JPH05133429A - Piston returning mechanism of disc brake - Google Patents

Piston returning mechanism of disc brake

Info

Publication number
JPH05133429A
JPH05133429A JP3294249A JP29424991A JPH05133429A JP H05133429 A JPH05133429 A JP H05133429A JP 3294249 A JP3294249 A JP 3294249A JP 29424991 A JP29424991 A JP 29424991A JP H05133429 A JPH05133429 A JP H05133429A
Authority
JP
Japan
Prior art keywords
piston
rubber ring
elastic
amount
ring
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
JP3294249A
Other languages
Japanese (ja)
Inventor
Shiro Nakajima
志郎 中島
Original Assignee
Sumitomo Electric Ind Ltd
住友電気工業株式会社
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 Sumitomo Electric Ind Ltd, 住友電気工業株式会社 filed Critical Sumitomo Electric Ind Ltd
Priority to JP3294249A priority Critical patent/JPH05133429A/en
Publication of JPH05133429A publication Critical patent/JPH05133429A/en
Pending legal-status Critical Current

Links

Abstract

PURPOSE:To fix a return amount of a piston according to the size of load fluid pressure when a piston is returned by the elastic restoring force of a rubber ring at the time of releasing pressure of a hydraulic oil pressure system. CONSTITUTION:An elastic ring 7 which is harder and has a higher elastic coefficient than a rubber ring 4 is installed between a sealing groove 5 on the inner surface of a cylinder 2 and an edge surface on an opposite side of fluid pressure of the rubber ring 4 for fluid sealing which is inserted into the groove and is fitted with an interference on the periphery of a piston 3. A space 6 which allows deformation of an elastic ring 7 is formed between the sealing groove 5 and the elastic ring 7, and the second space 8 is formed between the elastic ring 1 and the rubber ring 4 if necessary. As load fluid pressure rises, deformation of the elastic ring 7 increases, and a substantial chamfered amount (size of the space) which determines elastic deformation amount of a rubber ring 4 increases, so that the piston returning amount, increases according to fluid pressure. It is thus possible to solve the problem of an increase in dragging torque due to shortage of the piston returning amount, after high pressure is applied without an increase in the piston stroke when low pressure is applied.

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【産業上の利用分野】本発明は、液圧式ディスクブレー
キのピストンを、除圧時に引き戻すための機構、より詳
しくは、ピストンの戻り量が負荷液圧に応じた形で定ま
る戻し機構に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mechanism for returning the piston of a hydraulic disc brake during depressurization, and more particularly to a returning mechanism in which the amount of return of the piston is determined according to the load hydraulic pressure.

【0002】[0002]

【従来の技術】サービス型の液圧式ディスクブレーキに
は、ブレーキシリンダとブレーキピストン(以下では単
にシリンダ、ピストンと言う)間に設ける液封ゴムリン
グの弾性復元力を利用してピストンを除圧時に引き戻す
戻し機構が多用されている。このピストン戻し機構は、
図5に示すように、シリンダ2の内面に設けたシール溝
5内にゴムリング4を組付け、そのゴムリングをピスト
ン3の外周に締め代をつけて嵌めてある。また、シール
溝5は反液圧側(シリンダの入口に近い側)の溝縁を面
取りしてゴムリング4との間にそのリングの弾性変形を
許容する空所6を生じさせてある。
2. Description of the Related Art In a service type hydraulic disc brake, the elastic restoring force of a liquid sealing rubber ring provided between a brake cylinder and a brake piston (hereinafter simply referred to as a cylinder or piston) is used to depressurize the piston. A pullback mechanism is often used. This piston return mechanism is
As shown in FIG. 5, the rubber ring 4 is assembled in the seal groove 5 provided on the inner surface of the cylinder 2, and the rubber ring is fitted around the outer periphery of the piston 3 with a tightening margin. Further, the seal groove 5 is chamfered at the groove edge on the anti-hydraulic side (the side close to the inlet of the cylinder) to form a space 6 between the seal groove 5 and the rubber ring 4 which allows elastic deformation of the ring.

【0003】このようにしておくと、制動液圧でピスト
ンが押し出される加圧時にゴムリング4が空所6を埋め
る位置に引きずられて弾性変形し、その変形がゴムの復
元弾力で除圧時に元に戻るため、加圧により前進したピ
ストン3が除圧時に必ずある量引き戻される。
With this arrangement, when the piston is pushed out by the braking fluid pressure, the rubber ring 4 is dragged to the position where it fills the void 6 and elastically deforms. In order to return to the original state, the piston 3 advanced by pressurization is always pulled back by a certain amount at the time of depressurization.

【0004】このときの戻り量は、空所6の大きさLに
よってゴムリング4の弾性変形量がほぼ定まるため、負
荷液圧の大きさによる若干の増減はあるもののほぼ一定
になる。
Since the amount of elastic deformation of the rubber ring 4 is substantially determined by the size L of the space 6, the return amount at this time is substantially constant although there is a slight increase or decrease depending on the size of the load hydraulic pressure.

【0005】[0005]

【発明が解決しようとする課題】図5において、今ピス
トンの戻り量をRe、ディスクに摺接させるパッド9、
9の制動時圧縮歪量をδp、液圧によるキャリパ1の撓
み量をδcとすると、除圧により復帰したピストン3と
パッド9との間にはε=Re−(δc+2δp)の式で
求められる隙間εが生じる。
In FIG. 5, the return amount of the piston is now Re, the pad 9 for sliding contact with the disk,
Assuming that the amount of compressive strain during braking of 9 is δp and the amount of bending of the caliper 1 due to hydraulic pressure is δc, the distance between the piston 3 and the pad 9 restored by depressurization is determined by the equation ε = Re- (δc + 2δp). A gap ε is created.

【0006】その隙間εが常時必要最小限の値以上に保
たれるならば、ディスクDによるパッドの引きずりは起
こらない。しかしながら、パッドの圧縮歪量δpとキャ
リパ撓み量δcは、負荷液圧が大きくなるにつれて増大
する。一方、従来の戻し機構によれば、ピストンの戻り
量Reは一定であるので、負荷液圧が大きくなればεの
値が小さくなる。このため、戻り量Reの設定値が小さ
いと2δpとδcの和がRe以下になってε>0の関係
が成立し、非制動時にパッドがゴムリングの力でディス
クに押圧されたままとなっていわゆる引きずりトルクの
増加、パッドの無駄な摩耗等の問題が生じる。
If the gap ε is always kept above the required minimum value, the dragging of the pad by the disk D does not occur. However, the amount of compressive strain δp and the amount of caliper deflection δc of the pad increase as the load hydraulic pressure increases. On the other hand, according to the conventional return mechanism, since the return amount Re of the piston is constant, the value of ε decreases as the load hydraulic pressure increases. Therefore, when the set value of the return amount Re is small, the sum of 2δp and δc becomes Re or less and the relation of ε> 0 is established, and the pad remains pressed against the disc by the force of the rubber ring during non-braking. As a result, problems such as so-called increase in drag torque and unnecessary wear of the pad occur.

【0007】また、この問題に対処すべく、戻り量Re
を最大負荷時のキャリパ及びパッドの変形量を見込んだ
大きさにしておくと、負荷液圧が小さいときのピストン
ストロークが大きくなって所要ブレーキ液量の増加、ペ
ダルフィーリングの悪化を招く。本発明はこれ等の問題
点を無くすことを課題としている。
In order to deal with this problem, the return amount Re
If the amount of deformation of the caliper and the pad at the maximum load is taken into consideration, the piston stroke becomes large when the load hydraulic pressure is small, which increases the required brake fluid amount and deteriorates the pedal feel. An object of the present invention is to eliminate these problems.

【0008】[0008]

【課題を解決するための手段】本発明は、上記の課題を
解決するため、反液圧側の溝縁を面取りしてあるシール
溝とゴムリングの反液圧側端面との間にゴムリングより
も弾性係数の高い弾性リングをブレーキピストンとの間
に隙間をあけて介在する。
In order to solve the above-mentioned problems, the present invention provides a rubber ring between a seal groove having chamfered groove edges on the anti-hydraulic side and an end surface on the anti-hydraulic side of a rubber ring, rather than a rubber ring. An elastic ring having a high elastic coefficient is interposed with the brake piston with a gap.

【0009】[0009]

【作用】弾性リングは、負荷液圧が上昇するにつれてシ
ール溝との間の空所を埋める方向に変形し、シール溝の
面取部に規制されるところまで変形量を増していく。本
発明では、この弾性リングがゴムリングを支えるので、
弾性リングを最大負荷液圧時に変形量が最大となるよう
に設計しておけば、弾性リングの変形によりゴムリング
の弾性変形量を決める実質的な面取り量(空所サイズ)
が負荷液圧に応じて大きくなり、そのために、ピストン
の戻り量も負荷液圧の高まりに応じて大きくなる。
The elastic ring deforms in the direction of filling the space between the elastic ring and the seal groove as the load hydraulic pressure increases, and the deformation amount increases until it is restricted by the chamfered portion of the seal groove. In the present invention, since this elastic ring supports the rubber ring,
If the elastic ring is designed to maximize the amount of deformation at maximum load hydraulic pressure, the amount of chamfering that determines the amount of elastic deformation of the rubber ring due to the deformation of the elastic ring (void size)
Becomes larger according to the load hydraulic pressure, and therefore, the return amount of the piston also increases as the load hydraulic pressure increases.

【0010】このように、ピストンの戻り量が負荷液圧
に応じて定まるので、本発明によれば、低圧負荷時のピ
ストンストロークの増加、高圧負荷時のピストンとパッ
ド間の隙間の減少の問題が共に解決される。
As described above, since the amount of return of the piston is determined according to the load hydraulic pressure, according to the present invention, there is a problem that the piston stroke is increased under a low pressure load and the clearance between the piston and the pad is decreased under a high pressure load. Are solved together.

【0011】[0011]

【実施例】図1に本発明の一実施例を示す。図の1はシ
リンダ2を有するキャリパ、3はシリンダ2内に挿入し
たピストン、4はシリンダ2内面のシール溝5に挿入し
たゴムリングであり、ゴムリング4は、ピストン3の外
周に締め代をつけて嵌められている。また、シール溝5
の反液圧側溝縁部には、空所6を生じさせるための面取
りが施されている。
FIG. 1 shows an embodiment of the present invention. In FIG. 1, reference numeral 1 is a caliper having a cylinder 2, 3 is a piston inserted in the cylinder 2, 4 is a rubber ring inserted in a seal groove 5 on the inner surface of the cylinder 2, and the rubber ring 4 has a tightening margin on the outer circumference of the piston 3. It is attached and fitted. Also, the seal groove 5
A chamfer is formed on the edge portion of the anti-hydraulic side groove to create the void 6.

【0012】7は、本発明を特徴づける弾性リングであ
る。この弾性リングはゴムリング4よりも硬くて弾性係
数の高いゴムや合成樹脂によって形成されており、図の
ように、ピストン3との間に隙間を生じさせてゴムリン
グ4の反液圧側端面とシール溝5との間に介在される。
Reference numeral 7 is an elastic ring which characterizes the present invention. This elastic ring is made of rubber or synthetic resin that is harder than the rubber ring 4 and has a higher elastic coefficient. As shown in the figure, a gap is created between the elastic ring and the piston 3 and the end surface of the rubber ring 4 on the anti-hydraulic side. It is interposed between the seal groove 5.

【0013】8は、弾性リング7のゴムリング側内周縁
を面取りして生じさせた第2の空所であり、低圧負荷時
には、図2に示すように、ゴムリング4がこの第2の空
所8を埋めるように弾性変形する。このときのゴムリン
グの弾性変形量は、第2の空所8の大きさによって決ま
る量に弾性リングの変形によって生じる量を加算した値
になるが、弾性リングの変形による量は零または零に近
いので、ほぼ第2の空所8の大きさによって決まる量と
なる。
Reference numeral 8 designates a second cavity formed by chamfering the inner peripheral edge of the elastic ring 7 on the rubber ring side. When a low pressure load is applied, the rubber ring 4 is formed in the second cavity, as shown in FIG. Elastically deformed so as to fill the place 8. The elastic deformation amount of the rubber ring at this time is a value obtained by adding the amount determined by the size of the second space 8 and the amount generated by the deformation of the elastic ring, but the amount of elastic ring deformation is zero or zero. Since it is close, the amount is almost determined by the size of the second void 8.

【0014】一方、高圧負荷時には、ゴムリング4に押
されて弾性リング7も空所6を埋めつくす範囲内におい
て図3に示すように弾性変形する。従って、ゴムリング
4の弾性変形量は、図4に示すように、弾性リング7の
変形が止まるところまで液圧の上昇に伴なって比例的に
増加していくことになり、そのために、ピストン3の戻
り量も負荷液圧と共に大きくなる。
On the other hand, when a high pressure is applied, the elastic ring 7 is also elastically deformed as shown in FIG. Therefore, as shown in FIG. 4, the elastic deformation amount of the rubber ring 4 increases proportionally as the hydraulic pressure increases until the deformation of the elastic ring 7 stops. The return amount of 3 also increases with the load hydraulic pressure.

【0015】なお、低圧負荷時に弾性リング7の弾性変
形量のみでピストンの戻り量を不足なく確保できる場合
には、第2の空所8は不要である。
When the amount of elastic deformation of the elastic ring 7 is sufficient to ensure a sufficient amount of piston return when a low pressure load is applied, the second void 8 is not necessary.

【0016】また、低圧負荷時、高圧負荷時とも、パッ
ド9が摩耗すると従来のブレーキと同様にピストン3と
ゴムリング4との間に摩耗量に応じたスリップが起こる
ので、パッドの摩耗量によってピストンの戻り量が変化
することはない。
Further, when the pad 9 is worn under both low pressure load and high pressure load, a slip corresponding to the wear amount occurs between the piston 3 and the rubber ring 4 as in the conventional brake. The amount of piston return does not change.

【0017】[0017]

【発明の効果】以上述べたように、本発明によれば、ピ
ストンの戻り量が負荷液圧の大きさに応じた形で定まる
ので、低圧負荷時のペダルフィーリングを悪化させるピ
ストンストロークの増加の問題と、高圧負荷後のピスト
ン引戻し量の不足による引きずりトルクの増大の問題を
併せて解決することができ、ディスクブレーキの性能並
びに信頼性向上に役立つ。
As described above, according to the present invention, since the amount of return of the piston is determined according to the magnitude of the load hydraulic pressure, the piston stroke is increased which deteriorates the pedal feeling at low pressure load. Can be solved together with the problem of increase in drag torque due to insufficient amount of piston pullback after high-pressure load, which is useful for improving the performance and reliability of the disc brake.

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

【図1】(a)は本発明の一実施例を示す断面図、
(b)は同上の要部の拡大図
FIG. 1A is a sectional view showing an embodiment of the present invention.
(B) is an enlarged view of the main part of the above

【図2】低圧負荷時のゴムリングの変形状態を示す図FIG. 2 is a diagram showing a deformed state of a rubber ring under a low pressure load.

【図3】高圧負荷時のゴムリングと弾性リングの変形状
態を示す図
FIG. 3 is a diagram showing a deformed state of a rubber ring and an elastic ring under a high pressure load.

【図4】ピストンの戻り量と負荷液圧の関係を示すグラ
FIG. 4 is a graph showing the relationship between the piston return amount and the load hydraulic pressure.

【図5】従来のピストン戻し機構の要部を示す断面図FIG. 5 is a sectional view showing a main part of a conventional piston returning mechanism.

【符号の説明】[Explanation of symbols]

1 キャリパ 2 シリンダ 3 ピストン 4 ゴムリング 5 シール溝 6 空所 7 弾性リング 8 第2の空所 9 パッド D ディスク 1 Caliper 2 Cylinder 3 Piston 4 Rubber Ring 5 Seal Groove 6 Void 7 Elastic Ring 8 Second Void 9 Pad D Disc

Claims (2)

    【特許請求の範囲】[Claims]
  1. 【請求項1】 ブレーキシリンダ内面の反液圧側溝縁を
    面取りしたシール溝にゴムリングを嵌め、このゴムリン
    グをブレーキピストンの外周に圧接させて上記シリンダ
    とピストン間を液封すると共に、ブレーキピストンの加
    圧時に上記の面取りで生じた空所を埋めるように弾性変
    形する上記ゴムリングの復元力で除圧時にブレーキピス
    トンを引き戻すディスクブレーキのピストン戻し機構に
    おいて、上記シール溝とゴムリングの反液圧側端面との
    間にゴムリングよりも弾性係数の高い弾性リングをブレ
    ーキピストンとの間に隙間をあけて介在したことを特徴
    とするピストン戻し機構。
    1. A rubber ring is fitted in a seal groove having a chamfered groove edge on the inner side of a brake cylinder on the inner surface of the brake cylinder, and the rubber ring is pressed against the outer circumference of the brake piston to seal the liquid between the cylinder and the piston. In the piston brake return mechanism of the disc brake that pulls back the brake piston at the time of decompression by the restoring force of the rubber ring that elastically deforms so as to fill the void created by the chamfering when pressurizing the A piston return mechanism characterized in that an elastic ring having a higher elastic coefficient than a rubber ring is interposed between the pressure side end surface and the brake piston with a gap provided therebetween.
  2. 【請求項2】 上記弾性リングのゴムリング側内周縁部
    に面取部を設けてゴムリングとの間に所定サイズの第2
    の空所を生じさせてある請求項1記載のピストン戻し機
    構。
    2. A chamfered portion is provided on an inner peripheral edge portion of the elastic ring on the rubber ring side, and a second portion having a predetermined size is provided between the elastic ring and the rubber ring.
    2. The piston return mechanism according to claim 1, wherein the empty space is created.
JP3294249A 1991-11-11 1991-11-11 Piston returning mechanism of disc brake Pending JPH05133429A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP3294249A JPH05133429A (en) 1991-11-11 1991-11-11 Piston returning mechanism of disc brake

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP3294249A JPH05133429A (en) 1991-11-11 1991-11-11 Piston returning mechanism of disc brake

Publications (1)

Publication Number Publication Date
JPH05133429A true JPH05133429A (en) 1993-05-28

Family

ID=17805285

Family Applications (1)

Application Number Title Priority Date Filing Date
JP3294249A Pending JPH05133429A (en) 1991-11-11 1991-11-11 Piston returning mechanism of disc brake

Country Status (1)

Country Link
JP (1) JPH05133429A (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5826681A (en) * 1995-09-01 1998-10-27 Sumitomo Electric Industries, Ltd. Disk brake assembly with piston retraction seal
US20130116904A1 (en) * 2010-06-15 2013-05-09 Toyota Jidosha Kabushiki Kaisha Vehicle brake control device
US8631912B2 (en) * 2006-05-03 2014-01-21 Continental Teves Ag & Co. Ohg Brake caliper
CN103958920A (en) * 2011-09-27 2014-07-30 福乐尼·乐姆宝公开有限公司 Device for retracting a piston

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5826681A (en) * 1995-09-01 1998-10-27 Sumitomo Electric Industries, Ltd. Disk brake assembly with piston retraction seal
EP2016303B1 (en) * 2006-05-03 2021-01-20 Continental Teves AG & Co. OHG Combined brake caliper
US8631912B2 (en) * 2006-05-03 2014-01-21 Continental Teves Ag & Co. Ohg Brake caliper
US8914211B2 (en) * 2010-06-15 2014-12-16 Advics Co., Ltd. Vehicle brake control device
US20130116904A1 (en) * 2010-06-15 2013-05-09 Toyota Jidosha Kabushiki Kaisha Vehicle brake control device
CN103958920A (en) * 2011-09-27 2014-07-30 福乐尼·乐姆宝公开有限公司 Device for retracting a piston
US20140231190A1 (en) * 2011-09-27 2014-08-21 Freni Brembo, S.P.A. Device for retracting a piston
US9388870B2 (en) * 2011-09-27 2016-07-12 Freni Brembo, S.P.A. Device for retracting a piston

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