JPS596440A - Automatic clearance regulator - Google Patents

Automatic clearance regulator

Info

Publication number
JPS596440A
JPS596440A JP58105065A JP10506583A JPS596440A JP S596440 A JPS596440 A JP S596440A JP 58105065 A JP58105065 A JP 58105065A JP 10506583 A JP10506583 A JP 10506583A JP S596440 A JPS596440 A JP S596440A
Authority
JP
Japan
Prior art keywords
key shaft
key
sleeve
members
rack
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
Application number
JP58105065A
Other languages
Japanese (ja)
Other versions
JPH0427411B2 (en
Inventor
スベン・エリク・カレフ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of JPS596440A publication Critical patent/JPS596440A/en
Publication of JPH0427411B2 publication Critical patent/JPH0427411B2/ja
Granted legal-status Critical Current

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
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/561—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting within the confines of a drum brake
    • F16D65/562—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting within the confines of a drum brake arranged between service brake actuator and braking member, and subjected to service brake force
    • 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
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/26—Cranks
    • 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
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/28—Cams; Levers with cams
    • F16D2125/30—Cams; Levers with cams acting on two or more cam followers, e.g. S-cams

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

【発明の詳細な説明】 本発明はキ一部材によシ作動される車両用ブレーキ装置
の自動すきま調整装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an automatic clearance adjustment device for a vehicle brake system operated by a key member.

本発明においてキ一部材はシリンダ・ピストン装置を作
動する作動装置に連結されたキーシャフトに装着される
。キ一部材は力伝達部材を介し一対のブレーキ片な作動
する。又各力伝達部材は互いに延線動作可能な２つの延
線部材からなシ、一方のロンド状の延線部材の外周面並
びに他方のスリーブ状の姑縮部材の内周面にネジ山が形
成されている。２つのスリーブ状の延線部材の各外周面
には、歯部でなるラックが具備され、ラックはキ−シャ
フトに軸支される輪体の片面において半径方向に延設さ
れた溝と協働可能に設けられている。In the present invention, the key member is mounted on a key shaft connected to an actuating device for actuating the cylinder-piston device. The key member operates the pair of brake pieces via the force transmission member. In addition, each force transmitting member is composed of two wire-stretching members that can extend each other, and threads are formed on the outer peripheral surface of one of the wire-shaped wire members and the inner peripheral surface of the sleeve-like compression member of the other. has been done. Each outer circumferential surface of the two sleeve-like elongated wire members is provided with a rack consisting of teeth, and the rack cooperates with a groove extending radially on one side of the ring body pivoted on the key shaft. possible.

又、輪体に設けられた溝は、ラックが輪体に対し半径方
向妬移動されるときスリーブ状の延線部材の双方にトル
クが与えられ２つの力伝達部材の全長が増大され得るよ
う構成されている。Additionally, the groove provided in the wheel body is configured such that when the rack is moved in a radial direction relative to the wheel body, a torque can be applied to both of the sleeve-like elongated wire members and the overall length of the two force transmitting members can be increased. has been done.

この種の従来の自動すきま調整装置は、米国特許第３，
８９１，０６８号および第４，１６１，９９９号に開示
される。This type of conventional automatic clearance adjustment device is disclosed in U.S. Patent No. 3,
No. 891,068 and No. 4,161,999.

しかしながら実際上従来の自動すきま調整装置はその動
作が著しく緩慢であるため、制動時に行なわれるすきま
調整量を極めて小さくする必要がある。即ちすきま調整
量を極めて小さくした場合短時間にブレーキ面が摩耗し
且加熱されて調整を要するすきまが大となシ、調整量が
大巾に狂うことになる。仮に自動すきま調整作用が適度
に緩徐であれば、制動動作を重ねて摩耗を生ずると共に
ブレーキドラムが加熱されても調整量が大巾に狂うこと
はない。However, in practice, the conventional automatic clearance adjustment device operates extremely slowly, so it is necessary to make the amount of clearance adjustment performed during braking extremely small. That is, if the amount of clearance adjustment is made extremely small, the brake surface will wear and heat up in a short period of time, resulting in a large clearance that requires adjustment, and the amount of adjustment will be greatly deviated. If the automatic clearance adjustment action is suitably slow, the amount of adjustment will not be significantly deviated even if repeated braking operations cause wear and the brake drum is heated.

換言すれば自動すきま調整が過度に緩慢に行なわれるよ
う構成されると、適正のすきまを得るために極めて多数
回の制動動作が必要であり、且充分適正なすきまを得る
ことができなかった。この欠点を除去するには自動すき
ま調整装置の構成部材の製造精度および取付精度を高め
る必要があった。In other words, if the automatic clearance adjustment is performed too slowly, an extremely large number of braking operations are required to obtain an appropriate clearance, and it is not possible to obtain a sufficiently appropriate clearance. In order to eliminate this drawback, it was necessary to improve the manufacturing accuracy and mounting accuracy of the components of the automatic clearance adjustment device.

一般にすきま調整動作は、ブレーキ装置の固定部材に対
し制動力を伝達する部材が過度に移動される場合、ある
いは２つの力伝達部材が相対的に過度に移動される場合
に実現される。Generally, the clearance adjustment operation is realized when a member that transmits braking force is moved excessively with respect to a fixed member of a brake device, or when two force transmitting members are relatively moved excessively.

前者の場合、固定部拐の取付位置が正確でなかったり固
定部材の次の変位位置が正確に位置決めされるよう構成
されていない場合すきまの調整量が適正でなくなること
が理解されよう。後者の場合は、正確にある平面上にお
いて移動可能に構成すること又は正確な角度で偏位可能
に設けること如よシ所望のすきまを得るように作動され
るので、適正なすきまを得ることができる。本発明は後
者の場合如属する。すきま調整装置は一度ブレーキ装置
に組み込まれると正確に取シ付けられたか否かを点検す
ることは実質的に不可能である。In the former case, it will be understood that if the mounting position of the fixing member is not accurate or the structure is not configured such that the next displacement position of the fixing member is accurately positioned, the amount of adjustment of the clearance will not be appropriate. In the latter case, it is possible to obtain the desired clearance by configuring it to be movable on a precise plane or by providing it so that it can be deflected at a precise angle, so that it is difficult to obtain the appropriate clearance. can. The present invention pertains to the latter case. Once the clearance adjustment device is incorporated into the brake device, it is virtually impossible to check whether it has been installed correctly.

本発明の一目的はすきま調整に主として寄与する部拐が
取付中又は取付後にあっても実質的に変位されない自動
すきま調整装置を提供することにある。このため現場で
の点検が不必要となり適正なすきまが常に得られる。One object of the present invention is to provide an automatic clearance adjustment device in which the part that mainly contributes to clearance adjustment is not substantially displaced during or after installation. This eliminates the need for on-site inspections and ensures that appropriate clearances are always obtained.

本発明による自動すきま調整装置は又、車輪の軸方向に
延びる第２の面にキーシャフトに固設される弾性のバネ
ラッチ部材を受容可能な半径方向に延びる溝および棟部
が形成されていることを特徴とする。The automatic clearance adjustment device according to the present invention is further characterized in that a radially extending groove and a ridge portion capable of receiving an elastic spring latch member fixed to the key shaft are formed on the second surface extending in the axial direction of the wheel. It is characterized by

以下本発明による自動すきま調整装置を好ましい実施例
に沿って説明する。The automatic gap adjusting device according to the present invention will be explained below along with preferred embodiments.

第１図乃至第８図を参照するに本発明のすきま調整装置
を具備したブレーキ装置が示されている。Referring to FIGS. 1 to 8, a brake device equipped with a clearance adjustment device of the present invention is shown.

ブレーキ装置のシリンダ・ピストンを作動する作８　装
置１　（１）にはピストンロッド（２）が具備され、ピ
ストンロッド（２）の先端部にはキーシャフト（４）に
連結されたレバー（３）が枢支されている。一方前記キ
ーシャフト（４）は車輪（図示せず）に固設されたブレ
ーキドラム（５）内に突入されている。又、キーシャフ
ト（４）にはキ一部材（６）が装着され、キ一部材（６
）は力伝達部材（７１、（８）の凸状の端面を受容する
凹状のくほみ部を有している。前記力伝達部材（７１、
（８）は夫々互いに延線可能な２延縄部材（９）、θＯ
並びにｄｌｌ　。Operation 8 for operating the cylinder/piston of a brake device Device 1 (1) is equipped with a piston rod (2), and the tip of the piston rod (2) has a lever (3) connected to a key shaft (4). is supported. On the other hand, the key shaft (4) is inserted into a brake drum (5) fixed to a wheel (not shown). Further, a key member (6) is attached to the key shaft (4).
) has a concave recess that receives the convex end surface of the force transmitting member (71, (8)).
(8) are two longline members (9) that can be extended to each other, respectively, and θO
and dll.

（１２）からなる。又、力伝達部側（７１、（８）は夫
々ライニング萌、（至）を具備するブレーキ片α３．（
１４１に連係される。当該ブレーキ装置は第１図の状態
では解放位置にある、すなわちライニングθＧ、ａＧと
ブレーキドラム（５）の内面との間に間隙が存在してい
る。It consists of (12). In addition, the force transmitting part side (71, (8) is a brake piece α3.(
141. The brake device is in the release position in the state shown in FIG. 1, that is, a gap exists between the linings θG, aG and the inner surface of the brake drum (5).

制動動作は先ず圧縮空気を作動装置（１）ＶＣ供給する
ことによシ開始される。圧縮空気が作動装置（１）に供
給されると、ピストンロッド（２）が押進されレバー（
３）を介してキーシャフト（４）が回転される。キーシ
ャフト（４）の回転に伴いキ一部拐（６）が回転され力
伝達部材（７）　、　（８］が駆動されて、これによシ
ブレーキ片Ｑ３．α４のライニングＱ１１９　、　Ｑｅ
がブレーキドラム（５）に対し当接されることになる（
％に第２図参照）。The braking operation is first started by supplying compressed air to the actuating device (1) VC. When compressed air is supplied to the actuator (1), the piston rod (2) is pushed forward and the lever (
3) the key shaft (4) is rotated. As the key shaft (4) rotates, the key part (6) rotates and the force transmitting members (7) and (8) are driven, which in turn drives the linings Q119 and Qe of the brake pieces Q3 and α4.
will come into contact with the brake drum (5) (
% (see Figure 2).

この場合、所定の時間内に所定の制動力を得るため伝達
する力を大巾に変化させ続けると、ライニンｙａｅ、（
イ）およびブレーキドラム（５）に過度の摩耗が生じ、
ブレーキ装置による制動力が不充分になる。In this case, if the force to be transmitted continues to be changed widely in order to obtain a predetermined braking force within a predetermined time, the reining yae (
Excessive wear occurs on the brake drum (b) and the brake drum (5),
The braking force provided by the brake device becomes insufficient.

従ってブレーキ面の摩耗量に応じ力伝達部材の長さを増
大することができれば、ブレーキ装置は好適に作動可能
となる。本発明によれば、これを延線部材（（１）、　
ＯＯ並びに（１１）　、　（１’！Ｊを自動的に斜めに
変位可能になす構成をとることによシ実現する。更に詳
述するに、スリーブ状の延線部材αＧ、（１υは内周面
にネジ山が具備され、夫々外周面にこれと螺合するネジ
山を具備したロンド状の延線部材（９）。Therefore, if the length of the force transmitting member can be increased in accordance with the amount of wear on the brake surface, the brake device can operate suitably. According to the present invention, this wire extension member ((1),
This is achieved by adopting a configuration that allows automatic diagonal displacement of OO, (11), (1'! A rond-shaped wire extension member (9) having a threaded surface and a threaded thread on each outer circumferential surface thereof.

０２が受容されるように設けられ、且前記ロッド状の延
線部材（９３、（１２１は好適な構成をもって回転が防
止されるように設けられている。又各延縄部材αＧ。02 is received, and the rod-shaped elongated members (93, (121) are provided so as to be prevented from rotating with a suitable configuration. Also, each of the elongated wire members αG.

αυの外周部には多数の歯部０８からなるランクαηが
形成される。第３図、即ち第１図の線１−ＩＫ沿って切
断した断面図を参照するに、（同図においては他の部材
を示すためキ一部材（６）を省略しであるが、）輪体ａ
９がキーシャフト（４）の延長部に回転自在に軸支され
る。又弾性のバネラッチ部材（イ）がキーシャフト（４
）の外端面に固設されておシ、輪体Ｑ９をキーシャフト
（４）の端部から離れる方向即ち軸方向内向きに抑圧す
るよう機能する。輪体Ｑ９の下面には、半径Ｂ−Ａの領
域如延びかつ少なくとも一個の歯部０＆を受容可能で且
円周方向に傾斜した溝Ｑηが形成されている（第４図付
熱）。また輪体α９の反対面には半径方向に延びる溝い
および棟部−が形成されてお〕（第５図付熱）、前記溝
（ハ）にはバネラッチ部材（イ）の突出部（財）が係入
可能である（第６図付層）。同図は第３図の線Ｗ−Ｗか
ら見た状態を第４図および第５図と実質的に同寸に示し
である。A rank αη consisting of a large number of teeth 08 is formed on the outer periphery of αυ. Referring to FIG. 3, a cross-sectional view taken along line 1-IK in FIG. 1, the ring member (6) is omitted to show other members. body a
9 is rotatably supported by the extension of the key shaft (4). In addition, the elastic spring latch member (A) is attached to the key shaft (4).
) and functions to suppress the wheel Q9 in a direction away from the end of the key shaft (4), that is, inward in the axial direction. A groove Qη is formed on the lower surface of the wheel Q9, extending along a radius B-A, capable of receiving at least one tooth 0&, and inclined in the circumferential direction (see FIG. 4). In addition, a groove and a ridge extending in the radial direction are formed on the opposite surface of the ring α9 (see Figure 5), and the groove (c) is provided with a protruding portion (fabric) of the spring latch member (a). ) can be inserted (layer attached to Figure 6). This figure shows the state seen from line WW in FIG. 3 and is substantially the same size as FIGS. 4 and 5.

一方前記バネラッチ部材（ホ）の突出部（財）と反対側
の端部翰は棟部−の頂部に対し摺動可能に設けられてい
るので、バネラッチ部材−の突出部（ハ）によシ輪体ａ
９Ｋかかるバネ負荷の平衡化が図られ得る。On the other hand, the end ridge of the spring latch member (E) on the opposite side to the protrusion (F) is provided so as to be able to slide against the top of the ridge, so that the protrusion (C) of the spring latch member Circium a
A spring load of 9K can be balanced.

バネラッチ部材（ホ）と輪体ａ値との停台状態が第７図
に示される。２つの棟部翰間の斜め方向の距離よシ大に
バネラッチ部材−が移動されると、バネラッチ部材−の
突出部（ハ）は隣接する溝（イ）に導入される。この構
成によシパネラツチ部材（１）と輪体ａ９とはその相対
移動が一方向のみに制限される。即Ｑ４の先端面輪とが
当接される。この場合先端面一は面積が大きいのでそれ
ほど大ｉＪ　Ｋ摩耗されない。FIG. 7 shows the stopped state of the spring latch member (e) and the wheel a value. When the spring latch member is moved by a distance greater than the diagonal distance between the two ridges, the protrusion (c) of the spring latch member is introduced into the adjacent groove (a). This configuration limits the relative movement of the panel latch member (1) and the wheel a9 to only one direction. Immediately, it comes into contact with the end face ring of Q4. In this case, the area of the tip end surface is large, so it is not worn to a large extent.

一方突出部（ハ）の先縁部＠によシ突出部（ハ）が溝（
イ）Ｋ導入される時の位置が定まる。先縁部（財）はバ
ネランチ部材（１）自体が可撓性を持つから輪体０９が
移動される際に摩耗が大巾に低減される。On the other hand, the leading edge of the protruding part (C) @ has a groove (
b) The position when K is introduced is determined. Since the spring launch member (1) itself is flexible at the leading edge, wear is greatly reduced when the wheel body 09 is moved.

更に本発明の自動すきま調整装置の動作を詳述する。制
動力を加えると、力伝達部１（７１、（８）はキーシャ
フト（４１の軸線に対し外側へ作動されてブレーキ面、
即ちブレーキドラムとライニングが互いに当接される。Furthermore, the operation of the automatic gap adjustment device of the present invention will be explained in detail. When a braking force is applied, the force transmitting part 1 (71, (8) is actuated outward with respect to the axis of the key shaft (41), and the braking surface,
That is, the brake drum and the lining are brought into contact with each other.

力伝達部材（７１、（８１が外側へ作動される際、各力
伝達部側（７１、（８１の少なくとも−の歯部μｓが輪
体ａ９の溝（財）内に係入される。この場合溝なりは円
周方向に傾けられる、即ち半径方向に対しある角度をも
って形成されているので、力伝達部側（７１、（８１の
２つの歯部（至）が半径方向に互いに逆方向に移動され
るとき、これに伴い輪体Ｑｌが回転され得る。When the force transmitting members (71, (81) are operated outward, at least the negative teeth μs of each force transmitting portion side (71, (81) are engaged in the grooves of the wheel a9. In this case, the groove is inclined in the circumferential direction, that is, it is formed at a certain angle with respect to the radial direction. When moved, the ring body Ql may be rotated accordingly.

一方キ一部材（６）が回転されたとき力伝達部材（７）
。On the other hand, when the key member (6) is rotated, the force transmitting member (7)
.

（８）が同一平面上において回転されるので、輪体側の
ある固定部材に対する実際の回転、すなわち例えば第２
図においてキーシャフト（４）が軸支されている背平面
（図示せず）に対する輪体α９の実際の回転は小さい。(8) is rotated on the same plane, the actual rotation with respect to a fixed member on the wheel side, that is, for example, the second
In the figure, the actual rotation of the wheel α9 relative to the back plane (not shown) on which the key shaft (4) is pivotally supported is small.

又キーシャフト（４）の回転、延いてはキーシャフト（
４）に固設されるバネランチ部材翰の回転も同一方向に
行なわれるが、溝Ｑ１）が半径方向に対しある角度をも
って形成されているので、輸体Ｑ’Ｊとバネラッチ部栃
翰とは相対的に僅かに回転されることになる。又輸体ａ
９とバネラッチ部材−との相対回転はキーシャフト（４
）（延いては力伝達部材）の斜め方向の移動距離の函数
となる。In addition, the rotation of the key shaft (4), and by extension the key shaft (
The rotation of the spring latch member holder fixed to 4) is also performed in the same direction, but since the groove Q1) is formed at a certain angle with respect to the radial direction, the transport member Q'J and the spring latch member holder are relative to each other. It will be rotated slightly. Also, transfusion a
The relative rotation between 9 and the spring latch member is controlled by the key shaft (4
) (and by extension, the force transmitting member) is a function of the movement distance in the diagonal direction.

キーシャフト（４１（延いては力伝達部材）が斜め方向
に過度に移動された場合、上記の輪体（ｔＵとバネラッ
チ部材（ホ）との相対回転によシバネラツチ部材の突出
部（ハ）が輪体Ｑ鶴の隣接する溝（イ）Ｋ係入される。If the key shaft (41 (and by extension, the force transmitting member) is moved excessively in the diagonal direction, the protrusion (C) of the spring latch member (C) will be The adjacent groove (a) K of the ring body Q is engaged.

このとき制動力が解放されると、キーシャフト（４１が
逆方向に移動され、突出部（財）により輪体Ｑ９゜延い
ては延線部材（９）＋　（１２ｒに連係する歯部−を有
した延線部材Ｃ１（＃　、　（１１）にトルク力が加わ
シカ伝達部材（７）　、　（８）全体の長さが延長され
ることになる。When the braking force is released at this time, the key shaft (41) is moved in the opposite direction, and the protrusion extends the wheel body Q9° and connects the wire extension member (9) + (toothed part - linked to 12r). Torque force is applied to the extended wire member C1 (#, (11)), and the entire length of the deer transmission members (7), (8) is extended.

、すきま調整を行なう構成部材が対称、に構成されかつ
すき″！、調整を実現する主要部材が固定されていない
ので、本発明のすきま調整装置は高効率で作動し得、又
力伝達部拐の製造誤差によりブレーキ装置全体に寸法上
の差がある場合でも正常な制動動作が保証され得る。Since the constituent members for adjusting the clearance are symmetrically constructed and the main components for realizing the adjustment are not fixed, the clearance adjustment device of the present invention can operate with high efficiency, and the force transmitting part is not damaged. Normal braking operation can be guaranteed even if there are dimensional differences throughout the brake system due to manufacturing tolerances.

力伝達部材（７）　、　（８１、輪体０Ｉおよびバネラ
ッチ部拐（イ）は異なる寸法および形状のキ一部材（６
）を有した各種のブレーキ装置にも適用可能である。す
なわち、これは歯部０〜からなるランクαηを延線部材
（ＩＯ、（１１）に対し軸方向に移動可能に配設するこ
とによシ達成しうる。更にこれを詳述するに、第８図に
示す如く、止めネジ翰を緩めることによりラックＱηを
軸方向に所望の位置まで変位し多数の穴勾の一部に止め
ネジ翰を再び螺入可能に構成することＫよシ実現できる
。The force transmitting member (7), (81, wheel body 0I and spring latch part (a) are different in size and shape from the key member (6).
) can also be applied to various types of brake devices. That is, this can be achieved by arranging the ranks αη consisting of teeth 0 to 0 so as to be movable in the axial direction with respect to the wire extension member (IO, (11)). As shown in Figure 8, it is possible to displace the rack Qη in the axial direction to a desired position by loosening the setscrews, and to construct a structure in which the setscrews can be re-screwed into some of the many holes. .

第９図および第１０図には本発明の他の実施例が示され
ておシ、本実施例においては上述の実施例とは異なった
キ一部拐（６）が用いられている。第９図の実施例では
キ一部材（６）はその有効長が長く設けられ、又仮想線
（１）（キーシャフト（４）の軸線ｃ３１）と力伝達部
材（７）のブレーキ片０３に対する回転軸（至）とを結
ぶ線）と延線部材の有効半径Ｒを表わす線とのなす角度
αも大にされる。一方第１０図の実施例ではキ一部拐（
６）はその有効長が短かく設けられ又有効半径γを表わ
す線と上述と同様の仮想線（至）とのなす角度βも小さ
くされる。Another embodiment of the invention is shown in FIGS. 9 and 10, in which a key part (6) different from that of the above-described embodiment is used. In the embodiment shown in FIG. 9, the key member (6) is provided with a long effective length, and the imaginary line (1) (axis c31 of the key shaft (4)) and the brake piece 03 of the force transmitting member (7) are The angle α between the line connecting the rotating shaft (to) and the line representing the effective radius R of the wire extension member is also increased. On the other hand, in the embodiment shown in FIG.
6) is provided with a short effective length, and the angle β between the line representing the effective radius γ and the same imaginary line (to) as described above is also made small.

更に詳述するに、第９図においては変位可能なランク←
ηがその最基端位置装置かれておシ、この場合制動動作
時にはラック（１７）の歯部ｏ杓が最終移動位置（１８
ａ）まで移動され、一方回転軸（財）が位置（３２ａ）
まで移動されることＫなる。歯部の最基端位置並びに最
終移動位置（１８ａ）　’Ｊでの軸線０ηからの半径方
向の距離に応じて、輪体αＩ（第９図には図示せず）の
溝ＱＤに導入される歯部ＣＢの半径方向における導入路
が決まる。To be more detailed, in Fig. 9, the displaceable ranks ←
η is at its most proximal position, and in this case, during braking, the teeth of the rack (17) are at the final moving position (18).
a), while the rotating shaft (goods) is at position (32a)
It will be moved up to K. Depending on the radial distance from the axis 0η at the most proximal position of the tooth and the final movement position (18a) 'J, it is introduced into the groove QD of the ring body αI (not shown in FIG. 9). The introduction path in the radial direction of the tooth portion CB is determined.

第１０図の如く小さな角度βおよび小さな有効半径γを
有するブレーキ装置において、第９図と同一の溝Ｃ２１
）を有する同一の輪体ａ９を用いて変位可能なラックａ
力をいかに構成するかを示している。In a brake device having a small angle β and a small effective radius γ as shown in FIG. 10, the same groove C21 as in FIG.
) Displaceable rack a using the same wheels a9
It shows how power is structured.

第１Ｏ図において変位可能なラック０ηは、歯部の最終
移動位置（１８ａ）が溝Ｉ２１）の外端部近傍に位置す
るように構成され、一方歯部αａの移動開始位置が溝Ｑ
Ｄの端部間に位置するよう構成される。この場合第９図
に示す如くランクαηを位置させることは第１０図のキ
一部材を有するブレーキ装置において不適当であること
が理解されよう。即ち、輪体０９の直径が不足すること
Ｋなる。In FIG. 1O, the displaceable rack 0η is configured such that the final movement position (18a) of the tooth is located near the outer end of the groove I21), while the movement start position of the tooth αa is the groove Q
It is configured to be located between the ends of D. In this case, it will be understood that positioning the rank αη as shown in FIG. 9 is inappropriate for the brake device having the key member shown in FIG. 10. That is, the diameter of the ring body 09 is insufficient.

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

第１図は本発明の自動すきま調整装置を備えたブレーキ
装置の簡略側面図、第２図は同第１図と異なった動作状
態を示す簡略側面図、第３図は第１図の線ｍ−ｍから見
た一部を切開いて示す簡略平面図、第４図は同部分拡大
底面図、第５図、第６図は同部分拡大平面図、第７図は
第６図の線■−■から見た状態の簡略部分拡大説明図、
第８図乃至第１０図は夫々本発明の他の実施例の一部を
切開いて示す簡略部分拡大側面図である。 １・・作動装置、２・・・ピストンロンド、３・・・レ
バー、４・・キーシャフト、５・・ブレーキドラム、６
・・・キ一部側、７．８・・・力伝達部制、９乃至１２
・・延線部材、１３．１４・・・ブレーキ片、１５　、
１６・・・ライニング、１７・・・ラック、１８・・・
歯部、１９・・・輪体、２０・・・バネランチ部材、２
１．２２・・溝、２３・・・棟部、２４・・突出部、２
５・・端部、２６・・先端面、２７・・・先縁部、２８
・・・止めネジ、２９・・穴、３０・・・仮想線、３１
・・軸線、３２・・回転軸特許出願人Fig. 1 is a simplified side view of a brake device equipped with an automatic clearance adjustment device of the present invention, Fig. 2 is a simplified side view showing a different operating state from Fig. 1, and Fig. 3 is a line m in Fig. 1. 4 is an enlarged bottom view of the same portion, FIGS. 5 and 6 are enlarged plan views of the same portion, and FIG. 7 is the line of FIG. 6 - ■Simplified partial enlarged explanatory diagram of the state seen from
FIGS. 8 to 10 are simplified partially enlarged side views showing other embodiments of the present invention, with parts cut away. 1... Actuation device, 2... Piston rond, 3... Lever, 4... Key shaft, 5... Brake drum, 6
...Ki part side, 7.8...Force transmission system, 9 to 12
...Wire extension member, 13.14...Brake piece, 15,
16... Lining, 17... Rack, 18...
Tooth portion, 19... Ring body, 20... Spring launch member, 2
1.22...Groove, 23...Ridge, 24...Protrusion, 2
5... End, 26... Tip surface, 27... Leading edge, 28
... Set screw, 29 ... Hole, 30 ... Virtual line, 31
...Axis line, 32...Rotating axis patent applicant

Claims (2)

【特許請求の範囲】[Claims] （１）キーシャフトに固設されたキ一部材によシ作動さ
れる車両用のドラムブレーキ装置に適用可能に設けられ
、前記キーシャフトはシリンダ・ピストン装置を作動す
る作動装置に連結され、前記キ一部材は力伝達装置を介
し一対のブレーキ片を作動可能に設けられ、前記各力伝
達装置は延線可能な２つの処縮部材からなシ、前記の２
つの部材の一方は一ロンド状をなし外周面にネジ山が設
けられ、他方はスリーブ状をなし内周面にネジ山が設け
られ、前記ロンド状の部材は前記スリーブ状の部材内に
螺入され、前記各スリーブ状の部材の外周面には歯部で
なるラックが具備され、前記ラックは前記キーシャフト
上に支承された輪体の第１の面に設けられた半径方向に
延びる溝と協働可能に設けられ、前記溝は前記ラックが
前記輪体に対し半径方向に移動されたとき前記２つのス
リーブ状の部材にトルクが加わシ前記２つの延線部材の
全長が増大されるように設けられ、前記輪体の第２の面
には前記キーシャフト妬固設される弾性のバネラッチ部
材を受容可能な半径方向に延びる溝および棟部が設けら
れてなる自動すきま調整装置。(1) Applicable to a drum brake device for a vehicle that is operated by a key member fixed to a key shaft, the key shaft is connected to an actuating device that operates a cylinder/piston device, and the key shaft is connected to an actuating device that operates a cylinder/piston device; The key member is provided to be able to actuate a pair of brake pieces via a force transmitting device, and each of the force transmitting devices is composed of two extensionable processing members.
One of the two members has a rond shape and has a thread on its outer circumferential surface, the other has a sleeve shape and has a thread on its inner periphery, and the rond-like member is screwed into the sleeve-like member. and a rack consisting of teeth is provided on the outer circumferential surface of each sleeve-like member, and the rack is provided with a radially extending groove provided on a first surface of a wheel supported on the key shaft. The grooves are cooperably arranged so that when the rack is moved radially relative to the wheel, a torque is applied to the two sleeve-like members and the overall length of the two elongated wire members is increased. , wherein the second surface of the wheel body is provided with a radially extending groove and a ridge portion capable of receiving an elastic spring latch member fixedly attached to the key shaft. （２）２つのスリーブ状の部利は外周面に具備されるラ
ックが軸方向に移動可能姉連結されてなる特許請求の範
囲第１項記載の自動すきま調整装置。(2) The automatic clearance adjustment device according to claim 1, wherein the two sleeve-shaped parts are connected to each other so that the racks provided on the outer circumferential surfaces thereof are movable in the axial direction.
JP58105065A 1982-06-14 1983-06-14 Automatic clearance regulator Granted JPS596440A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US38816182A 1982-06-14 1982-06-14
US388161 1982-06-14

Publications (2)

Publication Number Publication Date
JPS596440A true JPS596440A (en) 1984-01-13
JPH0427411B2 JPH0427411B2 (en) 1992-05-11

Family

ID=23532951

Family Applications (1)

Application Number Title Priority Date Filing Date
JP58105065A Granted JPS596440A (en) 1982-06-14 1983-06-14 Automatic clearance regulator

Country Status (8)

Country Link
JP (1) JPS596440A (en)
BR (1) BR8303084A (en)
CA (1) CA1201984A (en)
DE (1) DE3321319A1 (en)
FR (1) FR2528513B1 (en)
GB (1) GB2121896B (en)
IT (1) IT1163513B (en)
SE (1) SE453420B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61252926A (en) * 1985-03-21 1986-11-10 ル−カス・インダストリ−ズ・パブリツク・リミテツド・カンパニ− Automatic regulator

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE447596B (en) * 1983-11-21 1986-11-24 Sven Erik Camph DEVICE FOR TRANSMISSION OF BRAKE POWER BETWEEN BRAKE KEY AND BRAKE BACK IN TRUMBROMS
GB8916046D0 (en) * 1989-07-13 1989-08-31 Lucas Ind Plc Brake actuator
TW477874B (en) * 1999-11-09 2002-03-01 Pbr Automotive Pty Ltd Adjuster strut
US9365194B2 (en) * 2014-11-01 2016-06-14 Bendix Spicer Foundation Brake Llc Drum brake S-cam having offset cam followers

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5382967A (en) * 1976-12-27 1978-07-21 Camph Eng Co Ab Automatic gap adjuster

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB634408A (en) * 1947-06-18 1950-03-22 Harry Parker Improvements in vehicle brakes
FR1340274A (en) * 1962-09-04 1963-10-18 Dba Sa Automatic wear adjustment device for drum brake
DE1600157B1 (en) * 1967-01-27 1970-08-06 Teves Gmbh Alfred Adjustment device for a floating caliper partially lined disc brake
SE383393B (en) * 1973-04-06 1976-03-08 S E Camph AUTOMATIC GAME DETECTION DEVICE FOR BRAKES

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5382967A (en) * 1976-12-27 1978-07-21 Camph Eng Co Ab Automatic gap adjuster

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61252926A (en) * 1985-03-21 1986-11-10 ル−カス・インダストリ−ズ・パブリツク・リミテツド・カンパニ− Automatic regulator

Also Published As

Publication number Publication date
SE453420B (en) 1988-02-01
DE3321319A1 (en) 1983-12-15
DE3321319C2 (en) 1992-05-14
GB8316049D0 (en) 1983-07-20
IT8321598A0 (en) 1983-06-13
GB2121896A (en) 1984-01-04
BR8303084A (en) 1984-01-31
IT1163513B (en) 1987-04-08
SE8303331D0 (en) 1983-06-13
FR2528513B1 (en) 1986-05-02
CA1201984A (en) 1986-03-18
SE8303331L (en) 1983-12-15
GB2121896B (en) 1986-02-12
FR2528513A1 (en) 1983-12-16
JPH0427411B2 (en) 1992-05-11

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