JP2510665Y2 - Disc brake - Google Patents
Disc brakeInfo
- Publication number
- JP2510665Y2 JP2510665Y2 JP40018090U JP40018090U JP2510665Y2 JP 2510665 Y2 JP2510665 Y2 JP 2510665Y2 JP 40018090 U JP40018090 U JP 40018090U JP 40018090 U JP40018090 U JP 40018090U JP 2510665 Y2 JP2510665 Y2 JP 2510665Y2
- Authority
- JP
- Japan
- Prior art keywords
- pad
- disc
- return spring
- point
- back 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.)
- Expired - Fee Related
Links
Landscapes
- Braking Arrangements (AREA)
Description
【0001】[0001]
【産業上の利用分野】この考案は、主として乗用車に用
いられるサービス型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 service type disc brake mainly used for passenger cars.
【0002】[0002]
【従来の技術】サービス型のディスクブレーキは、非制
動時のディスク(ディスクロータ)による摩擦パッド
(以下単にパッドと云う)の引きずりを無くすため、ピ
ストンシールの弾性変形を利用したシールリトラクショ
ン方式を採用して制動解除時にブレーキピストンを制動
位置から一定量戻すようにしたものが多い。しかし、ピ
ストンを引き戻してもパッドは制動位置に残ろうとする
ので引きずりの問題は完全に解消されない。そこで、図
5及び図6に示すように、ディスクDを間にして対向配
置したパッド2、3間にばね線材を曲げ加工して作られ
た戻しスプリング4を装着し、そのスプリングの力でパ
ッドをディスクから強制的に引き離すことが行われてい
る。2. Description of the Related Art Service-type disc brakes employ a seal retraction system utilizing elastic deformation of a piston seal in order to eliminate drag of a friction pad (hereinafter simply referred to as a pad) due to a disc (disc rotor) during non-braking. In many cases, when the brake is released, the brake piston is returned from the braking position by a certain amount. However, even if the piston is pulled back, the pad tries to remain in the braking position, so that the drag problem cannot be completely solved. Therefore, as shown in FIG. 5 and FIG. 6, a return spring 4 made by bending a spring wire rod is mounted between the pads 2 and 3 arranged to face each other with the disc D in between, and the pad force is applied by the spring force. Is being forced away from the disk.
【0003】スプリング4は、両端の足部4aをパッド
裏板の外周面(ディスク溝1aの溝底と向かい合う面)
に設けた穴に係止させ、この位置でパッドに押し戻し力
を加えるようにしてある。The spring 4 has the foot portions 4a at both ends on the outer peripheral surface of the pad back plate (the surface facing the groove bottom of the disk groove 1a).
It is locked in the hole provided in the pad and push-back force is applied to the pad at this position.
【0004】[0004]
【考案が解決しようとする課題】図6に示すように、ト
ルクメンバ5のパッドスライド部には通常錆付き防止の
ためのリテーナ6が装着される。この場合、同時にパッ
ドのがたつきに起因したラトル音、クロンク音を無くす
ためにリテーナ6にパッド加圧部6aを設けてパッドを
ディスク中心側から外向きに加圧している。As shown in FIG. 6, the pad slide portion of the torque member 5 is usually provided with a retainer 6 for preventing rusting. In this case, at the same time, in order to eliminate rattle noise and crawl noise caused by the rattling of the pad, the retainer 6 is provided with a pad pressing portion 6a to press the pad outward from the disk center side.
【0005】かかるケースでは図6のb点(トルクメン
バ5によるパッドのディスク径方向外方への移動拘束
点)、c点(加圧部6aによるパッド加圧点)の2個所
でパッドに摺動抵抗が加わるが、従来は戻しスプリング
4によるパッド加圧点をb、cの2点間から外れた位置
に設けていたので、a点からの離間距離が大きいc点に
は戻し力が伝わり難く、そのため、パッドの内周側の復
帰が不充分でまだ引きずりが生じている。In such a case, the pad is slid at two points in FIG. 6 (point b (point of restraint of movement of the pad by the torque member 5 outward in the radial direction of the disk)) and point c (point of pad pressure by the pressure portion 6a). Although a dynamic resistance is added, conventionally, the pad pressing point by the return spring 4 is provided at a position deviated from between the two points b and c, so that the return force is transmitted to the point c where the distance from the point a is large. It is difficult to do so, so that the return of the inner circumference of the pad is insufficient and dragging is still occurring.
【0006】なお、戻しスプリング4のばね力を大きく
してc点にも充分な戻し力が働くようにすると引きずり
をなくせるが、この方法は悪路走行時のピストンノック
バックを助長し、ペダルストロークが伸びるので好まし
くない。It should be noted that if the spring force of the return spring 4 is increased so that a sufficient return force acts on the point c, drag can be eliminated. However, this method promotes piston knockback during traveling on a rough road, and It is not preferable because the stroke is extended.
【0007】[0007]
【課題を解決するための手段】この考案は、スプリング
4のばね力を大きくせずにパッドの引きずりを無くすた
めに、上述のリテーナと戻しスプリングを用いるディス
クブレーキにおいて、戻しスプリングによるパッドの加
圧点を、トルクメンバによるパッドのディスク径方向外
方への移動拘束点と上記リテーナによるパッド加圧点と
に挾まれる領域内に設ける。SUMMARY OF THE INVENTION In order to eliminate the drag of the pad without increasing the spring force of the spring 4, this invention is a disc brake using the above-mentioned retainer and return spring, and pressurizes the pad by the return spring. The points are provided in a region sandwiched between the movement restraint point of the pad by the torque member outward in the disk radial direction and the pad pressing point by the retainer.
【0008】[0008]
【作用】非制動時にパッドが図6のc点を支点に傾いて
ディスクに押し付けられる力F0を、パッドに加わる力
のうち、図6のb点に働く摺動抵抗をf1、c点に働く
摺動抵抗f2、戻しスプリングの力をFとして図7で比
較すると次のようになる。The force F 0 is pressed against the disk tilts [action] is pad during non braking fulcrum point c in FIG. 6, of the force applied to the pad, f 1 the sliding resistance acting on the point b in FIG. 6, point c When the sliding resistance f 2 that acts on and the force of the return spring are F, the comparison is as follows in FIG.
【0009】図7の(A)はパッド加圧点(a点)が
b、c間の外にある従来、(B)はa点をb、c点間に
置いた本願の場合であって、l3は従来が5cm、本考案
が2cm、その他の数値は両者ともl1=1cm、l2=3
cm、f1=1kgfと仮定している。FIG. 7A shows a conventional case in which the pad pressing point (point a) is located outside b and c, and FIG. 7B shows the case of the present invention in which point a is located between points b and c. , L 3 is 5 cm in the past, 2 cm in the present invention, and other numerical values are both l 1 = 1 cm, l 2 = 3
It is assumed that cm and f 1 = 1 kgf.
【0010】従来の構造の場合、力のバランス式 F0a・l1=F・l3−f1・l2 にl3=5の上の数値を当てはめるとF0a=5F−3、 一方、本考案では、 F0b・l1=F・l3−f1・l2 の式にl3=2の上の数値を当てはめるとF0b=2F−
3、 従って、F=3とするとF0a=12kgf、F0b=3kgfと
なり、引きずり力がこのケースでは1/4に減少すること
になる。In the case of the conventional structure, when the force balance equation F 0 a · l 1 = F · l 3 −f 1 · l 2 is applied to the numerical value above l 3 = 5, F 0 a = 5F-3, On the other hand, in the present invention, when the numerical value above l 3 = 2 is applied to the formula of F 0 b · l 1 = F · l 3 −f 1 · l 2 , F 0 b = 2F−
3, therefore, when F = 3, F 0 a = 12 kgf and F 0 b = 3 kgf, and the drag force is reduced to 1/4 in this case.
【0011】[0011]
【実施例】図1は、実施例のディスクブレーキをキャリ
パ(図5、図6の1)を外した状態にしてディスク側か
ら見た図、図2はその上面図、図3は側面図である。図
2、図3ではトルクメンバも省略している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a view seen from the disk side with the caliper (1 in FIGS. 5 and 6) removed from the disk brake of the embodiment, FIG. 2 is its top view, and FIG. 3 is a side view. is there. The torque member is also omitted in FIGS. 2 and 3.
【0012】図に示すように、この考案では、戻しスプ
リング4によるパッド2、3の加圧点(a点)を前述の
b、c点間に挾まれる領域内に設けてある。As shown in the figure, in the present invention, the pressing point (point a) of the pads 2, 3 by the return spring 4 is provided in the area sandwiched between the points b and c.
【0013】スプリング4によるパッドの加圧は、スプ
リング4の両端にディスク軸方向に屈曲した足部4aを
設け、その足部をパッドの裏板に設けた係止穴7に裏板
の前面から挿入して行うとスプリング4を着脱し易い
が、これに限定されるものではない。To press the pad by the spring 4, foot portions 4a bent in the disc axial direction are provided at both ends of the spring 4, and the foot portions are inserted into locking holes 7 provided in the back plate of the pad from the front surface of the back plate. The spring 4 can be easily attached and detached by inserting it, but the present invention is not limited to this.
【0014】また、図のような係止構造にする場合に
は、パッドがフル摩耗してもスプリングがディスクに接
触しないようにするため、裏板の前面に係止穴7の部分
から裏板外周に至る溝8(図4参照)を設けてその溝に
スプリング4の一部(裏板前面に添う部分)を沈み込ま
せるのが望ましい。このようにしておくと、スプリング
4が足部4aを支点にして回転することも防止されるの
で、スプリング中央部がディスクDの外周に接触して折
損すると云う問題も併せて解決できる。Further, in the case of the locking structure as shown in the figure, in order to prevent the spring from coming into contact with the disc even when the pad is fully worn, the locking hole 7 is provided on the front surface of the back plate from the back plate. It is desirable to provide a groove 8 (see FIG. 4) that extends to the outer periphery and allow a part of the spring 4 (a portion along the front surface of the back plate) to be submerged in the groove. By doing so, the spring 4 is also prevented from rotating around the foot portion 4a as a fulcrum, so that the problem that the central portion of the spring comes into contact with the outer periphery of the disk D and breaks can also be solved.
【0015】なお、a点はb、c点に作用するばね力の
差を小さくするために、できればb、c点間の中央部に
位置させるのがよい。In order to reduce the difference in spring force acting on points b and c, point a is preferably located in the center between points b and c, if possible.
【0016】[0016]
【考案の効果】以上述べたように、この考案では戻しス
プリングによるパッド加圧点を摺動抵抗を生じる2点
間、即ちトルクメンバによるパッドのディスク径方向外
方への移動拘束点とリテーナによるパッド加圧点間に設
けてそれ等の個所に伝わる戻しスプリングの力の差を小
さくしたので、ばね力を大きくしなくてもパッドの全体
を平均点に押し戻すことができ、ピストンノックバック
によるペダルストロークの延びを招かずに非制動時の引
きずりを軽減して燃費を向上させるのに役立つ。As described above, according to the present invention, the pad pressurizing point by the return spring is between the two points that generate sliding resistance, that is, the pad is constrained by the torque member to the radial outward movement of the disk and the retainer. Since the difference between the force of the return springs that are transmitted between the pad pressure points is reduced, the entire pad can be pushed back to the average point without increasing the spring force. It is useful for reducing drag during non-braking without increasing stroke and improving fuel efficiency.
【図1】実施例のブレーキをキャリパを外してディスク
側から見た図FIG. 1 is a view of a brake according to an embodiment as seen from a disc side with a caliper removed.
【図2】実施例のブレーキをキャリパ、トルクメンバを
省いて示す上面図FIG. 2 is a top view showing the brake of the embodiment with the caliper and the torque member omitted.
【図3】同上の側面図FIG. 3 is a side view of the above.
【図4】スプリング係止部の変形例を示す斜視図FIG. 4 is a perspective view showing a modified example of a spring locking portion.
【図5】従来ブレーキの一部破断上面図FIG. 5 is a partially cutaway top view of a conventional brake.
【図6】図5のX−X線部の断面図6 is a cross-sectional view taken along the line XX of FIG.
【図7】パッドがディスクに接する力を比較するための
図であり、(A)が従来、(B)が本考案7A and 7B are views for comparing the force with which a pad contacts a disc, where FIG. 7A is a conventional device and FIG.
1 キャリパ 2、3 パッド 4 戻しスプリング 4a 足部 5 トルクメンバ 6 リテーナ 7 係止穴 8 溝 a スプリング4によるパッド加圧点 b パッドのディスク径方向外方への移動拘束点 c リテーナによるパッド加圧点 1 Caliper 2, 3 Pad 4 Return Spring 4a Foot 5 Torque Member 6 Retainer 7 Locking Hole 8 Groove a Pad Pad Pressing Point by Spring 4 b Pad Movement Limit Point to Disk Radial Direction c Pad Pressing by Retainer point
Claims (3)
トルクメンバのパッドスライド部に装着したリテーナで
ディスク中心から離れる方向に加圧し、かつ、その対の
パッド間にディスクを跨いで装着した戻しスプリングで
ディスクから離反する方向に加圧したディスクブレーキ
において、戻しスプリングによる摩擦パッドの加圧点
を、トルクメンバによるパッドのディスク径方向外方へ
の移動拘束点と上記リテーナによるパッド加圧点とに挾
まれる領域内に設けたことを特徴とするディスクブレー
キ。1. A pair of friction pads for gripping a disk,
In a disc brake in which pressure is applied in a direction away from the center of the disc by a retainer attached to the pad slide part of the torque member, and pressure is applied in a direction away from the disc by a return spring attached across the disc between the pair of pads, A disk characterized in that the pressing point of the friction pad by the return spring is provided in a region sandwiched between the point where the torque member restrains the movement of the pad radially outward of the disk and the pad pressing point by the retainer. brake.
屈曲した足部を設け、この足部を摩擦パッドの裏板に設
けた係止穴に裏板前面側から挿入して当該部で戻しスプ
リングによるパッドの加圧を行うようにした請求項1記
載のディスクブレーキ。2. A foot which is bent in the axial direction of the disc is provided at both ends of the return spring, and the foot is inserted into a locking hole provided in the back plate of the friction pad from the front side of the back plate, and the return spring is provided at that part. The disc brake according to claim 1, wherein the pad is pressed by the above method.
る溝を上記係止穴から裏板外周に至らしめて設けた請求
項2記載のディスクブレーキ。3. The disc brake according to claim 2, wherein a groove for fitting a return spring is provided on the front surface of the back plate so as to extend from the locking hole to the outer periphery of the back plate.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP40018090U JP2510665Y2 (en) | 1990-12-07 | 1990-12-07 | Disc brake |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP40018090U JP2510665Y2 (en) | 1990-12-07 | 1990-12-07 | Disc brake |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0487035U JPH0487035U (en) | 1992-07-29 |
JP2510665Y2 true JP2510665Y2 (en) | 1996-09-18 |
Family
ID=31878467
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP40018090U Expired - Fee Related JP2510665Y2 (en) | 1990-12-07 | 1990-12-07 | Disc brake |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2510665Y2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009041769A (en) * | 2007-07-17 | 2009-02-26 | Hitachi Ltd | Disk brake |
-
1990
- 1990-12-07 JP JP40018090U patent/JP2510665Y2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH0487035U (en) | 1992-07-29 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
LAPS | Cancellation because of no payment of annual fees |