JPS59109452A - Hydraulic booster - Google Patents

Abstract

PURPOSE:To improve response performance in trouble by restricting an oscillating element which is pivotally installed onto an operation pedal and operates a control valve by means of a restricting member when a hydraulic system is in trouble and properly adjusting the position of the restricting member and restricting properly the oscillation element. CONSTITUTION:The intermediate part of an oscillation element 35 in a form ''U'' is pivotally installed onto a brake pedal 31, and an output piston is attached onto the lower edge of the oscillation element 35, and a hydraulic control valve mechanism is attached onto the upper edge of the oscillation element 35. A restricting member 43 for restricting the swing of the oscillation element 35 when a hydraulic system is broken down is arranged, positioned under the supporting shaft 36 of the oscillation element 35. The restricting member 43 is formed into U-figure shape, and the both side surfaces of the pedal 3 are put between the both foot parts 43a, and said restricting member is held onto the pedal 31 by a bolt 54. The interval between the oscillation element 35 and the restricting member 43 is properly adjusted by turning the bolt 54. When the hydraulic system is broken down, the oscillation element swings, having the shaft 36 as a center, and the rear surface of the oscillation element is attached onto the restricting member 43, and the further oscillation is restricted.

Description

【発明の詳細な説明】 本発明は油圧ポンプ、蓄圧器等の油圧源からの圧油によ
って作動する油圧式倍力装置に関し、特ニ車両のブレー
キマスクシリンダ操作用に適するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic booster operated by pressure oil from a hydraulic source such as a hydraulic pump or a pressure accumulator, and is particularly suitable for operating a brake mask cylinder of a vehicle.

この押装置として、操作ペダルの踏込みにより、その操
作ペダルに枢着された揺動子を揺動させて摺動制御弁を
前進作動させ、これにより油圧源の圧油を・やワーフリ
ングに供給して出力ビストンを倍力作動するようにしだ
ものが考えられているが、油圧系統、例えば給油路に漏
洩故障が生じたような場合には揺動子の、摺動制御弁作
動方向への揺動を直ちに拘束して操作被ダルｌ）踏力を
出力１７トンに伝達し、それを前進作動させなければな
らない。この場合、揺動子に対する拘束部材は操作波ダ
ルまたは揺動子自体に配設されるが、揺動子、操作被ダ
ル等ｌｌ（は組付、製作誤差があるので、それらを吸収
し得るようにしておか々いと、油圧系統故障時に揺動子
を的確に拘束することができない。As this push device, when the operating pedal is depressed, the oscillator pivotally connected to the operating pedal is swung to move the sliding control valve forward, thereby supplying pressure oil from the hydraulic source to the wharf ring. However, if there is a leakage failure in the hydraulic system, for example in the oil supply path, the oscillator should be moved in the direction in which the sliding control valve operates. It is necessary to immediately restrain the swing and operate the pedal.l) The pedal force must be transmitted to an output of 17 tons, and it must be operated forward. In this case, the restraining member for the oscillator is disposed on the operating wave barrel or the oscillator itself, but since there are assembly and manufacturing errors in the oscillator, operated barrel, etc., it is possible to absorb them. Otherwise, the oscillator cannot be properly restrained in the event of a hydraulic system failure.

本発明は上記に鑑み、拘束部材の位置を適宜調節し得る
ようにして油圧系統故障時に揺動子を的確に拘束し、操
作ペダルと出力ビストン間の応答性を向上させた前記油
圧式倍力装置を提供することを目的とし、出玉ピヌトン
を摺合した・ぐワーフリングと；摺動制御弁を摺合し、
その摺動制御弁を介して油圧源と・ぞワーフリング間の
連通を制御すべくパワーンリングに並列に配設された制
御シリンダと；出力ピストンおよび摺動制御弁を操作す
る操作ペダルと；出力ビストンの後部に前端を連接され
た第１操作子と；摺動制御弁の後部に前端を連接された
第２操作子と；操作４ダルに枢着され、作動時一方向に
揺動して第２操作子を介し摺動制御弁を前進作動させる
と共に出力ビストンの前進作動に伴い他方向に揺動して
第１操作子を介し出力ビストンを押動する揺動子と；油
圧系統故障時に揺動子の、摺動側両弁作動方向への揺動
を拘束する拘束部材と；その拘束部材の位置調節手段と
；を備えたことを特徴とする。In view of the above, the present invention provides the above-mentioned hydraulic booster in which the position of the restraining member can be appropriately adjusted to accurately restrain the oscillator in the event of a failure of the hydraulic system, and the responsiveness between the operating pedal and the output piston is improved. For the purpose of providing a device, a wharf ring made by sliding a ball output pinuton; and a sliding control valve,
a control cylinder disposed in parallel with the power ring to control communication between the hydraulic power source and the wharf ring via the sliding control valve; an operating pedal for operating the output piston and the sliding control valve; A first operator whose front end is connected to the rear of the output piston; a second operator whose front end is connected to the rear of the sliding control valve; and a second operator which is pivotally connected to the operation lever and swings in one direction when activated. an oscillator that operates the sliding control valve forward through the second operator and swings in the other direction as the output piston moves forward to push the output piston through the first operator; The present invention is characterized by comprising: a restraining member that restrains the rocking member from swinging in the operating direction of both sliding valves; and means for adjusting the position of the restraining member.

以下、図面により本発明を車両のブレーキマスクシリン
ダ操作用油圧式倍力装置に適用した実施例について説明
すると、第１〜第６図において倍力装置本体１には棒状
をなす摺動制御弁２を摺合させた制御シリンダ３と、出
力ビストン４を摺合さぜた・ぐワーフリング５とが上下
に並列に配設される。まだ・ぐワーフリング５の前端に
は公知のブレーキマ。スタシリンダＭが取付けられ、そ
の作動ピストン６の後端に前記出力ピストン４の前端が
連接される。Hereinafter, an embodiment in which the present invention is applied to a hydraulic booster for operating a brake mask cylinder of a vehicle will be explained with reference to the drawings. A control cylinder 3 with which the output piston 4 is slid together and a wharf ring 5 with which the output piston 4 is slid together are arranged vertically in parallel. At the front end of the wharf ring 5 is a well-known brake machine. A star cylinder M is attached, and the front end of the output piston 4 is connected to the rear end of the operating piston 6.

制御シリンダ３内は隔壁体９により前部の排油室Ａと後
部の給油室Ｂとに区画され、その給油室Ｂ・は油圧源７
の蓄圧器１０、油圧ポンプ１１に連なる給油路１２に接
続され、一方排油室Ａは油圧源７の油溜１３に連なる排
油路１４に接続される。The inside of the control cylinder 3 is divided by a partition wall 9 into an oil drain chamber A at the front and an oil supply chamber B at the rear, and the oil supply chamber B is connected to a hydraulic source 7.
The oil drain chamber A is connected to an oil drain path 14 that connects to an oil reservoir 13 of a hydraulic power source 7.

摺動制御弁２は、隔壁体９と制御シリンダ３の後端壁と
に摺動自在に貫通支承され、その給油室Ｂ内に位置する
中間部に該室・Ｂ１内を前部の第１油室ｂ１と後部の第
２油室ｂ２とに区画する隔壁体１５が固着される。摺動
制御弁２は、その軸方向に両端を閉塞された通油孔１６
を形成されており、その通油孔１６の前端部には半径方
向に形成された排油孔１７が、また通油孔１６の中間部
と後端部には隔壁体１５を挾んで半径方向に形成された
導入孔１８と排出孔１９がそれぞれ連通している。The sliding control valve 2 is slidably supported through the partition wall body 9 and the rear end wall of the control cylinder 3, and has an intermediate portion located in the oil supply chamber B and a first valve in the front portion inside the oil supply chamber B1. A partition wall body 15 is fixed to partition the oil chamber b1 and the second oil chamber b2 at the rear. The sliding control valve 2 has an oil passage hole 16 that is closed at both ends in the axial direction.
An oil drain hole 17 is formed in the radial direction at the front end of the oil passage hole 16, and an oil drain hole 17 is formed in the radial direction at the middle and rear end of the oil passage hole 16 with the partition wall 15 in between. An introduction hole 18 and a discharge hole 19 formed in are in communication with each other.

第２、第５図に示すように排油室Ａ゛内において、その
前氷壁を構成するカップ状閉塞体２ｏ底壁と、摺動制御
弁２の前端部に嵌合された・リテーナ２１との間には戻
しばね２２が縮設さ几る。リテーナ２１は摺動制御弁２
に止着しだ止環２３により後方への移動を用土され、そ
の止環２３と隔壁体９との間において制御弁２に緩衝ゴ
ム環２４が嵌着される。As shown in FIGS. 2 and 5, in the oil drain chamber A, the bottom wall of the cup-shaped closing body 2o that constitutes the front ice wall, and the retainer 21 fitted to the front end of the sliding control valve 2. A return spring 22 is installed between the two. The retainer 21 is the sliding control valve 2
A retaining ring 23 prevents the valve from moving rearward, and a buffer rubber ring 24 is fitted to the control valve 2 between the retaining ring 23 and the partition wall 9.

前記制御シリンダ３およびその内部の摺動制御弁２、第
１および第２油室ｂ１、ｂ２等は油圧制御弁機構８を構
成する。The control cylinder 3, the sliding control valve 2 therein, the first and second oil chambers b1, b2, etc. constitute a hydraulic control valve mechanism 8.

・やワーフリンダ５内は、それに摺合する出力ビストン
４により前部の減圧室Ｃと後部の油圧室りとに区画され
る。出力ビストン４の前面に突設された第１ピストンロ
ッド２５．は、ノぐワーシリンダ５の前端壁を構成する
カンフ０状閉塞体２６の底壁に貫通支承され、その突出
瑞はブレーキマスクシリンダＭの作動ピストン６後端に
連接される。寸だ出力ビストン４の後面に突設された第
２ピストンロツド２５□は前部の大径部２７と、それに
連設された後部の小径部２８とを備え、その小径部２８
は・ぐワーシリンダ５の後端壁に貫通支承され、大径部
２７の環状後端面はパワーシリンダ５の後端壁内面に当
接して出力ビストン４の後退限規制用ストッパとして機
能する。減圧室Ｃ内には出カビストン４を後方へ付勢す
る戻しはね２９が縮設される。この戻しばね２９の弾発
力は前記摺動制御弁２の戻しばね２２のそれよりも犬き
く設定されている。The interior of the wharf lender 5 is divided into a decompression chamber C at the front and a hydraulic chamber at the rear by the output piston 4 that slides thereon. A first piston rod 25 protruding from the front surface of the output piston 4. is penetrated and supported by the bottom wall of the cylinder 0-shaped closing body 26 constituting the front end wall of the blower cylinder 5, and its protrusion is connected to the rear end of the actuating piston 6 of the brake mask cylinder M. The second piston rod 25 □ protruding from the rear surface of the output piston 4 has a large diameter portion 27 at the front and a small diameter portion 28 at the rear connected thereto.
The large diameter portion 27 is supported through the rear end wall of the power cylinder 5, and the annular rear end surface of the large diameter portion 27 comes into contact with the inner surface of the rear end wall of the power cylinder 5 to function as a stopper for regulating the backward limit of the output piston 4. A return spring 29 is provided in the decompression chamber C to urge the exit piston 4 backward. The elastic force of the return spring 29 is set to be stronger than that of the return spring 22 of the sliding control valve 2.

・ぞワーシリンダ５の減圧および油圧室Ｃ）、Ｉ）は倍
力装置本体１に形成された第１、第２連通油孔３０１．
３０□を介して制御７リンダ３の第２、第１油室ｂ２、
ｂｌにそれぞれ連通ずる。・The pressure reduction and hydraulic pressure chambers C) and I) of the lower cylinder 5 are connected to the first and second communication oil holes 301 formed in the booster main body 1.
The second and first oil chambers b2 of the control 7 cylinder 3 via 30□,
bl respectively.

倍力装置本体１の後方において、操作にダルとしてのブ
レーキ被ダル３１の基端部が車体３２の取付ブラケット
３３に基軸３４を介して前後方向に揺動自在に枢着され
ている。ブレーキぜダル３１の基端側には、その前部両
側面を挾むようにして、コ字形をなす揺動子３５の中間
部が支持軸３６を介して枢着される。揺動子３５の下瑞
には、前進を出力ビストン４の第２ピストンロツド２５
２後唱に連接した第１操作子３７．の佐瑞コ字形部３Ｂ
が揺動子３５の前部両側面を挾み第１枢軸３９１を介し
て枢着される。捷た揺動子３５の上Ｊ：ｆＡ　Ｋは、前
進を摺動制御弁２の後☆；台に連接した第２操作子３７
□の後端コ字形部４０が揺動子３５の前部両側面を挾み
第２枢輔３９．を介して枢着される。ブレーキペダル３
１の前縁部には各枢軸３９７．３９２との干渉を避ける
だめ切欠き４１．４２が形成される。At the rear of the booster main body 1, a base end portion of a brake lever 31 serving as a lever for operation is pivotally attached to a mounting bracket 33 of a vehicle body 32 via a base shaft 34 so as to be swingable in the front-rear direction. An intermediate portion of a U-shaped oscillator 35 is pivotally attached to the proximal end side of the brake pedal 31 via a support shaft 36 so as to sandwich both front side surfaces thereof. At the bottom of the oscillator 35, there is a second piston rod 25 of the forward output piston 4.
The first operator 37 connected to the second post-song. Sazui U-shaped part 3B
are pivotally mounted via a first pivot 391, sandwiching both front sides of the rocker 35. Above J: fA K of the undone oscillator 35, the forward movement is after the sliding control valve 2 ☆; The second operator 37 connected to the stand
□ The rear end U-shaped portion 40 sandwiches both front sides of the rocker 35 and the second pivot 39. It is pivotally connected via. brake pedal 3
Cutouts 41 and 42 are formed on the front edge of the shaft 1 to avoid interference with each pivot shaft 397 and 392.

プレーキイダル３１の後部において、揺動子３５の支持
軸３６の下方に位置させて油圧系統故障時ｈ６動子３５
の揺動を拘束する拘束部材４３が配設される。拘束部材
４３にＵ字形をなし、その両脚部４３ａでブレーキ４ダ
ル３１の両１１１１　面ヲ挾み、両脚部４３ａの接続部
４３ｂに形成された挿通孔５３にはボルト５４が遊挿さ
れ、そのボルト５４をブレーキ被ダル３１のねし孔５５
に螺合することにより拘束部材４３がプレー・キベダル
３１に保持される。ブレーキペダル３１の後端面に当接
されたリデーナ５６と接続部４３ｂ内面間にはポルｊ・
５４の緩止めをなすばね５７が縮設きれる。At the rear of the brake pedal 31, it is located below the support shaft 36 of the oscillator 35, so that the h6 oscillator 35 is
A restraining member 43 is provided to restrain the swinging of the shaft. The restraining member 43 has a U-shape, and its legs 43a sandwich both 1111 surfaces of the brake pedal 31, and a bolt 54 is loosely inserted into the insertion hole 53 formed in the connecting part 43b of both legs 43a. Insert the bolt 54 into the tapped hole 55 of the brake shoulder 31.
The restraint member 43 is held on the playback plate 31 by being screwed into the restraint member 43 . A por j.
The spring 57 that prevents the spring 54 from loosening can be fully retracted.

これにより両脚部４３ａの前端面が揺動子３５の両後瑞
面にそれぞれ対向し、ボルト５４を回すことにより揺動
子３５′と拘束部材４３との間隔を適宜調節することが
でき、したがって封？ルト５４は拘束部材４３の位置調
節手段として機能する。As a result, the front end surfaces of both leg portions 43a are opposed to both rear apertures of the oscillator 35, and by turning the bolt 54, the distance between the oscillator 35' and the restraint member 43 can be adjusted as appropriate. Seal? The bolt 54 functions as a position adjusting means for the restraining member 43.

倍力装置本体１０制御シリンダ３によび・ぐワーノリン
ダ５の前嬬開口部外周には一連のフランツ４４が突設さ
れている。フランツ４４の前端面には、押え板４５が当
接され、その押え板４５は制御ンリング３における左、
右のフランジ部分およヒノクワーシリンダ５における下
部のフランジ部分に螺着した３本の第１ビルト４６．に
よりフランツ４４に固着される。A series of flanges 44 are protruded from the outer periphery of the front opening of the booster main body 10 and the control cylinder 3 of the blower cylinder 5. A presser plate 45 is in contact with the front end surface of the Franz 44, and the presser plate 45 is attached to the left side of the control ring 3,
Three first bolts 46 screwed to the right flange portion and the lower flange portion of the hinokiwa cylinder 5. It is fixed to Franz 44 by.

またノｅワーンリンダ５における左、右のフランジ部分
にはそれぞれ押え板４５を貫通して前方に突出する２本
の第２ボルト４６２が固着されている。ブレーキマスク
シリンダＭの後端部は、押え板４５の挿通孔４８を貫通
して閉塞体２６内に嵌合され、また取付７ランジ４９に
画筆２ボルトキロ２をそれぞれ貫通させ、それら第２ボ
ルト４６□の取付フランツ４９からの突出部にそれぞれ
ナツト５０を螺着し、これによりブレーキマスタ／リン
ダＭ・の取付フランジ４９後面と・ぐワーフリンダ５の
フランジ４４前端面間に押え板４５を挾着してそれら三
部材４４．４５．４９が結合される。Further, two second bolts 462 are fixed to the left and right flange portions of the no-e-warn cylinder 5, respectively, so as to penetrate through the presser plate 45 and protrude forward. The rear end of the brake mask cylinder M passes through the insertion hole 48 of the holding plate 45 and is fitted into the closing body 26, and also passes through the mounting 7 flange 49 with two bolts 2 bolts, respectively, and connects the second bolt 46 to the second bolt 46. Screw the nuts 50 onto the protruding parts of the mounting flange 49 of □, and thereby clamp the retaining plate 45 between the rear surface of the mounting flange 49 of the brake master/linda M and the front end surface of the flange 44 of the wharf cylinder 5. The three members 44, 45, and 49 are then joined together.

このように押え板４５を制御シリンダ３およびノ９ワー
シリンダ５のフラン−、）４４に取付けるとブレーキマ
スクシリンダ・Ｍ・をパワーシリンダ５より取外しても
各閉塞体２０．２６が各シリンダ３．５内に油圧に抗し
て確実に保持されるので、倍力装置の単体作動試験を行
うことができる。またブレーキマスクシリンダＭの取付
フランジ４９とノぐワーフリンダ５のフラン−）４４間
に押え板４５が挾着されるので、制動時においては／Ｆ
クワ−リンダ５の作動油圧を押え板４５のみで支承する
ものではなく、しだがって押え板４５の変形といった不
具合を生じることがない。When the presser plate 45 is attached to the flange, ) 44 of the control cylinder 3 and the power cylinder 5 in this way, even if the brake mask cylinder M is removed from the power cylinder 5, each closing body 20, 26 remains in each cylinder 3. Since the booster is securely held within the pump 5 against hydraulic pressure, a single operation test of the booster can be performed. Also, since the holding plate 45 is clamped between the mounting flange 49 of the brake mask cylinder M and the flange 44 of the wharf cylinder 5, the /F
The hydraulic pressure of the quar cylinder 5 is not supported only by the presser plate 45, and therefore problems such as deformation of the presser plate 45 do not occur.

次にこの装置の作動を説明する。Next, the operation of this device will be explained.

ブレーキ被ダル３１の非操作時では、摺動制御弁２は戻
しばね２２の弾発力により図示の後退限に保持されてい
て、排油孔１７は閉鎖され、導入孔１８および排出孔１
９は第１、第２油室ｂ１、ｂ２にそれぞれ開放されてい
る。また出力ピグ１ン４も戻しばね２９の弾発力により
図示の後退限に保持されている。When the brake lever 31 is not operated, the sliding control valve 2 is held at the retreat limit shown in the figure by the elastic force of the return spring 22, the drain hole 17 is closed, and the oil drain hole 17 is closed, and the oil drain hole 17 is closed.
9 is open to the first and second oil chambers b1 and b2, respectively. Further, the output pig 1 pin 4 is also held at the retracting limit shown in the figure by the elastic force of the return spring 29.

給油路１２に故障がなく、蓄圧器１０が正常に作動して
いれば、蓄圧器１０の圧油が給油路１２、第１油室ｂ１
および第２連通油孔３０２を経て・やワーフリンダ５の
油圧室Ｄ・に進入し、一方策１油室ｂ１、導入孔１８、
通油孔１６、排出孔１９、第２油室ｂ２および第１連通
油孔３０１を経て・Ｑワーフリンダ５の減圧呈Ｃノに進
入する。これにより、制御シリンダ３においては第１油
室ｂ１と第２油室ｂ２の油圧が均衡し、また／、ｏワ・
−シリンダ５においては減圧室Ｃ）と油圧室Ｄ・の油圧
が均衡し、前述のように摺動制御弁２および出力ビスト
ン４は戻しばね２２．２９の弾発力によりそれぞれ後退
限に保持される。If there is no failure in the oil supply passage 12 and the pressure accumulator 10 is operating normally, the pressure oil in the pressure accumulator 10 will flow through the oil supply passage 12 and the first oil chamber b1.
and enters the hydraulic chamber D of the wharf cylinder 5 through the second communication oil hole 302, and enters the first oil chamber b1, the introduction hole 18,
It enters the reduced pressure C of the Q-wharf cylinder 5 through the oil passage hole 16, the discharge hole 19, the second oil chamber b2, and the first communication oil hole 301. As a result, in the control cylinder 3, the oil pressures in the first oil chamber b1 and the second oil chamber b2 are balanced, and/or the oil pressure is balanced.
- In the cylinder 5, the hydraulic pressures in the pressure reducing chamber C) and the hydraulic chamber D are balanced, and as mentioned above, the sliding control valve 2 and the output piston 4 are held at their retraction limits by the elastic force of the return springs 22 and 29, respectively. Ru.

次に、運転者が車両を制動すべくブレーキ被ダル３１を
踏込むと、それは基軸３４を中心にして揺動子３５と共
に前方へ揺動する。第１操作子３７１は戻しばね２９の
弾発力により前進を阻止されているので揺動子３５は支
持軸３６を中心に戻しばね２２の弾発力に抗して第２図
反時計方向に揺動し、第２操作子３７２を介し摺動制御
弁２を前進させて排油孔１７を排油室Δ１に連通すると
共に導入孔１８を閉鎖する。これにより・ぐワーフリン
ダ５の減圧室′Ｃ）の圧油が第１連通油孔３０１、第２
油室ｂ２、排出孔１９、通油孔１６および排油孔１７を
通じて排油室Ａに排出きれる。その結果、ノクワーシリ
ンダ５の減圧室−０１と油圧室りに差圧を生じるので、
その作動油圧および第１操作子３７１の押圧力により出
カビストン４が戻しばね２９に抗して前方へ出力作動し
てブレーキマスクシリンダＭ′の作動ピストン６を作動
させ、車両にＨ出動がかけられる。Next, when the driver depresses the brake lever 31 to brake the vehicle, it swings forward together with the rocker 35 about the base shaft 34. Since the first operator 371 is prevented from moving forward by the elastic force of the return spring 29, the oscillator 35 moves counterclockwise in FIG. 2 against the elastic force of the return spring 22 about the support shaft 36. The slide control valve 2 is swung forward through the second operator 372 to communicate the oil drain hole 17 with the oil drain chamber Δ1 and close the introduction hole 18. As a result, the pressure oil in the decompression chamber 'C) of the warflinder 5 is transferred to the first communicating oil hole 301 and the second
The oil can be discharged to the oil drain chamber A through the oil chamber b2, the drain hole 19, the oil passage hole 16, and the oil drain hole 17. As a result, a pressure difference is generated between the decompression chamber-01 and the hydraulic chamber of the knocker cylinder 5.
Due to the working oil pressure and the pressing force of the first operator 371, the output piston 4 is actuated forward against the return spring 29, actuating the actuating piston 6 of the brake mask cylinder M', and applying H-pulling to the vehicle. .

前述のように／Ｆクワ−リンダ５に差圧を生じたときに
は、制御シリンダ３においても第２油室ｂ２が排油室Ａ
に連通する結果箱１、第２油室ｂ１、ｂ２間に差圧を生
じ、その反動油圧および戻しばね２２の弾発力により摺
動制御弁２が後退し、これにより第２操作子３７２を介
して揺動子３５が支持軸３６を中心に第２図時計方向に
揺動するので、それに応じて第１操作子３７１が前進す
る。しだがってブレーキ被ダル３１の踏込みス・トロー
クと第１操作子３７．の、揺動子３５の揺動に伴う前進
量の和に対応してブレーキマヌタシリンダ・」ｆの作動
ピストン６を前進作動させることができ、これによりブ
レーキ被ダル３１の踏込み刀トロークを短縮することが
できる。As mentioned above, when a differential pressure is generated in the /F squirrel cylinder 5, the second oil chamber b2 is also connected to the oil drain chamber A in the control cylinder 3.
A differential pressure is generated between the result box 1 and the second oil chambers b1 and b2, which are in communication with each other, and the reaction oil pressure and the elastic force of the return spring 22 cause the slide control valve 2 to retreat, thereby causing the second operator 372 to move. Since the rocker 35 swings clockwise in FIG. 2 around the support shaft 36, the first operator 371 moves forward accordingly. Therefore, the depression stroke of the brake pedal 31 and the first operation element 37. The actuating piston 6 of the brake manuta cylinder "f" can be operated forward in response to the sum of the amount of advance caused by the rocking of the rocker 35, thereby shortening the treadle stroke of the brake lever 31. can do.

いま、油圧系統、例えば給油路１２に漏洩故障が生じる
と、制御シリンダ３の第１、第２油室ｂ１、ｂ２および
ノクワーシリンダ５の減圧室Ｃ５油圧室り内の油圧は極
度に低下、または大気圧となるので、このときブレーキ
被ダル３１を踏込めば、前述のように揺動子３５が支持
軸３６を中心に第２図反時計方向に揺動し、その後面が
拘束部材４３に当接する。これにより揺動子３５は揺動
を拘束されるのでブレーキペダル３１の踏力により第１
操作子３７．を介して出力ビストン４を機械的に前進作
動することができる。Now, if a leakage failure occurs in the hydraulic system, for example in the oil supply path 12, the oil pressure in the first and second oil chambers b1 and b2 of the control cylinder 3 and the pressure reduction chamber C5 of the knocker cylinder 5 will drop extremely. Or, since the pressure becomes atmospheric pressure, if the brake lever 31 is depressed at this time, the oscillator 35 will oscillate counterclockwise in FIG. comes into contact with. As a result, the oscillator 35 is restrained from swinging, so that the first
Operator 37. The output piston 4 can be mechanically moved forward via the .

第７図は本発明の他の実施例を示し、揺動子３５の下部
に延出部５１を形成し、その延出部５１の前面に突設し
たねじ筒５２に拘束部材４３′としてのボルトを螺合し
、その拘束部材４３′を回すことによりその後端面とブ
レーキ被ダル３１の前端面に形成された当接面５８との
間隔を適宜調節するようにしだものである。この場合拘
束部材４３′は位置調節手段としての機能も有する。５
９は拘束部材４３′のロックナツトである。FIG. 7 shows another embodiment of the present invention, in which an extending portion 51 is formed at the lower part of the oscillator 35, and a threaded cylinder 52 protruding from the front surface of the extending portion 51 is used as a restraining member 43'. By screwing the bolts together and turning the restraining member 43', the distance between the rear end surface and the contact surface 58 formed on the front end surface of the brake shoulder 31 can be adjusted as appropriate. In this case, the restraining member 43' also functions as a position adjusting means. 5
9 is a lock nut of the restraining member 43'.

以上のように本発明によれば、位置調節手段により拘束
部材の位置を適宜調節し得るので油圧系統故障時に揺動
子を的確に拘束し、操作被ダルと出力ビストン間の応答
性を向上させることができる。As described above, according to the present invention, since the position of the restraint member can be adjusted appropriately by the position adjustment means, the rocker can be restrained accurately in the event of a hydraulic system failure, and the responsiveness between the operated lever and the output piston can be improved. be able to.

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

第１乃至第６図は本発明の第１実施例を示すもので、第
１図は平面図、第２図は第１図ｒｒ　−ｒｒ線線断断側
面図第３図は第２図１ｖ矢視図、第４図は第２図１ｖ矢
視図、第５図は第２図Ｖ矢視部の拡大図、第６図は第２
図ＶＴ−ＶＩ線断面図、第７図は第２実施例の部分側面
図である。 ２・・・摺動制御弁　　　３・・・制御シリンダ４・・
出力ヒストン　　５・・・、９ワーフリンダ７・・・油
圧源 ３１・・操作被ダルとしてのブレーキ被ダル３５　・揺
動子 ３７．３７２　・・第１、第２操作子 ４３．４３′・・・拘束部材 ５４・・・位置調節手段としてのボルト特許出願人　　
日信工業株式会社 第５図 第４図 第３図 第７図 ＼　ゝ 〃 ７−−−−〜、 ３７′　　　　　　　よ ゝ、′、 −（ いＸ○ Ｘ日 ゝ１１−１ ＼＼・・１ ３７１　　　鬼 第６図1 to 6 show a first embodiment of the present invention, FIG. 1 is a plan view, FIG. 2 is a cross-sectional side view taken along line rr-rr in FIG. Fig. 4 is a view from the arrow 1V in Fig. 2, Fig. 5 is an enlarged view of the section seen from the V in Fig. 2, and Fig. 6 is a view from the arrow 2 in Fig. 2.
FIG. 7 is a sectional view taken along the line VT-VI, and FIG. 7 is a partial side view of the second embodiment. 2...Sliding control valve 3...Control cylinder 4...
Output histones 5..., 9 Wharf cylinder 7...Hydraulic power source 31...Brake subject 35 as operation subject ・Oscillator 37.372...First and second operating elements 43, 43'... Restraint member 54... Bolt as position adjustment means Patent applicant
Nissin Kogyo Co., Ltd. Figure 5 Figure 4 Figure 3 Figure 7 371 Oni Figure 6

Claims (1)

【特許請求の範囲】[Claims] 出力ビストンを摺什した・ぐワーシリンダと；摺動制御
弁を摺合し、該摺動制御弁を介して油圧源と・ぐツーシ
リンダ間の連通を制御すべく前記パワーシリンダに並列
に配設された制御シリンダと；前記出力ビストンおよび
前記摺動制御弁を操作する操作ペダルと；前記出力ビス
トンの後端に前端を連接された第１操作子と；前記摺動
制御弁の後端に前端を連接された第２操作子と；前記操
作ペダルに枢着され、作動時一方向に揺動じて前記第２
操作子を介し前記摺動制御弁を前進作動させると共に前
記出力ビストンの前進作動に伴い他方向に揺動して前記
第１操作子を介し該出力ビストンを押動する揺動子と；
油圧系統故障時に前記揺動子の、摺動制御弁作動方向へ
の揺動を拘束する拘束部材と；該拘束部材の位置調節手
段と】を備えた油圧式倍力装置。A power cylinder on which an output piston is slid; and a sliding control valve arranged in parallel with the power cylinder to control communication between the hydraulic power source and the cylinder through the sliding control valve. a control cylinder that operates the output piston and the sliding control valve; a first operator whose front end is connected to the rear end of the output piston; and a front end connected to the rear end of the sliding control valve. a second operating element connected to the operating pedal; which is pivotally connected to the operating pedal and swings in one direction when activated;
an oscillator that operates the sliding control valve forward via the operator and swings in the other direction as the output piston moves forward to push the output piston via the first operator;
A hydraulic booster comprising: a restraining member that restrains the rocking member from swinging in the sliding control valve operating direction when a hydraulic system malfunctions; and means for adjusting the position of the restraining member.