JP3976047B2 - Disc brake device - Google Patents

Disc brake device Download PDF

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JP3976047B2
JP3976047B2 JP2004330553A JP2004330553A JP3976047B2 JP 3976047 B2 JP3976047 B2 JP 3976047B2 JP 2004330553 A JP2004330553 A JP 2004330553A JP 2004330553 A JP2004330553 A JP 2004330553A JP 3976047 B2 JP3976047 B2 JP 3976047B2
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piston
seal
groove
seal groove
brake
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JP2005090757A (en
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敦嗣 久保
篤夫 松本
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Sumitomo Electric Industries Ltd
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Sumitomo Electric Industries Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To constantly keep a specific clearance just enough between a pad and a piston in non-braking by changing the piston returning quantity in accordance with a load liquid pressure of a disc brake. <P>SOLUTION: In a retraction mechanism wherein a seal groove 5 is formed on a inner face of a cylinder 3 of a caliper 2, a piston seal 1 accommodated in the seal groove 5 is allow to follow the piston 4 within a range of a chamfered part 6 in advancing the piston 4, and the piston 4 is retracted in depressurization by the generated elastic restoring force of the piston seal 1, a width of the seal groove 5 is narrowed at an outer diameter-side area corresponding to 25-70% of a groove depth L of the seal groove 5 to make an axial clearance between an outer diameter part of the piston seal 1 and the seal groove 5 zero or to provide the piston seal 1 with an axial tightening margin. The piston returning quantity by the piston seal 1 corresponding to the load liquid pressure can be achieved by combining this technology and the selection of a dimension of the chamfered part 6 as a conventional technology. <P>COPYRIGHT: (C)2005,JPO&amp;NCIPI

Description

本発明は、自動車・二輪車等の車両用或いは産業用のピストンリトラクション（ピストン戻し）機構を持ったディスクブレーキ装置に関する。   The present invention relates to a disc brake device having a piston retraction (piston return) mechanism for vehicles such as automobiles and motorcycles or for industrial use.

液圧作動の一般的なディスクブレーキにおいては、制動時に前進して摩擦パッド（以下、単にパッドと云う）をディスクロータ（以下、ディスクと云う）に押し付けたブレーキピストン（以下、ピストンと云う）を、除圧時（制動解除時）にピストンシールと称されるゴムリングで引き戻すピストンリトラクション機構が設けられている。   In a general disk brake operated by hydraulic pressure, a brake piston (hereinafter referred to as a piston) that moves forward during braking and presses a friction pad (hereinafter simply referred to as a pad) against a disk rotor (hereinafter referred to as a disk) is used. A piston retraction mechanism is provided that is pulled back by a rubber ring called a piston seal when pressure is released (when braking is released).

この機構は、図１に示すように、キャリパ２に加工されるシリンダ３の内面にシール溝５を設け、この溝５にピストンシール１を納めてこのシールの内径側をシリンダ３に挿入したピストン４の外周に圧接させるもので、シール溝５の反液圧側（ディスクに近い側）の溝縁が適度に面取りされ（図１（ｂ）の６が面取り部）、その面取りの範囲でピストンシール１の内径側が前進するピストン４に追従して図２（ｂ）のように弾性変形し、それによって生じる弾性復元力で除圧後にピストン４が図２（ｃ）のように引き戻されるようになっている。   As shown in FIG. 1, this mechanism is provided with a seal groove 5 provided on the inner surface of a cylinder 3 processed into a caliper 2, a piston seal 1 is placed in the groove 5, and an inner diameter side of the seal is inserted into the cylinder 3. 4, the groove edge on the anti-hydraulic pressure side (side closer to the disk) of the seal groove 5 is appropriately chamfered (6 in FIG. 1 (b) is a chamfered portion), and the piston seal is within the range of the chamfer. 2 is elastically deformed as shown in FIG. 2 (b) following the piston 4 moving forward, and the piston 4 is pulled back as shown in FIG. 2 (c) after being depressurized by the elastic restoring force generated thereby. ing.

なお、ピストンシール１の弾性変形がシール溝５の面取り部６によって制限された位置からピストン４が更に押し出されるとシールとピストン間に滑りが生じ、これにより、パッドの摩耗に対する補償がなされてピストンの戻しが常時、同じ条件のもとで行われるようになっている。   When the piston 4 is further pushed out from the position where the elastic deformation of the piston seal 1 is restricted by the chamfered portion 6 of the seal groove 5, slipping occurs between the seal and the piston, thereby compensating for the wear of the pad. Is always performed under the same conditions.

この機構によるピストン戻し量は、後述する理由からディスクブレーキの仕様に合わせてそれぞれにその値を定める必要があるが、これまでは、上述したシール溝の反ディスク側溝縁の面取りの大きさ（図２（ａ）のＷ）を変える方法でその戻し量の調整を行っていたため、下記の問題が生じていた。   The piston return amount by this mechanism must be determined in accordance with the specifications of the disc brake for the reasons described later. Until now, the chamfered size of the seal groove on the side opposite to the disk side (see FIG. Since the return amount was adjusted by the method of changing W) of 2 (a), the following problems occurred.

制動時の負荷液圧によるキャリパの撓み量とパッドの圧縮変形量はブレーキの仕様によって異なる。図６に、あるブレーキにおける任意の液圧Ｐでのパッドの圧縮変形量とキャリパの撓み量の関係を示す。ピストン戻し量はパッドの圧縮変形量とキャリパの撓みが大きくなればその分大きくする必要があるが、従来のリトラクション機構による戻し量は、線Ｃ1 、Ｃ2 で示すようにやや傾斜した直線或いはこれに近似した曲線で表され、曲線Ａ（最少必要戻し量）から大きくかけ離れている。 The amount of caliper deflection and the amount of pad compression deformation due to load hydraulic pressure during braking differ depending on the brake specifications. FIG. 6 shows the relationship between the amount of compressive deformation of the pad and the amount of caliper deflection at an arbitrary hydraulic pressure P in a certain brake. The piston return amount needs to be increased if the amount of compressive deformation of the pad and the caliper bend increases, but the return amount by the conventional retraction mechanism is a slightly inclined straight line as shown by lines C 1 and C 2. Alternatively, it is represented by a curve that approximates this, and is far from curve A (minimum required return amount).

従来の機構では、ピストンの進み量がシール溝の面取り量よりも小さいときにもピストンシールが液圧に押されて面取り部による移動規制位置まで変形し、それによりピストン戻し量が平均化（低圧域では液圧増に応じて急増し、高圧域では殆ど増加しない、の意。）されてしまう結果、戻し量が負荷液圧に対応しない。   In the conventional mechanism, even when the advance amount of the piston is smaller than the chamfering amount of the seal groove, the piston seal is pushed by the hydraulic pressure and deformed to the movement restriction position by the chamfered portion, thereby averaging the piston return amount (low pressure As a result, the amount of return does not correspond to the load hydraulic pressure.

従って、今、図１中のブレーキについてピストン戻し量が線Ｃ1に沿うように設定されているとしたら、負荷液圧Ｐ1 時を境にして、また、設定戻し量が線Ｃ2に沿うものである場合には負荷液圧Ｐ2時を境にしてそれぞれピストン戻し量が液圧大の領域で不足し、液圧小の領域で過大になってしまう。 Accordingly, now, assuming that the piston return amount is set along the line C 1 for the brake in FIG. 1, the set return amount is along the line C 2 at the load hydraulic pressure P 1 as a boundary. If it is, the piston return amount is insufficient in the region where the hydraulic pressure is large at the load hydraulic pressure P 2 and becomes excessive in the region where the hydraulic pressure is small.

このうち、戻し量不足はパッドによる引きずりトルク増大の原因となり、一方、戻し量過大は、パッドとピストンとの間の非制動時隙間が必要以上にあいてブレーキペダルの遊び（無効ストローク）を大きくし、かつ、ペダルフィーリングを悪化させる原因となる。   Of these, an insufficient return amount causes an increase in drag torque due to the pad, while an excessive return amount results in a large brake pedal play (invalid stroke) because the non-braking gap between the pad and piston is more than necessary. In addition, the pedal feeling is deteriorated.

そこで、下記特許文献１、２等に示されるような改善策が考えられているが、これ等は、広い範囲でピストン戻り量が液圧に応じて理想的に変わるものにはなっていないか、又は部品点数が増し手段が複雑である等の問題がある。
特開平５−１３３４２９号公報 特開平６−２４９２７５号公報 Therefore, improvement measures such as those shown in Patent Documents 1 and 2 below have been considered, but these may be ideally changing the piston return amount in accordance with the hydraulic pressure over a wide range. Or the number of parts is increased and the means is complicated.
JP-A-5-133429 JP-A-6-249275

本発明は、上記の問題を無くすために、ピストン戻り量を簡単かつ確実に理想曲線に近づけられるようにすることを課題としている。   An object of the present invention is to make it possible to easily and reliably bring the piston return amount close to an ideal curve in order to eliminate the above-described problem.

上記の課題を解決するため、本発明においては、ピストンシールを納めるシール溝の外径側（シール溝深さの２５〜７０％に相当する領域）、かつ、前記面取り部の径方向外端よりも外径側に位置する領域でピストンシールをシール溝との軸方向隙間が零又は適度な締代が生じる状態にして固定し、さらに、シール溝の溝幅を狭くした領域と狭くしていない領域との間に軸方向の段差を生じさせて前記シリンダにブレーキピストンを組み付ける時にピストンシールが逃げ込む隙間を液圧側に設ける。この構造の場合、シールのゴム硬度は８０ＩＲＨ以下であってもよい。 In order to solve the above-described problems, in the present invention, from the outer diameter side of the seal groove that accommodates the piston seal (area corresponding to 25 to 70% of the depth of the seal groove) and from the radially outer end of the chamfered portion. In the region located on the outer diameter side, the piston seal is fixed with zero axial clearance with the seal groove or with moderate tightening allowance , and the groove width of the seal groove is not narrowed with the region narrowed. A gap in which the piston seal escapes when the brake piston is assembled to the cylinder by providing an axial step with the region is provided on the hydraulic pressure side. In the case of this structure, the rubber hardness of the seal may be 80 IRH or less.

なお、ここで云うシール溝深さとは、シール溝中間点の深さＬ（図３参照）を云う。また、適度な締代とは軸方向圧縮率が１５％程度までを云う。   The seal groove depth referred to here refers to the depth L (see FIG. 3) of the seal groove middle point. Moreover, the moderate tightening margin means that the axial compression ratio is up to about 15%.

この発明ではピストンシールの外径側をシール溝に固定するので、シール外周部からシール溝との間に軸方向隙間が生じる位置に至る空気抜き路を備えさせておくのが望ましい。   In the present invention, since the outer diameter side of the piston seal is fixed to the seal groove, it is desirable to provide an air vent path that reaches a position where an axial clearance is generated between the seal outer periphery and the seal groove.

ピストン戻り量を理想曲線に近づけるためには、従来のピストン戻し特性において、低液圧負荷時のピストン戻し量（イニシャル値）を低減させ、かつ、負荷液圧に対するピストン戻し量の増加割合（図６の線Ｃ1 、Ｃ2 の傾き度合）を大きくしなければならない。そこで、一般にピストン戻し量の決定因子となるシール溝溝縁の面取り量、ピストンシールの材料硬度、ピストン及びピストンシールの相互接触面の面粗度、ピストンシールの径方向圧縮率（締め代）の４つの因子のうち、ピストン戻し量とその戻し量の増加割合に及ぼす影響が特に大きいものについて調べた。図７がその結果である。ここでのピストン戻し量は、自動車における制動液圧を考慮し、０〜１４０ｋｇｆ／ｃｍ2 の間でピストン戻し量及びその変化割合を調べた。この試験結果から、ピストン戻し量とその戻し量の増加割合を大きく左右するのは、シール溝の面取り量とピストンシールの硬度であることが判る。 In order to bring the piston return amount closer to the ideal curve, in the conventional piston return characteristics, the piston return amount (initial value) at low hydraulic pressure load is reduced and the rate of increase of the piston return amount with respect to the load hydraulic pressure (Fig. 6) The slopes of the lines C 1 and C 2 must be increased. Therefore, the chamfering amount of the seal groove groove edge, the piston seal material hardness, the surface roughness of the mutual contact surface of the piston and the piston seal, and the radial compression ratio (tightening allowance) of the piston seal, which generally determine the piston return amount Of the four factors, the piston return amount and the effect on the rate of increase of the return amount were particularly large. FIG. 7 shows the result. The piston return amount here was determined by considering the brake hydraulic pressure in the automobile and examining the piston return amount and the rate of change between 0 and 140 kgf / cm 2 . From this test result, it can be seen that it is the chamfering amount of the seal groove and the hardness of the piston seal that greatly influence the piston returning amount and the increasing rate of the returning amount.

そこで、本発明においては、ピストンシールの外径側をシール溝に（シリンダに）固定するようにした。これによりシールの拘束点が内径面に近づき、ゴム硬度を高めたときと同様、シールの腰が強くなるため、ブレーキ作動時のシール変形が少なくなり、「ピストンの進み量がシール溝面取り量よりも小さいときにもシールが液圧に押されて面取り部による移動規制位置まで変形してしまう」不具合が改善される。また、シールの外径側が固定されていることでピストンをゴム弾性力で戻すときの復元スピードが速くなり、復元位置もより確実に元の位置に戻るようになる。これは、速いスピードでブレーキを繰り返し踏んだ時、ブレーキのストロークの変化が少なくなってペダルフィーリングの変化が生じ難いと云う効果に結びつく。   Therefore, in the present invention, the outer diameter side of the piston seal is fixed to the seal groove (on the cylinder). As a result, the seal restraint point approaches the inner diameter surface, and the rubber stiffness increases, resulting in less seal deformation during brake operation. Even when it is small, the seal is pushed by the hydraulic pressure and deformed to the movement restriction position by the chamfered portion. Further, since the outer diameter side of the seal is fixed, the restoring speed when the piston is returned by the rubber elastic force is increased, and the restoring position is more reliably returned to the original position. This leads to an effect that, when the brake is stepped repeatedly at a high speed, the change in the brake stroke is reduced and the change in the pedal feeling is less likely to occur.

図１乃至図５を参照して本発明のピストンリトラクション機構付きディスクブレーキ装置の具体例について説明する。   A specific example of a disc brake device with a piston retraction mechanism according to the present invention will be described with reference to FIGS.

図１は、浮動型ディスクブレーキを示しており、キャリパ２のインナ側に形成されるシリンダ３にピストン４が挿入されている。また、シリンダ３の内径面にはシール溝５が設けられ、その溝にリング状のピストンシール１が納められている。そのピストンシール１は、ピストン４の外周に締め代をもたせて嵌めてあり、ピストン外周の液封がこのピストンシール１によって行われる。なお、図１（ａ）の７はパッド、８はディスクを示している。   FIG. 1 shows a floating disc brake, in which a piston 4 is inserted into a cylinder 3 formed on the inner side of the caliper 2. A seal groove 5 is provided on the inner diameter surface of the cylinder 3, and a ring-shaped piston seal 1 is accommodated in the groove. The piston seal 1 is fitted on the outer periphery of the piston 4 with a tightening margin, and the liquid sealing of the outer periphery of the piston is performed by the piston seal 1. In FIG. 1A, 7 indicates a pad, and 8 indicates a disk.

シール溝５の反液圧側には、溝縁を図２（ａ）に示すＷの大きさに除去する面取り部６が設けられている。   A chamfered portion 6 for removing the groove edge to the size W shown in FIG. 2A is provided on the counter-hydraulic side of the seal groove 5.

以上の構成は、従来のピストンリトラクション機構のディスクブレーキと同じである。即ち、例示のブレーキは、従来品との相違点として、ピストンリトラクション機構を構成するシール溝５の溝底側の幅を狭くしその部分にピストンシール１の外径側をシール溝との間の軸方向隙間がほぼ零となるか又は適度の締代が生じる状態に挿入している。   The above configuration is the same as the disc brake of the conventional piston retraction mechanism. That is, the illustrated brake is different from the conventional product in that the width of the groove bottom side of the seal groove 5 constituting the piston retraction mechanism is narrowed, and the outer diameter side of the piston seal 1 is placed between the seal groove and the seal groove. Is inserted in a state in which the axial clearance of is almost zero or a moderate tightening margin is generated.

従来の機構の場合、ピストンシールの硬度が低い（即ち剛性が低い）ため、ピストン変位量が小さい低液圧負荷時にも図２（ｂ）のように、ピストンシール１が面取り部６に規制される位置まで動いてしまうが、本発明では、そのピストンシール１の低負荷液圧時の変形量が小さく、ピストン変位が小さければ図２（ｄ）のようにピストンシール内径側の変形も小さく抑えられる。また、負荷液圧が高まって図２（ｄ）の位置からピストン４がさらに左方に動くとピストンシール１は面取り部６による移動規制を受けるところまで追従して変形し、その変形が負荷液圧に対応したものになる。したがって液圧変動巾の増加に従い、ピストン戻し量も大きくなる。   In the case of the conventional mechanism, since the piston seal has low hardness (that is, low rigidity), the piston seal 1 is restricted to the chamfered portion 6 as shown in FIG. In the present invention, if the deformation amount of the piston seal 1 at low load hydraulic pressure is small and the piston displacement is small, the deformation on the inner diameter side of the piston seal is also suppressed as shown in FIG. It is done. Further, when the load hydraulic pressure increases and the piston 4 further moves to the left from the position of FIG. 2D, the piston seal 1 is deformed following the movement restriction by the chamfered portion 6, and the deformation is the load liquid. It corresponds to the pressure. Therefore, the piston return amount increases as the fluid pressure fluctuation range increases.

図３は、本発明のブレーキの要部を示している。このディスクブレーキは、ピストンリトラクション機構を構成するシール溝５の溝底側の幅を狭くしてその部分にピストンシール１の外径側を、シール溝との間の軸方向隙間がほぼ零となるか又は適度の締代が生じる状態に挿入している。   FIG. 3 shows a main part of the brake of the present invention. In this disc brake, the width of the groove bottom side of the seal groove 5 constituting the piston retraction mechanism is narrowed so that the outer diameter side of the piston seal 1 is provided at that portion, and the axial clearance between the seal groove and the seal groove is substantially zero. Or is inserted in a state where a moderate allowance is generated.

これにより、ピストンシール１の外径側がキャリパ２に固定され、低液圧負荷時にシール内径側が必要以上に変形することが抑制される。また、図のように、溝幅を狭くした部分とそうでない部分に段差ｈができるため、その部分に生じる隙間ｇによりピストンシール１に続いてピストン４を組付ける時、溝のエッジとピストン間にシール１が挾まれて傷付くと云う問題も解消される。   Thereby, the outer diameter side of the piston seal 1 is fixed to the caliper 2, and the inner diameter side of the seal is prevented from being deformed more than necessary at the time of low hydraulic pressure load. Also, as shown in the figure, a step h is formed between the narrowed portion and the non-grooved portion, so that when the piston 4 is assembled after the piston seal 1 by the gap g generated in that portion, the gap between the groove edge and the piston The problem that the seal 1 is rubbed and damaged is also eliminated.

なお、ピストンシール１の外径側の固定領域は、シール溝巾（軸方向）中間点における溝深さＬの２５〜７０％程度とする。固定領域がそれより狭いと変形抑制の効果が充分でなく、逆に広過ぎると変形抑制の効果が過大になって負荷液圧に対するピストン戻し量の増加割合を大きくするのが難しくなる。   The fixed region on the outer diameter side of the piston seal 1 is about 25 to 70% of the groove depth L at the intermediate point of the seal groove width (axial direction). If the fixed region is narrower than that, the effect of suppressing deformation is not sufficient, and if it is too wide, the effect of suppressing deformation becomes excessive and it is difficult to increase the rate of increase of the piston return amount with respect to the load hydraulic pressure.

また、この図３のピストンシール１をシール溝５に組付ける時、溝の狭幅部の入口がシールに塞がれると溝内の空気の逃げ場がなくなってシールの組付けに支障が出る。従って、逃げ道となる空気抜き路をピストンシール１に設けておくのがよく、その空気抜き路は、図４に示すように、外径側から内径側に向かって延びる溝９（この溝は最低ひとつあればよい）を設けて、或いは図５に示すように、複数の突起１０を設けて作り出すことができる。シールの外周から端面の途中に抜ける孔を設けてそこから空気を抜くことも可能であるが、シールの加工性を考えると、図４、５の溝や突起の方が有利である。   Further, when the piston seal 1 shown in FIG. 3 is assembled in the seal groove 5, if the narrow-width inlet of the groove is blocked by the seal, there is no air escape space in the groove, which hinders the assembly of the seal. Therefore, it is preferable to provide an air vent path in the piston seal 1 as an escape path, and the air vent path has a groove 9 extending from the outer diameter side toward the inner diameter side as shown in FIG. Or a plurality of protrusions 10 as shown in FIG. Although it is possible to provide a hole that goes out from the outer periphery of the seal in the middle of the end face and extract air from the hole, the grooves and protrusions shown in FIGS. 4 and 5 are more advantageous in view of the workability of the seal.

以上述べたように、本発明によれば、ディスクブレーキの負荷液圧に応じてピストン戻し量が理想的に変わるので戻し量の過不足が抑えられてパッドとピストンとの間の非制動時隙間が常時ほぼ一定に保たれ、ブレーキペダルの遊び量の増加やペダルフィーリングの悪化を懸念することなく引きずりトルクの低減を図ることができる。   As described above, according to the present invention, since the piston return amount changes ideally according to the load hydraulic pressure of the disc brake, the excess or shortage of the return amount is suppressed, and the non-braking gap between the pad and the piston is suppressed. However, the drag torque can be reduced without worrying about an increase in the amount of play of the brake pedal and a deterioration of the pedal feeling.

従って、引きずりトルクの低減による燃費改善やブレーキペダル（或いはブレーキレバー）のフィーリングが重視される自動車・二輪車用ディスクブレーキに適用すると特に大きな効果を期待できる。   Therefore, a particularly great effect can be expected when applied to a disc brake for automobiles and motorcycles where importance is attached to fuel efficiency improvement by reducing drag torque and feeling of a brake pedal (or brake lever).

（ａ）：浮動型ディスクブレーキの断面図、（ｂ）：同上のブレーキのピストンリトラクション機構の拡大図(A): sectional view of floating disc brake, (b): enlarged view of piston retraction mechanism of the brake ピストンリトラクション機構によるピストン引戻しの原理を、（ａ）：液圧無負荷時、（ｂ）：液圧負荷時、（ｃ）：液圧解除時、（ｄ）本発明での低液圧負荷時の４状態に分けて示す図The principle of piston retraction by the piston retraction mechanism is as follows: (a): no hydraulic pressure, (b): hydraulic pressure, (c): hydraulic pressure release, (d) low hydraulic pressure load in the present invention Figure divided into four states of time ピストンシールの外径側をシール溝に固定したこの発明のブレーキの要部拡大断面図The principal part expanded sectional view of the brake of this invention which fixed the outer diameter side of the piston seal to the seal groove （ａ）：図３のピストンシールを溝付きのものにした状態の断面図、（ｂ）：同上の溝付きピストンシールの背面図(A): Cross-sectional view of the piston seal in FIG. 3 with a groove, (b): Rear view of the grooved piston seal of the above. （ａ）：図３のピストンシールを突起付きのものにした状態の断面図、（ｂ）：同上の突起付きピストンシールの背面図(A): Cross-sectional view of the piston seal of FIG. 3 with protrusions, (b): Rear view of the same piston seal with protrusions ディスクブレーキのピストン変化量の違いと従来の機構によるピストン戻し量を示す図表Chart showing the difference in piston variation of disc brake and piston return by conventional mechanism ピストン戻し量と戻し量の変化割合に対する変動因子の影響度合を示す図表Chart showing the degree of influence of variable factors on piston return amount and return rate change rate

符号の説明Explanation of symbols

１ ピストンシール
２ キャリパ
３ シリンダ
４ ピストン
５ シール溝
６ 面取り部
７ パッド
８ ディスク
９ 溝
１０ 突起
ｈ 段差
ｇ 隙間 1 Piston seal 2 Caliper 3 Cylinder 4 Piston 5 Seal groove 6 Chamfer 7 Pad 8 Disc 9 Groove 10 Projection h Step g Gap

Claims (2)

キャリパに加工されるシリンダの内面に、反液圧側溝縁を面取りしたシール溝を設け、そのシール溝にゴム製ピストンシールを嵌め、このピストンシールを前記シリンダに挿入されるブレーキピストンの外周に圧接させて前記シリンダとブレーキピストン間を液封すると共に、ブレーキピストンによるパッド加圧時に前記面取り部の範囲でピストンシールの内径側をブレーキピストンに追従させて弾性変形させ、シリンダの除圧時にそのシールの弾性復元力で前記ピストンを引き戻すピストンリトラクション機構のディスクブレーキ装置において、前記シール溝の溝深さＬの２５〜７０％に相当する外径側領域、かつ、前記面取り部の径方向外端よりも外径側に位置する領域でシール溝の溝幅を狭くしてピストンシールとシール溝との軸方向隙間を零にするか又はピストンシールに軸方向の締代をもたせて前記ピストンシールの低負荷液圧時の液圧による前記面取り部の範囲での変形量を小さくし、さらに、シール溝の溝幅を狭くした領域と狭くしていない領域との間に軸方向の段差を生じさせて前記シリンダにブレーキピストンを組み付ける時にピストンシールが逃げ込む隙間を液圧側に設けたことを特徴とするディスクブレーキ装置。 A seal groove with a chamfered anti-hydraulic side groove is provided on the inner surface of the cylinder processed into the caliper, and a rubber piston seal is fitted into the seal groove. The cylinder and the brake piston are liquid-sealed, and when the pad is pressed by the brake piston, the inner diameter side of the piston seal is made to follow the brake piston and elastically deform within the range of the chamfered portion. In a disc brake device of a piston retraction mechanism that pulls back the piston with an elastic restoring force, an outer diameter side region corresponding to 25 to 70% of a groove depth L of the seal groove, and a radially outer end of the chamfered portion The axial direction of the piston seal and the seal groove by narrowing the groove width of the seal groove in the area located on the outer diameter side To reduce the deformation amount in the range of the chamfer by the liquid pressure in the low load liquid pressure time before Symbol piston seal remembering tightening margin of axially or piston seal to zero between, further, the seal groove A disc brake characterized in that a gap is provided on the hydraulic pressure side so that a piston seal escapes when a brake piston is assembled to the cylinder by generating an axial step between a region where the groove width is narrowed and a region where the groove width is not narrowed. apparatus. 前記ピストンシールに、そのシールの内周側からシール外周に至る空気抜き路を設けたことを特徴とする請求項１に記載のディスクブレーキ装置。   2. The disc brake device according to claim 1, wherein the piston seal is provided with an air vent path from an inner peripheral side of the seal to an outer periphery of the seal.
JP2004330553A 2004-11-15 2004-11-15 Disc brake device Expired - Fee Related JP3976047B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004330553A JP3976047B2 (en) 2004-11-15 2004-11-15 Disc brake device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004330553A JP3976047B2 (en) 2004-11-15 2004-11-15 Disc brake device

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
JP7225461A Division JPH0972361A (en) 1995-09-01 1995-09-01 Disk brake device

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JP2005090757A JP2005090757A (en) 2005-04-07
JP3976047B2 true JP3976047B2 (en) 2007-09-12

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Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101753266B1 (en) 2016-05-31 2017-07-19 주식회사 만도 Electric disk brake

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4978442B2 (en) * 2007-11-30 2012-07-18 日立オートモティブシステムズ株式会社 Disc brake
JP7350124B1 (en) 2022-03-31 2023-09-25 本田技研工業株式会社 Caliper seal structure

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101753266B1 (en) 2016-05-31 2017-07-19 주식회사 만도 Electric disk brake

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