JPS6235122A - Actuator for disk brake - Google Patents
Actuator for disk brakeInfo
- Publication number
- JPS6235122A JPS6235122A JP60175351A JP17535185A JPS6235122A JP S6235122 A JPS6235122 A JP S6235122A JP 60175351 A JP60175351 A JP 60175351A JP 17535185 A JP17535185 A JP 17535185A JP S6235122 A JPS6235122 A JP S6235122A
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- bag
- actuator
- friction material
- wall
- 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.)
- Granted
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
- F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
-
- 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
- F16D2125/00—Components of actuators
- F16D2125/02—Fluid-pressure mechanisms
- F16D2125/14—Fluid-filled flexible members, e.g. enclosed air bladders
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、流体圧によって作動するディスクブレーキ
用アクチュエータ、特に、ブレーキの寸法を大きくせず
に制動力を増大させ得るアクチュ二一夕に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an actuator for a disc brake operated by fluid pressure, and particularly to an actuator that can increase braking force without increasing the size of the brake.
ディスクロータ(以下では単にディスクと云う)を両側
から押圧して制動力を発生させるディスクブレーキには
、(1)入力に比例したブレーキ力が得られる。(2)
ディスクの遠心力で泥水を振り飛ばすので水濡回復性が
良い。(3)摩擦材の交換等のメンテナンスが容易であ
ると云った利点がある。A disc brake that generates braking force by pressing a disc rotor (hereinafter simply referred to as a disc) from both sides can (1) obtain a braking force proportional to the input. (2)
The centrifugal force of the disc shakes off muddy water, so it has good water recovery properties. (3) There is an advantage that maintenance such as replacement of friction materials is easy.
ところで、ディスクブレーキの7クチユエータとしては
、伝統的に円形のシリンダと液圧作動ピストンを組合せ
たものが採用されているが、このアクチュエータは流体
圧の受圧面が円をなすので限られた半径方向スペース内
で大きな出力を得ることが難しく、従って在来のディス
クブレーキをドラムブレーキの採用されているような組
付スペースの狭い車輌、例えばホイールサイズが小さく
、かつ、ステアリング機構の一部が内蔵されている小型
フォークリフト車等の車輌にドラムブレーキに代えて塔
載し、上記の利点を生かそうとした場合、スペース的な
制限により小径のピストンを同一円周上に数個配列して
所要のブレーキ力を確保することになる。ところが、数
個のピストンを1つのキャリパボディに組込むと、キャ
リパボディのディスク周方向寸法が太き(なってスペー
ス面でディスクブレーキの採用が不可能になることがあ
る。By the way, the 7-actuator for disc brakes has traditionally been a combination of a circular cylinder and a hydraulically actuated piston, but since this actuator has a circular fluid pressure receiving surface, it can only be used in a limited radial direction. It is difficult to obtain a large output within a space, so conventional disc brakes are replaced with drum brakes on vehicles with narrow assembly space, such as those with small wheels and a part of the steering mechanism built-in. When trying to take advantage of the above advantages by installing a drum brake on a vehicle such as a small forklift truck, due to space limitations, it is necessary to arrange several small-diameter pistons on the same circumference to achieve the required brake. It will secure power. However, when several pistons are assembled into one caliper body, the caliper body becomes thick in the circumferential direction of the disc (which may make it impossible to use a disc brake due to space considerations).
また、シリンダ間の作動液の連絡路が複雑になるとか、
部品点数が増えると云った製造コストへの影響も無視出
来ない。Also, the communication path for hydraulic fluid between cylinders becomes complicated.
The impact on manufacturing costs due to an increase in the number of parts cannot be ignored.
この発明は、か\る問題点を無くすため、キャリパボデ
ィを大きくせずに制動力を増大させることができるホイ
ールとハブ間の環状空間を最大限に活用したアクチュエ
ータを提供することを目的としている。In order to eliminate such problems, the present invention aims to provide an actuator that makes maximum use of the annular space between the wheel and the hub, which can increase braking force without increasing the size of the caliper body. .
上記の目的を達成するため、この発明ではキャリパボデ
ィに形成するシリンダを非円形とした。In order to achieve the above object, in the present invention, the cylinder formed in the caliper body is made non-circular.
また、そのシリンダ内には一端の開放した膜状弾性体の
袋を内壁に沿って挿入し、この袋の一端側壁を全周に亘
ってシリンダの奥所をこ挾着保持した。Further, a bag made of a film-like elastic material with one end open was inserted into the cylinder along the inner wall, and the side wall of the one end of the bag was clamped and held at the inner part of the cylinder over the entire circumference.
さらに、弾性体の袋Oこは、周壁をシリンダ内壁との同
番こ挿入し、周壁に連なる底励を摩擦材の裏板との開に
介在するカップ状のリテーナを被せ、内面に流体圧を受
ける上記袋の膨張力をこのリテーナを介して摩擦材に伝
達し、その力でH追付を前進せしめてディスクに摺接さ
せるようにした。Furthermore, the elastic bag Oko is inserted with the peripheral wall at the same number as the inner wall of the cylinder, and a cup-shaped retainer interposed between the bottom excitation connected to the peripheral wall and the back plate of the friction material is placed, and a fluid pressure is applied to the inner surface. The expansion force of the bag receiving the disk is transmitted to the friction material through this retainer, and the force is used to advance the H-mounter so that it comes into sliding contact with the disk.
以上の如く構成されたアクチュエータは、シリンダの断
面形状を矩形とすることができるので、流体圧の受圧面
積がディスクの半径方向及び周方向寸法の等しい円形受
圧面に比して増大し、このため、受圧面積によって決定
される制動力も増大する。従って、アクチュエータを複
数に分けずに必要な制動力を確保でき、組付はスペース
の制限が緩和される。In the actuator configured as described above, since the cross-sectional shape of the cylinder can be rectangular, the pressure-receiving area of the fluid pressure is larger than that of a circular pressure-receiving surface with equal radial and circumferential dimensions of the disk. , the braking force determined by the pressure receiving area also increases. Therefore, the necessary braking force can be secured without dividing the actuator into a plurality of parts, and space restrictions for assembly are alleviated.
添付図に、この発明の浮動型ディスクブレーキへの適用
例を示す。The attached drawings show an example of application of the present invention to a floating disc brake.
第1図乃至第3図の符号1はディスクD(第1図)を跨
ぐキャリパボディで、このボディは、ディスクの片面側
に非円形のシリンダ2を備える基部3と、それにボルト
止めしたカバー4から成る。5はディスクの回入側と回
出側に設けたスライド部6.6′を介してキャリパボデ
ィをディスク軸方向に摺動自在に保持し、さらに、ディ
スクの両面に対向させた摩擦材7.7′ も同一方向に
摺動自在に保持するトルクメンバ、8はリトラクション
プレート9を含む摩擦材の間隙調整機構である。Reference numeral 1 in FIGS. 1 to 3 is a caliper body that straddles the disk D (FIG. 1), and this body consists of a base 3 having a non-circular cylinder 2 on one side of the disk, and a cover 4 bolted to it. Consists of. Reference numeral 5 holds the caliper body slidably in the disk axial direction via slide portions 6.6' provided on the insertion side and the rotation side of the disk, and furthermore, friction materials 7.5 are opposed to both surfaces of the disk. 7' is also a torque member which is slidably held in the same direction, and 8 is a friction material gap adjustment mechanism including a retraction plate 9.
この発明のアクチュエータ10は、上記シリンダ2と、
その中に挿入した膜状弾性体の袋11と、この袋の外面
に被せるリテーナ12から成る。The actuator 10 of the present invention includes the cylinder 2,
It consists of a membrane-like elastic bag 11 inserted into the bag 11 and a retainer 12 placed over the outside of the bag.
シリンダ2は第2図Qこ示すように矩形であり、その奥
所には基部のカバー取付面に抜ける大径部13が形成さ
れている。The cylinder 2 has a rectangular shape as shown in FIG. 2Q, and a large diameter portion 13 is formed in the inner part of the cylinder 2 so as to pass through to the cover mounting surface of the base.
袋11は、一端を開放させたもので、図のようにシリン
ダ2の内壁に沿う周壁11aの開口側端部にフランジl
lbをつけ、周壁の反対側の端部にはシリンダの開口を
塞ぐ底壁11cを連設したカップ状のものが望ましく、
そのフランジ11bを」二記大径部13の端部と大径部
に挿入してカバー4により加圧した密封板14との間に
挾持する。The bag 11 has one end open, and a flange l is attached to the open end of the peripheral wall 11a along the inner wall of the cylinder 2 as shown in the figure.
lb, and a cup-shaped one with a bottom wall 11c connected to the end opposite to the peripheral wall that closes the opening of the cylinder is desirable.
The flange 11b is held between the end of the large diameter section 13 and a sealing plate 14 which is inserted into the large diameter section and pressurized by the cover 4.
リテーナ12は、袋11とシリンダ内壁との間に挿入す
る周壁12aの一端に底壁12bを連ねたカップ状とし
、底壁12bが袋11と摩擦材7の裏板7aとの間に位
置するように袋に被せる。The retainer 12 has a cup shape with a bottom wall 12b connected to one end of a peripheral wall 12a inserted between the bag 11 and the inner wall of the cylinder, and the bottom wall 12b is located between the bag 11 and the back plate 7a of the friction material 7. Cover the bag like this.
このリテーナには作動流体の圧力で変形しない剛性を付
与しておく、金属板をプレス成形したものであればその
要求に応えることができる。This requirement can be met if the retainer is press-formed from a metal plate and has rigidity that does not deform under the pressure of the working fluid.
符号15は、カバー4に設けた流体圧の導入孔で、この
孔は、シリンダ2の一端を閉鎖する密封板14に設けた
貫通孔16を介してシリンダ2の内室に通じている。ま
た、シリンダ内の空気抜きのため、密封板14にはブリ
ーダバルブ17への連絡孔18に通じる溝19を設けで
ある。さらに、カバー4の接合界面には流体圧の遺漏防
止のため、連絡孔18の連結部を取巻くシール20と、
カバー4と密封板14の面取りされた後面外周との間に
位置してシリンダ部をシールするO型シール21をめぐ
らしてあり、こ゛のため、シリンダ2の内部は密封状態
に保たれ、そこに流体圧が導入されると袋11がバルー
ンとなって動きの拘束されないディスク側に膨らみ、摩
擦材を押圧する。Reference numeral 15 denotes a fluid pressure introduction hole provided in the cover 4, and this hole communicates with the inner chamber of the cylinder 2 via a through hole 16 provided in a sealing plate 14 that closes one end of the cylinder 2. Further, in order to vent air within the cylinder, the sealing plate 14 is provided with a groove 19 communicating with a communication hole 18 to the bleeder valve 17. Further, a seal 20 surrounding the connecting portion of the communicating hole 18 is provided at the joint interface of the cover 4 to prevent leakage of fluid pressure.
An O-type seal 21 is placed between the cover 4 and the outer periphery of the chamfered rear surface of the sealing plate 14 to seal the cylinder part. When fluid pressure is introduced, the bag 11 becomes a balloon and inflates toward the disk side where movement is not restricted, pressing the friction material.
次に、摩擦材の間隙調整機構8について述べる。Next, the friction material gap adjustment mechanism 8 will be described.
この調整機構は、シリンダ2を基準にしてディスクの回
入側と回出側の2個所に設けられる。2つの調整機構は
同一構成であって、第3図に示すように、摩擦材7とリ
テーナ12との間に挾み込むリトラクションプレート9
と、キャリパボディ1に保持されるディスク軸方向のり
トラクタピン22と、一端をプレート9に固着してビン
22を包囲したスリーブ23と、ビン22の先端に後記
リトラクタスプリングの付勢圧よりも若干大きな摺動抵
抗を生じるように外嵌して一端をプレート9に当接させ
るリトラクションブツシュ24と、そのブツシュに被せ
たハウジング25とスリーブ23内面のスナップリング
26に支持される座板27との間に懸架したりトラクタ
スプリング28から成り、制動時にプレート9に追従す
る座板27がハウジング25に当接してブツシュをビン
22に対してライニング7b、7b’ の摩耗量相当
分スライドさせ、除圧時に常時一定した量へ×だけ摩擦
材をディスクから自動的に離反させる。This adjustment mechanism is provided at two locations, one on the insertion side and one on the rotation side of the disk, with the cylinder 2 as a reference. The two adjustment mechanisms have the same configuration, and as shown in FIG. 3, a retraction plate 9 is inserted between the friction material 7 and the retainer 12.
A retractor pin 22 held in the caliper body 1 in the disk axial direction, a sleeve 23 whose one end is fixed to the plate 9 and surrounds the bin 22, and a pressure slightly greater than the biasing pressure of the retractor spring described later at the tip of the bin 22. A retraction bushing 24 that is fitted externally to create a large sliding resistance and has one end abutted against the plate 9, a housing 25 that covers the bushing, and a seat plate 27 that is supported by a snap ring 26 on the inner surface of the sleeve 23. The seat plate 27, which is suspended between the wheels and consists of a tractor spring 28 and follows the plate 9 during braking, comes into contact with the housing 25 and slides the bush against the bin 22 by an amount equivalent to the amount of wear on the linings 7b and 7b'. When pressure is applied, the friction material is automatically separated from the disk by a constant amount x.
△Xは、浮動型ディスクブレーキの場合、対の摩擦材7
.7′がディスクから離れる量の和であり、各摩擦材の
ディスクに対する間隙は各々△X/2に保たれる。29
はスリーブの外周をシールするシール材である。△X is the pair of friction materials 7 in the case of a floating disc brake.
.. 7' is the sum of the distances from the disk, and the gap between each friction material and the disk is maintained at ΔX/2. 29
is a sealing material that seals the outer periphery of the sleeve.
スライド部6.6′は、一方の摩擦材をアクチュエータ
で押圧し、他方の摩擦材は反力で移動したキャリパのア
ウター爪で押圧する浮動型ディスクブレーキにおいては
、他方の摩擦材への反力の伝達とライニングの摩耗量吸
収のためにキャリパボディをアクチュエータ側に移動さ
せる必要があるのでその移動ガイドとして設けられるも
ので周知の構造でよい。図のそれは、両方を第4図に示
す構成、即ち、キャリパボディ1に螺着したスライドビ
ン30のステム30aをトルクメンバ5の貫通孔31に
組込まれたゴム製のビンブーツ32に摺動自在に挿入し
た構成とするか又は一方は第4図の構成、他方はスライ
ドピンのステム上にトルクメンバの孔に直接挿入されて
両端がブーツで封止されるガイドスリーブを備える構成
とされている。In a floating type disc brake, where one friction material is pressed by an actuator and the other friction material is pressed by the outer claw of the caliper moved by the reaction force, the slide portion 6.6' is configured to handle the reaction force on the other friction material. Since it is necessary to move the caliper body toward the actuator side in order to transmit the noise and absorb the amount of wear on the lining, a well-known structure may be used as a movement guide. In the figure, both are configured as shown in FIG. One of them has the configuration shown in FIG. 4, and the other has a guide sleeve on the stem of the slide pin that is directly inserted into the hole of the torque member and sealed at both ends with boots.
符号33はトルクメンバに設けた摩擦材7.7′のガイ
ド溝、34は摩擦材の裏板側面を当接させるトルク受は
面である。Reference numeral 33 indicates a guide groove of the friction material 7, 7' provided in the torque member, and 34 indicates a surface of the torque receiver against which the side surface of the back plate of the friction material comes into contact.
なお、この発明のアクチュエータは、キャリパ浮動型、
固定型を問わず、流体圧を作動源とするディスクブレー
キの全てに適用できる。Note that the actuator of this invention is a floating caliper type,
It can be applied to all disc brakes that use fluid pressure as an operating source, regardless of fixed type.
以上述べたように、この発明によれば、非円形のシリン
ダ内に導入される流体圧を弾性体の袋の内面に作用させ
、その袋の膨張力を利用して摩擦材をディスクに摺接さ
せるようにしたので、限られたスペース内で流体圧の受
圧面積を最大限に増加させて制動力を高めることが可能
になる。つまり、小型のディスクブレーキで大きな出力
が得られ、このため、ブレーキ組込み時のスペー゛ス的
な制限が緩和される。As described above, according to the present invention, the fluid pressure introduced into the non-circular cylinder is applied to the inner surface of the elastic bag, and the expansion force of the bag is used to slide the friction material against the disk. This makes it possible to maximize the fluid pressure receiving area within a limited space and increase the braking force. In other words, a large output can be obtained with a small disc brake, which eases space restrictions when installing the brake.
また、弾性体によって形成される受圧体(袋)は成形が
容易であり、ピストンに比べて材料も安くつくこと、そ
の受圧体の膨張、収納を利用して摩擦材を押圧するので
゛、ピストンを使用するときに必要な摺動面の精密加工
が不要で鋳造シリンダをそのま\使用できること、シリ
ンダが1個であるので作動流体圧の連絡路を加工せずに
済むこと、その他の部品点数も少なくて済むこと等によ
りブレーキの製造、コスト面でも有利となる。In addition, the pressure receiving body (bag) formed of an elastic body is easy to mold, and the material is cheaper than a piston, and the expansion and storage of the pressure receiving body is used to press the friction material. The cast cylinder can be used as is without the need for precision machining of the sliding surface, which is required when using a cylinder, and since there is only one cylinder, there is no need to machining the working fluid pressure communication path, and the number of other parts It is also advantageous in terms of manufacturing and cost of the brake, as less is required.
第1図は、この発明のアクチュエータを採用したディス
クブレーキの一例をディスク軸方向の線に沿って切断し
た断面図、第2図はその一部切欠き正面図、第3図は同
じく一部を切欠いた状態の平面図、第4図は第2図のA
−A線に沿った断面図である。
1・・・キャリパボディ、2・・・シリンダ、3・・・
基部、4・・・カバー、5・・・トルクメンバ、6.6
′・・・スライド部、7.7′・・・摩擦材、8・・・
摩擦材の間隙調整機構、10・・・アクチュエータ、1
1・・・弾性体の袋、12・・・リテーナ、14・・・
密封板、21・・・0型シールFig. 1 is a cross-sectional view of an example of a disc brake employing the actuator of the present invention taken along the axial line of the disc, Fig. 2 is a partially cutaway front view, and Fig. 3 is a partially cutaway view. A plan view of the cutaway state, Figure 4 is A of Figure 2.
- It is a sectional view along the A line. 1... Caliper body, 2... Cylinder, 3...
Base, 4... Cover, 5... Torque member, 6.6
'...Slide part, 7.7'...Friction material, 8...
Friction material gap adjustment mechanism, 10... actuator, 1
1... Elastic bag, 12... Retainer, 14...
Sealing plate, 21...0 type seal
Claims (1)
内壁に沿ってシリンダ内に挿入し、開放した一端の縁壁
を全周に亘ってシリンダの奥所に挾着保持する膜状弾性
体の袋と、その袋に被せて周壁をシリンダ内壁との間に
挿入し、周壁に連なる底壁を摩擦材の裏板との間に介在
するカップ状リテーナとで構成され、上記袋がシリンダ
内への導入流体圧を内面に受け、リテーナを介した摩擦
材を押圧前進せしめてディスクロータに摺接させる如く
構成されたディスクブレーキ用アクチュエータ。A non-circular cylinder formed in the caliper body, and a membrane-like elastic bag that is inserted into the cylinder along its inner wall, and the open edge wall of one end is clamped and held deep inside the cylinder around the entire circumference. and a cup-shaped retainer, the peripheral wall of which is placed over the bag and inserted between the inner wall of the cylinder, and the bottom wall connected to the peripheral wall is interposed between the back plate of the friction material, and the bag is inserted into the cylinder. An actuator for a disc brake configured to receive introduced fluid pressure on its inner surface to press and advance a friction material through a retainer so as to come into sliding contact with a disc rotor.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP60175351A JPH0617701B2 (en) | 1985-08-07 | 1985-08-07 | Actuator for disk break |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP60175351A JPH0617701B2 (en) | 1985-08-07 | 1985-08-07 | Actuator for disk break |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6235122A true JPS6235122A (en) | 1987-02-16 |
JPH0617701B2 JPH0617701B2 (en) | 1994-03-09 |
Family
ID=15994548
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP60175351A Expired - Lifetime JPH0617701B2 (en) | 1985-08-07 | 1985-08-07 | Actuator for disk break |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0617701B2 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5259484A (en) * | 1991-02-15 | 1993-11-09 | Nissin Kogyo Co., Ltd. | Reaction force type disc brake |
US5259483A (en) * | 1992-02-13 | 1993-11-09 | Pelfrey Rick D | Low profile disk brake caliper |
KR100917160B1 (en) | 2009-06-03 | 2009-09-21 | 박중화 | Oil leak prevention device for calliper breake |
US20140216864A1 (en) * | 2011-09-06 | 2014-08-07 | Tsutomu Suzuki | Caliper brake apparatus |
DE102020200132A1 (en) * | 2020-01-08 | 2021-07-08 | Zf Friedrichshafen Ag | Carrier device and disc brake |
-
1985
- 1985-08-07 JP JP60175351A patent/JPH0617701B2/en not_active Expired - Lifetime
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5259484A (en) * | 1991-02-15 | 1993-11-09 | Nissin Kogyo Co., Ltd. | Reaction force type disc brake |
US5259483A (en) * | 1992-02-13 | 1993-11-09 | Pelfrey Rick D | Low profile disk brake caliper |
KR100917160B1 (en) | 2009-06-03 | 2009-09-21 | 박중화 | Oil leak prevention device for calliper breake |
US20140216864A1 (en) * | 2011-09-06 | 2014-08-07 | Tsutomu Suzuki | Caliper brake apparatus |
US9308924B2 (en) * | 2011-09-06 | 2016-04-12 | Kyb Corporation | Caliper brake apparatus |
DE102020200132A1 (en) * | 2020-01-08 | 2021-07-08 | Zf Friedrichshafen Ag | Carrier device and disc brake |
Also Published As
Publication number | Publication date |
---|---|
JPH0617701B2 (en) | 1994-03-09 |
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