JPH094660A - Disk brake - Google Patents
Disk brakeInfo
- Publication number
- JPH094660A JPH094660A JP15336395A JP15336395A JPH094660A JP H094660 A JPH094660 A JP H094660A JP 15336395 A JP15336395 A JP 15336395A JP 15336395 A JP15336395 A JP 15336395A JP H094660 A JPH094660 A JP H094660A
- Authority
- JP
- Japan
- Prior art keywords
- vibration
- friction member
- pad
- disc
- disk
- 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
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
- F16D65/0006—Noise or vibration control
- F16D65/0012—Active vibration dampers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Braking Arrangements (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車両等の制動に用いる
ディスクブレーキ、特に、ブレーキ振動を減じる制振装
置を付加して制動時の異音（いわゆる鳴き）の発生を防
止するタイプのディスクブレーキに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disc brake used for braking a vehicle or the like, and more particularly to a disc brake of a type for preventing abnormal noise (so-called squeal) from being generated by adding a vibration damping device for reducing brake vibration. Regarding brakes.
【０００２】[0002]
【従来の技術】ディスクブレーキにおいては、様々な原
因により、制動時にディスクロータ（本発明ではこれを
単にディスクと云う）とこれに摺接させる摩擦部材（パ
ッド）に振動が生じて鳴き現象を発生することがあり、
従って、この鳴きを止めるために様々な工夫がなされて
いる。2. Description of the Related Art In a disc brake, a squeal phenomenon is generated due to various causes due to vibrations of a disc rotor (which is simply referred to as a disc in the present invention) and a friction member (pad) slidingly contacting the disc rotor during braking. May
Therefore, various measures have been taken to stop this squeal.
【０００３】例えば、実開平２−１３４３３１号公報に
は、パッドをディスク径方向に押圧して拘束する手段を
設け、制動時にその手段が非制動時よりも強い力、具体
的には、ブレーキピストンに作用させるブレーキ液圧に
比例した力でパッドを拘束するようにしてパッドの振動
を止める技術が示されている。For example, Japanese Utility Model Laid-Open No. 2-134331 provides means for pressing and constraining a pad in the radial direction of a disk, and the means has a stronger force during braking than that during non-braking, specifically, a brake piston. A technique is disclosed in which the vibration of the pad is stopped by restraining the pad with a force proportional to the brake fluid pressure applied to the pad.
【０００４】また、特開平４−５４３２４号公報等に
は、圧電素子を用いてパッドの振動を検出し、その検出
信号に基づき、圧電素子でパッドをブレーキ振動が打ち
消される方向に加振して鳴きを抑える制振装置が示され
ている。Further, in Japanese Patent Laid-Open No. 4-54324 and the like, vibration of a pad is detected by using a piezoelectric element, and based on the detection signal, the pad is excited by the piezoelectric element in a direction in which the brake vibration is cancelled. A damping device that suppresses squeal is shown.
【０００５】[0005]
【発明が解決しようとする課題】パッドの振動を振動検
出信号に基づく加振を行って減衰させる方法は、高精度
の振動検出と正確な加振を必要とし、思い通りの制御を
行うのが難しい。The method of dampening the vibration of the pad by vibrating it based on the vibration detection signal requires high-precision vibration detection and accurate vibration, and it is difficult to control as desired. .
【０００６】一方、パッドを拘束する方法は、パッドの
振動の動き代そのものを無くしてしまうので前者の方法
よりも制御がし易いが、実開平２−１３４３３１号公報
に示されるように、拘束力をブレーキ液圧に比例して高
める方法ではパッドの振動が確実に止まることが保証さ
れない。On the other hand, the method of restraining the pad is easier to control than the former method because it eliminates the movement allowance of the vibration of the pad, but as shown in Japanese Utility Model Laid-Open No. 2-134331, the restraining force is reduced. It is not guaranteed that the vibration of the pad is stopped by the method of increasing the pressure in proportion to the brake fluid pressure.
【０００７】パッドの振動はブレーキ液圧に比例して大
きくなるものではなく、ブレーキ液圧が低くても大きな
振動が起こることがある。従って、この方法では、拘束
力がパッドを動かそうとする力に負けてパッドの振動が
起こることがあり、鳴きを完全に止めることができな
い。このほかにも様々な鳴き対策が考えられているが、
現在に至っても真に満足できるものはできていないのが
実状である。The vibration of the pad does not increase in proportion to the brake fluid pressure, and a large vibration may occur even if the brake fluid pressure is low. Therefore, in this method, the restraint force may lose the force for moving the pad to cause vibration of the pad, and the squeal cannot be completely stopped. In addition to this, various squeal measures are being considered,
The reality is that none of them are truly satisfying even today.
【０００８】そこで、本発明は、パッド拘束の適切化を
図ってディスクブレーキの制動時の鳴きを完全に止める
ことを課題としている。[0008] Therefore, an object of the present invention is to make proper pad restraint to completely stop the squeal of the disc brake during braking.
【０００９】[0009]
【課題を解決するための手段】上記の課題を解決するた
め、本発明においては、ディスクに摺接させる摩擦部材
の振動を検出する装置と、摩擦部材を拘束する手段と、
その拘束手段の制御装置とを具備させ、前記制御装置に
よる制御で前記拘束手段による摩擦部材の拘束が、前記
振動検出装置による検出振動の振幅に応じた力で行われ
るものにしたのである。In order to solve the above-mentioned problems, in the present invention, a device for detecting the vibration of a friction member which is in sliding contact with a disk, a means for restraining the friction member,
The restraint means control device is provided, and the friction member is restrained by the restraint means under the control of the control device by a force corresponding to the amplitude of the vibration detected by the vibration detection device.
【００１０】このディスクブレーキは、振動検出装置を
摩擦部材のディスク接線方向振動を検出する位置に設
け、前記拘束手段は摩擦部材のトルク伝達面をディスク
接線方向に加圧して拘束する構成にするとより望ましい
ものになる。In this disc brake, a vibration detecting device is provided at a position for detecting vibration of the friction member in the tangential direction of the disc, and the restraining means restrains the torque transmitting surface of the friction member by pressing in the tangential direction of the disc. Would be desirable.
【００１１】また、ディスクを間にして対向配置される
対の摩擦部材の振動検出と拘束手段による拘束を、各摩
擦部材毎に独立して行う構成も好ましい。Further, it is also preferable that the vibration detection and the restraint by the restraining means of the pair of friction members arranged to face each other with the disc in between are independently performed for each friction member.
【００１２】[0012]
【作用】ディスクブレーキの鳴きは、摩擦振動であるス
ティックスリップ振動が発端となって振動が始まり、そ
れが自励振動となって鳴き音が生じると考えられる。そ
の証拠に、鳴きが発生する直前には、摩擦部材（パッ
ド）にスティックスリップ振動と思われるディスク周方
向及びそれに連動したディスク軸方向の特徴的振動が生
じる。本発明では、この振動を検出装置で検出し、拘束
手段により検出振動に応じた力で摩擦部材を拘束するの
で、拘束力が摩擦部材を動かそうとする力に負けること
がなく、摩擦部材の振動が自励振動となる前に確実に押
え込まれて鳴きが発生しない。It is considered that the squeal of the disc brake starts from the stick-slip vibration, which is a frictional vibration, and starts to vibrate, which then becomes a self-excited vibration to generate a squeal. The evidence is that, immediately before the squeal occurs, the friction member (pad) produces characteristic vibrations in the disk circumferential direction, which are considered to be stick-slip vibrations, and in the disk axial direction which is linked to it. In the present invention, this vibration is detected by the detection device, and the friction member is constrained by the force corresponding to the detected vibration by the constraining means. Therefore, the constraining force does not lose the force for moving the friction member, Before the vibration becomes self-excited vibration, it is securely pressed in and no squeaking occurs.
【００１３】なお、ディスクブレーキでは、設置可能な
拘束手段の大きさ及び設置場所が制限される。これを考
えると摩擦部材をディスク軸方向に押圧して拘束する構
造では鳴きの抑制効果を充分に引き出すのが難しい。即
ち、鳴きの振動モードによって最適拘束点が変化し、ま
た、摩擦部材の全域の中で拘束を行える位置、面積は限
られており、鳴きのモードに応じて拘束点を移動させる
ことも困難なため、最も効果のある位置を拘束すること
ができず、制振効率が高まらない。In the disc brake, the size of the restraint means that can be installed and the installation place are limited. Considering this, it is difficult to sufficiently bring out the squeal suppressing effect in the structure in which the friction member is pressed and restrained in the disc axial direction. That is, the optimum constraint point changes depending on the vibration mode of the squeal, and the position and area where the constraint can be performed are limited in the entire area of the friction member, and it is difficult to move the constraint point according to the squeal mode. Therefore, the most effective position cannot be restricted, and the vibration damping efficiency does not increase.
【００１４】これに対し、トルク伝達面をディスク接線
方向に加圧して摩擦部材を拘束する請求項２の構成であ
ればトルク伝達面の面積は狭く、その面の全域又はほぼ
全域を拘束できるため、鳴きのモードが変化しても制振
効率は変わらず、あらゆる周波数の鳴きに対処できる。On the other hand, if the friction member is constrained by pressing the torque transmission surface in the tangential direction of the disk, the area of the torque transmission surface is small and the entire surface or almost the entire surface can be restricted. , Even if the squealing mode changes, the damping efficiency does not change, and it is possible to deal with squealing at any frequency.
【００１５】また、ディスクの両側におかれる２つの摩
擦部材は、鳴きが生じて共振状態となる前には必ずしも
同調して振動するとは限らないが、振動検出と拘束を各
摩擦部材について個々に行う請求項３の構成であれば、
各摩擦部材の振幅が違っていても安定した制御が行われ
る。Further, the two friction members placed on both sides of the disk do not necessarily vibrate in synchronism before a squeal is generated and a resonance state is generated, but vibration detection and restraint are individually performed for each friction member. According to the configuration of claim 3,
Stable control is performed even if the amplitude of each friction member is different.
【００１６】[0016]
【実施例】図１に、本発明を浮動型ディスクブレーキに
適用した例を示す。図１（ａ）は、ブレーキの全体をア
ウタ側からディスク軸方向に見た図であって、パッド
（摩擦部材）１は、ディスク接線方向両端の耳部をトル
クメンバ２に設けたガイド溝に緩く嵌合させてディスク
軸方向に摺動可能に支持されている。また、キャリパ７
は、スライドピン８（図１（ｂ）参照）をトルクメンバ
のピン穴（図示せず）に挿入してトルクメンバ２でディ
スク軸方向に摺動可能に支持しており、キャリパのイン
ナ側のシリンダに挿入したブレーキピストン（これも図
示せず）でインナ側のパッドをディスクに押し当て、そ
の際の反力でキャリパ７がインナ側にスライドしてキャ
リパのアウタ爪がアウタ側のパッドをディスクに押圧す
る構造になっている。1 shows an example in which the present invention is applied to a floating disc brake. FIG. 1A is a view of the entire brake as viewed from the outer side in the disc axial direction. The pad (friction member) 1 has ears at both ends in the disc tangential direction as guide grooves provided in the torque member 2. It is loosely fitted and supported slidably in the disc axial direction. Also, caliper 7
Inserts a slide pin 8 (see FIG. 1B) into a pin hole (not shown) of the torque member to support the torque member 2 slidably in the disc axial direction. The brake piston (also not shown) inserted into the cylinder presses the inner pad against the disc, and the reaction force at that time causes the caliper 7 to slide to the inner side, causing the outer pawl of the caliper to slide the outer pad against the outer pad. It is structured to be pressed against.
【００１７】このブレーキのトルクメンバ２のガイド溝
の部分に、パッド１のトルク伝達面に接する振動検出器
６が検出面をトルク受け面２ａから僅かに突出させて埋
め込まれている。この振動検出器６は制御回路５に接続
されている。また、制御回路５は油圧発生装置４に、そ
の油圧発生装置４はトルクメンバ２に設けたシリンダ９
に各々接続され、このシリンダ９にディスク接線方向に
進退する小型の拘束用ピストン３が挿入されている。A vibration detector 6 contacting the torque transmitting surface of the pad 1 is embedded in the guide groove portion of the torque member 2 of the brake with the detecting surface slightly protruding from the torque receiving surface 2a. The vibration detector 6 is connected to the control circuit 5. Further, the control circuit 5 is provided in the hydraulic pressure generator 4, and the hydraulic pressure generator 4 is provided in the cylinder 9 provided in the torque member 2.
, And a small restraining piston 3 that moves forward and backward in the disc tangential direction is inserted into the cylinder 9.
【００１８】振動検出器６及びピストン３は、アウタ側
だけでなく、図１（ｂ）に示すように、インナ側のパッ
ドにも対応させて設けられており、インナパッド、アウ
タパッドの拘束制御がここでは独立して行われるように
なっている。The vibration detector 6 and the piston 3 are provided not only on the outer side but also on the inner side pad as shown in FIG. 1 (b), and the restraint control of the inner pad and the outer pad is performed. It is set up independently here.
【００１９】このように構成した例示のディスクブレー
キにおいては、制動が行われるとディスク正転時のディ
スク回出側トルク受け面部に設けられた振動検出器６が
パッド１のディスク接線方向への振動を検出し、その検
出情報が制御回路５に流れる。この制御回路５の中に
は、検出した振動が鳴きの抑制制御を必要とするものか
否かを振幅、周波数を調べて判断する回路が含まれてお
り、この回路から制御実行信号が出力されると制御回路
５から油圧発生装置４に制御信号（電流や電圧）が流れ
る。その制御信号は、油圧発生装置４から出力される油
圧を検出振動の振幅に応じて増大させるように調整され
ており、その信号に基づいて制御された油圧がピストン
３の一面に加えられる。そのためにピストン３がシリン
ダ９から突出してパッド１の正転時ディスク回入側のト
ルク伝達面を振動振幅に応じた力でディスク回出側に向
けて押圧し、その力でパッド１のディスク回出側トルク
伝達面が回出側のトルク受け面２ａに押し当てられてパ
ッド１が確実に拘束され、その拘束で優れた制振作用が
生じて鳴きが防止される。In the exemplary disc brake having such a structure, when braking is performed, the vibration detector 6 provided on the disc feed-out side torque receiving surface portion at the time of normal rotation of the disc causes the pad 1 to vibrate in the disc tangential direction. Is detected, and the detection information flows to the control circuit 5. The control circuit 5 includes a circuit that determines whether or not the detected vibration requires squeal suppression control by checking the amplitude and frequency, and outputs a control execution signal from this circuit. Then, a control signal (current or voltage) flows from the control circuit 5 to the hydraulic pressure generator 4. The control signal is adjusted so as to increase the hydraulic pressure output from the hydraulic pressure generator 4 according to the amplitude of the detected vibration, and the hydraulic pressure controlled based on the signal is applied to one surface of the piston 3. Therefore, the piston 3 protrudes from the cylinder 9 and presses the torque transmitting surface on the disk advancing side at the time of normal rotation of the pad 1 toward the disk advancing side with a force according to the vibration amplitude, and the force causes the disk rotating of the pad 1 The output-side torque transmitting surface is pressed against the feed-out side torque receiving surface 2a to securely restrain the pad 1, and the restraint produces an excellent vibration damping action to prevent squeaking.
【００２０】なお、例示のブレーキは、振動検出器６と
して圧電素子を用いたが、この検出器６としては、加速
度センサや歪ゲージなどを用いてもよい。また、パッド
の拘束は、ピストン３に代えて逆圧電効果を利用する圧
電素子を用い、この素子でパッドを押圧する方法でも実
現できる。In the example brake, a piezoelectric element is used as the vibration detector 6, but an acceleration sensor, a strain gauge or the like may be used as the detector 6. The pad can also be restrained by using a piezoelectric element that utilizes an inverse piezoelectric effect instead of the piston 3 and pressing the pad with this element.
【００２１】さらに、各パッドの拘束制御を独立して行
う場合には、油圧発生装置４を２組設けてインナ、アウ
タの各シリンダ９に供給する油圧を個々に制御するが、
油圧発生装置４を１組とし、２つの検出器６、６の信号
のうち振幅が大きい方の信号に油圧を比例させる制御で
も目的を達成できる。この構成は油圧発生装置が１組で
足りるためコスト的に有利である。Furthermore, when the restraint control of each pad is performed independently, two sets of hydraulic pressure generators 4 are provided to individually control the hydraulic pressures supplied to the inner and outer cylinders 9, respectively.
The purpose can also be achieved by controlling the hydraulic pressure generation device 4 as one set and making the hydraulic pressure proportional to the one of the two detectors 6, 6 which has a larger amplitude. This configuration is advantageous in terms of cost because only one hydraulic pressure generator is required.
【００２２】このほか、例示のブレーキは、コストを考
えてディスク正転時の鳴きにのみ対応する構成にしたが
（鳴きは一般に車両前進時に発生し易いのでこれでも充
分に用をなす）、振動検出器６の設置点をトルク受け面
以外の部分にずらしてピストン３とそれを挿入するシリ
ンダ９を左右のトルク受け部に設ければ、ディスク逆転
時の鳴きにも対応できる。In addition to the above, the example brake has a structure corresponding to only the squeal at the time of normal rotation of the disk in consideration of the cost (since squeal is generally likely to occur when the vehicle is moving forward, this is sufficient), but vibration If the installation point of the detector 6 is shifted to a portion other than the torque receiving surface and the piston 3 and the cylinder 9 into which the piston 3 is inserted are provided in the left and right torque receiving portions, it is possible to cope with squeal when the disc is rotated in reverse.
【００２３】以下に、例示のディスクブレーキを用いた
効果の確認試験結果について記す。試験は、例示のブレ
ーキを装着した車両を使ってダイナモ試験機にて行っ
た。本発明の構成が鳴き止めに有効かどうかは、鳴きが
安定して再現される制動条件の下で比較評価を行わなけ
れば正確な判断が下せないので、ここでは、ほぼ例外な
く鳴きが生じるタイヤ回転初速３０ｋｍ／ｈ、ブレーキ
液圧２ｋｇｆ／ｃｍ2 、ディスク温度８０℃の条件を選
んだ。The results of the confirmation test of the effect using the exemplified disc brake will be described below. The test was carried out on a dynamo tester using a vehicle equipped with an example brake. Whether or not the configuration of the present invention is effective for squealing cannot be accurately determined unless comparative evaluation is performed under braking conditions in which squealing is stably reproduced, so squeaking occurs almost without exception here. Conditions were selected such that the tire rotation speed was 30 km / h, the brake fluid pressure was 2 kgf / cm 2 , and the disk temperature was 80 ° C.
【００２４】試験結果を図２に示す。ダイナモ試験機
は、タイヤが回転するタイプであるので、参考までにタ
イヤ空転時のノイズについても調べ、これを図２（ｃ）
に示した。The test results are shown in FIG. Since the dynamo tester is of a type in which the tire rotates, for reference, noise during tire idling was also checked, and this was shown in Fig. 2 (c).
It was shown to.
【００２５】鳴きの測定は、マイクで制動音を検出して
音圧を調べ、フーリエ変換（ＦＦＴ）で周波数表示を行
った。パッドの拘束を行わない非制動時には、図２
（ａ）のように、検出音の中に鳴きの共振周波数である
ピークがはっきりと現われている。これに対し、パッド
をその振動振幅に応じた力で拘束して制振を行った場合
には、図２（ｂ）のように、ブレーキノイズが少なくて
検出音がタイヤ空転時と同等レベルまで減衰しており、
聴感上での鳴きは全く認められなかった。The squeal was measured by detecting the braking sound with a microphone to check the sound pressure, and displaying the frequency by Fourier transform (FFT). When not braking the pad is not restrained,
As in (a), a peak, which is the resonance frequency of the squeal, clearly appears in the detected sound. On the other hand, when the pad is restrained by a force corresponding to the vibration amplitude to suppress the vibration, as shown in FIG. 2B, the brake noise is small and the detected sound reaches the same level as that when the tire is idling. Is decaying,
No audible squeal was observed.
【００２６】また、制動条件を変えて振動モードの異な
る鳴きについても調べたところ、結果は上の試験と殆ど
変わらず、本発明の構成は、あらゆるモードの鳴きに対
して有効な策であることを確認した。Further, when the squeal of different vibration modes was examined by changing the braking condition, the result was almost the same as the above test, and the configuration of the present invention is an effective measure for the squeal of all modes. It was confirmed.
【００２７】[0027]
【発明の効果】以上説明したように、本発明において
は、拘束手段による摩擦部材の拘束が、摩擦部材の振動
振幅に応じた力で行われるようにしたので、鳴きを生じ
る前の特徴的振動を検出してこの振動を確実に減衰させ
ることができ、ディスクブレーキの鳴きの完全な防止が
可能になる。As described above, in the present invention, since the friction member is restrained by the restraining means by the force corresponding to the vibration amplitude of the friction member, the characteristic vibration before the squeaking occurs. The vibration can be reliably dampened by detecting the noise, and the squeal of the disc brake can be completely prevented.
【００２８】特に、摩擦部材のディスク接線方向振動を
検出し、トルク伝達面をディスク接線方向に押圧して摩
擦部材を拘束するものは、制振効果に優れ、あらゆる周
波数の鳴きに対しても優れた抑止効果を発揮する。In particular, the one that detects the vibration of the friction member in the tangential direction of the disk and presses the torque transmitting surface in the tangential direction of the disk to restrain the friction member has an excellent vibration damping effect and is excellent in squeaking at all frequencies. Exerts a deterrent effect.
【００２９】また、各摩擦材の振動検出と拘束を独立し
て行うものや別々に検出した２つの振動信号のうち振幅
の大きいものを基準にして拘束制御を行うものは制御の
安定性が増し、鳴き止めの効果がよりよくなる。Further, the stability of control is increased when the vibration of each friction material is detected and restrained independently, or when the restraint control is performed on the basis of one of the two separately sensed vibration signals having a large amplitude. , The anti-squeal effect is better.
【図面の簡単な説明】[Brief description of drawings]
【図１】（ａ）：実施例のブレーキのアウタ側の端面図 （ｂ）：同上のブレーキをディスク外周側からディスク
中心側に向かって見た図FIG. 1A is an outer end view of a brake according to an embodiment of the present invention, and FIG. 1B is a view of the same brake as seen from a disc outer peripheral side toward a disc center side.
【図２】（ａ）：非制振時の音圧と周波数の関係の実測
データを示す図表 （ｂ）：制振時の音圧と周波数の関係の実測データを示
す図表 （ｃ）：タイヤ空転ノイズを示す図表[FIG. 2] (a): A chart showing measured data on the relationship between sound pressure and frequency when not damping (b): A chart showing measured data on the relationship between sound pressure and frequency when damping (c): Tire Chart showing idling noise
１ パッド ２ トルクメンバ ２ａ トルク受け面 ３ 拘束用ピストン ４ 油圧発生装置 ５ 制御回路 ６ 振動検出器 ７ キャリパ ８ スライドピン ９ シリンダ 1 Pad 2 Torque Member 2a Torque Receiving Surface 3 Restraining Piston 4 Hydraulic Pressure Generator 5 Control Circuit 6 Vibration Detector 7 Caliper 8 Slide Pin 9 Cylinder
Claims (3)
し、摩擦部材からの制動トルクをトルク受け面で受け止
めて制動を行うディスクブレーキにおいて、前記摩擦部
材の振動を検出する装置と、摩擦部材を拘束する手段
と、その拘束手段の制御装置とを有し、前記制御装置に
よる制御で前記拘束手段による摩擦部材の拘束が、前記
振動検出装置による検出振動の振幅に応じた力で行われ
ることを特徴とするディスクブレーキ。1. A disc brake, wherein a friction member is pressed against a disc by a pressing means and braking torque from the friction member is received by a torque receiving surface for braking, a device for detecting vibration of the friction member, and a friction member. A restraint means and a control device for the restraint means are provided, and the friction member is restrained by the restraint means under the control of the control device by a force according to the amplitude of the vibration detected by the vibration detection device. Characteristic disc brake.
接線方向振動を検出する位置に設け、前記拘束手段は摩
擦部材のトルク伝達面をディスク接線方向に加圧して拘
束する構成にした請求項１記載のディスクブレーキ。2. The vibration detecting device is provided at a position where vibration of a friction member in a disc tangential direction is detected, and the restraint means constrains a torque transmission surface of the friction member by pressing in a disc tangential direction. Disc brake as described.
摩擦部材の振動検出と拘束手段による拘束を、各摩擦部
材毎に独立して行う構成にした請求項１又は２記載のデ
ィスクブレーキ。3. The disc brake according to claim 1 or 2, wherein vibration detection of a pair of friction members disposed opposite to each other with the disc interposed therebetween and restraint by a restraining means are performed independently for each friction member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15336395A JPH094660A (en) | 1995-06-20 | 1995-06-20 | Disk brake |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15336395A JPH094660A (en) | 1995-06-20 | 1995-06-20 | Disk brake |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH094660A true JPH094660A (en) | 1997-01-07 |
Family
ID=15560822
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15336395A Pending JPH094660A (en) | 1995-06-20 | 1995-06-20 | Disk brake |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH094660A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20150143696A (en) * | 2013-04-17 | 2015-12-23 | 아이티티 매뉴팩츄어링 엔터프라이즈, 엘엘씨 | Method and device for real time estimation of the applied pressure and of noisiness in a brake element, in particular a brake pad |
| CN117901814A (en) * | 2024-03-15 | 2024-04-19 | 山西承信新能源科技装备有限公司 | Trackless rubber-tyred vehicle based on noise control |
-
1995
- 1995-06-20 JP JP15336395A patent/JPH094660A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20150143696A (en) * | 2013-04-17 | 2015-12-23 | 아이티티 매뉴팩츄어링 엔터프라이즈, 엘엘씨 | Method and device for real time estimation of the applied pressure and of noisiness in a brake element, in particular a brake pad |
| CN117901814A (en) * | 2024-03-15 | 2024-04-19 | 山西承信新能源科技装备有限公司 | Trackless rubber-tyred vehicle based on noise control |
| CN117901814B (en) * | 2024-03-15 | 2024-05-24 | 山西承信新能源科技装备有限公司 | Trackless rubber-tyred vehicle based on noise control |
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