JPH0412850Y2 - - Google Patents
Info
- Publication number
- JPH0412850Y2 JPH0412850Y2 JP51987U JP51987U JPH0412850Y2 JP H0412850 Y2 JPH0412850 Y2 JP H0412850Y2 JP 51987 U JP51987 U JP 51987U JP 51987 U JP51987 U JP 51987U JP H0412850 Y2 JPH0412850 Y2 JP H0412850Y2
- Authority
- JP
- Japan
- Prior art keywords
- booster
- booster piston
- valve
- piston
- locking
- 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
Links
- 230000003014 reinforcing effect Effects 0.000 claims description 40
- 210000000078 claw Anatomy 0.000 claims description 39
- 230000005489 elastic deformation Effects 0.000 claims description 11
- 238000005192 partition Methods 0.000 claims 1
- 230000002093 peripheral effect Effects 0.000 description 12
- 239000011324 bead Substances 0.000 description 7
- 238000006243 chemical reaction Methods 0.000 description 6
- 230000001105 regulatory effect Effects 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 229920001971 elastomer Polymers 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- KXGFMDJXCMQABM-UHFFFAOYSA-N 2-methoxy-6-methylphenol Chemical compound [CH]OC1=CC=CC([CH])=C1O KXGFMDJXCMQABM-UHFFFAOYSA-N 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 229920001568 phenolic resin Polymers 0.000 description 1
- 239000005011 phenolic resin Substances 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- 230000003313 weakening effect Effects 0.000 description 1
Landscapes
- Braking Systems And Boosters (AREA)
Description
【考案の詳細な説明】
Ａ 考案の目的
(1) 産業上の利用分野
本考案は、例えば車両のブレーキマスタシリン
ダの作動に用いられる負圧式倍力装置、特に、ブ
ースタシエルと；該ブースタシエル内を負圧源に
連なる第１作動室と、制御弁を介して該第１作動
室または大気に選択的に連通される第２作動室と
に区画すべく、前記ブースタシエル内に前後往復
動自在に収容されるブースタピストンと；該ブー
スタピストンの中心に存する弁筒嵌入孔に嵌合さ
れて抜止めフランジを該ブースタピストン前面に
重合した制御弁用弁筒と；前記抜止めフランジを
前記ブースタピストンと協働して挟止すべく該抜
止めフランジ前面に重合する挟止板と；を少なく
とも備え、前記挟止板には、該板の抜止めフラン
ジに対する所定の回転方向への相対回転により、
該ブースタピストンに切起された複数の係止爪に
係合する複数の弾性係合片が一体に形成された形
式の装置に関する。[Detailed description of the invention] A. Purpose of the invention (1) Industrial application field The present invention is a negative pressure booster used, for example, to operate a brake master cylinder of a vehicle, particularly a booster shell; The booster shell is capable of freely reciprocating back and forth within the booster shell to divide the booster shell into a first working chamber connected to a negative pressure source and a second working chamber selectively communicated with the first working chamber or the atmosphere via a control valve. a booster piston housed in the booster piston; a valve barrel for a control valve that is fitted into a valve barrel fitting hole in the center of the booster piston and has a retaining flange superimposed on the front surface of the booster piston; and a clamping plate superimposed on the front surface of the retaining flange in order to clamp the retaining flange in cooperation with the retaining flange.
The present invention relates to a device in which a plurality of elastic engagement pieces that engage with a plurality of locking pawls cut and raised on the booster piston are integrally formed.
(2) 従来の技術
本出願人は、先に、この種装置として特開昭60
−67251号公報に開示されるものを提案している。(2) Prior art The present applicant previously developed a device of this type in Japanese Patent Application Laid-open No. 1983
-We are proposing what is disclosed in Publication No. 67251.
(3) 考案が解決しようとする課題
前記従来装置においては、各係止爪の切起し孔
と弁筒嵌入孔との間に周方向に沿う補強リブを設
けて切起し孔の形成に伴うブースタピストンの弱
化を防止している。(3) Problems to be solved by the invention In the conventional device described above, a reinforcing rib along the circumferential direction is provided between the cut-and-bore hole of each locking pawl and the valve barrel insertion hole to facilitate the formation of the cut-and-bore hole. This prevents the booster piston from weakening.
本考案はこの種装置において、ブースタピスト
ンの切起し孔周辺を一層有効に補強し、またその
補強手段を挟止板の外れ止めとして兼用し得るよ
うにして構造の簡素化を図ることができる負圧式
倍力装置を提供することを目的とする。 The present invention makes it possible to more effectively reinforce the area around the cut and raised hole of the booster piston in this type of device, and to simplify the structure by allowing the reinforcing means to also serve as a stopper for the clamping plate to come off. The purpose of the present invention is to provide a negative pressure booster.
Ｂ 考案の構成
(1) 課題を解決するための手段
斯かる目的を達成するために本考案によれば、
前記形式の負圧式倍力装置において、前記ブース
タピストンには、前記挟止板の前記回転方向と交
差するように延びる補強リブが、前記各係止爪の
切起し孔の前記回転方向後側に近接して設けら
れ、その補強リブは、前記各係止爪に各係合片を
係合させるべく前記挟止板を回転させる際の該各
係合片の移動軌跡内に配置され、前記係合片は、
それを各係止爪に係合させるべく前記挟止板を回
転させる際には自己の弾性変形により前記補強リ
ブを乗り越え、また該係合片を各係止爪に係合さ
せた状態では前記弾性変形から復元していて該補
強リブの側面に対面するように形成される。B. Structure of the invention (1) Means for solving the problem According to the invention, in order to achieve this purpose,
In the negative pressure booster of the type described above, the booster piston has a reinforcing rib that extends so as to intersect with the rotational direction of the locking plate, on the rear side in the rotational direction of the cut-and-raised hole of each of the locking claws. The reinforcing rib is disposed in the locus of movement of each engaging piece when the clamping plate is rotated to engage each engaging piece with each of the locking claws, The engagement piece is
When the clamping plate is rotated to engage with each locking pawl, it overcomes the reinforcing rib due to its own elastic deformation, and when the engaging piece is engaged with each locking pawl, It has recovered from elastic deformation and is formed so as to face the side surface of the reinforcing rib.
(2) 作用
ブースタピストンに上記補強リブが形成される
ことで、同ピストンの切起し孔周辺部が有効に補
強される。(2) Effect By forming the reinforcing ribs on the booster piston, the area around the cut and raised hole of the piston is effectively reinforced.
また各係合片を係止爪に係合させるべく挟止板
を所定方向に回転させる際には、その係合片が、
それの移動軌跡内に在る上記補強リブを自己の弾
性変形により乗り越える。そしてその係合片は、
各係止爪と係合した状態では前記弾性変形から復
元していて該補強リブの側面に対面するから、係
合片ひいては挟止板の、前記所定回転方向と反対
方向の回転が規制され、従つて該補強リブが係合
片の係止爪からの外れ止めとして機能する。 In addition, when rotating the clamping plate in a predetermined direction to engage each engaging piece with the locking pawl, the engaging piece
It overcomes the reinforcing ribs in its movement locus by its own elastic deformation. And the engagement piece is
When engaged with each of the locking claws, it is restored from the elastic deformation and faces the side surface of the reinforcing rib, so that the rotation of the engagement piece, and thus the clamping plate, in the opposite direction to the predetermined rotation direction is regulated; Therefore, the reinforcing rib functions to prevent the engagement piece from coming off from the locking claw.
(3) 実施例
第１，第２図において、ブースタシエル１内に
ブースタピストン２が前後往復動自在に収容さ
れ、そのブースタピストン２によりブースタシエ
ル１内は前部の第１作動室Ａと後部の第２作動室
Ｂとに区画される。(3) Embodiment In FIGS. 1 and 2, a booster piston 2 is housed in a booster shell 1 so as to be able to reciprocate back and forth. and a second working chamber B.
ブースタピストン２の後面にダイヤフラム３が
重合され、その外周ビード３ａはブースタシエル
１の周壁、したがつてブースタシエル１を構成す
る前、後部シエル１ａ，１ｂの衝合部に画成され
た環状溝４に結着され、また内周ビード３ｂはブ
ースタピストン２の内周部に結着される。この内
周ビード３ｂの結着構造については後述する。 A diaphragm 3 is superimposed on the rear surface of the booster piston 2, and its outer peripheral bead 3a is an annular groove defined in the peripheral wall of the booster shell 1, and thus in the abutting portion of the front and rear shells 1a and 1b that constitute the booster shell 1. 4, and the inner circumference bead 3b is attached to the inner circumference of the booster piston 2. The binding structure of this inner peripheral bead 3b will be described later.
第１作動室Ａは負圧導入管５を介して負圧源で
ある内燃機関の吸気マニホールド（図示せず）内
に常時連通し、第２作動室Ｂは後述する制御弁６
を介して第１作動室Ａまたはブースタシエル１の
後方延長筒７の端壁８に開口する大気導入口９に
選択的に連通されるようになつている。 The first working chamber A is always in communication with the intake manifold (not shown) of the internal combustion engine, which is a negative pressure source, through a negative pressure introduction pipe 5, and the second working chamber B is connected to a control valve 6, which will be described later.
It is configured to selectively communicate with the first working chamber A or an atmosphere inlet 9 opened in the end wall 8 of the rear extension tube 7 of the booster shell 1 through the opening.
ブースタピストン２は第１作動室Ａに縮設され
た戻しばね１０により常時後退方向、即ち第２作
動室Ｂ側に弾発され、その後退限はダイヤフラム
３の背面に***形成した突起１１がブースタシエ
ル１の後壁内面に当接することにより規制され
る。 The booster piston 2 is always urged in the backward direction, that is, toward the second working chamber B, by a return spring 10 contracted in the first working chamber A, and its backward limit is reached by a protrusion 11 formed protrudingly formed on the back surface of the diaphragm 3. It is regulated by coming into contact with the inner surface of the rear wall of the shell 1.
ブースタピストン２に、その中心部から後方に突
出する制御弁用弁筒１２が設けられ、その弁筒１
２は前記後方延長筒７に設けた平軸受１３に摺動
自在に支承され、その後端は前記大気導入口９に
向つて開放される。The booster piston 2 is provided with a control valve valve cylinder 12 that protrudes rearward from its center.
2 is slidably supported by a flat bearing 13 provided on the rear extension cylinder 7, and its rear end is open toward the atmosphere inlet 9.
弁筒１２内に、制御弁６が次のように構成され
る。即ち、弁筒１２の前部内壁に環状の第１弁座
１４1が形成され、弁筒１２の前部に、入力杆１
５に連結されてその前端部を構成する弁ピストン
１６が摺合され、この弁ピストン１６後端に前記
第１弁座１４1に囲繞される環状の第２弁座１４2
が形成される。 The control valve 6 is configured in the valve cylinder 12 as follows. That is, an annular first valve seat 14 1 is formed on the inner wall of the front part of the valve cylinder 12 , and an input rod 1 is formed in the front part of the valve cylinder 12 .
A valve piston 16 is connected to the valve piston 16 and forms a front end portion of the valve piston 16, and an annular second valve seat 14 2 surrounded by the first valve seat 14 1 is attached to the rear end of the valve piston 16 .
is formed.
弁筒１２の内壁に、両端を開放した筒状の弁体
１７の基端部１８が弁筒１２に嵌着される弁体保
持筒１９を介して挟止される。この弁体１７はゴ
ム等の弾性材より形成されたもので、その基端部
１８から薄肉のダイヤフラム２０が半径方向内方
へ延出し、その内周端に厚肉の弁部２１が連設さ
れており、その弁部２１は前記第１および第２弁
座１４1，１４2と対向する。而して弁部２１はダ
イヤフラム２０の変形により前後に移動でき、そ
して弁体保持筒１９の前端面に当接することもで
きる。 A base end portion 18 of a cylindrical valve body 17 with both ends open is clamped on the inner wall of the valve cylinder 12 via a valve body holding cylinder 19 that is fitted into the valve cylinder 12 . The valve body 17 is made of an elastic material such as rubber, and a thin diaphragm 20 extends radially inward from its base end 18, and a thick valve portion 21 is connected to the inner peripheral end thereof. The valve portion 21 faces the first and second valve seats 14 1 and 14 2 . Thus, the valve portion 21 can move back and forth by deforming the diaphragm 20, and can also come into contact with the front end surface of the valve body holding cylinder 19.
弁部２１に環状の補強板２２が埋設され、これ
に弁部２１を両弁座１４1，１４2に向つて付勢す
べく弁ばね６０が連結される。 An annular reinforcing plate 22 is embedded in the valve portion 21, and a valve spring 60 is connected to this to bias the valve portion 21 toward both valve seats 14 1 and 14 2 .
第１弁座１４1の外側部は弁筒１２の通孔２３
を介して第１作動室Ａに、また第１および第２弁
座１４1，１４2の中間部は別の通孔２４を介して
第２作動室Ｂに、さらに第２弁座１４2の内側部
は弁体１７内部を介して大気導入口９にそれぞれ
常時連通する。 The outer part of the first valve seat 141 is the through hole 23 of the valve cylinder 12.
The intermediate portion of the first and second valve seats 14 1 , 14 2 is connected to the second working chamber B through another through hole 24 , and the second valve seat 14 2 is connected to the first working chamber A through the second valve seat 14 2 . The inner portions are always in communication with the atmosphere inlet 9 through the inside of the valve body 17 .
弁筒１２に、その前面中心部に開口する大径の
シリンダ孔２５と、そのシリンダ孔２５の奥部端
面に開口する小径のシリンダ孔２６が設けられ、
その大径のシリンダ孔２５にその奥よりゴム等よ
りなる弾性ピストン２７およびそれと同径の出力
ピストン２８が順次摺合され、また小径のシリン
ダ孔２６に弾性ピストン２７より小径の反動ピス
トン２９が摺合される。さらに小径のシリンダ孔
２６に前記弁ピストン１６の前端面から突出する
小軸３０が突入して反動ピストン２９の後端面に
対向する。出力ピストン２８の前面に出力杆３１
が突設され、その出力杆３１は図示しないブレー
キマスタシリンダの作動ピストンに連結される。 The valve cylinder 12 is provided with a large-diameter cylinder hole 25 that opens at the center of its front surface, and a small-diameter cylinder hole 26 that opens at the inner end surface of the cylinder hole 25.
An elastic piston 27 made of rubber or the like and an output piston 28 of the same diameter are sequentially slid into the large diameter cylinder hole 25 from the back thereof, and a reaction piston 29 with a smaller diameter than the elastic piston 27 is slid into the small diameter cylinder hole 26. Ru. Further, a small shaft 30 protruding from the front end surface of the valve piston 16 enters the small diameter cylinder hole 26 and opposes the rear end surface of the reaction piston 29 . An output rod 31 is installed in front of the output piston 28.
is provided in a protruding manner, and its output rod 31 is connected to an operating piston of a brake master cylinder (not shown).
入力杆１５は戻しばね３２により常時後退方向
へ弾発され、その後退限は、入力杆１５に螺合し
て取付けた可動ストツパ板３３が後方延長筒７の
端壁８の内側に当接することにより規制される。 The input rod 15 is always urged in the backward direction by the return spring 32, and its retreat limit is reached when the movable stopper plate 33 screwed onto the input rod 15 comes into contact with the inside of the end wall 8 of the rear extension tube 7. regulated by.
而して可動ストツパ板３３を回転すれば、それ
と入力杆１５との螺合位置が変わるので入力杆１
５の後退限を前後に調節することができる。その
調節後の可動ストツパ板３３の固定は、同じく入
力杆１５に螺合したロツクナツト３４の緊締によ
り行われる。可動ストツパ板３３にこれが前記大
気導入口９を閉塞しないように通気孔３５が形成
される。 When the movable stopper plate 33 is rotated, the screwing position between it and the input rod 15 changes, so the input rod 1
The retraction limit of 5 can be adjusted back and forth. After the adjustment, the movable stopper plate 33 is fixed by tightening a lock nut 34 which is also screwed onto the input rod 15. A vent hole 35 is formed in the movable stopper plate 33 so as not to block the air inlet 9.
弁筒１２の外端開口部に、大気導入口９からの
導入空気を浄化し、且つ入力杆１５の作動を妨げ
ないように変形し得るフイルタ３６，３７が装着
される。 Filters 36 and 37 are attached to the outer end opening of the valve cylinder 12 to purify the air introduced from the atmospheric air inlet 9 and to be deformable so as not to interfere with the operation of the input rod 15.
次にブースタピストン２に対する弁筒１２の組
付構造について説明すると、ブースタピストン２
はその価格を低減すべく薄肉鋼板より略円盤状に
成形されたもので、その中心にが装着される。 Next, the assembly structure of the valve cylinder 12 to the booster piston 2 will be explained.
In order to reduce the cost, it is formed from a thin steel plate into a roughly disc shape, and the disc is attached to the center of the disc.
弁筒１２はフエノール樹脂等の合成樹脂より成
形されたもので、弁筒嵌入孔３８に嵌合、したが
つて内周ビード３ｂの内周面に嵌着される筒体３
９と、その筒体３９の前端外周面に突設されて後
面ａをブースタピストン２前面ｂに重合した抜止
めフランジ４０とよりなる。 The valve cylinder 12 is molded from a synthetic resin such as phenolic resin, and is fitted into the valve cylinder fitting hole 38, and therefore the cylinder body 3 is fitted onto the inner peripheral surface of the inner peripheral bead 3b.
9, and a retaining flange 40 projecting from the outer peripheral surface of the front end of the cylindrical body 39 and having its rear surface a overlapped with the front surface b of the booster piston 2.
抜止めフランジ４０の外周部において、その抜
止めフランジ４０の中心に関し点対称となるよう
に一対の切欠き状凹部４１が形成され、両凹部４
１に係合する一対の凸部４２がブースタピストン
２の前面ｂに膨出成形される。これら凹部４１お
よび凸部４２は、ブースタピストン２に対する弁
筒１２の回止めをなす凹凸係合部を構成する。 A pair of notch-like recesses 41 are formed on the outer circumference of the retaining flange 40 so as to be point symmetrical with respect to the center of the retaining flange 40, and both recesses 4
A pair of convex portions 42 that engage with the booster piston 1 are bulgingly formed on the front surface b of the booster piston 2. These concave portions 41 and convex portions 42 constitute a concave-convex engaging portion that prevents the valve cylinder 12 from rotating with respect to the booster piston 2.
第２図に明示するように、両凸部４２を結ぶ直
線Ｘ−Ｘの両側において、ブースタピストン２
に、抜止めフランジ４０の周囲に位置するように
それぞれ一対の鉤形第１，第２係止爪４３1，４
３2が隣接して切起しにより形成される。 As clearly shown in FIG. 2, the booster piston 2
A pair of hook-shaped first and second hook-shaped locking claws 43 1 , 4 are located around the retaining flange 40 .
3 2 are formed adjacently by cutting and raising.
前記直線Ｘ−Ｘの両側に存する両第１係止爪４
３1相互および両第２係止爪４３2相互はブースタ
ピストン２の中心に関し点対称となつており、前
記直線Ｘ−Ｘを挟んで一側の第１係止爪４３1と
他側の第２係止爪４３2の両先端部４４1，４４2
が互いに対向するようになつている。 Both first locking claws 4 existing on both sides of the straight line XX
3.1 and both second locking claws 43.2 are point symmetrical with respect to the center of the booster piston 2, with the first locking claw 43.1 on one side and the second locking claw on the other side across the straight line XX. Both tips 44 1 , 44 2 of the 2 locking claws 43 2
are now facing each other.
各第１，第２係止爪４３1，４３2に、その先端
部４４1，４４2からブースタピストン２の平坦部
４５に延びるように補強リブ４６1，４６2が膨出
成形される。 Reinforcing ribs 46 1 , 46 2 are bulgingly formed on each of the first and second locking claws 43 1 , 43 2 so as to extend from their tip portions 44 1 , 44 2 to the flat portion 45 of the booster piston 2 .
挟止板４６は鋼板より成形され、抜止めフラン
ジ４０の中心線回りに第２図時計方向に回転させ
ることによりブースタピストン２に組付けられて
そのブースタピストン２との協働の下に抜止めフ
ランジ４０を挟止するもので、抜止めフランジ４
０の前面ｃに重合する挟止板本体４７と、その挟
止板本体４７の外周部に相対向するように形成さ
れて抜止めフランジ４０の外周面に遊嵌する一対
の弓形折曲げ部４８と、各折曲げ部４８の先端外
周縁より抜止めフランジ４０の半径方向外方に向
けて突設され、各第１，第２係止爪４３1，４３2
の先端部４４1，４４2内面に弾性係合する一対の
第１，第２係合片４９1，４９2とを有する。 The clamping plate 46 is formed from a steel plate, and is assembled to the booster piston 2 by rotating clockwise in FIG. It clamps the flange 40, and the retaining flange 4
0, and a pair of arcuate bent portions 48 that are formed to face each other on the outer circumference of the stopper plate body 47 and loosely fit into the outer circumferential surface of the retaining flange 40. First and second locking claws 43 1 , 43 2 are provided to protrude outward in the radial direction of the retaining flange 40 from the outer peripheral edge of the tip of each bent portion 48 .
It has a pair of first and second engagement pieces 49 1 and 49 2 that elastically engage the inner surfaces of the tip portions 44 1 and 44 2 .
第３図に明示するように、各第１係合片４９1
はその挟止板回転方向後側の側縁に、また各第２
係合片４９2はその挟止板回転方向前側の側縁に、
それぞれブースタピストン２の平坦部４５に近接
するように内方へ折曲がる外れ止め５０1，５０2
を一体に有する。ブースタピストン２の平坦部４
５に挟止板４６の回転方向と交差するように延び
て第１，第２係止爪４３1，４３2の切起し孔５１
１，５１2を挟むよう、それら切起し孔５１1，５
１2にそれぞれ近接する各一対の補強リブ５２1，
５２2が膨出成形され、各第１係合片４９1の外れ
止め５０1先端は挟止板回転方向後側に存する一
方の補強リブ５２1の側面に対向し、また各第２
係合片４９2の外れ止め５０2先端は、第２係止爪
４３2の挟止板回転方向前側の側縁とブースタピ
ストン２の平坦部４５間を連結する側壁５３に衝
合する。この側壁５３は第２係止爪４３2の切起
しと同時に成形される。 As clearly shown in FIG. 3, each first engaging piece 49 1
is on the rear side edge of the clamping plate in the rotating direction, and each second
The engagement piece 49 2 has a side edge on the front side in the direction of rotation of the clamping plate,
Retainers 50 1 and 50 2 bent inward to approach the flat portion 45 of the booster piston 2, respectively.
It has integrally. Flat part 4 of booster piston 2
5, cut-and-raised holes 51 of the first and second locking claws 43 1 , 43 2 extend so as to intersect with the rotational direction of the clamping plate 46 .
The cut and raised holes 51 1 , 5 sandwich the holes 51 1 , 51 2 .
Each pair of reinforcing ribs 52 1 adjacent to 1 2 ,
52 2 is bulge-molded, and the disengagement stopper 50 1 tip of each first engagement piece 49 1 faces the side surface of one reinforcing rib 52 1 that exists on the rear side in the rotational direction of the stopper plate, and each second
The tip of the retainer 50 2 of the engagement piece 49 2 abuts against a side wall 53 that connects the front side edge of the second retaining pawl 43 2 in the rotating direction of the retaining plate and the flat portion 45 of the booster piston 2 . This side wall 53 is formed at the same time as the second locking pawl 43 2 is cut and raised.
挟止板４６をブースタピストン２に取付けるべ
く後述するように所定方向（即ち第２図時計方
向）に回転させる際には、特に第１係合片４９1
の外れ止め５０1が、それの移動軌跡内に在る一
方の補強リブ５２1を自己の弾性変形により乗り
越え、そして該係合片４９1は、第１係止爪４３1
と係合した状態では前記弾性変形から復元してい
て補強リブ５２1の側面に対面するから、係合片
４９1ひいては挟止板４６の、前記所定回転方向
と反対方向（即ち第２図反時計方向）の回転が、
該補強リブ５２2によつて規制される。一方、第
２係合片４９2の外れ止め５０2は、第２係止爪４
３2の前記側壁５３と係合して、挟止板の４６の
前記所定方向（即ち第２図時計方向）の回転を規
制する。 When rotating the clamping plate 46 in a predetermined direction (i.e., clockwise in FIG. 2) as described later to attach the clamping plate 46 to the booster piston 2, the first engaging piece 49 1
The retainer 50 1 overcomes one of the reinforcing ribs 52 1 in its movement locus by its own elastic deformation, and the engaging piece 49 1 overcomes the first retaining claw 43 1 .
In the engaged state, it has recovered from the elastic deformation and faces the side surface of the reinforcing rib 521 , so that the engagement piece 491 and, by extension, the clamping plate 46 rotate in the opposite direction to the predetermined rotation direction (i.e., in the opposite direction in FIG. 2). clockwise) rotation,
It is regulated by the reinforcing rib 52 2 . On the other hand, the second engagement piece 49 2 is detachable from the second engagement claw 4 .
3 engages with the side wall 53 of 2 to restrict rotation of the stopper plate 46 in the predetermined direction (ie, clockwise in FIG. 2).
そして各一対の補強リブ５２1，５２2は切起し
孔５１1，５１2の周辺を有効に補強する。 Each pair of reinforcing ribs 52 1 , 52 2 effectively reinforces the periphery of the cut and raised holes 51 1 , 51 2 .
而してこの実施例では、前記各第１係止爪４３
１が本考案の係止爪を、また前記各第１係合片４
９1が本考案の係合片を、更に前記挟止板回転方
向後側に存する各補強リブ５２1が本考案の補強
リブをそれぞれ構成している。 In this embodiment, each of the first locking claws 43
1 represents the locking claw of the present invention, and each of the first engaging pieces 4
9 1 constitutes the engagement piece of the present invention, and each reinforcing rib 52 1 existing on the rear side in the rotating direction of the blocking plate constitutes a reinforcing rib of the present invention.
またダイヤフラム３の内周ビード３ｂは、弁筒
嵌入孔３８口縁と弁筒１２外面間に結着され、こ
れにより弁筒嵌入孔３８がシールされる。挟止板
本体４７に一対の窓５４が形成され、その一方の
窓５４が弁筒１２における通孔２３の開口部に対
向する。 Further, the inner peripheral bead 3b of the diaphragm 3 is bonded between the mouth edge of the valve sleeve fitting hole 38 and the outer surface of the valve sleeve 12, thereby sealing the valve sleeve fitting hole 38. A pair of windows 54 are formed in the blocking plate main body 47 , one of which faces the opening of the through hole 23 in the valve barrel 12 .
ブースタピストン２に対する挟止板４６の組付
けは次のように行われる。 The clamping plate 46 is assembled to the booster piston 2 as follows.
即ち、第２，第３図鎖線示のように挟止板本体
４７を抜止めフランジ４０の前面ｃに重合すると
共に各折曲げ部４８を抜止めフランジ４０外周面
に遊嵌して各第１係合片４９1を挟止板回転方向
後側の各補給リブ５２1の上方に、また各第２係
合片４９2を相隣る第１，第２係止爪４３1，４３
２間にそれぞれ配設する。そして挟止板４６を、
それにより抜止めフランジ４０を押圧してダイヤ
フラム３の内周ビード３ｂを圧縮しながら第２図
時計方向に回転して各第１，第２係合片４９1，
４９2を各第１，第２係止爪４３1，４３2の先端
部４４1，４４2内面に強制的に摺合させる。 That is, as shown by the chain lines in FIGS. 2 and 3, the retaining plate main body 47 is overlapped with the front surface c of the retaining flange 40, and each bent portion 48 is loosely fitted to the outer peripheral surface of the retaining flange 40, and each first The engagement piece 49 1 is placed above each replenishment rib 52 1 on the rear side in the rotational direction of the clamping plate, and each second engagement piece 49 2 is placed above the adjacent first and second locking claws 43 1 , 43 .
Place each between the two . And the clamping plate 46,
As a result, while pressing the retaining flange 40 and compressing the inner peripheral bead 3b of the diaphragm 3, the respective first and second engaging pieces 49 1 rotate clockwise in FIG.
49 2 are forcibly slid onto the inner surfaces of the tip portions 44 1 , 44 2 of the respective first and second locking claws 43 1 , 43 2 .
この場合、抜止めフランジ４０の各凹部４１が
ブースタピストン２の各凸部４２に係合してブー
スタピストン２に対する弁筒１２の回止めが確実
に行われているので、各第１，第２係合片４９1，
４９2を各第１，第２係止爪４３1，４３2に係合
する際、ダイヤフラム３の内周ビード３ｂを捩る
ことがない。 In this case, since each concave portion 41 of the retaining flange 40 engages with each convex portion 42 of the booster piston 2 and the valve cylinder 12 is reliably prevented from rotating relative to the booster piston 2, each of the first and second Engagement piece 49 1 ,
49 2 to the respective first and second locking claws 43 1 and 43 2 , the inner peripheral bead 3b of the diaphragm 3 is not twisted.
また各第１係合片４９1の外れ止め５０1はその
弾性により各補強リブ５２1を容易に乗越え、し
たがつて各補強リブ５２1は挟止板４６の係合方
向への回転を許容し、その上各第１，第２係止爪
４３1，４３2における挟止板回転方向後側の側縁
にブースタピストン２の平坦部４５から遠去かる
ように外方へ折曲がるガイド５５1，５５2が形成
され、また各第１係合片４９1の挟止板回転方向
前側の側縁にはブースタピストン２の平坦部４５
に近接するように内方に折曲がるガイド５６が形
成されると共に各第２係合片４９2の外れ止め５
０2がガイド作用をなすので、各第１，第２係止
爪４３1，４３2に対する各第１，第２係合片４９
１，４９2の摺合がスムーズに行われる。 Further, the retainer 50 1 of each first engagement piece 49 1 easily overcomes each reinforcing rib 52 1 due to its elasticity, and therefore each reinforcing rib 52 1 allows rotation of the clamping plate 46 in the engagement direction. Moreover, a guide 55 is provided on the rear side edge of each of the first and second locking claws 43 1 , 43 2 in the direction of rotation of the clamping plate, and is bent outward so as to move away from the flat portion 45 of the booster piston 2 . 1 , 55 2 are formed, and a flat portion 45 of the booster piston 2 is formed on the front side edge of each first engaging piece 49 1 in the rotational direction of the blocking plate.
A guide 56 is formed that bends inward so as to be close to the second engagement piece 492, and a guide 56 is formed to prevent the second engagement piece 492 from coming off.
0 2 acts as a guide, each of the first and second engaging pieces 49 for each of the first and second locking claws 43 1 and 43 2
1 , 49 2 sliding is carried out smoothly.
第４図ａに明示するように、抜止めフランジ４
０の前面ｃ外周部は、その前面ｃより後面ａに向
つて先広がりのテーパ面５７に形成され、そのテ
ーパ面５７と、それに対向する挟止板４６の係合
片連設部４６ａ後面との間には弧状空間Ｓが画成
される。この空間Ｓにより各第１，第２係合片４
９1，４９2における撓みの支点f1がテーパ面５７
の前縁部となつて、その支点f1と各第１，第２係
合片４９1，４９2間の距離が長くなるので、各第
１，第２係合片４９1，４９2のばね作用が増し、
これにより各第１，第２係止爪４３1，４３2に対
する各第１，第２係合片４９1，４９2の摺合が容
易となり、また各第１，第２係合片４９1，４９2
の弾性係合力が増加される。 As shown in Figure 4a, the retaining flange 4
The outer periphery of the front surface c of 0 is formed into a tapered surface 57 that widens from the front surface c toward the rear surface a. An arcuate space S is defined between them. By this space S, each of the first and second engaging pieces 4
The fulcrum f 1 of deflection at 9 1 , 49 2 is the tapered surface 57
Since the distance between the fulcrum f 1 and each of the first and second engaging pieces 49 1 and 49 2 becomes longer, the distance between each of the first and second engaging pieces 49 1 and 49 2 becomes longer. The spring action increases,
This facilitates sliding of each of the first and second engaging pieces 49 1 and 49 2 on each of the first and second locking claws 43 1 and 43 2 , and also allows each of the first and second engaging pieces 49 1 and 49 2 to slide together easily. 49 2
The elastic engagement force of is increased.
さらに第４図ａに明示するように抜止めフラン
ジ４０の後面ａ外周部全周に、両凹部４１を含む
逃げ５８が形成され、その逃げ５８は、両凹部４
１以外の部分に在つてブースタピストン２の前面
ｂより離間する当接面５８ａを持つている。その
当接面５８ａと対向するようにブースタピストン
２の平坦部４５に、両端を両凸部４２に連結した
一対の半環状補強リブ５９が膨出成形される。各
補強リブ５９は横断面円弧状に形成されている。 Furthermore, as clearly shown in FIG.
The booster piston 2 has a contact surface 58a located at a portion other than 1 and spaced apart from the front surface b of the booster piston 2. A pair of semi-annular reinforcing ribs 59 whose opposite ends are connected to both convex portions 42 are bulge-molded on the flat portion 45 of the booster piston 2 so as to face the contact surface 58a. Each reinforcing rib 59 has an arcuate cross section.
当接面５８ａおよび補強リブ５９間には所定の
間隔ｄが設けられ、これによりブースタピストン
２の撓みの支点f2が、当接面５８ａと後面ａ間の
連設面５８ｂの後縁となり、したがつてその支点
f2と各第１，第２係止爪４３1，４３2間の距離が
長くなるので、各第１，第２係止爪４３1，４３2
のばね作用が増し、これにより各第１，第２係止
爪４３1，４３2に対する各第１，第２係合片４９
１，４９2の摺合が容易に行われる。 A predetermined interval d is provided between the contact surface 58a and the reinforcing rib 59, so that the fulcrum f2 of the deflection of the booster piston 2 becomes the rear edge of the connecting surface 58b between the contact surface 58a and the rear surface a, Therefore its fulcrum
Since the distance between f 2 and each of the first and second locking claws 43 1 , 43 2 becomes longer, each of the first and second locking claws 43 1 , 43 2
This increases the spring action of each of the first and second engaging pieces 49 for each of the first and second locking claws 43 1 , 43 2 .
1,492 can be easily slid together .
両環状補強リブ５９は、ブースタピストン２の
前方への撓み量が増大したとき、当接面５８ａに
当接して前記撓み量を規制するもので、この当接
時において、各第１，第２係合片４９1，４９2が
各第１，第２係止爪４３1，４３2から外れないよ
うに各第１，第２係合片４９1，４９2の弾性係合
力が設定される。 When the amount of forward deflection of the booster piston 2 increases, both annular reinforcing ribs 59 come into contact with the contact surface 58a to regulate the amount of deflection. The elastic engagement forces of the first and second engagement pieces 49 1 and 49 2 are set so that the engagement pieces 49 1 and 49 2 do not come off the respective first and second locking claws 43 1 and 43 2 . .
次にこの実施例の作用について説明すると、第
１図の状態は非作動状態を示すもので、互いに連
結した弁ピストン１６および入力杆１５は、可動
ストツパ板３３が固定の端壁８に当接する所定の
後退位置に戻しばね３２のばね力を以て保持さ
れ、そして弁ピストン１６は第２弁座１４2を介
し弁部２１の前面を押圧して、これを弁体保持筒
１９の前面に軽く接触させるまで後退させ、それ
によつて第１弁座１４1と弁部２１間に僅かな間
隙ｇを形成している。このような状態は前記した
可動ストツパ板３３の調節により容易に得ること
ができる。 Next, to explain the operation of this embodiment, the state shown in FIG. 1 shows a non-operating state, in which the valve piston 16 and the input rod 15 are connected to each other, and the movable stopper plate 33 is in contact with the fixed end wall 8. The valve piston 16 is returned to the predetermined retracted position and held by the spring force of the spring 32, and the valve piston 16 presses the front surface of the valve portion 21 through the second valve seat 142 to lightly contact the front surface of the valve body holding cylinder 19. By this, a small gap g is formed between the first valve seat 14 1 and the valve portion 21 . Such a state can be easily obtained by adjusting the movable stopper plate 33 described above.
以上により、エンジン運転中、常に負圧を蓄え
ている第１作動室Ａは通孔２３，間隙ｇおよび通
孔２４を介して第２作動室Ｂと連通し、また弁部
２１の前面開口部は第２弁座１４2により閉鎖さ
れるので、第２作動室Ｂには第１作動室Ａの負圧
が伝達して両作動室Ａ，Ｂの気圧が平衡してい
る。したがつてブースタピストン２も戻しばね１
０の弾発力を以て図示の後退位置を占める。 As described above, during engine operation, the first working chamber A, which always stores negative pressure, communicates with the second working chamber B through the through hole 23, the gap g, and the through hole 24, and also through the front opening of the valve part 21. is closed by the second valve seat 142 , the negative pressure in the first working chamber A is transmitted to the second working chamber B, and the air pressures in both working chambers A and B are balanced. Therefore, the booster piston 2 also returns the spring 1.
It assumes the retracted position shown with a spring force of zero.
いま、車両を制動すべく図示しないブレーキペ
ダルを踏込み、入力杆１５および弁ピストン１６
を前進させれば、弁ばね６０により前方へ付勢さ
れる弁部２１は弁ピストン１６に追従して前進す
るが、第１弁座１４1と弁部２１との間隙ｇが前
述のように極めて狭いので、弁部２１は、直ちに
第１弁座１４1に着座して両作動室Ａ，Ｂ間の連
通を遮断し、同時に第２弁座１４2は弁部２１か
ら離れて第２作動室Ｂを通孔２４および弁体１７
内部を介して大気導入口９に連通させる。したが
つて第２作動室Ｂには大気が素早く導入され、該
室Ｂが第１作動室Ａよりも高圧となり、両室Ａ，
Ｂ間に生じる気圧差によりブースタピストン２が
戻しばね１０に抗し前進して、弾性ピストン２７
を介して出力杆３１を前進させるので、ブレーキ
マスタシリンダの作動ピストンを前方へ駆動し、
車両に制動がかけられる。 Now, in order to brake the vehicle, the brake pedal (not shown) is depressed, and the input rod 15 and valve piston 16 are pressed down.
When the valve spring 60 moves forward, the valve part 21 moves forward following the valve piston 16, but the gap g between the first valve seat 141 and the valve part 21 is as described above. Since the valve portion 21 is extremely narrow, the valve portion 21 immediately seats on the first valve seat 14 1 to cut off communication between the two working chambers A and B, and at the same time, the second valve seat 14 2 separates from the valve portion 21 and enters the second working chamber. Chamber B through hole 24 and valve body 17
It communicates with the atmosphere inlet 9 through the inside. Therefore, the atmosphere is quickly introduced into the second working chamber B, and the pressure in the second working chamber B becomes higher than that in the first working chamber A.
Due to the pressure difference generated between B, the booster piston 2 moves forward against the return spring 10, and the elastic piston 27
Since the output rod 31 is advanced through the
Braking is applied to the vehicle.
弁ピストン１６の小軸３０がその前進により反
動ピストン２９を介して弾性ピストン２７に当接
すると、出力杆３１の作動反力による弾性ピスト
ン２９側への膨出変形により前記反力の一部が弁
ピストン１６を介してブレーキペダル側にフイー
ドバツクされ、これにより操縦者は出力杆３１の
出力、即ち制動力を感知することができる。 When the small shaft 30 of the valve piston 16 comes into contact with the elastic piston 27 via the reaction piston 29 due to its advancement, part of the reaction force is bulged and deformed toward the elastic piston 29 due to the operational reaction force of the output rod 31. Feedback is provided to the brake pedal side via the valve piston 16, so that the driver can sense the output of the output rod 31, that is, the braking force.
ブースタピストン２の前進時、両作動室Ａ，Ｂ
間に生じる気圧差によりブースタピストン２が前
方へ撓むが、そのときの撓みは抜止めフランジ４
０後面の前記支点f2により支承される。 When the booster piston 2 moves forward, both working chambers A and B
The booster piston 2 is bent forward due to the pressure difference between the booster pistons 2 and 4.
It is supported by the fulcrum f2 on the rear surface.
一方、両作動室Ａ，Ｂ間に生じる気圧差が過大
となつてブースタピストン２の前方への撓み量が
増大し、第４図ｂに示すように各補強リブ５９が
抜止めフランジ４０の各当接面５８ａに当接する
と、ブースタピストン２の前記撓み量が規制さ
れ、それ以上各第１，第２係止爪４３1，４３2が
前方へ移動することがなく、またこの状態では各
第１，第２係止爪４３1，４３2に対する各第１，
第２係合片４９1，４９2の弾性係合力が維持され
ているので、各第１，第２係合片４９1，４９2が
各第１，第２係止爪４３1，４３2から外れること
はない。 On the other hand, the pressure difference generated between the working chambers A and B becomes excessive, and the amount of forward deflection of the booster piston 2 increases, and as shown in FIG. When it comes into contact with the contact surface 58a, the amount of deflection of the booster piston 2 is restricted, and the first and second locking claws 43 1 and 43 2 do not move forward any more, and in this state, each Each of the first and second locking claws 43 1 and 43 2
Since the elastic engagement force of the second engagement pieces 49 1 , 49 2 is maintained, the respective first and second engagement pieces 49 1 , 49 2 are connected to the respective first and second locking claws 43 1 , 43 2 . It will never come off.
またブースタピストン２の撓みは、補強リブ５
９と当接面５８ａとの当接部を支点f3として支承
され、このように両作動室Ａ，Ｂ間に生じる気圧
差の大小によりブースタピストン２の撓みを支承
する支点f2，f3が変わるので、ブースタピストン
２の一箇所に前記撓みに起因した応力が集中的に
作用することがなく、これによりブースタピスト
ン２の耐久性を向上させることができる。 In addition, the deflection of the booster piston 2 is determined by the reinforcing rib 5.
The fulcrums f 2 and f 3 support the deflection of the booster piston 2 depending on the magnitude of the pressure difference generated between the working chambers A and B. Since this changes, the stress caused by the deflection does not act concentratedly on one location of the booster piston 2, and thereby the durability of the booster piston 2 can be improved.
次に、ブレーキペダルの踏込み力を解放する
と、先ず弁ピストン１６にかかる前記反力および
戻しばね３２の弾発力により入力杆１５が後退
し、これにより第２弁座１４2を弁部２１に着座
させると共にその弁部２１を弁体保持筒１９の前
面に当接させるので、弁部２１は入力杆１５の後
退力を受けて軸方向に圧縮変形を生じる。その結
果、第１弁座１４1と弁部２１との間には当初の
間隙ｇより大きな間隙が形成されるため、その大
きな間隙を通して両作動室Ａ，Ｂの気圧が相互に
素早く均衡し、それらの気圧差がなくなれば、ブ
ースタピストン２は、戻しばね１０の弾発力で後
退し、ダイヤフラム３の突起１１がブースタシエ
ル１の後壁内面に当接して停止する。そして、入
力杆１５が端壁８に当接したとき、弁部２１は入
力杆１５の後退力から解放されて原形に復元する
ので、第１弁座１４1との間隙を再び小間隙ｇに
挟めることができる。 Next, when the depression force of the brake pedal is released, the input rod 15 is moved backward due to the reaction force applied to the valve piston 16 and the elastic force of the return spring 32, and this causes the second valve seat 142 to be pressed against the valve portion 21. Since the valve portion 21 is seated and brought into contact with the front surface of the valve body holding cylinder 19, the valve portion 21 receives the retreating force of the input rod 15 and undergoes compressive deformation in the axial direction. As a result, a gap larger than the initial gap g is formed between the first valve seat 14 1 and the valve part 21, so that the air pressures in both working chambers A and B are quickly balanced with each other through this large gap. When the pressure difference between them disappears, the booster piston 2 moves back due to the elastic force of the return spring 10, and the projection 11 of the diaphragm 3 comes into contact with the inner surface of the rear wall of the booster shell 1 and stops. Then, when the input rod 15 comes into contact with the end wall 8, the valve part 21 is released from the retreating force of the input rod 15 and returns to its original shape, so that the gap with the first valve seat 141 is reduced to the small gap g again. It can be sandwiched.
Ｃ 考案の効果
本考案によれば、抜止めフランジ前面に重合す
る挟止板に、該板の抜止めフランジに対する所定
の回転方向への相対回転により、ブースタピスト
ンに切起された複数の係止爪に係合する複数の弾
性係合片が一体に形成された負圧式倍力装置にお
いて、ブースタピストンには、挟止板の前記回転
方向と交差するように延びる補強リブが、各係止
爪の切起し孔の前記回転方向後側に近接して設け
られるので、その補強リブによりブースタピスト
ンの切起し孔周辺部を有効に補強することができ
る。C. Effects of the invention According to the invention, a plurality of locks are formed on the booster piston by rotating the plate relative to the retaining flange in a predetermined rotational direction on the retaining plate superimposed on the front surface of the retaining flange. In a negative pressure booster in which a plurality of elastic engagement pieces that engage with pawls are integrally formed, the booster piston has a reinforcing rib that extends in a direction intersecting with the rotational direction of the clamping plate, and each of the pawls Since the reinforcing rib is provided close to the rear side of the cut and raised hole in the rotational direction, the area around the cut and raised hole of the booster piston can be effectively reinforced by the reinforcing rib.
また前記補強リブは、各係止爪に各係合片を係
合させるべく挟止板を回転させる際の該各係合片
の移動軌跡内に配置され、前記係合片は、それを
各係止爪に係合させるべく挟止板を回転させる際
には自己の弾性変形により前記補強リブを乗り越
え、また該係合片を各係止爪に係合させた状態で
は前記弾性変形から復元していて該補強リブの側
面に対面するように形成されるので、係合片と係
止爪との係合状態ではその係合片に上記補強リブ
の側面が対面していて、係合片ひいては挟止板
の、前記回転方向と反対方向の回転が規制され、
従つて該補強リブを、係合片の係止爪からの外れ
止め手段に兼用することができるから、それだけ
構造が簡素化されコストダウンに寄与することが
できる。また係合片を係止爪に係合させるべく挟
止板を所定方向に回転させる際には、該係合片
が、それの移動軌跡内に在る上記補強リブを自己
の弾性変形により乗り越えることができるから、
係合片と係止爪との係合を難なく、しかも挟止板
の回転に伴ない自動的に行わせることができ、操
作性が良好である。 Further, the reinforcing ribs are disposed within the locus of movement of each of the engagement pieces when rotating the clamping plate to engage each of the engagement pieces with each of the engagement claws. When the clamping plate is rotated to engage with the locking claws, it overcomes the reinforcing ribs due to its own elastic deformation, and when the engaging pieces are engaged with each of the locking claws, it recovers from the elastic deformation. Since the engaging piece is formed so as to face the side surface of the reinforcing rib, when the engaging piece and the locking pawl are engaged, the side side of the reinforcing rib faces the engaging piece, and the engaging piece In turn, the rotation of the clamping plate in the opposite direction to the rotational direction is restricted,
Therefore, the reinforcing rib can also be used as a means for preventing the engaging piece from coming off the locking claw, which can simplify the structure and contribute to cost reduction. Furthermore, when the clamping plate is rotated in a predetermined direction to cause the engaging piece to engage with the locking pawl, the engaging piece overcomes the reinforcing rib located within its movement locus by its own elastic deformation. Because you can
The engagement piece and the locking pawl can be easily and automatically engaged with each other as the locking plate rotates, resulting in good operability.
図面は本考案の一実施例を示し、第１図は全体
の縦断面図で、第２図−線断面に相当し、第
２図は第１図−矢視図、第３図は第２図−
線断面図、第４図はブースタピストンに対する
弁筒の組付け部分の拡大縦断面図で、ａはブース
タピストンが撓む前の状態を、ｂはブースタピス
トンが撓んだ状態をそれぞれ示す。
Ａ，Ｂ……第１，第２作動室、ｂ……前面、１
……ブースタシエル、２……ブースタピストン、
６……制御弁、１２……弁筒、３８……弁筒嵌入
孔、４３1……係止爪としての第１係止爪、４６
……挟止板、４９1……係合片としての第１係合
片、５１1……切起し孔、５２1……補強リブ。
The drawings show one embodiment of the present invention, and FIG. 1 is a longitudinal cross-sectional view of the whole, which corresponds to a cross-sectional view taken along the line in FIG. 2, FIG. Figure-
The line sectional view and FIG. 4 are enlarged longitudinal sectional views of the part where the valve cylinder is assembled to the booster piston, where a shows the state before the booster piston is bent, and b shows the state where the booster piston is bent. A, B...First and second working chambers, b...Front, 1
...Booster Ciel, 2...Booster Piston,
6... Control valve, 12... Valve cylinder, 38... Valve cylinder fitting hole, 43 1 ... First locking claw as a locking claw, 46
...Pinch plate, 49 1 ...First engagement piece as an engagement piece, 51 1 ... Cut and raised hole, 52 1 ... Reinforcement rib.
Claims (1)
負圧源に連なる第１作動室Ａと、制御弁６を介し
て該第１作動室Ａまたは大気に選択的に連通され
る第２作動室Ｂとに区画すべく、前記ブースタシ
エル１内に前後往復動自在に収容されるブースタ
ピストン２と；該ブースタピストン２の中心に存
する弁筒嵌入孔３８に嵌合されて抜止めフランジ
４０を該ブースタピストン２前面に重合した制御
弁用弁筒１２と；前記抜止めフランジ４０を前記
ブースタピストン２と協働して挟止すべく該抜止
めフランジ４０前面に重合する挟止板４６と；を
少なくとも備え、前記挟止板４６には、該板４６
の抜止めフランジ４０に対する所定の回転方向へ
の相対回転により、該ブースタピストン２に切起
された複数の係止爪４３1に係合する複数の弾性
係合片４９1が一体に形成されてなる負圧式倍力
装置において、前記ブースタピストン２には、前
記挟止板４６の前記回転方向と交差するように延
びる補強リブ５２1が、各係止爪４３1の切起し孔
５１1の前記回転方向後側に近接して設けられ、
その補強リブ５２は、各係止爪４３1に各係合片
４９1を係合させるべく前記挟止板４６を回転さ
せる際の該各係合片４９1の移動軌跡内に配置さ
れ、前記各係合片４９1は、それを各係止爪４３1
に係合させるべく前記挟止板４６を回転させる際
には自己の弾性変形により前記補強リブ５２1を
乗り越え、また該係合片４９1を各係止爪４３1に
係合させた状態では前記弾性変形から復元してい
て該補強リブ５２1の側面に対面するように形成
されたことを特徴とする、負圧式倍力装置。 A booster shell 1; a first working chamber A connected to a negative pressure source within the booster shell 1; and a second working chamber B selectively communicated with the first working chamber A or the atmosphere via a control valve 6. A booster piston 2 is housed in the booster shell 1 so as to be able to reciprocate back and forth in order to partition the booster piston 2 into the booster piston. 2; and a clamping plate 46 that overlaps with the front surface of the retaining flange 40 to clamp the retaining flange 40 in cooperation with the booster piston 2. , the clamping plate 46 includes the plate 46
When the booster piston 2 is rotated relative to the retaining flange 40 in a predetermined rotational direction, a plurality of elastic engaging pieces 49 1 are integrally formed that engage with a plurality of locking claws 43 1 cut and raised on the booster piston 2. In this negative pressure booster, the booster piston 2 has reinforcing ribs 52 1 extending perpendicularly to the rotational direction of the clamping plate 46 in the cutout holes 51 1 of each locking claw 43 1 . provided close to the rear side in the rotational direction,
The reinforcing rib 52 is disposed within the locus of movement of each engaging piece 49 1 when rotating the clamping plate 46 to engage each engaging piece 49 1 with each locking pawl 43 1 . Each engagement piece 49 1 connects it to each locking claw 43 1
When the locking plate 46 is rotated to engage with the locking plate 46, it overcomes the reinforcing rib 521 due to its own elastic deformation, and when the locking piece 491 is engaged with each locking pawl 431 , A negative pressure booster, characterized in that it has recovered from the elastic deformation and is formed so as to face the side surface of the reinforcing rib 521 .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP51987U JPH0412850Y2 (en) | 1987-01-06 | 1987-01-06 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP51987U JPH0412850Y2 (en) | 1987-01-06 | 1987-01-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63108856U JPS63108856U (en) | 1988-07-13 |
| JPH0412850Y2 true JPH0412850Y2 (en) | 1992-03-26 |
Family
ID=30777562
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP51987U Expired JPH0412850Y2 (en) | 1987-01-06 | 1987-01-06 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0412850Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0611280Y2 (en) * | 1989-11-20 | 1994-03-23 | 日信工業株式会社 | Negative pressure booster |
-
1987
- 1987-01-06 JP JP51987U patent/JPH0412850Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63108856U (en) | 1988-07-13 |
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