２次モーメント
Ｉ2 ：第２の空気流路１７のＡ2 範囲断面の断面２次モーメント
Ｔ ：ディスクロータ１の厚さ
ｂ1 ：第１の空気流路１５の外周部の周方向幅
ｂ2 ：第２の空気流路１７の外周部の周方向幅
ｈ1 ：第１の空気流路１５の流路幅
ｈ2 ：第２の空気流路１７の流路幅
ａ ：リブ３の厚さ（周方向の厚さ）
第１と第２の空気流路１５，１７の各外周部の周方向幅ｂ1 ，ｂ2 間の寸法関係がｂ2 ＝２ｂ1 ＋ａになるので（リブ１本を削除して第２の空気流路１７を形成していることによる寸法関係である）、断面２次モーメントＩ1 ，Ｉ2 が等しくなる各流路幅ｈ2 ，ｈ1 間の比は次式で求められる。
【００２５】
ｈ2 ／ｈ1 ＝｛２ｂ1 ／（２ｂ1 ＋ａ）｝1/3 （３）
いま、第１の空気流路１５の外周部の周方向幅ｂ1 とリブ３の厚さａとを等しい寸法（ｂ1 ＝ａ）に設定すれば、（３）式は、

Figure 0003663894
が得られる。こうして、Ｉ1 ＝Ｉ2 を満足するｈ2 ／ｈ1 が得られ、例えば製造上の条件からｈ2 を設定するとｈ1 が求められる。
【００２６】
つぎに、ディスクロータ１の作用を説明する。
【００２７】
第１と第２の空気流路１５，１７のＡ1 ，Ａ2 範囲断面の各断面２次モーメントＩ1 ，Ｉ2 がほぼ等しくなるよう関連部の諸元が設定されているので、ディスクロータ１の周方向の剛性がほぼ均一化され、ローラーバニッシュ加工時の圧接面１ａ，１ｂの変形を弾性域内にとどめることができ、不均一な変形の発生が抑制されて、圧接面１ａ，１ｂが良好な平面に仕上げられる。
【００２８】
また、制動中のディスクロータ１の圧接面１ａ，１ｂの熱変形も抑制され、ブレーキ鳴きが防止されると共にウーというような異音の発生が防止される。
【図面の簡単な説明】
【図１】本発明の一実施形態のリブの配置状態を模式的に示す図である。
【図２】一実施形態のディスクロータの外周の展開図である。
【図３】従来例のディスクロータの外周の展開図である。
【符号の説明】
１ ディスクロータ
１ａ，１ｂ フレーキディスク圧接面
３ リブ
１５ 第１の空気流路
１７ 第２の空気流路
Ａ1 第１の空気流路の所定範囲
Ａ2 第２の空気流路の所定範囲
Ｔ ディスクロータの厚さ
ａ リブの厚さ
ｂ1 第１の空気流路の外周部の周方向幅
ｂ2 第２の空気流路の外周部の周方向幅
ｈ1 第１の空気流路の流路幅
ｈ2 第２の空気流路の流路幅
Ｉ1 第１の空気流路部の断面２次モーメント
Ｉ2 第２の空気流路部の断面２次モーメント[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a disc rotor for a hung-up disc brake.
[0002]
[Prior art]
As a conventional disk rotor of this type, for example, the one shown in FIG. 3 is described in Japanese Patent Application Laid-Open No. 58-24629.
[0003]
FIG. 3 shows the outer periphery of the disk rotor 101 in a developed state. Ribs 103, 103, 103... Are arranged at equal pitches P 1 between the upper and lower pressure contact surfaces 101a, 101b, and the ribs 103 are connected to each other. In between, air flow paths 105a and 105b for cooling are formed. On the other hand, the widths W 1 and W 2 of the air flow paths 105 a and 105 b in the rotor thickness direction are not uniform, and the wide air flow path 105 b and the narrow air flow path 105 a extend over the entire circumference of the disk rotor 101. Arranged appropriately and configured so that the weight distribution in the circumferential direction becomes non-uniform. As a result, the occurrence of the squealing phenomenon of the brake is prevented by suppressing the occurrence of the equally divided resonance waveform in the disc rotor 101.
[0004]
[Problems to be solved by the invention]
However, since the circumferential rigidity is non-uniform, the deformation of the pressure contact surfaces 101a and 101b during processing, thermal deformation during braking, and the like become non-uniform, and periodic torque fluctuations occur in the disk rotor 101. Occasionally, an abnormal noise such as woo may occur.
[0005]
Accordingly, an object of the present invention is to prevent the generation of abnormal noise as well as the prevention of brake squeal.
[0006]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the invention according to claim 1 is characterized in that the brake discs on both sides to which the brake pads are pressed, and a plurality of ribs radially arranged equally between the two brake discs, e Bei an air passage formed between the respective ribs, as the air flow path, the first air passage and the second air channel is provided, the air flow passage of said second circumferential etc. Are formed by removing one rib at each of a plurality of locations, and the flow width in the thickness direction between both brake disks of the second air flow path is the same flow path of the first air flow path. A disk rotor of a disk brake set smaller than the width , wherein the second circumference is disposed between the circumferential centers of the ribs provided on both sides of the circumferential direction of the second air flow path. A directional range and the same circumferential length as the second circumferential range, In a first circumferential region including an air flow path, wherein the second moment relative to the center axis of the disk rotor thickness is set to be substantially equal.
[0009]
The invention according to claim 2 is the disk rotor of the disk brake according to claim 1 , wherein a thickness of the rib in the circumferential direction is a, and the outer periphery of the brake disk of the first and second air flow paths. Where b 1 and b 2 are the widths in the circumferential direction, the ratio of the channel widths h 1 and h 2 between the brake disks of the first and second air channels is h 2 / h 1 = { 2b 1 / (2b 1 + a)} 1/3 .
[0010]
【The invention's effect】
According to invention of Claim 1, between the 1st air flow paths with small width of the peripheral direction, the 2nd air flow path formed in the same width by rib removal is arranged, Since the weight distribution in the circumferential direction of the disk rotor becomes non-uniform, the equally divided resonance waveform generated in the disk rotor is suppressed and the squealing of the brake is prevented.
[0012]
According to the first aspect of the present invention, since the second air flow path having an increased circumferential width is formed by thinning out the ribs equally arranged on the entire circumference between the brake disks, the disk rotor is formed. The mold can be formed and cast easily, and the cost can be reduced.
[0013]
According to the invention described in claim 1, a first circumferential extent, in a second circumferential extent, and set as the second moment relative to the center axis of the disk rotor thickness is substantially equal because there, the rigidity of the brake disk is uniform in the circumferential direction.
[0014]
According to the second aspect of the present invention, for example, if the circumferential width b 1 at the outer periphery of the brake disk of the first air flow path is set equal to the rib thickness a, the first and second air flow paths The ratio h 2 / h 1 of each flow path width for equalizing the secondary moments of each cross section in the same predetermined range in the circumferential direction is as follows:
h 2 / h 1 = {2b 1 / (2b 1 + a)} 1/3
= (2/3) 1/3
= 0.874
If h 2 is appropriately set from the manufacturing conditions, h 1 is derived.
[0015]
Thus, the specifications of the rib and the first and second air flow paths can be easily calculated, and the same effect as that of the invention of claim 1 can be obtained.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
An embodiment of the present invention will be described with reference to FIGS. FIG. 1 schematically shows the arrangement state of the ribs of the disk rotor of this embodiment, and FIG. 2 shows the outer periphery of the disk rotor in an unfolded state.
[0017]
As shown in FIGS. 1 and 2, 30 ribs 3 are arranged radially between the brake disk pressure-contact surfaces 1 a and 1 b on both sides of the disk rotor 1. This is a state in which 36 ribs are arranged on the entire circumference, and 6 ribs (arrow portions in FIG. 1) are removed one by one at six locations equally divided in the circumferential direction. belongs to.
[0018]
A first air flow path 15 is formed between the ribs 3 and 3 at portions where the rib 3 is not deleted, and a second air flow path 17 is formed at the deleted position. Thus, the circumferential width b 2 on the outer periphery of the disk rotor 1 of each of the six second air passages 17 in the circumferential direction is formed larger than the width b 1 of the first air passage 15. Air flows from the center side of the disk rotor 1 to the outside in the air flow paths 15 and 17 to cool the disk rotor 1.
[0019]
The number of ribs 3 to be deleted is not limited to the above six, and may be equally divided into 2, 3, 4, 5,.
[0020]
The brake disc pressure contact surfaces 1a and 1b of the disk rotor 1 are roller burnished by rolling a roller having a hard surface against the pressure contact surfaces 1a and 1b in the circumferential direction. At this time, the thickness of the second air flow path 17 portion having a large circumferential width of the brake disc pressure contact surfaces 1a and 1b is bent by the pressing load and does not cause plastic deformation. It is set larger than the thickness of the flow path 15 part. That is, the channel width h 2 between two brake discs of the second air passage 17 is first smaller than the common origin path width h 1 of the air passage 15 parts (h 2 <h 1) Configuration .
[0021]
Details of the dimension setting method of the rib 3 and the first and second air flow paths 15 and 17 will be described below.
[0022]
As shown in FIG. 2, the secondary cross section of the cross section of the A 2 range (second peripheral range) as the predetermined range in the circumferential direction of the second air flow path 17 with respect to the central axis of the thickness T of the disk rotor 1. moment I 2, as the a 1 ranges the second moment I 1 of the cross section of the (first circumferential range) as the range of the first air passage 15 adjacent are substantially equal, the ribs 3 The specifications of the first and second air flow paths 15 and 17 are set.
[0023]
A 1, A 2 ranges each second moment I 1 of, I 2 is represented by the following formula.
[0024]
I 1 = {2 (b 1 + a) T 3 −2b 1 ・ H 1 Three } / 12 ………… (1)
I 2 = {2 (b 1 + a) T 3 − (2b 1 + A) h 2 Three } / 12 …… (2)
here,
I 1 : Cross section secondary moment of the A 1 range cross section of the first air flow path 15 I 2 : Cross section secondary moment of the A 2 range cross section of the second air flow path 17 T: Thickness of the disc rotor 1 b 1 : Circumferential width of the outer peripheral portion of the first air passage 15 b 2 : circumferential width of the outer peripheral portion of the second air passage 17 h 1 : passage width of the first air passage 15 h 2 : first Channel width a of the second air channel 17 a: thickness of the rib 3 (thickness in the circumferential direction)
Since the dimensional relationship between the circumferential widths b 1 and b 2 of the outer peripheral portions of the first and second air passages 15 and 17 is b 2 = 2b 1 + a (the second rib is removed and the second The ratio between the channel widths h 2 and h 1 at which the secondary moments I 1 and I 2 are equal is obtained by the following equation.
[0025]
h 2 / h 1 = {2b 1 / (2b 1 + a)} 1/3 (3)
If the circumferential width b 1 of the outer peripheral portion of the first air flow path 15 and the thickness a of the rib 3 are set to the same dimension (b 1 = a), the expression (3) is
Figure 0003663894
Is obtained. Thus, obtained h 2 / h 1 satisfying the I 1 = I 2, h 1 is obtained by setting the h 2, for example, from the conditions of manufacture.
[0026]
Next, the operation of the disc rotor 1 will be described.
[0027]
The specifications of the related portions are set so that the secondary moments I 1 and I 2 of the first and second air flow passages 15 and 17 in the A 1 and A 2 range cross sections are substantially equal. 1 is almost uniform, the deformation of the pressure contact surfaces 1a and 1b during roller burnishing can be kept within the elastic region, and the occurrence of non-uniform deformation is suppressed, so that the pressure contact surfaces 1a and 1b Finished on a good flat surface.
[0028]
Further, thermal deformation of the pressure contact surfaces 1a and 1b of the disc rotor 1 during braking is suppressed, so that brake noise is prevented and abnormal noise such as woo is prevented.
[Brief description of the drawings]
FIG. 1 is a diagram schematically showing an arrangement state of ribs according to an embodiment of the present invention.
FIG. 2 is a development view of the outer periphery of a disc rotor according to an embodiment.
FIG. 3 is a developed view of the outer periphery of a conventional disc rotor.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Disc rotor 1a, 1b Flakes disc press-contact surface 3 Rib 15 1st air flow path 17 2nd air flow path A 1 The predetermined range of 1st air flow path A 2 The predetermined range of 2nd air flow path T Disk Rotor thickness a Rib thickness b 1 Circumferential width b of the outer periphery of the first air flow path b 2 Circumferential width h 1 of the outer periphery of the second air flow path 1 Flow path of the first air flow path Width h 2 Flow path width of the second air flow path I 1 Cross section secondary moment of the first air flow path section I 2 Cross section secondary moment of the second air flow path section

Claims (2)

ブレーキパッドが圧接される両側のブレーキディスクと、前記両ブレーキディスク間に放射状に周方向等分に配置される複数のリブと、前記各リブ間に形成される空気流路とを備え、前記空気流路として、第１の空気流路及び第２の空気流路を設け、該第２の空気流路は、周方向等分の複数箇所で各々１本のリブをリブ抜きすることにより形成され、前記第２の空気流路の両ブレーキディスク間の厚さ方向の流路幅を第１の空気流路の同流路幅よりも小さく設定したデイスクブレーキのディスクロータであって、
前記第２の空気流路の周方向の両側に設けられた各リブの周方向の中心同士の間に配置された第２の周方向範囲と、該第２の周方向範囲と同一の周方向長さを有し、２つの第１の空気流路を含む第１の周方向範囲とにおける、ディスクロータの厚さの中心軸に対する断面２次モーメントがほぼ等しくなるように設定したことを特徴とするデイスクブレーキのディスクロータ。 E Bei both sides of the brake disc the brake pad is pressed against a plurality of ribs which are radially disposed circumferentially equal intervals between the two brake discs, and an air passage formed between the respective ribs, the As the air flow path , a first air flow path and a second air flow path are provided, and the second air flow path is formed by ribbing one rib at each of a plurality of locations equally in the circumferential direction. A disk rotor of a disc brake , wherein a flow path width in a thickness direction between both brake disks of the second air flow path is set smaller than the same flow path width of the first air flow path ,
A second circumferential range disposed between the circumferential centers of the ribs provided on both sides in the circumferential direction of the second air flow path, and the same circumferential direction as the second circumferential range The second moment of the cross section with respect to the central axis of the thickness of the disk rotor in the first circumferential range including the two first air flow paths is set so as to be substantially equal. Disc brake disc rotor. 請求項１記載のデイスクブレーキのディスクロータであって、
前記リブの周方向の厚さをａとし、前記第１と第２の空気流路のブレーキディスク外周部における周方向の幅をそれぞれｂ1 ，ｂ2 としたとき、
第１と第２の空気流路の両ブレーキディスク間の各流路幅ｈ1 ，ｈ2 の比をｈ2 ／ｈ1 ＝｛２ｂ1 ／（２ｂ1 ＋ａ）｝1/3 に設定することを特徴とするデイスクブレーキのディスクロータ。A disk rotor for a disk brake according to claim 1 ,
When the circumferential thickness of the rib is a, and the circumferential widths of the first and second air passages at the outer periphery of the brake disk are b 1 and b 2 , respectively,
The ratio of the flow path widths h 1 and h 2 between the brake disks of the first and second air flow paths is set to h 2 / h 1 = {2b 1 / (2b 1 + a)} 1/3 Disc brake disc rotor featuring
JP06346998A 1998-03-13 1998-03-13 Disc brake disc rotor Expired - Fee Related JP3663894B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP06346998A JP3663894B2 (en) 1998-03-13 1998-03-13 Disc brake disc rotor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP06346998A JP3663894B2 (en) 1998-03-13 1998-03-13 Disc brake disc rotor

Publications (2)

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JPH11257388A JPH11257388A (en) 1999-09-21
JP3663894B2 true JP3663894B2 (en) 2005-06-22

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Family Applications (1)

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