JPS5917035A - Disk rotor for disk brake - Google Patents

Disk rotor for disk brake

Info

Publication number
JPS5917035A
JPS5917035A JP12528682A JP12528682A JPS5917035A JP S5917035 A JPS5917035 A JP S5917035A JP 12528682 A JP12528682 A JP 12528682A JP 12528682 A JP12528682 A JP 12528682A JP S5917035 A JPS5917035 A JP S5917035A
Authority
JP
Japan
Prior art keywords
disc
diameter
rigidity
disc rotor
sliding plate
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.)
Pending
Application number
JP12528682A
Other languages
Japanese (ja)
Inventor
Hiromasa Okamura
広正 岡村
Masahiro Yamada
正弘 山田
Michio Akiyoshi
秋「よし」　巳智雄
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toyota Motor Corp filed Critical Toyota Motor Corp
Priority to JP12528682A priority Critical patent/JPS5917035A/en
Priority to GB08319266A priority patent/GB2125911B/en
Priority to DE19833325831 priority patent/DE3325831A1/en
Publication of JPS5917035A publication Critical patent/JPS5917035A/en
Pending legal-status Critical Current

Links

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
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes
    • 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
    • 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
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/1308—Structure one-part
    • 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
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/1328—Structure internal cavities, e.g. cooling channels

Landscapes

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

Abstract

PURPOSE:To reduce a brake noise effectively by making the rigidity of a portion along one diameter of the annular sliding plate of a disk rotor smaller than that of other portions by a predetermined quantity. CONSTITUTION:A recess 13a with a width t1 in the thickness direction, a width w1 in the circumferential direction, and a depth h1 in the radial direction is provided inside a portion along one diameter L1 of the annular sliding plate 13 of a disk rotor 10, and the mass and rigidity of the portion 10a along L1 is made smaller than that of other portions by a predetermined quantity. Therefore, at the disk rotor 10, the portion 10a invariably becomes the node or loop of an oscillation mode, a pair of node and loop (10a) can be fixed to the disk rotor for all oscillation modes, the node or loop of all oscillation modes can be rotated in one unit with the rotating disk rotor 10, thereby the normal oscillation mode of all diameter nodes can be prevented from occurring.

Description

【発明の詳細な説明】 本発明は、所定の板厚と所定の径を有して一対のブレー
キパットにより挟圧される環状摺動板部をハフ部の外周
に一体的に形成してなるディスクブレーキ用ディスクロ
ータに関する。DETAILED DESCRIPTION OF THE INVENTION The present invention includes an annular sliding plate portion having a predetermined thickness and a predetermined diameter, which is pressed between a pair of brake pads and is integrally formed on the outer periphery of a huff portion. This invention relates to a disc rotor for disc brakes.

一般に、この種のディスクブレーキ用ディスクロータに
おいては、その環状摺動板部が円周方向において均質に
形成されていて、環状摺動板部の円周方向におりる質量
及び剛性分布が一様になっているため、当該ディスクロ
ータをその環状摺動板部の一点にて加振した場合に生し
る振動モードにおける節・腹の位置は、加振点の位置を
変えればそれにつれて変り、加振点の位置によって定ま
る。このことは、ブレーキパッドとの摺接により加振さ
れて生じるディスクロークの撮動モードにおける節・腹
の位置が加振点であるブレーキパッドの位置によって定
まり、ブレーキ作用時には空間に対して動かない節・腹
を持つ定常な振動モード（定寓波）が当該ディスクロー
タに生しることを意味する。ところで、かかる定常な振
動モードは所謂・ブレーキ鳴きを発生さ−Ｕる。しかし
て、通當問題となるブレーキ鳴きは、当該ディスクブレ
ーキの全体構成と密接な関係があり、全てのディスクブ
レーキにおいて同し定常な振動モードにて発生ずるもの
ではなく、また同一のディスクブレーキにおいても複数
の定常な振動モードにて発生ずることが多い。したがっ
て、全てのディスクブレーキにおいて効果的にブレーキ
鳴きを低減させるためには、全ての定常な振動モートの
発生を防止する必要がある。Generally, in this type of disc rotor for disc brakes, the annular sliding plate is uniformly formed in the circumferential direction, and the mass and rigidity distribution in the circumferential direction of the annular sliding plate is uniform. Therefore, when the disc rotor is excited at one point on its annular sliding plate, the positions of the nodes and antinodes in the vibration mode will change accordingly if the position of the excitation point is changed. Determined by the position of the excitation point. This means that the position of the nodes and antinodes of the disc in the imaging mode, which are generated by vibration due to sliding contact with the brake pad, is determined by the position of the brake pad, which is the vibration point, and does not move relative to space when the brake is applied. This means that a steady vibration mode (stationary wave) with nodes and antinodes is generated in the disc rotor. By the way, such a steady vibration mode generates so-called brake squeal. However, brake squeal, which is a common problem, is closely related to the overall structure of the disc brake, and does not occur in the same steady vibration mode in all disc brakes, and even in the same disc brake. Also, vibrations often occur in multiple steady vibration modes. Therefore, in order to effectively reduce brake squeal in all disc brakes, it is necessary to prevent all steady vibration motors from occurring.

本発明はかかる必要性に鑑みなされたもので、その要旨
はディスクロータにおける環状摺動板部の１直径に沿う
部位の剛性を他の部位の剛性に比し゛ζ所定量低くした
ごとにある。かかるディスク瞥コータによれば、その環
状摺動板部の１直径に沿う部位が雷に振動モードの節（
又は腹）となり、全ての振動モートにおいて一対の節（
又は腹）が１直径Ｇご沿って当該ディスクロークに対し
て固定される。ごのよ・うに、１直径に沿って一対の節
（又は腹）が固定されると、例えば、２直径節（４節）
の振動モートの場合、他の一対の節（又は腹）が−し記
した一タ・１の節（又は１ｌｌｊ）にり・１して円周方
向に９０度偏位した部位に自然に生じ、二対の節（又は
腹）がディスクロータに円周方向にて等間隔に固定され
る。これと同様に、ｎ　（ｒ＋＝３．　４゜５・・・）
直径節の振動モートの場合にも、他の（ｎ−１）対の節
（又は腹）が上記した一対の節（又は腹）に対して円周
方向に等間隔偏位した部位に自然に生じ、ｎ対の節（又
は腹）がディスクロータに円周方向にて等間隔に固定さ
れる。（これは、発明者等の実験によって確認されてい
る。）したがって、本発明によるディスクロータによれ
ば、全ての振動モードにおいてその節（又は腹）をディ
スクロータに対して固定することができ、回転するディ
スクロータと一体的に全ての振動モートの節（又は腹）
を回転させることができて、全ての直径節の定席な振動
モードの発生を防止することができる。The present invention has been made in view of this need, and its gist lies in that the rigidity of a portion of the disc rotor along one diameter of the annular sliding plate portion is lowered by a predetermined amount of ζ compared to the rigidity of other portions. According to such a disc coater, a portion along one diameter of the annular sliding plate portion is a vibration mode node (
or antinode), and a pair of nodes (
(or an antinode) is fixed to the disc cloak along one diameter G. If a pair of nodes (or antinodes) are fixed along one diameter, for example, two diameter nodes (four nodes)
In the case of the vibration mode of , two pairs of nodes (or antinodes) are fixed to the disc rotor at equal intervals in the circumferential direction. Similarly, n (r+=3.4゜5...)
In the case of a diametral node vibration mote, the other (n-1) pairs of nodes (or antinodes) are naturally located at positions equidistant in the circumferential direction with respect to the above pair of nodes (or antinodes). n pairs of nodes (or antinodes) are fixed to the disc rotor at equal intervals in the circumferential direction. (This has been confirmed by the inventors' experiments.) Therefore, according to the disc rotor according to the present invention, the nodes (or antinodes) can be fixed to the disc rotor in all vibration modes, All vibration motor nodes (or antinodes) integrally with the rotating disc rotor
can be rotated to prevent the occurrence of constant vibration modes at all diameter nodes.

以下に、本発明の各実施例を図面に基づいて説明する。EMBODIMENT OF THE INVENTION Below, each Example of this invention is described based on drawing.

第１図及び第２図はソリッド型のディスクロータに本発
明を実施した例を示していて、このディスクロータ１ｏ
においては、取付孔１１〜１１を有するハブ部１２の外
周に、所定の板厚Ｔ。1 and 2 show an example in which the present invention is applied to a solid type disc rotor, and this disc rotor 1o
, the outer periphery of the hub portion 12 having the mounting holes 11 to 11 has a predetermined plate thickness T.

と所定の径り。を有して一対のブレーキバット（図示−
已ず）により挟圧される環状摺動板部】３が一体的に形
成されている。and the prescribed diameter. with a pair of brake butts (as shown)
An annular sliding plate portion 3 which is compressed by a wafer is integrally formed.

しかして、本実施例においては、環状摺動板部１３の１
直径Ｌ１に沿う部位の内部に、板厚方向の中１１１円周
方向の中ｗ１．及び半径方向の深さｈｌ　の凹所１３ａ
、１３ａが設けていて、環状摺動板部１３の１直径Ｌ１
に沿う部位１０ａ、１０ａの質量及び剛性が他の部位の
それに比して所定量低くされている。Therefore, in this embodiment, one of the annular sliding plate parts 13 is
Inside the portion along the diameter L1, there is a center 111 in the thickness direction, and a center w1 in the circumferential direction. and a recess 13a with a radial depth hl
, 13a are provided, and one diameter L1 of the annular sliding plate portion 13 is provided.
The mass and rigidity of the portions 10a, 10a along the line are made lower by a predetermined amount than those of other portions.

ところで、上記構成のディスクロータ１０においては、
」二記した部位１０ａ、１０ａが、その質量及び剛性を
他の部位のそれに比して所定量低されているために、木
に振動モートの節又は腹となり、全ての振動モートにお
いて一対の節又はｙｓ、＜ｔｏａ、１０ａ）がディスク
ロータ１０に対して固定される。したがって、このディ
スクローク１０によれは、頭書に述べた現象によって全
ての撮動モートにおいてその全ての節又は腹〔上記した
一対の節又は腹四Ｑａ、１０ａ）が含まれる〕をディス
クロータｌＯに対して固定することができ、回転するデ
ィスクロータｌＯと一体的に全ての振動モートの節又は
膿を回転させることができて、全ての直径節の定宙な振
動モートの発生を防止することができる。By the way, in the disc rotor 10 having the above configuration,
” Since the parts 10a and 10a described in 2 have their mass and rigidity lowered by a predetermined amount compared to those of other parts, they become nodes or antinodes of vibration motes in the tree, and all vibration motes have a pair of nodes. or ys, <toa, 10a) is fixed to the disc rotor 10. Therefore, due to the phenomenon described in the introduction, this disc rotor 10 transfers all nodes or antinodes (including the above-mentioned pair of nodes or anodes 4Qa, 10a) to the disk rotor lO in all photographing modes. It can be fixed to the rotating disc rotor lO and all the vibration mote nodes or pus can be rotated integrally with the rotating disc rotor lO, thereby preventing the generation of fixed-air vibration motes of all diameter nodes. can.

上記構成のディスクロータｌＯ１特に、径１３゜が２０
４ｍｍ、環状摺動板部１３の板厚’］’、が１０ｍｍ、
環状摺動板部１３の半径方向の長さＨ６が４ｊｍｍであ
って、利質が鋳鉄であるディスクロークにおいて、凹所
１３ａ、１３ａの各寸法ｔ１゜ｗｌ、ｈｌ　を種々変更
して実験した結果、０．０５≦ｖ／Ｉ／／Ｄｏ≦ｏ、ｌ
ｓ、’％、≧０．０５．ヌ。≦０゜５のとき、全ての振
動モートにおいてその全ての節、腹をディスクロータ１
０に対して良好に固定することができた。In particular, the disc rotor lO1 with the above configuration has a diameter of 13°.
4 mm, the plate thickness of the annular sliding plate part 13 ']' is 10 mm,
Results of experiments with various dimensions t1゜wl, hl of the recesses 13a, 13a in a disc loak in which the radial length H6 of the annular sliding plate portion 13 is 4 mm and the material is cast iron. , 0.05≦v/I//Do≦o, l
s,'%,≧0.05. Nu. When ≦0゜5, all nodes and antinodes of all vibration motors are connected to disc rotor 1.
It was possible to fix it well with respect to 0.

なお、上記実施例においては、ソリッド型のディスクロ
ータ１０において、そのＩ直径り、に沿う部位１０ａ、
１０ａの内部に、所定の大きさの凹所１３ａ、１３ａを
設けて、環状摺動板部１３の部位１０ａ、ｉｏａの質量
及び剛性を他の部位のそれに比して所定量低くしたが、
本発明の実施に際しては、第３図にて示したように、ソ
リッド型のディスクロータ２０において、環状摺動板部
２３の１直径Ｌ２に沿う部位２０ａ、、２０ａの内部に
穴径ｄ２．半径方向の深さＨ２の穴２３ａ。In the above embodiment, in the solid disc rotor 10, the portion 10a along the I diameter,
Recesses 13a, 13a of a predetermined size are provided inside the annular sliding plate 13, so that the mass and rigidity of the portion 10a, ioa of the annular sliding plate portion 13 are lowered by a predetermined amount compared to those of other portions.
In carrying out the present invention, as shown in FIG. 3, in a solid type disc rotor 20, a hole having a diameter d2. Hole 23a with radial depth H2.

２３ａを設けて、１直径Ｌ２　に沿う部位２０ａ。23a is provided, and a portion 20a along one diameter L2.

２０ａの質量及び剛性を他の部位のそれに比し一ζ所定
量低くしたり、第４図にて示したように、ソリッド型の
ディスクローク３０において、環状摺動板部３３の１直
径り、に沿う部位３０ａ、３０ａの内部に、穴径ｄＪ、
半径方向の深さＪ　の穴３３ａ、３３ａを間隔θにてそ
れぞれ２１１１ｉ１設りて、■直径ＬＪ　に沿う部位３
０ａ、３０ａの質量及び剛性を他の部位のそれに比して
所定量低くしてもよく、これら各ディスクローク２０．
３０においても、上記したディスクローク１０と同様の
作用・効果が１ηられる。なお、これらのディスクロー
タ２０．３０においても、各穴２３ａ、３３ａの最適な
寸法（Ｈ２、Ｈ２、ｄｉ　、　　ｈ、３　、θの値）は
、」二記したディスクロータ１０と同様に、実験に基づ
いこ定められるものである。The mass and rigidity of 20a are lowered by a predetermined amount of 1ζ compared to those of other parts, and as shown in FIG. Inside the portions 30a, 30a along the hole diameter dJ,
Holes 33a and 33a with a depth J in the radial direction are provided at intervals of θ, respectively, and a portion 3 along the diameter LJ is formed.
The mass and rigidity of each of these disc cloaks 20.
30 also has the same actions and effects as the disc cloak 10 described above. In addition, in these disc rotors 20 and 30, the optimal dimensions (values of H2, H2, di, h, 3, θ) of each hole 23a, 33a were determined through experiments as in the case of the disc rotor 10 described in 2. This is determined based on the following.

また・本発明の実施に際しては、上記した凹所１３ａ、
穴２３ａ又は穴３３ａに、当該ディスクロ−ク１０，２
０．３０と同種の＋Ａ料で形成されたインサートを埋設
して、環状摺動板部１３，２３、又は３３の１　ｉｆ径
り、　、　　Ｌ、　、又は１１．に沿う部位１０ａ、ｌ
ｏａ、２０　ａ、　　２０　ａ、又は３Ｑａ、３０ａの
剛性のみを他の部位の剛性に比し°ζ所定量低くしても
、上記した各ディスクロータ１０．２０．３０と同様の
作用・効果が得られる。In addition, when implementing the present invention, the above-mentioned recess 13a,
The disc cloak 10, 2 is inserted into the hole 23a or the hole 33a.
An insert made of +A material of the same type as 0.30 is embedded and the annular sliding plate portion 13, 23, or 33 has a diameter of 1 if, L, or 11. The parts 10a, l along
Even if only the rigidity of oa, 20a, 20a, or 3Qa, 30a is lowered by a predetermined amount compared to the rigidity of other parts, the same actions and effects as those of each disc rotor 10, 20, and 30 described above can be obtained. can get.

またディスクロータ１０において凹所１３ａの巾ｔ１　
を小さくすれば、部位１０ａ、１０ａの質量をほとんど
変化させることなく、部位１０ａ、１０ａの剛性のみを
所定量低くすることができるため、このようにして本発
明を実施することも可能である。Also, in the disc rotor 10, the width t1 of the recess 13a
By reducing , only the rigidity of the parts 10a, 10a can be lowered by a predetermined amount without substantially changing the mass of the parts 10a, 10a, so it is also possible to implement the present invention in this way.

第５図及び第６図は、ヘンチレーテノト型のディスクロ
ークに本発明を実施した例を示していて、このディスク
ローク４０においては、取付孔４１〜４１を有するハブ
部４２の外周に、所定の板厚′ｒ１　と所定の径Ｄ１を
有して一対のブレーキパッド（図示せず）により挟圧さ
れる環状摺動板部４３が一対的に形成されている。また
環状摺動板部４３の内部には、放射状に延びる多数の冷
却フィン４３ａ〜４３ａが円周方向にて所定間隔へだて
て偶数個、すなわち１直径Ｌヰに対して線対称に設けら
れ、各冷却フィン４３８間が通気孔４３ｂとなっている
。FIGS. 5 and 6 show an example in which the present invention is applied to a Henchleit-type disc cloak 40. In this disc cloak 40, a predetermined plate is attached to the outer periphery of a hub portion 42 having mounting holes 41 to 41. A pair of annular sliding plate portions 43 having a thickness 'r1 and a predetermined diameter D1 are formed to be pressed between a pair of brake pads (not shown). Further, inside the annular sliding plate part 43, a large number of radially extending cooling fins 43a to 43a are provided in an even number at predetermined intervals in the circumferential direction, that is, in line symmetry with respect to one diameter L. Ventilation holes 43b are formed between the cooling fins 438.

しかして、本実施例においては、■直径り牛に沿う冷却
フィン４３’　８間の円周方向における間隔αが他の冷
却フィン４３ａ間の円周方向における間隔βより所定量
広くされていて、環状摺動板部４３の１直径に沿う部位
４０ａ、４０ａの質量及び剛性が他の部位のそれに比し
゛ζ所定量低くされている。このため、このディスクロ
ーク４０においても、上記した各ディスクロータ１０，
２０゜３０と同様の作用・効果が得られ、全ての直径節
の定品な振動モードを防止することができる。Therefore, in this embodiment, (1) the interval α in the circumferential direction between the cooling fins 43' 8 along the diameter is made wider by a predetermined amount than the interval β in the circumferential direction between the other cooling fins 43a; The mass and rigidity of the portions 40a, 40a along one diameter of the annular sliding plate portion 43 are made lower by a predetermined amount than those of other portions. Therefore, also in this disc rotor 40, each of the above-mentioned disc rotors 10,
The same action and effect as 20°30 can be obtained, and regular vibration modes of all diameter nodes can be prevented.

なお、本発明の実施に際しては、第７図にて示したよう
に、ヘンチレーテノド型のディスクロータ５０において
、ｌ直径Ｌ５に沿う一対の冷却フィン５３ａ１の半径方
向の長さＪ２＋を他の冷却フィン５３ａ２　（−＝ｌＳ
は図示省略されている）の長さて２より所定量短かくし
たり、第８図にて示したように、ヘンチレーテノト型の
ディスクロータ６０において、■直径Ｌ６に沿う一対の
冷却フィン６３ａ、の肉厚ｍ１を他の冷却フィン６３ａ
２（一部は図示省略されている）の肉厚ｍ２により所定
量薄くして、環状摺動板部５３又は６３の１直径Ｌ５又
はＬ６に沿う部位５０ａ、ｓｏａ又は６０ａ、６０ａの
質量及び剛性を他の部位の質量及び剛性に比して所定量
低くしても、上記した各ディスクロータ１０〜４０と同
様の作用・効果が得られる。また、本発明の実施に際し
ては、第９図及び第１０図にて示したように、ヘンチレ
ーテント型のディスクロータ７０において、■直径Ｌ７
に沿う一対の冷却フィン７３ａに所定の中ｔλ及び深さ
ｈ４　の切込７３ａ１を設けて、環状摺動板部７３の１
直径Ｌ７　に沿う部位７０ａ、７０ａの質量及び剛性を
他の部分の質量及び剛性に比して所定量低くしても、上
記した各ディスクロータ１０〜６０と同様の作用・効果
が得られる。このディスクロータ７０において、切込７
３ａ１の中Ｌ２を小さくすれば、部位７０ａ、７０ａの
質量をほとんど変化させることなく、部位７０ａ、７０
ａの剛性のみを低くすることができて、一対の節又は腹
をディスクロータ７０に対して固定することができるた
め、このようにして本発明を実施することも可能である
。In carrying out the present invention, as shown in FIG. 7, in the henchless-node type disc rotor 50, the radial length J2+ of the pair of cooling fins 53a1 along the diameter L5 is set to the length J2+ of the other cooling fin 53a2. (-=lS
(not shown) may be made shorter by a predetermined amount than 2, or as shown in FIG. m1 as the other cooling fin 63a
The mass and rigidity of the portion 50a, soa or 60a, 60a along one diameter L5 or L6 of the annular sliding plate portion 53 or 63 is Even if it is lowered by a predetermined amount compared to the mass and rigidity of other parts, the same operation and effect as each of the disc rotors 10 to 40 described above can be obtained. Further, when carrying out the present invention, as shown in FIGS. 9 and 10, in the Henchley tent type disc rotor 70,
A notch 73a1 with a predetermined medium tλ and depth h4 is provided in a pair of cooling fins 73a along the annular sliding plate portion 73.
Even if the mass and rigidity of the portions 70a, 70a along the diameter L7 are lowered by a predetermined amount compared to the mass and rigidity of other portions, the same functions and effects as those of each of the disc rotors 10 to 60 described above can be obtained. In this disc rotor 70, the notch 7
By reducing the middle L2 of 3a1, the parts 70a, 70 can be reduced without changing the mass of the parts 70a, 70a.
It is also possible to implement the present invention in this way, since only the rigidity of a can be lowered and the pair of nodes or antinodes can be fixed to the disc rotor 70.

なお、上記した各ヘンチレーテノト型のディスクローク
４０，５０，６０．７０においても、冷却フィン４３ａ
間の最適な間隔（α）、冷却フィン５３　ａｌ　の最適
な長さく１１）冷却フィン６３ａＩ　　の最適な肉厚（
ｍ、）、切込７３ａノ　の最適な中（Ｌ２）及び深さく
ｈ４）は、上記したディスクロータｌＯと同様に、実験
に基づいて定められるものである。It should be noted that in each of the above-mentioned Henchleit type disc cloaks 40, 50, 60.70, the cooling fins 43a are
11) Optimum spacing (α) between cooling fins 53a, optimal length of cooling fins 53al, and optimal wall thickness of cooling fins 63aI (11)
The optimum medium (L2) and depth h4) of the cutting depth 73a) are determined based on experiments, as in the case of the disc rotor IO described above.

【図面の簡単な説明】[Brief explanation of drawings]

第１図は本発明を実施してなるソリノ１型ディスクロー
タの正面図、第２図は第１図の■−■線に沿う縦断面図
、第３図及び第４図は本発明を実施してなる他のソリソ
ト型ディスクロークの正面図、第５図は本発明を実施し
てなるベンチレーテッド型ディスクロークの正面図、第
６図は第５図のＶ［−Ｖｌ線に沿う断面図、第７図、第
８図及び第９図は本発明を実施してなる他のベンチレー
テッド型ディスクロークの正面図、第１Ｏ図は第９図の
Ｘ−Ｘ線に沿う部分断面図である。 符号の説明 １０、２０．３０．４０．５０．６０．７０・・・ディ
スクロータ、１３，２３，３３，４３，５３．６３．７
３・・・環状摺動板部、４３ａ、５３ａ＋　　、５３ａ
２．６３ａ＋　　、６３ａ２　．７３ａ・・　・冷却フ
ィン、ＬＩ　　、ｔ、２．ＬＪ　、Ｌ４　、’４；　。 、　　　Ｌ６．Ｌ７　・・−１直径、１０ａ、２０ａ、
３０ａ、４０ａ、５０ａ、６０ａ、１０ａ・・・環状摺
動板部の１直径に沿う部位、１３ａ・・・凹所、２３ａ
、３３ａ・・・穴、α・・・冷却フィンの円周方向にお
ける間隔、治、、、冷却フィンの半径方向の長さ、ｍ　
・・・冷却フィンの肉厚、ｔ２　　・・・冷却フィンに
設けた切込の中、ｈ、・・・冷却フィンに設けた切込の
深さ。 出願人　トヨタ自動車株式会社 代理人　弁理士　長　谷　照　− 第５図　　　　　第６図Fig. 1 is a front view of a Solino type 1 disc rotor in which the present invention is implemented, Fig. 2 is a vertical sectional view taken along the line ■-■ in Fig. 1, and Figs. 3 and 4 are in which the present invention is implemented. FIG. 5 is a front view of a ventilated disk cloak obtained by implementing the present invention, and FIG. 6 is a cross section taken along the line V[-Vl in FIG. 5. 7, 8, and 9 are front views of other ventilated disk cloaks according to the present invention, and FIG. 1O is a partial sectional view taken along the line X-X in FIG. 9. It is. Explanation of symbols 10, 20.30.40.50.60.70... Disc rotor, 13, 23, 33, 43, 53.63.7
3... Annular sliding plate part, 43a, 53a+, 53a
2.63a+, 63a2. 73a... Cooling fin, LI, t, 2. LJ, L4, '4;. , L6. L7...-1 diameter, 10a, 20a,
30a, 40a, 50a, 60a, 10a... Portion along one diameter of the annular sliding plate portion, 13a... Recess, 23a
, 33a... Hole, α... Spacing of the cooling fins in the circumferential direction, , , Length of the cooling fins in the radial direction, m
... Thickness of the cooling fin, t2 ... Inside the cut made in the cooling fin, h... Depth of the cut made in the cooling fin. Applicant Toyota Motor Corporation Representative Patent Attorney Teru Hase - Figure 5 Figure 6

Claims (7)

【特許請求の範囲】[Claims] （１）所定の板厚と所定の径を有して一対のブレーキバ
ンドにより挟圧される環状摺動板部をハブ部の外周に一
体的に形成してなるディスクブレーキ用ディスクロータ
において、前記環状摺動板部の１直径に沿う部位の剛性
を他の部位の剛性に比して所定量低くしたことを特徴と
するディスクブレーキ用ディスクロータ。(1) In a disc rotor for a disc brake, the annular sliding plate part having a predetermined thickness and a predetermined diameter and being pressed between a pair of brake bands is integrally formed on the outer periphery of the hub part. A disc rotor for a disc brake, characterized in that the rigidity of a portion along one diameter of an annular sliding plate portion is lowered by a predetermined amount than the rigidity of other portions. （２）前記ディスクブレーキ用ディスクロータがソリッ
ド型のディスクロータであって、前記環状摺動板部の１
直径に沿う部位の内部に所定の板厚方向の中、所定の円
周方向の中及び所定の半径方向の深さの凹所を設けて、
１直径に沿う部位の剛性を他の部位の剛性に比して所定
量低くしたことを特徴とする特許請求の範囲第１項に記
載のディスクブレーキ用ディスクローク(2) The disc rotor for a disc brake is a solid disc rotor, and one of the annular sliding plate parts
A recess is provided inside the portion along the diameter at a predetermined thickness direction, a predetermined circumferential direction, and a predetermined radial depth,
A disc brake disc claw according to claim 1, wherein the rigidity of a portion along one diameter is lowered by a predetermined amount than the rigidity of other portions. （３）前記ディスクブレーキ用ディスクロータがソリッ
ド型のディスクロータであって、前記環状摺動板部の１
直径に沿う部位の内部に所定の径及び所定の半径方向の
深さの穴を設りて、ｌ直径に沿う部位の剛性を他の部位
の剛性に比して所定量低くしたことを特徴とする特許請
求の範囲第１項に記載のディスクブレーキ用ディスクロ
ーク。(3) The disc rotor for a disc brake is a solid disc rotor, and one of the annular sliding plate parts
A hole having a predetermined diameter and a predetermined radial depth is provided inside the portion along the diameter, so that the rigidity of the portion along the diameter is lowered by a predetermined amount compared to the rigidity of other portions. A disc claw for a disc brake according to claim 1. （４）前記ディスクブレーキ用ディスクロータが前記環
状摺動板部の内部に放射状に延ひる多数の冷却フィンを
円周方向に゛ζ所定間隔へだてて偶数個備えてなるヘン
チレーテソト型のディスクロータであって、ｌ直径に沿
う前記冷却フィン間の円周方向における間隔を他の冷却
フィン間の円周方向における間隔より所定量広くして、
前記環状摺動板部の１直径に沿う部位の剛性を他の部位
の剛性に比して所定量低くしたことを特徴とする特許請
求の範囲第１項に記載のディスクブレーキ用ディスクロ
ータ。(4) The disc rotor for a disc brake is a henchless type disc rotor comprising an even number of cooling fins extending radially inside the annular sliding plate part and spaced at predetermined intervals in the circumferential direction. and making the interval in the circumferential direction between the cooling fins along the l diameter wider by a predetermined amount than the interval in the circumferential direction between other cooling fins,
2. The disc rotor for a disc brake according to claim 1, wherein the rigidity of a portion along one diameter of the annular sliding plate portion is lowered by a predetermined amount than the rigidity of other portions. （５）前記ディスクブレーキ用ディスクロータが前記環
状摺動板部の内部に放射状に延びる多数の冷却フィンを
円周方向にて所定間隔へだてて偶数（固備えてなるヘン
チレーテソｌ°型のディスクロータであって、■直径に
沿う一対の冷却フィンの半径方向の長さを他の冷却フィ
ンの半径方向の長さより所定量短かくして、前記環状摺
動板部の１直径に沿う部位の剛性を他の部位の剛性に比
して所定量低くしたことを特徴とする特許請求の範囲第
１項に記載のディスクブレーキ用ディスクロータ。(5) The disc rotor for disc brakes is a Henchley Tesol type disc rotor in which a large number of cooling fins extending radially inside the annular sliding plate portion are arranged at predetermined intervals in the circumferential direction to provide an even number of cooling fins. (1) The radial length of the pair of cooling fins along the diameter is made shorter by a predetermined amount than the radial length of the other cooling fin, so that the rigidity of the portion along one diameter of the annular sliding plate portion is made shorter than the other. The disc rotor for a disc brake according to claim 1, characterized in that the rigidity of the disc rotor is lowered by a predetermined amount compared to the rigidity of the parts. （６）前記ディスクブレーキ用ディスクロータが前記環
状摺動板部の内部に放射状に延びる多数の冷却フィンを
円周方向にて所定間隔へたてて偶数＋１１ｉ１　（ＩＩ
Ｉえてなるヘンチレーテソド型のディスクロータであっ
て、■直径に沿う一対の冷却フィンの肉厚を他の冷却フ
ィンの肉厚より所定量薄くして、前記環状摺動板部の１
直径に沿う部位の剛性を他の部位の剛性に比して所定量
低くしたことを特徴とする特許請求の範囲第１項に記載
のディスクブレーキ用ディスクロータ。(6) The disc rotor for a disc brake has a large number of cooling fins extending radially inside the annular sliding plate part, with an even number +11i1 (II
1. A henchless rotor type disc rotor comprising: 1) the wall thickness of a pair of cooling fins along the diameter is made thinner by a predetermined amount than the wall thickness of the other cooling fins;
The disc rotor for a disc brake according to claim 1, wherein the rigidity of a portion along the diameter is lowered by a predetermined amount than the rigidity of other portions. （７）前記ディスクブレーキ用ディスクロータが前記環
状摺動板部の内部に放射状に延びる多数の冷却フィンを
円周方向にて所定間隔へだてて偶数個備えてなるヘンチ
レーテノド型のディスクロークであって、■直径に沿う
一対の冷却フィンに所定の中及び深さの切込を設けて、
前記環状摺動板部の１直径に沿う部位の剛性を他の部位
の剛性に比して所定量低くしたことを特徴とする特許請
求の範囲第１項に記載のディスクブレーキ用ディスクロ
ータ。(7) The disc rotor for disc brakes is a henchless-nosed disc rotor comprising an even number of cooling fins extending radially inside the annular sliding plate part at predetermined intervals in the circumferential direction, ■A pair of cooling fins along the diameter are provided with a predetermined medium and deep cut,
2. The disc rotor for a disc brake according to claim 1, wherein the rigidity of a portion along one diameter of the annular sliding plate portion is lowered by a predetermined amount than the rigidity of other portions.
JP12528682A 1982-07-19 1982-07-19 Disk rotor for disk brake Pending JPS5917035A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP12528682A JPS5917035A (en) 1982-07-19 1982-07-19 Disk rotor for disk brake
GB08319266A GB2125911B (en) 1982-07-19 1983-07-15 Rotary disc for disc brake assembly
DE19833325831 DE3325831A1 (en) 1982-07-19 1983-07-18 BRAKE DISC

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP12528682A JPS5917035A (en) 1982-07-19 1982-07-19 Disk rotor for disk brake

Publications (1)

Publication Number Publication Date
JPS5917035A true JPS5917035A (en) 1984-01-28

Family

ID=14906312

Family Applications (1)

Application Number Title Priority Date Filing Date
JP12528682A Pending JPS5917035A (en) 1982-07-19 1982-07-19 Disk rotor for disk brake

Country Status (3)

Country Link
JP (1) JPS5917035A (en)
DE (1) DE3325831A1 (en)
GB (1) GB2125911B (en)

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JPS58221026A (en) * 1982-06-15 1983-12-22 Toyota Motor Corp Disk rotor for disk brake
DE3576187D1 (en) * 1985-06-10 1990-04-05 Motor Wheel Corp BRAKE DISC WITH HARMONIC VIBRATION SUPPRESSION.
GB2232449B (en) * 1989-06-07 1993-06-16 Bba Group Plc A friction brake assembly and a method of alleviating brake squeal noise in such an assembly
JPH06185552A (en) * 1991-07-23 1994-07-05 Akebono Brake Res & Dev Center Ltd Disc rotor for preventing generation of noise
JP3480264B2 (en) * 1997-09-18 2003-12-15 日産自動車株式会社 Ventilated rotor
DE19822577A1 (en) * 1998-05-20 1999-12-09 Daimler Chrysler Ag Squeak-resistant brake disc
JP3777811B2 (en) * 1998-07-29 2006-05-24 日産自動車株式会社 Brake disc rotor
US8668058B2 (en) 2005-03-30 2014-03-11 Federal-Mogul Worldwide, Inc. Vented disc brake rotor
US20100252376A1 (en) 2009-04-02 2010-10-07 Ford Global Technologies Llc Vehicle Braking Assembly
US9175733B2 (en) 2009-04-02 2015-11-03 Ford Global Technologies, Llc Transmission clutch assemblies with squawk reduction techniques
DE102010060781A1 (en) * 2010-11-24 2012-05-24 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ventilated brake disc for motor car, has connection node and rib element which are arranged in periphery of brake disc to locally change rigidity of brake disc in circumferential direction or in radial direction
US8857577B2 (en) 2011-12-21 2014-10-14 Brembo North America, Inc. Damped brake rotor

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JPS51137032A (en) * 1975-05-21 1976-11-26 Hitachi Ltd A carburetor having a throttle valve shaft torque control apparatus

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JPS51137032A (en) * 1975-05-21 1976-11-26 Hitachi Ltd A carburetor having a throttle valve shaft torque control apparatus

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH075470U (en) * 1993-06-30 1995-01-27 貨泉プラスチック株式会社 Eating device

Also Published As

Publication number Publication date
GB8319266D0 (en) 1983-08-17
DE3325831A1 (en) 1984-01-26
GB2125911B (en) 1986-01-15
GB2125911A (en) 1984-03-14

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