JPS6360252B2 - - Google Patents
Info
- Publication number
- JPS6360252B2 JPS6360252B2 JP56122032A JP12203281A JPS6360252B2 JP S6360252 B2 JPS6360252 B2 JP S6360252B2 JP 56122032 A JP56122032 A JP 56122032A JP 12203281 A JP12203281 A JP 12203281A JP S6360252 B2 JPS6360252 B2 JP S6360252B2
- Authority
- JP
- Japan
- Prior art keywords
- brake rotor
- gap
- brake
- pressure contact
- width
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000013016 damping Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
Classifications
-
- 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
- F16D65/78—Features relating to cooling
- F16D65/84—Features relating to cooling for disc brakes
- F16D65/847—Features relating to cooling for disc brakes with open cooling system, e.g. cooled by air
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Description
【発明の詳細な説明】
産業上の利用分野
本発明はデイスクブレーキのブレーキロータに
関し、とりわけ、両側に設けたブレーキパツドの
圧接面間に半径方向に延びる複数のリブによつて
間隙を形成し、この間隙を伝つて空気が流通され
るようにしたブレーキロータに関する。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a brake rotor for a disc brake, and more particularly to a brake rotor in which a gap is formed by a plurality of ribs extending in the radial direction between the pressure contact surfaces of brake pads provided on both sides. This invention relates to a brake rotor in which air is allowed to flow through a gap.
従来の技術
この種のブレーキロータはベンチレーテツドタ
イプのブレーキロータと称せられ、制動時つまり
ブレーキパツドが圧接面に圧接した時に摩擦熱を
効率良く放熱できる点で近年多用されている。BACKGROUND ART This type of brake rotor is called a ventilated type brake rotor, and has been widely used in recent years because it can efficiently dissipate frictional heat during braking, that is, when a brake pad is pressed against a pressure contact surface.
たとえば、第１図および第２図に実開昭55−
55633号公報にて知られる前記ベンチレーテツド
タイプのブレーキロータ１を示し、２，２ａは該
ブレーキロータ１の両側周縁部に形成され、図外
のブレーキパツドが制動時に圧接する圧接面、３
はこれら圧接面２，２ａ間に半径方向に延びる複
数のリブで、これらリブ３間には前記圧接面２，
２ａの内、外径側を連通する間隙４が形成されて
いる。５は前記ブレーキロータ１を図外の取付
部、たとえば車輪のハブ等に取り付けるためのボ
ルト挿通孔である。 For example, in Figures 1 and 2,
55633, the ventilated type brake rotor 1 is shown, and 2 and 2a are pressure contact surfaces formed on both side peripheral edges of the brake rotor 1 and are pressed against brake pads (not shown) during braking;
are a plurality of ribs extending in the radial direction between the pressure contact surfaces 2 and 2a, and between these ribs 3 are the pressure contact surfaces 2 and 2a.
A gap 4 is formed that communicates the inner and outer diameter sides of 2a. Reference numeral 5 denotes a bolt insertion hole for attaching the brake rotor 1 to a mounting portion (not shown), such as a wheel hub.
そして、前記ブレーキロータ１はこれが回転す
ることによつて遠心力で間隙４を空気が流通し、
圧接面２，２ａにブレーキパツドが圧接した際の
摩擦熱を効率良く放熱するようになつている。 As the brake rotor 1 rotates, air flows through the gap 4 due to centrifugal force.
The frictional heat generated when the brake pad is pressed against the pressure contact surfaces 2, 2a is efficiently radiated.
発明が解決しようとする課題
しかしながら、かかる従来のベンチレーテツド
タイプのブレーキロータ１は、各リブ３の肉厚ｔ
が均一で、かつ、該リブ３のピツチｐも均一であ
るため、前記ブレーキロータ１の円周方向の重量
分布が均一となつていた。このため、該ブレーキ
ロータ１は第３図に模式的に示すように円周方向
の当分割共振波形ｅ（固有共振波形で図示例では
４節共振波形となつている。）を生じ易く、当分
割共振波形ｅが生ずると、ブレーキロータ１の振
動減衰能を著しく悪化してしまうことが知られて
いる。Problems to be Solved by the Invention However, in such a conventional ventilated type brake rotor 1, each rib 3 has a wall thickness t.
is uniform, and the pitch p of the ribs 3 is also uniform, so that the weight distribution in the circumferential direction of the brake rotor 1 is uniform. Therefore, as schematically shown in FIG. 3, the brake rotor 1 tends to generate a circumferentially divided resonance waveform e (a natural resonance waveform, which is a four-node resonance waveform in the illustrated example). It is known that when the split resonance waveform e occurs, the vibration damping ability of the brake rotor 1 is significantly deteriorated.
このように、振動減衰能が著しく悪い従来のブ
レーキロータ１にあつては、制動時に耳ざわりな
異音、謂わゆるブレーキ鳴きを発生してしまうと
いう課題があつた。 As described above, the conventional brake rotor 1, which has extremely poor vibration damping ability, has a problem in that it generates a harsh noise, so-called brake squeal, during braking.
そこで、本発明はかかる従来の課題に鑑みて、
ブレーキロータの円周方向における重量分布を不
均一として、該ブレーキロータに発生する当分割
共振波形を抑制するようにしたデイスクブレーキ
のブレーキロータを提供することを目的とする。 Therefore, in view of such conventional problems, the present invention
It is an object of the present invention to provide a brake rotor for a disc brake in which the weight distribution in the circumferential direction of the brake rotor is made non-uniform to suppress a divisional resonance waveform generated in the brake rotor.
課題を解決するための手段
かかる目的を達成するために本発明は、両側に
ブレーキパツドの圧接面を有し、これら圧接面間
に半径方向に延びる複数のリブによつて間隙を形
成し、この間隙を伝つて空気が流通されるように
したデイスクブレーキのブレーキロータにおい
て、前記複数の間隙のうち一部の間隙のブレーキ
ロータ厚さ方向幅を、前記圧接面の内側から該間
隙の周方向全幅に亙つて一体に形成される肉厚増
大部を設けることにより他部の間隙と違え、該肉
厚増大部により円周方向における重量分布が不均
一になるように構成する。Means for Solving the Problems In order to achieve the above object, the present invention has brake pad pressure contact surfaces on both sides, a gap is formed between these pressure contact surfaces by a plurality of ribs extending in the radial direction, and this gap is In the brake rotor of the disc brake, the width of some of the gaps in the brake rotor thickness direction is increased from the inside of the pressure contact surface to the entire width of the gap in the circumferential direction. By providing an integrally formed thickened portion, the weight distribution in the circumferential direction is made uneven due to the thickened portion, unlike gaps in other parts.
作 用
以上の構成により、本発明のデイスクブレーキ
のブレーキロータにあつては、複数の間隙のうち
一部の間隙に肉厚増大部が設けられることによ
り、該肉厚増大部の重量をもつてブレーキロータ
の円周方向の重量分布を不均一にすることが可能
となり、該ブレーキロータに発生する当分割共振
波形を抑制して、ブレーキ鳴きが防止若しくは著
しく低減されるようになる。Effect With the above configuration, in the brake rotor of the disc brake of the present invention, the increased wall thickness portion is provided in some of the gaps among the plurality of gaps, so that the weight of the increased wall thickness portion is reduced. It becomes possible to make the weight distribution of the brake rotor non-uniform in the circumferential direction, and the divided resonance waveform generated in the brake rotor is suppressed, so that brake squeal is prevented or significantly reduced.
実施例
以下、本発明に実施例を図に基づいて詳細に説
明する。Embodiments Hereinafter, embodiments of the present invention will be described in detail based on the drawings.
第４図は本発明の一実施例であるベンチレーテ
ツドタイプのブレーキロータ１０の円周の一部分
を示す端面図で、１１，１１ａは圧接面、１２は
リブ、１３は間隙で、この実施例にあては前記リ
ブ１２をそれぞれ同一ピツチp1に形成して前記間
隙１３の円周方向幅１をそれぞれ同一にしてあ
る。 FIG. 4 is an end view showing a part of the circumference of a ventilated type brake rotor 10 according to an embodiment of the present invention, in which 11 and 11a are pressure contact surfaces, 12 is a rib, and 13 is a gap. In this case, the ribs 12 are formed at the same pitch p1 , and the circumferential width 1 of the gap 13 is made the same.
ここで、本実施例は前記圧接面１１，１１ａの
内側に肉厚増大部１５を設けることにより、前記
間隙１３のブレーキロータ１０厚さ方向幅ｗを、
該ブレーキロータ１０の全周に亙つて適宜変更、
つまり、該厚さ方向幅ｗの広い間隙１３ａと狭い
間隙１３ｂを形成することによつて、圧接面１
１，１１ａを形成した両側に円板部分１４，１４
ａに部分的な厚肉部、薄肉部を形成し、前記ブレ
ーキロータ１０の円周方向における重量分布が不
均一になるように構成してある。尚、図示した実
施例は、前記間隙１３の厚さ方向幅ｗに対する中
心線c1をブレーキロータ１０の厚さに対する中心
線c2に一致させて、前記円板部分１４，１４ａの
部分的肉厚が前記中心線c2に対して対称となるよ
うにしてあるが、これに限ることなく第５図に示
すように、間隙１３ｂの中心線c1，ブレーキロー
タ１０の中心線c2および間隙１３ａの中心線c3を
それぞれ一致させることなく、前記円板部分１
４，１４ａの肉厚を、一方が厚く他方が薄くなる
ように形成してもよい。また、前記肉厚増大部１
５は間隙１３ｂの周方向全幅に亙つて形成されて
いる。 Here, in this embodiment, by providing the thickened portion 15 on the inner side of the pressure contact surfaces 11 and 11a, the width w in the thickness direction of the brake rotor 10 of the gap 13 is
Appropriately changing the entire circumference of the brake rotor 10,
That is, by forming the wide gap 13a and the narrow gap 13b with the width w in the thickness direction, the pressure contact surface 1
Disk portions 14, 14 on both sides forming 1, 11a.
Partial thick portions and thin portions are formed at portion a so that the weight distribution of the brake rotor 10 in the circumferential direction is non-uniform. In the illustrated embodiment, the center line c 1 of the gap 13 in the thickness direction width w is made to coincide with the center line c 2 of the brake rotor 10 in terms of the thickness, so that the partial thickness of the disc portions 14, 14a is reduced. Although the thickness is made to be symmetrical with respect to the center line c2 , the thickness is not limited to this, and as shown in FIG. 13a without making the center lines c 3 coincide with each other, the disk portion 1
4 and 14a may be formed so that one side is thicker and the other side is thinner. Further, the increased wall thickness portion 1
5 is formed over the entire circumferential width of the gap 13b.
以上の構成により、本実施例のブレーキロータ
１０は肉厚増大部１５が設けられることにより、
円周方向における重量分布が不均一となり、前記
第３図によつて示したように当分割共振波形（固
有共振波形）ｅが発生されるのが抑制される。こ
のため、本実施例のブレーキロータ１０は振動減
衰能が著しく向上し、ブレーキ鳴きを防止若しく
は著しく低減することができる。また、ブレーキ
ロータ１０の回転バランスを図ると同時に、重量
分布を不均一にするために設計計算を容易に行う
ことができる。 With the above configuration, the brake rotor 10 of this embodiment is provided with the thickened portion 15, so that
The weight distribution in the circumferential direction becomes non-uniform, and the generation of the divided resonance waveform (natural resonance waveform) e as shown in FIG. 3 is suppressed. Therefore, the brake rotor 10 of this embodiment has a significantly improved vibration damping ability, and brake squeal can be prevented or significantly reduced. Further, design calculations can be easily performed to balance the rotation of the brake rotor 10 and to make the weight distribution uneven.
尚、前記ブレーキロータ１０は円周方向におけ
る重量分布を回転バランスをとりつつ不均一にな
るように計算して取付が行われるが、該ブレーキ
ロータ１０の取付け誤差等により回転バランスが
くずれることがある。この回転バランスをとるた
めに従来から第６図に示すように、間隙１３内の
バランスウエイト２０を装着して調整する手段が
講じられている。 The brake rotor 10 is installed by calculating the weight distribution in the circumferential direction so that it is rotationally balanced and uneven, but the rotational balance may be lost due to installation errors of the brake rotor 10. . In order to maintain this rotational balance, conventional means have been taken to adjust the rotation by attaching a balance weight 20 within the gap 13, as shown in FIG.
ところで、前述した本発明の実施例にあつて
は、各間隙１３の円周方向幅１がそれぞれ一定に
形成されているので、前記バランスウエイト２０
を１種類のみ用意しておけば、いずれの間隙１３
にも装着することができる。このとき、前記バラ
ンスウエイト２０は前記間隙１３内のブレーキロ
ータ１０回転方向側面、つまり、リブ１２の内側
面１２ａに圧入により係止されているので、前記
バランスウエイト２０と前記間隙１３とのブレー
キロータ１０厚さ方向間に間隙が生じても、実際
の機能に支障が来されることはない。 By the way, in the embodiment of the present invention described above, since the circumferential width 1 of each gap 13 is formed constant, the balance weight 20
If you prepare only one type of
It can also be installed. At this time, the balance weight 20 is press-fitted to the side surface in the rotational direction of the brake rotor 10 within the gap 13, that is, the inner surface 12a of the rib 12, so that the balance weight 20 and the brake rotor in the gap 13 are 10 Even if a gap occurs in the thickness direction, the actual function will not be affected.
尚、本実施例は前述したように各リブ１２を同
一ピツチp1に形成したものを示したが、これに限
ることなく該ピツチp1をそれぞれ違えて各間隙１
３の円周方向幅１を不均一にしたもの、また、前
述リブ１２の形状をそれぞれ不均一にしたものに
あつても、本発明を適用できることはいうまでも
ない。 Although this embodiment shows that each rib 12 is formed at the same pitch p 1 as described above, the pitch p 1 is not limited to this, and each gap 1 is formed at a different pitch p 1.
It goes without saying that the present invention can be applied to the case where the circumferential width 1 of the rib 3 is made non-uniform, and the shape of the rib 12 is made non-uniform.
発明の効果
以上説明したように、本発明のデイスクブレー
キのブレーキロータにあつては、複数の間隙のう
ち一部の間隙のブレーキロータ厚さ方向の幅を、
圧接面の内側から該間隙の周方向全幅に亙つて一
体に形成される肉厚増大部を設けることにより他
部の間隙と違え、この肉厚増大部により該ブレー
キロータの円周方向における重量分布が不均一に
なるように構成したので、ブレーキロータの発生
する当分割共振波形を抑制して振動減衰能を向上
し、ブレーキ鳴きを著しく低減することができ
る。また、間隙のブレーキロータ厚さ方向の幅を
変更するという手段を講ずることによつて、ブレ
ーキロータの回転バランスをとりつつ重量分布を
不均一にするための計算がしやすく、設計上の自
由度を増大することができる。更に、前記圧接面
から前記肉厚増大部が一体に形成されていること
により、該肉厚増大部が補強部材となつてブレー
キロータの変形、つまり、当分割共振波形の更な
る抑制を図ることができると共に、前記肉厚増大
部は間隙の周方向全幅に亙つて形成されることに
より、ブレーキロータ変形時の応力集中を防止す
ることができるという各種優れた効果を奏する。Effects of the Invention As explained above, in the brake rotor of the disc brake of the present invention, the width of some of the gaps in the brake rotor thickness direction is
By providing an increased wall thickness portion integrally formed from the inside of the pressure contact surface over the entire circumferential width of the gap, unlike other gaps, this increased wall thickness portion improves the weight distribution in the circumferential direction of the brake rotor. Since the brake rotor is configured to be non-uniform, it is possible to suppress the divided resonance waveform generated by the brake rotor, improve vibration damping ability, and significantly reduce brake squeal. In addition, by changing the width of the gap in the thickness direction of the brake rotor, it is easier to calculate how to balance the rotation of the brake rotor while making the weight distribution non-uniform, allowing for greater flexibility in design. can be increased. Furthermore, since the increased wall thickness portion is integrally formed from the pressure contact surface, the increased wall thickness portion serves as a reinforcing member to further suppress deformation of the brake rotor, that is, the resonant waveform of the division. In addition, since the thickened portion is formed over the entire width of the gap in the circumferential direction, various excellent effects such as being able to prevent stress concentration during deformation of the brake rotor can be achieved.
第１図は従来のブレーキロータの正面図、第２
図は第１図中の―線断面図、第３図は従来の
ブレーキロータに発生する当分割共振波形の模式
図、第４図は本発明にかかるブレーキロータの一
部分を示す端面図、第５図は本発明の他の実施例
を示し第４図に対応する端面図、第６図はバラン
スウエイトの取付状態を示す説明図である。
１，１０…ブレーキロータ、２，２ａ，１１，
１１ａ…圧接面、３，１２…リブ、１３…間隙、
１５…肉厚増大部、２０…バランスウエイト、
ｐ，p1…リブのピツチ、ｗ…間隙の厚さ方向幅。
Figure 1 is a front view of a conventional brake rotor, Figure 2 is a front view of a conventional brake rotor.
The figures are a sectional view taken along the line -- in Fig. 1, Fig. 3 is a schematic diagram of the divided resonance waveform generated in a conventional brake rotor, Fig. 4 is an end view showing a part of the brake rotor according to the present invention, and Fig. 5 The figures show another embodiment of the present invention, and are an end view corresponding to FIG. 4, and FIG. 6 is an explanatory view showing the state in which the balance weight is attached. 1, 10...brake rotor, 2, 2a, 11,
11a... Pressure contact surface, 3, 12... Rib, 13... Gap,
15...Increased wall thickness part, 20...Balance weight,
p, p 1 ...Rib pitch, w...Gap width in the thickness direction.
Claims (1)
ら圧接面間に半径方向に延びる複数のリブによつ
て間隙を形成し、この間隙を伝つて空気が流通さ
れるようにしたデイスクブレーキのブレーキロー
タにおいて、前記複数の間隙のうち一部の間隙の
ブレーキロータ厚さ方向幅を、前記圧接面の内側
から該間隙の周方向全幅に亙つて一体に形成され
る肉厚増大部を設けることにより他部の間隙と違
え、該肉厚増大部により円周方向における重量分
布が不均一になるように構成したことを特徴とす
るデイスクブレーキのブレーキロータ。1. In a brake rotor for a disc brake that has brake pad pressure contact surfaces on both sides, a gap is formed between these pressure contact surfaces by a plurality of ribs extending in the radial direction, and air is allowed to flow through this gap. , the width of some of the gaps in the brake rotor thickness direction is increased by providing an increased wall thickness portion that is integrally formed from the inside of the pressure contact surface to the entire width of the gap in the circumferential direction. A brake rotor for a disc brake, characterized in that, unlike the gap, the thickened portion makes the weight distribution uneven in the circumferential direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12203281A JPS5824629A (en) | 1981-08-04 | 1981-08-04 | Brake rotor of disc brake |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12203281A JPS5824629A (en) | 1981-08-04 | 1981-08-04 | Brake rotor of disc brake |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5824629A JPS5824629A (en) | 1983-02-14 |
| JPS6360252B2 true JPS6360252B2 (en) | 1988-11-24 |
Family
ID=14825900
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12203281A Granted JPS5824629A (en) | 1981-08-04 | 1981-08-04 | Brake rotor of disc brake |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5824629A (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58189827U (en) * | 1982-06-12 | 1983-12-16 | アイシン高丘株式会社 | Ventilated desk rotor |
| JPS613974U (en) * | 1984-06-13 | 1986-01-11 | トヨタ自動車株式会社 | Distributor for spark ignition internal combustion engine |
| JPS61261674A (en) * | 1985-05-15 | 1986-11-19 | Nippon Denso Co Ltd | Ignition distributor for internal combustion engine |
| JPH03100637U (en) * | 1990-02-03 | 1991-10-21 | ||
| DE4101652A1 (en) * | 1990-10-18 | 1992-07-30 | Duerrwaechter E Dr Doduco | DISTRIBUTOR CAP OF AN IGNITION DISTRIBUTOR WITH A SHIELDING HOOD AND SHIELDING HOOD THEREFOR |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3983973A (en) * | 1974-05-25 | 1976-10-05 | Knorr-Bremse Gmbh | Vibration damper for a brake disk |
-
1981
- 1981-08-04 JP JP12203281A patent/JPS5824629A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3983973A (en) * | 1974-05-25 | 1976-10-05 | Knorr-Bremse Gmbh | Vibration damper for a brake disk |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5824629A (en) | 1983-02-14 |
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