JP2001063549A - Negative pressure booster - Google Patents
Negative pressure boosterInfo
- Publication number
- JP2001063549A JP2001063549A JP23888199A JP23888199A JP2001063549A JP 2001063549 A JP2001063549 A JP 2001063549A JP 23888199 A JP23888199 A JP 23888199A JP 23888199 A JP23888199 A JP 23888199A JP 2001063549 A JP2001063549 A JP 2001063549A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- piston
- negative pressure
- booster
- input
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Braking Systems And Boosters (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は，自動車のブレーキ
マスタシリンダの倍力作動のために用いられる負圧ブー
スタに関し，特に，ブースタシェルに，その内部を負圧
源に連なる前側の負圧室と後側の作動室とに区画するブ
ースタピストンを収容し，このブースタピストンに，前
記ブースタシェルの後壁に摺動自在に支承される弁筒を
連設し，この弁筒内に，前後動可能の入力杆と，この入
力杆の前後動に応じて作動室を負圧室と大気とに連通切
換えする制御弁とを配設し，前記弁筒及び入力杆と，前
記ブースタシェルに摺動可能に支持される出力杆との間
に，入力杆に対する入力と，作動室及びを負圧室間の気
圧差による前記ブースタピストンの推力との合力を該出
力杆に伝達する反力機構を介裝したものゝ改良に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a negative pressure booster used for boosting operation of a brake master cylinder of an automobile, and more particularly, to a booster shell having a front negative pressure chamber connected to a negative pressure source. A booster piston partitioned into a rear working chamber is accommodated, and a valve cylinder slidably supported on the rear wall of the booster shell is connected to the booster piston, and the valve cylinder can be moved back and forth in the valve cylinder. An input rod and a control valve for switching the working chamber between a negative pressure chamber and the atmosphere in accordance with the forward and backward movement of the input rod are disposed, and are slidable on the valve cylinder, the input rod, and the booster shell. A reaction force mechanism for transmitting a resultant force of the input to the input rod and the thrust of the booster piston due to the pressure difference between the working chamber and the negative pressure chamber to the output rod. What did you do?
【０００２】[0002]
【従来の技術】従来，かゝる負圧ブースタにおいて，例
えば特開平９−２２４６号公報に開示されているよう
に，緊急ブレーキ時には，ソレノイド装置の励磁により
制御弁の作動量を増加させ，作動室に大量の大気を素早
く導入して出力杆に倍力限界の高出力を発揮させるよう
にしたものが知られている。2. Description of the Related Art Conventionally, in such a negative pressure booster, as disclosed in, for example, Japanese Patent Application Laid-Open No. 9-2246, the amount of operation of a control valve is increased by exciting a solenoid device during emergency braking. 2. Description of the Related Art There has been known an apparatus in which a large amount of air is quickly introduced into a room so that an output rod exhibits a high output of a boosting limit.
【０００３】[0003]
【発明が解決しようとする課題】上記公報に開示された
負圧ブースタでは，高価なソレノイド装置のみならず，
緊急ブレーキ状態を検知するセンサを必要とするので，
構成が複雑の上，コストが高くつく欠点がある。In the negative pressure booster disclosed in the above publication, not only an expensive solenoid device,
Since a sensor that detects the emergency braking condition is required,
There are disadvantages in that the configuration is complicated and the cost is high.
【０００４】本発明は，かゝる事情に鑑みてなされたも
ので，簡単で安価な構造を付加するだけで，緊急ブレー
キ時には，作動室に大量の大気を素早く導入して出力杆
に倍力限界の高出力を発揮させる得るようにした，前記
負圧ブースタを提供することを目的とする。SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and only by adding a simple and inexpensive structure, during an emergency brake, a large amount of air is quickly introduced into the working chamber to boost the output rod. It is an object of the present invention to provide the above-mentioned negative pressure booster capable of exhibiting a maximum high output.
【０００５】[0005]
【課題を解決するための手段】上記目的を達成するため
に，本発明は，ブースタシェルに，その内部を負圧源に
連なる前側の負圧室と後側の作動室とに区画するブース
タピストンを収容し，このブースタピストンに，前記ブ
ースタシェルの後壁に摺動自在に支承される弁筒を連設
し，この弁筒内に，前後動可能の入力杆と，この入力杆
の前後動に応じて作動室を負圧室と大気とに連通切換え
する制御弁とを配設し，前記弁筒及び入力杆と，前記ブ
ースタシェルに摺動可能に支持される出力杆との間に，
入力杆に対する入力と，作動室及びを負圧室間の気圧差
による前記ブースタピストンの推力との合力を該出力杆
に伝達する反力機構を介裝した負圧ブースタにおいて，
前記入力杆に，前記反力機構に連なる入力プランジャを
連結し，この入力プランジャの外周に弁ピストンを，こ
れが入力プランジャに対して軸方向に沿う後退位置及び
前進位置間を移動し得るように嵌合すると共に，この弁
ピストンを戻しばねにより前記後退位置側へ付勢し，こ
の弁ピストンを前記制御弁に，この弁ピストンが前記前
進位置まで前進したとき前記制御弁を前記作動室と大気
との最大連通状態に切換えるように連結し，前記弁筒及
び弁ピストンに，これらの軸方向相対移動に応じて互い
に半径方向に重なりながら軸方向に相対移動する第１永
久磁石及び第２永久磁石をそれぞれ付設し，これら第１
及び第２永久磁石は，前記弁ピストンの入力プランジャ
に対する後退位置からの前進が所定距離に満たないとき
には，互いに同極を半径方向及び軸方向に対向させて前
記弁ピストン（３３）を前記後退位置側へ付勢する反発
力を発生し，前記弁ピストンの入力プランジャに対する
後退位置からの前進が所定距離を超えると，互いに異極
を半径方向及び軸方向に対向させて前記弁ピストンを前
記前進位置まで移動させる吸引力を発生するように構成
されることを第１の特徴とする。SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a booster piston having a booster shell, the interior of which is divided into a front negative pressure chamber connected to a negative pressure source and a rear working chamber. And a valve cylinder slidably supported on the rear wall of the booster shell is connected to the booster piston, and an input rod movable forward and backward and a longitudinal movement of the input rod are provided in the valve cylinder. And a control valve for switching the working chamber between the negative pressure chamber and the atmosphere in accordance with the control valve, between the valve cylinder and the input rod and the output rod slidably supported by the booster shell.
In a negative pressure booster provided with a reaction force mechanism for transmitting to the output rod a resultant force of the input to the input rod and the thrust of the booster piston due to the pressure difference between the working chamber and the negative pressure chamber,
An input plunger connected to the reaction force mechanism is connected to the input rod, and a valve piston is fitted on the outer periphery of the input plunger so that the valve piston can move between a retracted position and an advanced position along the axial direction with respect to the input plunger. At the same time, the valve piston is urged toward the retracted position by a return spring, and the valve piston is moved to the control valve, and when the valve piston advances to the forward position, the control valve is moved to the working chamber and the atmosphere. The first permanent magnet and the second permanent magnet which are connected so as to be switched to the maximum communication state, and which move relative to each other in the axial direction while overlapping each other in the radial direction according to their relative movement in the axial direction. The first of these
And a second permanent magnet for moving the valve piston (33) to the retracted position by causing the same polarity to oppose each other in the radial and axial directions when the advancement of the valve piston from the retracted position with respect to the input plunger is less than a predetermined distance. When a repulsive force is generated that urges the valve piston toward the input plunger and the advancement of the valve piston from the retracted position exceeds a predetermined distance, the opposite ends of the valve piston are radially and axially opposed to each other to move the valve piston to the advanced position. The first feature is that it is configured to generate a suction force for moving the suction force.
【０００６】この第１の特徴によれば，弁ピストンの弁
筒に対する前進が所定距離未満となる通常ブレーキ時に
は，第１及び第２永久磁石は反発状態を維持し，それら
の反発力が弁ピストンを後退方向へ付勢し続けるので，
弁ピストンを後退位置側へ付勢する戻しばねのセット荷
重を小さく設定することが可能となる。したがって，入
力杆を急速に前進させる緊急ブレーキ時には，弁筒の作
動遅れに伴い弁筒に対して弁ピストンが入力杆と共に前
進して所定距離を超えることにより，第１及び第２永久
磁石が反発状態から吸引状態に切換わるや否や，第１及
び第２永久磁石相互の吸引力により，戻しばねの抵抗を
あまり受けずに，弁ピストンを素早く前進させ，制御弁
を作動室と大気との最大連通状態に切換える。その結
果，作動室に大量の大気が一挙に導入され，作動室及び
負圧室間の気圧差が最大となってブースタピストンの推
力，即ち出力杆の出力を倍力限界点まで即座に増大させ
ることができる。このような簡単な構成の採用により，
緊急ブレーキに対応した強力なブレーキ力を発生するこ
とができる。According to this first feature, during normal braking in which the advance of the valve piston with respect to the valve cylinder is less than a predetermined distance, the first and second permanent magnets maintain a repulsive state, and their repulsive force is reduced by the valve piston. Continue to bias in the backward direction,
The set load of the return spring that biases the valve piston toward the retracted position can be set small. Therefore, at the time of emergency braking for rapidly moving the input rod, the first and second permanent magnets are repelled by the valve piston moving forward with the input rod and exceeding a predetermined distance with respect to the valve cylinder due to the operation delay of the valve cylinder. As soon as the state is switched from the suction state to the suction state, the valve piston is quickly advanced without much resistance of the return spring due to the attraction force of the first and second permanent magnets, and the control valve is moved to the maximum between the working chamber and the atmosphere. Switch to the communication state. As a result, a large amount of air is introduced into the working chamber at once, and the pressure difference between the working chamber and the negative pressure chamber is maximized, thereby immediately increasing the thrust of the booster piston, that is, the output of the output rod, to the boosting limit point. be able to. By adopting such a simple configuration,
A strong braking force corresponding to emergency braking can be generated.
【０００７】また本発明は，上記特徴に加えて，前記入
力プランジャに前記入力杆の球状前端部を首振り可能に
かしめ結合すると共に，そのかしめ結合部を前記弁ピス
トンで覆い，この弁ピストンの後端に形成した大気導入
弁座と，この大気導入弁座を環状通路を挟んで囲繞する
ように前記弁筒に形成した負圧導入弁座と，前記弁筒に
前後動可能に取付けられて前記負圧導入弁座及び大気導
入弁座に前端の弁部を対向させる弁体と，この弁体の弁
部を前記両弁座との着座方向へ付勢する弁ばねとから前
記制御弁を構成すると共に，前記弁体の内側を大気に連
通し，前記負圧導入弁座を前記負圧室に連通する第１ポ
ートと，前記環状通路を前記作動室に連通する第２ポー
トとを前記弁筒に設け，前記弁ピストンの，前記環状通
路に臨む外周面を後端に向かって小径となるテーパ状に
形成したことを第２の特徴とする。Further, in addition to the above-mentioned features, the present invention further comprises the steps of caulking and connecting the spherical front end of the input rod to the input plunger so as to swing, and covering the caulked connection with the valve piston. An air introduction valve seat formed at a rear end, a negative pressure introduction valve seat formed on the valve cylinder so as to surround the air introduction valve seat with an annular passage interposed therebetween, and attached to the valve cylinder so as to be movable back and forth. The control valve is formed by a valve body having a front end valve portion opposed to the negative pressure introduction valve seat and the air introduction valve seat, and a valve spring for urging the valve portion of the valve body in the seating direction of the two valve seats. A first port communicating the inside of the valve body to the atmosphere and communicating the negative pressure introducing valve seat to the negative pressure chamber, and a second port communicating the annular passage to the working chamber. The outer peripheral surface of the valve piston facing the annular passage is provided on the valve cylinder. That it has tapered to a smaller diameter toward the end as a second feature.
【０００８】この第２の特徴によれば，弁ピストンの外
周面を，大気導入弁座に向かって小径となるテーパ状に
形成したので，大気導入弁座の全開時には，大量の大気
を弁ピストンのテーパ状外周面により作動室へスムーズ
に誘導して，ブースタピストンの応答性を向上に寄与す
ることができ，しかも弁ピストンが入力杆及び入力プラ
ンジャのかしめ結合部を覆って，該かしめ部による風切
り音の発生を抑えることができる。According to the second feature, since the outer peripheral surface of the valve piston is formed in a tapered shape having a smaller diameter toward the air introduction valve seat, when the air introduction valve seat is fully opened, a large amount of air is supplied to the valve piston. Can smoothly guide into the working chamber by the tapered outer peripheral surface, which can contribute to the improvement of the responsiveness of the booster piston. In addition, the valve piston covers the caulked joint of the input rod and the input plunger, and the caulked portion The generation of wind noise can be suppressed.
【０００９】[0009]
【実施例の形態】本発明の実施の形態を，添付図面に示
す本発明の実施例に基づいて説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.
【００１０】図１は本発明の実施例に係るタンデム型負
圧ブースタの縦断面図，図２は図１の２部拡大図，図３
は上記負圧ブースタの作用説明図，図４は上記負圧ブー
スタの倍力特性を示す線図である。FIG. 1 is a longitudinal sectional view of a tandem type negative pressure booster according to an embodiment of the present invention, FIG. 2 is an enlarged view of a part of FIG. 1, and FIG.
FIG. 4 is an explanatory diagram of the operation of the negative pressure booster, and FIG. 4 is a diagram showing boosting characteristics of the negative pressure booster.
【００１１】図１及び図２において，負圧ブースタＢの
ブースタシェル１は，対向端を相互に結合する前後一対
のシェル半体１ａ，１ｂと，両シェル半体１ａ，１ｂ間
に挟止されてブースタシェル１内部を前部シェル室２と
後部シェル室３とに仕切る隔壁板１ｃとから構成され，
その後部シェル半体１ｂが自動車の車室前壁Ｆにボルト
８により固定して支持され，前部シェル半体１ａには，
該ブースタＢにより作動されるブレーキマスタシリンダ
ＭのシリンダボディＭａがボルト９により固着される。In FIG. 1 and FIG. 2, a booster shell 1 of a negative pressure booster B is sandwiched between a pair of front and rear shell halves 1a and 1b connecting opposite ends to each other, and between both shell halves 1a and 1b. And a partition plate 1c that partitions the inside of the booster shell 1 into a front shell chamber 2 and a rear shell chamber 3.
The rear shell half 1b is fixedly supported by bolts 8 to the vehicle interior front wall F, and the front shell half 1a is
The cylinder body Ma of the brake master cylinder M operated by the booster B is fixed by bolts 9.
【００１２】前部シェル室２は，それに前後往復動可能
に収容される前部ブースタピストン４と，その後面に重
ねて結着されると共に前部シェル半体１ａと隔壁板１ｃ
間に挟着される前部ダイヤフラム５とにより，前側の前
部負圧室２ａと後側の前部作動室２ｂとに区画される。
そして，前部負圧室２ａは，負圧導入管１４を介して負
圧源Ｖ（例えば内燃機関の吸気マニホールド内部）と接
続される。The front shell chamber 2 has a front booster piston 4 accommodated therein so as to be able to reciprocate back and forth, and is bonded to and overlapped with a rear surface thereof, and has a front shell half 1a and a partition plate 1c.
The front diaphragm 5 sandwiched therebetween partitions into a front front negative pressure chamber 2a on the front side and a rear front working chamber 2b on the rear side.
The front negative pressure chamber 2a is connected to a negative pressure source V (for example, the inside of an intake manifold of an internal combustion engine) via a negative pressure introducing pipe 14.
【００１３】また後部シェル室３は，それに前後往復動
可能に収容される後部ブースタピストン６と，その後面
に重ねて結着され，且つ隔壁板１ｃと共に両シェル半体
１ａ，１ｂ間に固着される後部ダイヤフラム７とによ
り，前側の後部負圧室３ａと後側の後部作動室３ｂとに
区画される。The rear shell chamber 3 is connected to a rear booster piston 6 housed in the rear shell chamber 3 so as to be able to reciprocate back and forth, and is fixed together with the partition plate 1c between the two shell halves 1a and 1b. The rear diaphragm 7 defines a front rear negative pressure chamber 3a on the front side and a rear operating chamber 3b on the rear side.
【００１４】前，後部ブースタピストン４，６はそれぞ
れ鋼板により環状に成形されており，これらは中心部に
固着される合成樹脂製の弁筒１０を介して一体に連結さ
れる。弁筒１０は，隔壁板１ｃにシール部材１１を介し
て，また後部シェル半体１ｂの中心部に形成された後方
延長筒１２にシール部材１３を介して摺動自在に支承さ
れる。両ブースタピストン４，６の後退限は，後部ダイ
ヤフラム７の後面に多数***させた突起７ａがブースタ
シェル１の後壁に当接することにより規定される。The front and rear booster pistons 4, 6 are each formed in a ring shape from a steel plate, and are integrally connected via a synthetic resin valve cylinder 10 fixed to the center. The valve cylinder 10 is slidably supported by a partition plate 1c via a seal member 11 and a rear extension cylinder 12 formed at the center of the rear shell half 1b via a seal member 13. The retreat limit of both booster pistons 4, 6 is defined by a large number of raised projections 7 a abutting the rear wall of the booster shell 1 on the rear surface of the rear diaphragm 7.
【００１５】弁筒１０の前端部は大径ピストン１５に形
成され，この大径ピストン１５の中心部に形成されて，
その前面に開口する有底のシリンダ孔１６に，大径ピス
トン１５より一定の割合で縮径した小径ピストン１７が
摺動自在に嵌装され，この小径ピストン１７の後端面
に，弁筒１０前部の中心部を摺動自在に貫通する入力プ
ランジャ１８の前端が当接する。The front end of the valve cylinder 10 is formed on a large-diameter piston 15 and is formed at the center of the large-diameter piston 15.
A small-diameter piston 17 reduced in diameter at a fixed rate from the large-diameter piston 15 is slidably fitted in a bottomed cylinder hole 16 opened in the front surface thereof. The front end of the input plunger 18 that slidably penetrates the center of the section abuts.
【００１６】入力プランジャ１８の後端部に形成された
連結筒部１９には，弁筒１０の後端から挿入される入力
杆２０の前端の球状部２０ａが嵌合されると共に，その
抜け止めのために連結筒部１９の一部１９ａが内方へか
しめる。こうして入力杆２０は入力プランジャ１８に首
振り可能に連結される。A spherical portion 20a at the front end of an input rod 20 inserted from the rear end of the valve cylinder 10 is fitted into a connecting tube portion 19 formed at the rear end of the input plunger 18 and is prevented from coming off. Due to this, a part 19a of the connecting tubular portion 19 is crimped inward. Thus, the input rod 20 is swingably connected to the input plunger 18.
【００１７】大径ピストン１５の外周にはカップ体２１
が摺動自在に嵌合され，このカップ体２１には大径及び
小径ピストン１５，１７に対向する偏平な弾性ピストン
２２が充填される。A cup 21 is provided on the outer periphery of the large-diameter piston 15.
The cup body 21 is filled with a flat elastic piston 22 opposed to the large-diameter and small-diameter pistons 15 and 17.
【００１８】大径ピストン１５及び弾性ピストン２２の
対向端面の一方（図示例では大径ピストン１５の前端に
は環状段部２３が凹設される。One of the opposed end surfaces of the large-diameter piston 15 and the elastic piston 22 (in the illustrated example, an annular step 23 is formed at the front end of the large-diameter piston 15).
【００１９】以上において，大径ピストン１５，小径ピ
ストン１７，弾性ピストン２２及びカップ体２１は，入
力杆２０に対する入力とブースタピストン４，６の推力
との合力を出力杆２５に伝達する反力機構２４を構成す
る。In the above, the large-diameter piston 15, the small-diameter piston 17, the elastic piston 22, and the cup 21 are a reaction force mechanism for transmitting the combined force of the input to the input rod 20 and the thrust of the booster pistons 4, 6 to the output rod 25. 24.
【００２０】カップ体２１の前面には出力杆２５が突設
され，この出力杆２５は前記ブレーキマスタシリンダＭ
のピストンＭｂに連接される。またカップ体２１及び弁
筒１０の前端面に当接するリテーナ２６が配設され，こ
のリテーナ２６とブースタシェル１の前壁との間に弁筒
戻しばね２７が縮設される。An output rod 25 protrudes from the front surface of the cup body 21. The output rod 25 is connected to the brake master cylinder M.
Of the piston Mb. In addition, a retainer 26 is provided in contact with the cup body 21 and the front end face of the valve cylinder 10, and a valve cylinder return spring 27 is contracted between the retainer 26 and the front wall of the booster shell 1.
【００２１】弁筒１０には，前後部の負圧室２ａ，３ａ
間を連通する第１連通路２８ａと，前後部の作動室２
ｂ，３ｂ間を連通する第２連通路２８ｂと，第１連通路
２８ａに連なって弁筒１０内周面に開口する第１ポート
２９ａと，第２連通路２８ｂに連なると共に，第１ポー
ト２９ａより前方で弁筒１０内周面に開口する第２ポー
ト２９ｂとが形成される。それら第１及び第２ポート２
９ａ，２９ｂの前後方向中間の弁筒１０内周面に環状の
負圧導入弁座３０とが形成される。また弁筒１０の前部
内周面に円筒状の弁ピストン３３が摺動自在に嵌装さ
れ，この弁ピストン３３の後端には，第２ポート２９ｂ
に連なる環状通路３２を挟んで負圧導入弁座３０に囲繞
される環状の大気導入弁座３１が形成されており，負圧
導入弁座３０及び大気導入弁座３１に対向する共通一個
の弁体３４が弁筒１０内に配設される。この弁体３４
は，負圧導入弁座３０及び大気導入弁座３１に着座可能
に対向する環状の弁部３４ａを前端に，環状の取付けビ
ード部３４ｂを後端に，その両部分３４ａ，３４ｂを軸
方向相対変位可能に連結するダイヤフラム部３４ｃを中
間部にそれぞれ形成してなるもので，取付けビード部３
４ｂは，弁筒１０の後部内周面に嵌着される円筒状の弁
ホルダ３５の前端部により，弁筒１０内周面に取付けら
れる。そして，その弁部３４ａを両弁座３０，３１との
着座方向へ付勢する弁ばね３６が弁部３４ａと入力杆２
０との間に縮設される。The valve cylinder 10 has front and rear negative pressure chambers 2a and 3a.
A first communication passage 28a for communicating between
b, 3b, a first port 29a communicating with the first communication passage 28a and opening on the inner peripheral surface of the valve cylinder 10, and a first port 29a communicating with the second communication passage 28b. A second port 29b that opens to the inner peripheral surface of the valve cylinder 10 further forward is formed. Their first and second ports 2
An annular negative pressure introduction valve seat 30 is formed on the inner peripheral surface of the valve cylinder 10 in the middle in the front-rear direction of 9a and 29b. A cylindrical valve piston 33 is slidably fitted on the inner peripheral surface of the front part of the valve cylinder 10, and a second port 29b is provided at the rear end of the valve piston 33.
An annular air introduction valve seat 31 is formed which is surrounded by a negative pressure introduction valve seat 30 with an annular passage 32 connected thereto, and one common valve opposed to the negative pressure introduction valve seat 30 and the atmosphere introduction valve seat 31. A body 34 is disposed in the valve sleeve 10. This valve body 34
The annular valve portion 34a facing the negative pressure introducing valve seat 30 and the atmosphere introducing valve seat 31 so as to be seated is at the front end, the annular mounting bead portion 34b is at the rear end, and the two portions 34a, 34b are axially opposed to each other. Displaceably connected diaphragm portions 34c are formed in the middle portions, respectively.
4b is attached to the inner peripheral surface of the valve cylinder 10 by the front end of a cylindrical valve holder 35 fitted to the inner peripheral surface of the rear part of the valve cylinder 10. A valve spring 36 for urging the valve portion 34a in the seating direction between the valve seats 30 and 31 is provided between the valve portion 34a and the input rod 2.
It is contracted between 0.
【００２２】以上において，上記両弁座３０，３１，弁
体３４及び弁ばね３６は制御弁３８を構成する。In the above, the two valve seats 30, 31, the valve element 34 and the valve spring 36 constitute a control valve 38.
【００２３】また上記環状通路３２を構成する弁ピスト
ン３３の外周面３２ａは，大気導入弁座３１に向かって
小径となると共に，第２ポート２９ｂの内周面に連続す
るテーパ状に形成される。The outer peripheral surface 32a of the valve piston 33 constituting the annular passage 32 has a smaller diameter toward the air introduction valve seat 31, and is formed in a tapered shape continuous with the inner peripheral surface of the second port 29b. .
【００２４】後方延長筒１２の後端には，中心部に大気
導入口３９が開口する内向きフランジ１２ａが一体に形
成されており，このフランジ１２ａの内側面に当接して
入力杆２０の後退限を規定するストッパ板４０が入力杆
２０に前後方向調節可能に固着され，その後退限に向か
って入力杆２０は，弁ホルダ３５に支持される入力戻し
ばね４１により付勢される。At the rear end of the rear extension cylinder 12, an inward flange 12a having an air inlet 39 opened at the center is integrally formed. The input rod 20 is retracted by contacting the inner surface of the flange 12a. A stopper plate 40 defining a limit is fixed to the input rod 20 so as to be adjustable in the front-rear direction, and the input rod 20 is biased toward the retreat limit by an input return spring 41 supported by the valve holder 35.
【００２５】また弁筒１０の後端部内周には，エアフィ
ルタ４２が装着され，それを通して大気導入弁座３１の
内周は大気導入口３９と常時連通している。上記エアフ
ィルタ４２は，入力杆２０の弁筒１０に対する前後動を
妨げないように柔軟性を有する。An air filter 42 is mounted on the inner periphery of the rear end of the valve cylinder 10, and the inner periphery of the air introduction valve seat 31 is always in communication with the air introduction port 39 through the air filter 42. The air filter 42 has flexibility so as not to prevent the input rod 20 from moving back and forth with respect to the valve cylinder 10.
【００２６】入力プランジャ１８には，円筒状の弁ピス
トン３３の内周面にシール部材４３を介して摺動自在に
嵌合する外向きフランジ１８ａが，また弁ピストン３３
には，入力プランジャ１８の連結筒部１９の外周面に摺
動自在に嵌合する内向きフランジ３３ａがそれぞれ一体
に形成されており，これら両フランジ１８ａ，３３ａ間
に，これらを前後に引き離す方向へ付勢する戻しばね４
４が縮設されると共に，内向きフランジ３３ａの後端面
を受けるストッパ環４５が連結筒部１９に係止される。
また弁ピストン３３の内周面には，外向きフランジ１８
ａの後端面に所定の間隙ｇを存して対向する当接段部４
６が形成される。弁ピストン３３は，この間隙ｇの範囲
内で，内向きフランジ３３ａをストッパ環４５に当接さ
せる後退位置Ｒ（図２参照）と，当接段部４６を外向き
フランジ１８ａに当接させる前進位置Ｆ（図３参照）と
の間を移動することができる。The input plunger 18 has an outward flange 18a slidably fitted on the inner peripheral surface of a cylindrical valve piston 33 via a seal member 43.
Has an inward flange 33a which is slidably fitted to the outer peripheral surface of the connecting cylindrical portion 19 of the input plunger 18, and is integrally formed between the two flanges 18a, 33a. Return spring 4 for urging
4, the stopper ring 45 receiving the rear end face of the inward flange 33a is locked to the connecting tubular portion 19.
The inner peripheral surface of the valve piston 33 has an outward flange 18.
a abutting step 4 which is opposed to the rear end face with a predetermined gap g
6 are formed. Within the range of the gap g, the valve piston 33 is moved backward to contact the inward flange 33a against the stopper ring 45 (see FIG. 2), and is moved forward to contact the contact step 46 to the outward flange 18a. It can move between the position F (see FIG. 3).
【００２７】尚，戻しばね４４のセット荷重は，前記弁
ばね３６のそれより大きく設定される。したがって，入
力杆２０による入力プランジャ１８の後退時には，戻し
ばね４４を圧縮させることなく弁ピストン３３により弁
体３４の弁部３４ａを弁ばね３６のセット荷重に抗して
後方へ変位させることができる。The set load of the return spring 44 is set larger than that of the valve spring 36. Therefore, when the input plunger 18 is retracted by the input rod 20, the valve portion 34a of the valve body 34 can be displaced rearward by the valve piston 33 against the set load of the valve spring 36 without compressing the return spring 44. .
【００２８】弁ピストン３３において，外向きフランジ
１８ａが嵌合する内周面の内径Ｄ１と，弁体３４が着座
する大気導入弁座３１の有効径Ｄ２とは，互いに等しく
設定される。こうすると，弁体３４が大気導入弁座３１
に着座しているとき，負圧室２ａ，３ａの負圧が第１ポ
ート２９ａから弁ピストン３３の前後に作用した場合で
も，弁ピストン３３の前端部及び後端部に働く負圧によ
る推力を互いに相殺させることができる。In the valve piston 33, the inner diameter D1 of the inner peripheral surface on which the outward flange 18a is fitted and the effective diameter D2 of the air introduction valve seat 31 on which the valve body 34 is seated are set to be equal to each other. In this case, the valve body 34 is connected to the air introduction valve seat 31.
When the seat is seated, even if the negative pressure in the negative pressure chambers 2a, 3a acts on the front and rear of the valve piston 33 from the first port 29a, the thrust due to the negative pressure acting on the front end and the rear end of the valve piston 33 can be reduced. Can offset each other.
【００２９】弁筒１０には，外向きフランジ１８ａの前
方で入力プランジャ１８を囲繞する円筒部５０が形成さ
れており，この円筒部５０の外周に環状の第１永久磁石
５１が係止環５３により固着され，この第１永久磁石５
１に半径方向で重なりながら軸方向に相対移動し得る環
状の第２永久磁石５２が弁ピストン３３の前端に接着等
により固着される。これら第１及び第２永久磁石５１，
５２は，軸方向両端に両極Ｎ，Ｓを有するが，第１及び
第２永久磁石５１，５２のＮ，Ｓ極は，互いに向きが逆
になっている。即ち，図示例では，第１永久磁石５１で
は前，後端にＳ，Ｎ極が配され，第２永久磁石５２では
前，後端にＮ，Ｓ極が配される。しかも，第１及び第２
永久磁石５１，５２は，弁ピストン３３の入力プランジ
ャ１８に対する後退位置Ｒからの前進が所定距離ｓに満
たないときには，互いに同極即ちＮ，Ｎ極を半径方向及
び軸方向に対向させて弁ピストン３３を後退位置Ｒ側へ
付勢する反発力を発生し，弁ピストン３３の入力プラン
ジャ１８に対する後退位置Ｒからの前進が所定距離ｓを
超えると，互いに異極即ちＳ，Ｎ極を半径方向及び軸方
向に対向させて前記弁ピストン３３を前進位置Ｆまで移
動させる吸引力を発生するように配置される。前記入力
戻しばね４１のセット荷重は，両永久磁石５１，５２が
吸引状態になったとき発生する吸引力より大きく設定さ
れる。A cylindrical portion 50 surrounding the input plunger 18 is formed in the valve cylinder 10 in front of the outward flange 18a, and an annular first permanent magnet 51 is provided on the outer periphery of the cylindrical portion 50 with a locking ring 53. The first permanent magnet 5
An annular second permanent magnet 52 that can move relatively in the axial direction while overlapping with the radial direction 1 is fixed to the front end of the valve piston 33 by bonding or the like. These first and second permanent magnets 51,
52 has both poles N and S at both ends in the axial direction, but the N and S poles of the first and second permanent magnets 51 and 52 have opposite directions. That is, in the illustrated example, the first permanent magnet 51 has S and N poles at the front and rear ends, and the second permanent magnet 52 has N and S poles at the front and rear ends. Moreover, the first and second
When the forward movement of the valve piston 33 from the retreat position R with respect to the input plunger 18 is less than a predetermined distance s, the permanent magnets 51 and 52 cause the valve piston 33 to have the same pole, that is, the N and N poles in the radial and axial directions to face each other. When a repulsive force for urging the valve piston 33 toward the retreat position R is generated, and the advance of the valve piston 33 from the retreat position R with respect to the input plunger 18 exceeds a predetermined distance s, the opposite poles, i. It is arranged so as to generate a suction force for moving the valve piston 33 to the forward position F in the axial direction. The set load of the input return spring 41 is set to be larger than the attraction force generated when both the permanent magnets 51 and 52 are in the attraction state.
【００３０】次にこの実施例の作用について説明する。 ［負圧ブースタの休止］負圧ブースタＢの休止状態で
は，図１に示すように，入力杆２０は後退限に位置し，
制御弁３８は，弁体３４を大気導入弁座３１及び負圧導
入弁座３０に着座させて前，後部両作動室２ｂ，３ｂを
両負圧室２ａ，３ａ及び大気導入口３９のいずれとも不
通にした中立状態にあり，このような制御弁３８によ
り，両負圧室２ａ，３ａには，負圧導入管１４を通して
供給される負圧源の負圧が蓄えられ，両作動室２ｂ，３
ｂには，大気により適当に希釈された負圧が保持され
る。こうして前，後部ブースタピストン４，６には，前
部の負圧室２ａと作動室２ｂ，後部の負圧室３ａと作動
室３ｂの各間に生じる僅かな気圧差により小さな前進力
が与えられるが，これらの前進力と弁筒戻しばね２７の
力とが釣合って，両ブースタピストン４，６は後退限か
ら僅かに前進したところで停止している。 ［通常ブレーキ］車両を制動すべくブレーキペダルＰを
通常の速度で踏込み，入力杆２０，入力プランジャ１８
及び弁ピストン３３を介して大気導入弁座３１を前進さ
せれば，当初，両ブースタピストン４，６は不動である
から，大気導入弁座３１が弁体３４から直ちに離れて，
第２ポート２９ｂを環状通路３２を介して大気導入口３
９に連通させる。その結果，大気導入口３９から弁筒１
０内に流入した大気は大気導入弁座３１を通過し，第２
ポート２９ｂを経て両作動室２ｂ，３ｂに素早く導入さ
れ，該室２ｂ，３ｂを両負圧室２ａ，３ａより高圧にす
るので，それらの気圧差に基づく大きな前方推力を得て
両ブースタピストン４，６は，弁筒１０及び大径ピスト
ン１５を伴いながら弁筒戻しばね２７の力に抗して入力
杆２０の動きに追従するように前進する。この両ブース
タピストン４，６の前進推力は，大径ピストン１５から
弾性ピストン２２に伝達して，カップ体２１，即ち出力
杆２５を前方へ押動するので，ブレーキマスタシリンダ
ＭをブレーキペダルＰの踏込みに遅れなく作動させ，車
両に制動かけることができる。Next, the operation of this embodiment will be described. [Suspension of Negative Pressure Booster] In the rest state of the negative pressure booster B, as shown in FIG. 1, the input rod 20 is located at the retreat limit.
The control valve 38 allows the front and rear working chambers 2b, 3b to be connected to both the negative pressure chambers 2a, 3a and the air introduction port 39 by seating the valve body 34 on the atmosphere introduction valve seat 31 and the negative pressure introduction valve seat 30. In the neutral state in which the operation is interrupted, the negative pressure of the negative pressure source supplied through the negative pressure introducing pipe 14 is stored in the two negative pressure chambers 2a and 3a by the control valve 38, and the two operating chambers 2b and 3
At b, a negative pressure appropriately diluted with the atmosphere is maintained. Thus, a small forward force is applied to the front and rear booster pistons 4 and 6 due to a slight pressure difference between the front negative pressure chamber 2a and the working chamber 2b and between the rear negative pressure chamber 3a and the working chamber 3b. However, these forward forces are balanced with the force of the valve-cylinder return spring 27, and the booster pistons 4, 6 are stopped when they slightly advance from the retreat limit. [Normal brake] The brake pedal P is depressed at a normal speed to brake the vehicle, and the input rod 20 and the input plunger 18 are depressed.
If the air introduction valve seat 31 is moved forward via the valve piston 33 and the booster pistons 4 and 6 are initially immobile, the air introduction valve seat 31 immediately separates from the valve body 34,
The second port 29b is connected to the air inlet 3 through the annular passage 32.
Communicate with 9. As a result, the valve cylinder 1
The air that has flowed into the chamber passes through the air introduction valve seat 31, and
It is quickly introduced into both working chambers 2b, 3b through the port 29b, and the chambers 2b, 3b are made higher in pressure than the two negative pressure chambers 2a, 3a. , 6 move forward with the movement of the input rod 20 against the force of the valve cylinder return spring 27 with the valve cylinder 10 and the large-diameter piston 15. The forward thrust of the booster pistons 4 and 6 is transmitted from the large-diameter piston 15 to the elastic piston 22 and pushes the cup body 21, that is, the output rod 25, forward. It can be activated without delay and brake the vehicle.
【００３１】ところで，このような制動中，弾性ピスト
ン２２の後端面には，大径ピストン１５に加わる両ブー
スタピストン４，６の推力と，入力杆２０から小径ピス
トン１７に加わる操縦者の踏力とが作用し，またその前
端面には，出力杆２５の作動反力が作用し，これによっ
て弾性ピストン２２は前後に圧縮される。その結果，出
力杆２５の作動反力の一部が弾性ピストン２２を介して
入力杆２０に伝達されることになり，操縦者は出力杆２
５の出力，即ち制動力の大きさを感受することができ
る。During the braking, the thrust of the booster pistons 4 and 6 applied to the large-diameter piston 15 and the pedaling force of the operator applied to the small-diameter piston 17 from the input rod 20 are applied to the rear end face of the elastic piston 22. Acts on the front end face thereof, and the reaction force of the output rod 25 acts thereon, whereby the elastic piston 22 is compressed back and forth. As a result, a part of the operation reaction force of the output rod 25 is transmitted to the input rod 20 via the elastic piston 22, and the operator can control the output rod 2.
5, the magnitude of the braking force can be sensed.
【００３２】而して，出力杆２５の出力が倍力限界に達
するまでは（図４の線ａ−ｂ参照），ブースタピストン
４，６と一体の弁筒１０は，入力杆２０の前進量だけ前
進するもので，入力杆２０が前進を止めると，弁筒１０
と共に前進してきた弁体３４が大気導入弁座３１に再び
着座して，作動室２ｂ，３ｂへの大気のそれ以上の導入
を阻止するので，ブースタピストン４，６の前進も停止
し，入力に対応した倍力出力が得られることになる。と
ころで，大径ピストン１５は，当初，環状段部２３を除
く前端面を弾性ピストン２２に当接させているが，出力
杆２５の出力が所定値を超えると，環状段部２３をも弾
性ピストン２２に当接させるようになるため，大径ピス
トン１５及び小径ピストン１７の弾性ピストン２２に対
する受圧面積比の変化により，図４に線ａ−ｂ−ｃで示
すように倍力比が途中から増加する。Until the output of the output rod 25 reaches the boosting limit (see the line ab in FIG. 4), the valve cylinder 10 integrated with the booster pistons 4, 6 moves the input rod 20 forward. Only when the input rod 20 stops moving forward.
Together with the valve body 34, which is moved forward, is seated again on the air introduction valve seat 31 to prevent the air from being further introduced into the working chambers 2b, 3b. A corresponding boost output will be obtained. By the way, the large-diameter piston 15 initially has its front end surface excluding the annular step portion 23 abutting on the elastic piston 22, but when the output of the output rod 25 exceeds a predetermined value, the annular step portion 23 is also moved by the elastic piston. As the pressure-receiving area ratio of the large-diameter piston 15 and the small-diameter piston 17 to the elastic piston 22 changes, the boosting ratio increases from the middle as shown by the line abc in FIG. I do.
【００３３】そして，出力杆２５の出力が倍力限界を超
えると，ブースタピストン４，６の気圧差による推力が
最大となり，大気導入弁座３１は弁体３４から離間した
まゝとなるので，出力杆２５の出力は，ブースタピスト
ン４，６の気圧差による最大推力と，ブレーキペダルＰ
への踏力による入力杆２０の推力との和となる（図４の
線ｃ−ｄ参照）。When the output of the output rod 25 exceeds the boosting limit, the thrust due to the pressure difference between the booster pistons 4 and 6 is maximized, and the air introduction valve seat 31 remains separated from the valve body 34. The output of the output rod 25 is determined by the maximum thrust due to the pressure difference between the booster pistons 4 and 6 and the brake pedal P
And the thrust of the input rod 20 due to the treading force (see the line cd in FIG. 4).
【００３４】上記のように，弁筒１０が入力杆２０の前
進に殆ど遅れなく追従する場合には，弁筒１０の第１永
久磁石５１と弁ピストン３３の第２永久磁石５２との相
対変位は前記所定距離ｓを超えることがなく，両永久磁
石５１，５２は互いに軸方向に反発し続けるので，弁ピ
ストン３３は，図２に示すように，内向きフランジ３３
ａを入力プランジャ１８のストッパ環４５に当接させる
後退位置Ｒに保持される。このことは，弁ピストン３３
を後退位置Ｒ側へ付勢する戻しばね４４のセット荷重を
小さく設定することが可能となったことを意味する。 ［緊急ブレーキ］ブレーキペダルＰを急速に踏み込む緊
急ブレーキ時には，弁筒１０の作動遅れに伴い，弁筒１
０に対して弁ピストン３３が入力杆２０と共に前進し
て，第２永久磁石５２が第１永久磁石５１に対して所定
距離ｓ以上前進すると，前述のように，第２永久磁石５
２の前，後端端極（Ｓ，Ｎ極）が第１永久磁石５１の
前，後端極（Ｎ，Ｓ極）に半径方向及び軸方向に対向す
るようになり，両永久磁石５１，５２は反発状態から吸
引状態に切換わるので，それらの吸引力により，弁ピス
トン３３は，戻しばね４４のセット荷重に抗して，外向
きフランジ１８ａに当接する前進位置Ｆ（図３の状態）
まで前進して，大気導入弁座３１を弁体３４から最大に
引き離し，全開状態とする。As described above, when the valve cylinder 10 follows the advance of the input rod 20 with almost no delay, the relative displacement between the first permanent magnet 51 of the valve cylinder 10 and the second permanent magnet 52 of the valve piston 33. Does not exceed the predetermined distance s, and the two permanent magnets 51 and 52 continue to repel each other in the axial direction. Therefore, as shown in FIG.
a is held at the retracted position R where the a contacts the stopper ring 45 of the input plunger 18. This means that the valve piston 33
Means that the set load of the return spring 44 for urging the spring toward the retreat position R side can be set small. [Emergency brake] During emergency braking in which the brake pedal P is rapidly depressed, the valve cylinder 1
0, the valve piston 33 advances with the input rod 20, and the second permanent magnet 52 advances more than a predetermined distance s with respect to the first permanent magnet 51, as described above.
2, the front and rear end poles (S and N poles) are radially and axially opposed to the front and rear end poles (N and S poles) of the first permanent magnet 51. 52 is switched from the repulsive state to the suction state, so that the suction force causes the valve piston 33 to advance against the set load of the return spring 44 and to be in the forward position F in contact with the outward flange 18a (the state shown in FIG. 3).
Until the air introduction valve seat 31 is maximally separated from the valve body 34 to bring it into a fully opened state.
【００３５】こゝで，特に注目すべくき点は，戻しばね
４４のセット荷重が，前述のように両永久磁石５１，５
２が反発状態にあるときの反発力の利用により小さく設
定してあるので，両永久磁石５１，５２が反発状態から
吸引状態に切換わるや否や，戻しばね４４のセット荷重
にあまり抵抗させずに，瞬間的に弁ピストン３３を急速
に前進させ，大気導入弁座３１を即座に全開させること
である。Here, it should be noted that the set load of the return spring 44 is, as described above, the two permanent magnets 51,5.
2 is set small by utilizing the repulsive force when in the repulsive state, so that as soon as the two permanent magnets 51 and 52 switch from the repulsive state to the attracted state, they do not significantly resist the set load of the return spring 44. That is, the valve piston 33 is rapidly advanced instantaneously, and the air introduction valve seat 31 is fully opened immediately.
【００３６】その結果，大気導入口３９から両作動室２
ｂ，３ｂに大量の大気が一挙に導入されることになるの
で，作動室２ｂ，３ｂ及び負圧室２ａ，３ａ間の気圧差
によるブレーキピストン４，６推力，即ち出力杆２５の
出力が倍力限界まで直ちに増大し，ブレーキマスタシリ
ンダＭを急速且つ強力に作動させることができる。この
ような緊急ブレーキ操作は，図４にＰ１，Ｐ２，Ｐ３で
示すように，ブレーキ開始と同時であろうと，通常ブレ
ーキ時の途中であろうと，また通常ブレーキ時において
倍力比が変化した後であろうと，これを行えば，常に，
そのときから出力を倍力限界まで直ちに増大させること
ができる。As a result, the two working chambers 2
Since a large amount of air is introduced into the b and 3b all at once, the thrust of the brake pistons 4 and 6 due to the pressure difference between the working chambers 2b and 3b and the negative pressure chambers 2a and 3a, that is, the output of the output rod 25 is doubled. It increases immediately to the force limit, and the brake master cylinder M can be operated quickly and powerfully. As shown by P1, P2, and P3 in FIG. 4, such an emergency brake operation is performed at the same time as the start of braking, during the normal braking, or after the boosting ratio changes during the normal braking. If you do this,
From then on, the output can be increased immediately to the boost limit.
【００３７】また弁ピストン３３の，環状通路３２に臨
む外周面３２ａは，第２ポート２９ｂの内周面に連続
し，且つ大気導入弁座３１に向かって小径となるするテ
ーパ面としてあるので，大気導入弁座３１の全開に伴
い，大量の大気が環状通路３２から第２ポート２９ｂに
流入するとき，その空気の流れが乱れることなくスムー
ズであり，弁ピストン３３が入力杆２０及び入力プラン
ジャ１８のかしめ結合部１９ａを覆っていることゝ相俟
って風切り音などの騒音の発生を抑えることができる。The outer peripheral surface 32a of the valve piston 33 facing the annular passage 32 is a tapered surface that is continuous with the inner peripheral surface of the second port 29b and has a smaller diameter toward the air introduction valve seat 31. When a large amount of air flows into the second port 29b from the annular passage 32 with the full opening of the air introduction valve seat 31, the flow of the air is smooth without being disturbed, and the valve piston 33 is connected to the input rod 20 and the input plunger 18. Covering the caulking connection portion 19a can also suppress the generation of noise such as wind noise.
【００３８】このように，ブレーキペダルＰによる入力
杆２０の急速前進時には，弁ピストン３３を弁筒１０及
び弁ピストン３３にそれぞれ付設した第１及び第２永久
磁石５１，５２間の吸引力により大気導入弁座３１を全
開状態にさせるようにした簡単な構成を採用することに
より，緊急ブレーキに対応し得る負圧ブースタＢを安価
に提供することができる。 ［緊急ブレーキの解除］緊急ブレーキ状態を解除すべ
く，ブレーキペダルＰから踏力を解放すると，入力杆２
０及び入力プランジャ１８が入力戻しばね４１の力をも
って後退する。そのとき，入力戻しばね４１のセット荷
重は両永久磁石５１，５２間の吸引力より大きく設定し
てあるから，入力プランジャ１８が上記吸引力に抗して
弁ピストン３３を後退させることになり，その後退に伴
い両永久磁石５１，５２が反発状態になれば，その反発
力と戻しばね４４の力によって弁ピストン３３は，内向
きフランジ３３ａを入力プランジャ１８のストッパ環４
５に当接させる後退位置Ｒに直ちに戻ることができる。
そして，弁ピストン３３は大気導入弁座３１を弁体３４
に着座させると共に，その弁体３４を負圧導入弁座３０
から大きく離間させるので，それ以後は通常ブレーキの
解除時と同様に，両作動室２ｂ，３ｂは，第２ポート２
９ｂ，環状通路３２及び第１ポート２９ａを介して両負
圧室２ａ，３ａと連通する。その結果，両作動室２ｂ，
３ｂへの大気の導入が阻止される一方，両作動室２ｂ，
３ｂの空気が両負圧室２ａ，３ａを経て負圧限Ｖに吸入
され，それらの気圧差が無くなるため，ブースタピスト
ン４，６も，弁筒戻しばね２７の力をもって後退し，マ
スタシリンダＭの作動を解除していく。As described above, when the input rod 20 is rapidly advanced by the brake pedal P, the atmospheric pressure is generated by the attractive force between the first and second permanent magnets 51 and 52 attached to the valve cylinder 10 and the valve piston 33, respectively. By adopting a simple configuration in which the introduction valve seat 31 is fully opened, a negative pressure booster B that can cope with emergency braking can be provided at low cost. [Release of emergency brake] When the pedaling force is released from the brake pedal P to release the emergency brake state, the input rod 2
0 and the input plunger 18 are retracted by the force of the input return spring 41. At this time, since the set load of the input return spring 41 is set to be larger than the attraction force between the two permanent magnets 51 and 52, the input plunger 18 retracts the valve piston 33 against the attraction force. When the two permanent magnets 51 and 52 are repelled by the retraction, the repulsive force and the force of the return spring 44 cause the valve piston 33 to move the inward flange 33 a to the stopper ring 4 of the input plunger 18.
5 can be immediately returned to the retracted position R where it abuts.
Then, the valve piston 33 connects the air introduction valve seat 31 to the valve body 34.
And the valve body 34 is connected to the negative pressure introducing valve seat 30.
After that, both working chambers 2b and 3b are connected to the second port 2 in the same manner as when the normal brake is released.
9b, the annular passage 32 and the first port 29a communicate with both negative pressure chambers 2a and 3a. As a result, both working chambers 2b,
3b is prevented from being introduced into the atmosphere, while both working chambers 2b,
3b is sucked into the negative pressure limit V through the two negative pressure chambers 2a, 3a, and the pressure difference between them is eliminated. Therefore, the booster pistons 4, 6 also retreat with the force of the valve cylinder return spring 27, and the master cylinder M Cancel the operation of.
【００３９】入力杆２０がストッパ板４０を後方延長筒
１２の内向きフランジ１２ａに当接させる後退限まで後
退すると，後部ブースタピストン６は，一旦，後部ダイ
ヤフラム７の突起７ａをブースタシェル１の後壁に当接
させる後退限まで戻り，今度は負圧導入弁座３０を弁体
３４に着座させると共に，弁体３４を大気導入弁座３１
から離間させるので，再び両作動室２ｂ，３ｂに大気が
導入されるが，それにより生ずる気圧差により両ブース
タピストン４，６が僅かに前進すれば，負圧導入弁座３
０にも弁体３４が着座し，制御弁３８を当初の中立状態
にする。こうして両作動室２ｂ，３ｂには，大気に希釈
された負圧が保持され，負圧ブースタＢは，図１及び図
２の休止状態となる。When the input rod 20 moves backward until the stopper plate 40 comes into contact with the inward flange 12a of the rear extension cylinder 12, the rear booster piston 6 once moves the projection 7a of the rear diaphragm 7 to the rear of the booster shell 1. Returning to the retreat limit to be brought into contact with the wall, the negative pressure introduction valve seat 30 is seated on the valve body 34 and the valve body 34 is moved to the atmosphere introduction valve seat 31 this time.
The air is again introduced into the two working chambers 2b and 3b, but if the booster pistons 4 and 6 advance slightly due to the resulting pressure difference, the negative pressure introducing valve seat 3 will be released.
At 0, the valve body 34 is seated, and the control valve 38 is returned to the initial neutral state. In this way, the working chambers 2b and 3b hold the negative pressure diluted with the atmosphere, and the negative pressure booster B enters the rest state shown in FIGS.
【００４０】本発明は，上記実施例に限定されるもので
はなく，その要旨を逸脱しない範囲で種々の設計変更が
可能である。例えば，第１永久磁石５１では前後にＮ，
Ｓ極を配する一方，第２永久磁石５２では前後にＳ，Ｎ
極を配することもできる。また負圧ブースタＢは，ブー
スタピストンを単一とするシングル型に構成することも
できる。さらに入力杆２０のストッパ板４０及び後方延
長筒１２の内向きフランジ１２ａを廃止し，負圧ブース
タＢの休止時には，負圧導入弁座３０を開放したまゝに
して，作動室２ｂ，３ｂを負圧室２ａ，３ａとの連通状
態に保持するようにしてもよい。また環状段部２３を廃
止して弾性ピストン２２の受圧面積を一定にし，倍力比
を一定にしておくこともできる。The present invention is not limited to the above embodiment, and various design changes can be made without departing from the gist of the present invention. For example, in the first permanent magnet 51, N,
While the S pole is provided, the second permanent magnet 52 has S, N
Poles can also be arranged. Further, the negative pressure booster B may be configured as a single type having a single booster piston. Further, the stopper plate 40 of the input rod 20 and the inward flange 12a of the rear extension cylinder 12 are eliminated, and when the negative pressure booster B is stopped, the operating chambers 2b and 3b are kept open while the negative pressure introducing valve seat 30 is kept open. The communication with the negative pressure chambers 2a and 3a may be maintained. In addition, the annular step portion 23 can be eliminated to keep the pressure receiving area of the elastic piston 22 constant and to keep the boost ratio constant.
【００４１】[0041]
【発明の効果】以上のように本発明の第１の特徴によれ
ば，ブレーキペダルによる入力杆の急速前進時には，弁
筒及び弁ピストンにそれぞれ付設した第１及び第２永久
磁石の吸引力を利用して，大気導入弁座を全開状態にさ
せるようにした簡単な構成を採用することにより，緊急
ブレーキに対応し得る負圧ブースタを安価に提供するこ
とができる。特に，弁ピストンの弁筒に対する前進が所
定距離未満となる通常ブレーキ時には，第１及び第２永
久磁石は反発状態を維持させ，それらの反発力により弁
ピストンを後退方向へ付勢するようにしたので，弁ピス
トンを後退位置側へ付勢する戻しばねのセット荷重を小
さく設定することが可能となり，その結果，緊急ブレー
キ時，弁筒に対して弁ピストンが所定距離を超えて前進
することにより，第１及び第２永久磁石が反発状態から
吸引状態に切換わるや否や，第１及び第２永久磁石相互
の吸引力により，戻しばねの抵抗をあまり受けずに，弁
ピストンを素早く前進させ，制御弁を作動室と大気との
最大連通状態に切換え，作動室に大量の大気を一挙に導
入して，出力杆の出力を倍力限界点まで即座に増大さ
せ，緊急ブレーキに的確に対応することができる。As described above, according to the first aspect of the present invention, when the input rod is rapidly advanced by the brake pedal, the attraction force of the first and second permanent magnets respectively attached to the valve cylinder and the valve piston is increased. By adopting a simple configuration in which the air introduction valve seat is fully opened by using the same, a negative pressure booster capable of coping with emergency braking can be provided at low cost. In particular, at the time of normal braking in which the advance of the valve piston with respect to the valve cylinder is less than a predetermined distance, the first and second permanent magnets maintain a repulsive state, and the repulsive force urges the valve piston in the backward direction. Therefore, it is possible to reduce the set load of the return spring that urges the valve piston to the retracted position side. As a result, during emergency braking, the valve piston moves forward beyond a predetermined distance with respect to the valve cylinder. As soon as the first and second permanent magnets are switched from the repelled state to the attracted state, the attraction force of the first and second permanent magnets causes the valve piston to quickly move forward without much resistance of the return spring, The control valve is switched to the maximum communication state between the working chamber and the atmosphere, a large amount of air is introduced into the working chamber at once, and the output of the output rod is immediately increased to the boosting limit point, so that emergency braking can be properly handled. It is possible.
【００４２】また本発明の第２の特徴によれば，弁ピス
トンの，環状通路に臨む外周面を大気導入弁座に向かっ
て小径となるテーパ状に形成したので，大気導入弁座の
全開時には，大量の大気を弁ピストンのテーパ状外周面
により作動室へスムーズに誘導して，ブースタピストン
の応答性向上に寄与することができ，しかも，弁ピスト
ンが入力杆及び入力プランジャのかしめ結合部を覆って
いるので，該かしめ部による風切り音の発生を抑えるこ
とができ，大気の作動室への流入がスムーズであること
ゝ相俟って全体の作動騒音を効果的に下げることができ
る。According to the second feature of the present invention, since the outer peripheral surface of the valve piston facing the annular passage is formed in a tapered shape having a small diameter toward the air introduction valve seat, when the air introduction valve seat is fully opened. A large amount of air can be smoothly guided to the working chamber by the tapered outer peripheral surface of the valve piston, which can contribute to the improvement of the response of the booster piston. In addition, the valve piston connects the input rod and the caulked joint of the input plunger. Since the cover is covered, the generation of wind noise by the caulking portion can be suppressed, and the smooth flow of the atmosphere into the working chamber can be effectively reduced.
【図１】本発明の実施例に係るタンデム型負圧ブースタ
の縦断面図。FIG. 1 is a longitudinal sectional view of a tandem type negative pressure booster according to an embodiment of the present invention.
【図２】図１の２部拡大図。FIG. 2 is an enlarged view of a part of FIG.
【図３】上記負圧ブースタの作用説明図。FIG. 3 is an explanatory diagram of an operation of the negative pressure booster.
【図４】上記負圧ブースタの倍力特性を示す線図。FIG. 4 is a diagram showing boost characteristics of the negative pressure booster.
Ｂ・・・・負圧ブースタ Ｆ・・・・弁ピストンの前進位置 Ｒ・・・・弁ピストンの後退位置 Ｖ・・・・負圧源 ｓ・・・・第１，第２永久磁石を反発状態から吸引状態
に切換えるために弁ピストンが前進する所定距離 １・・・・ブースタシェル ２ａ・・・負圧室（前部負圧室） ３ａ・・・負圧室（後部負圧室） ２ｂ・・・作動室（前部作動室） ３ｂ・・・作動室（後部作動室） ４・・・・ブースタピストン（前部ブースタピストン） ６・・・・ブースタピストン（後部ブースタピストン） １０・・・弁筒 １８・・・入力プランジャ ２０・・・入力杆 ２４・・・反力機構 ２５・・・出力杆 ２９ａ ・・第１ポート ２９ｂ ・・第２ポート ３０・・・負圧導入弁座 ３１・・・大気導入弁座 ３２・・・環状通路 ３３・・・弁ピストン ３４・・・弁体 ３４ａ・・弁部 ３６・・・弁ばね ３８・・・制御弁 ４４・・・戻しばね ５１・・・第１永久磁石 ５２・・・第２永久磁石B: Negative pressure booster F: Advance position of valve piston R: Retreat position of valve piston V: Negative pressure source s: Repel first and second permanent magnets A predetermined distance at which the valve piston moves forward to switch from the state to the suction state 1... Booster shell 2a... Negative pressure chamber (front negative pressure chamber) 3a. ... working chamber (front working chamber) 3b ... working chamber (rear working chamber) 4 ... booster piston (front booster piston) 6 ... booster piston (rear booster piston) 10 ...・ Valve cylinder 18 ・ ・ ・ Input plunger 20 ・ ・ ・ Input rod 24 ・ ・ ・ Reaction mechanism 25 ・ ・ ・ Output rod 29a ..First port 29b ··· Second port 30 ··· Negative pressure introduction valve seat 31 ··· Atmospheric introduction valve seat 32 ··· Annular passage 33 ··· valve piston 34 ··· valve body 34a ··· valve part 36 ··· valve Spring 38 ・ ・ ・ Control valve 44 ・ ・ ・ Return spring 51 ・ ・ ・ First permanent magnet 52 ・ ・ ・ Second permanent magnet
───────────────────────────────────────────────────── フロントページの続き (72)発明者 川上 洋生 埼玉県和光市中央１丁目４番１号 株式会 社本田技術研究所内 Ｆターム(参考） 3D048 BB21 BB29 BB31 CC27 EE00 EE15 EE16 EE20 EE25 MM02 NN04 QQ08 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Hiroki Kawakami 1-4-1 Chuo, Wako-shi, Saitama F-term in Honda R & D Co., Ltd. (Reference) 3D048 BB21 BB29 BB31 CC27 EE00 EE15 EE16 EE20 EE25 MM02 NN04 QQ08
Claims (2)
圧源（Ｖ）に連なる前側の負圧室（２ａ，３ａ）と後側
の作動室（２ｂ，３ｂ）とに区画するブースタピストン
（４，６）を収容し，このブースタピストン（４，６）
に，前記ブースタシェル（１）の後壁に摺動自在に支承
される弁筒（１０）を連設し，この弁筒（１０）内に，
前後動可能の入力杆（２０）と，この入力杆（２０）の
前後動に応じて作動室（２ｂ，３ｂ）を負圧室（２ａ，
３ａ）と大気とに連通切換えする制御弁（３８）とを配
設し，前記弁筒（１０）及び入力杆（２０）と，前記ブ
ースタシェル（１）に摺動可能に支持される出力杆（２
５）との間に，入力杆（２０）に対する入力と，作動室
（２ｂ，３ｂ）及びを負圧室（２ａ，３ａ）間の気圧差
による前記ブースタピストン（４，６）の推力との合力
を該出力杆（２５）に伝達する反力機構（２４）を介裝
した負圧ブースタにおいて，前記入力杆（２０）に，前
記反力機構（２４）に連なる入力プランジャ（１８）を
連結し，この入力プランジャ（１８）の外周に弁ピスト
ン（３３）を，これが入力プランジャ（１８）に対して
軸方向に沿う後退位置（Ｒ）及び前進位置（Ｆ）間を移
動し得るように嵌合すると共に，この弁ピストン（３
３）を戻しばね（４４）により前記後退位置（Ｒ）側へ
付勢し，この弁ピストン（３３）を前記制御弁（３８）
に，この弁ピストン（３３）が前記前進位置（Ｆ）まで
前進したとき前記制御弁（３８）を前記作動室（２ｂ，
３ｂ）と大気との最大連通状態に切換えるように連結
し，前記弁筒（１０）及び弁ピストン（３３）に，これ
らの軸方向相対移動に応じて互いに半径方向に重なりな
がら軸方向に相対移動する第１永久磁石（５１）及び第
２永久磁石（５２）をそれぞれ付設し，これら第１及び
第２永久磁石（５１，５２）は，前記弁ピストン（３
３）の入力プランジャ（１８）に対する後退位置（Ｒ）
からの前進が所定距離（ｓ）に満たないときには，互い
に同極を半径方向及び軸方向に対向させて前記弁ピスト
ン（３３）を前記後退位置（Ｒ）側へ付勢する反発力を
発生し，前記弁ピストン（３３）の入力プランジャ（１
８）に対する後退位置（Ｒ）からの前進が所定距離
（ｓ）を超えると，互いに異極を半径方向及び軸方向に
対向させて前記弁ピストン（３３）を前記前進位置
（Ｆ）まで移動させる吸引力を発生するように構成され
ることを特徴とする，負圧ブースタ。1. A booster piston which partitions a booster shell (1) into a front negative pressure chamber (2a, 3a) connected to a negative pressure source (V) and a rear working chamber (2b, 3b). (4,6), and this booster piston (4,6)
A valve cylinder (10) slidably supported on the rear wall of the booster shell (1) is connected to the valve shell (1).
An input rod (20) that can be moved back and forth, and the working chambers (2b, 3b) are moved according to the forward and backward movement of the input rod (20) into the negative pressure chambers (2a, 2a).
3a) and a control valve (38) for switching between communication with the atmosphere, the valve cylinder (10) and the input rod (20), and the output rod slidably supported by the booster shell (1). (2
5) between the input to the input rod (20) and the thrust of the booster pistons (4, 6) due to the pressure difference between the working chambers (2b, 3b) and the negative pressure chambers (2a, 3a). In a negative pressure booster provided with a reaction force mechanism (24) for transmitting a resultant force to the output rod (25), an input plunger (18) connected to the reaction force mechanism (24) is connected to the input rod (20). A valve piston (33) is fitted on the outer periphery of the input plunger (18) so that the valve piston (33) can move between the retreat position (R) and the advance position (F) along the axial direction with respect to the input plunger (18). And the valve piston (3
3) is urged toward the retracted position (R) by a return spring (44), and this valve piston (33) is moved to the control valve (38).
When the valve piston (33) has advanced to the advance position (F), the control valve (38) is connected to the working chamber (2b, 2b).
3b) is connected so as to switch to a maximum communication state with the atmosphere, and the valve cylinder (10) and the valve piston (33) move relative to each other in the axial direction while overlapping each other in the radial direction according to their relative movement in the axial direction. A first permanent magnet (51) and a second permanent magnet (52) are provided respectively, and the first and second permanent magnets (51, 52) are attached to the valve piston (3).
3) Retraction position (R) with respect to input plunger (18)
When the forward movement from the valve is less than a predetermined distance (s), a repulsive force is generated which urges the valve piston (33) toward the retreat position (R) by causing the same poles to face each other in the radial direction and the axial direction. , The input plunger (1) of the valve piston (33)
8) When the advance from the retreat position (R) with respect to the retreat position (R) exceeds a predetermined distance (s), the valve piston (33) is moved to the advance position (F) with the opposite poles facing each other in the radial and axial directions. A negative pressure booster characterized by being configured to generate a suction force.
前記入力プランジャ（１８）に前記入力杆（２０）の球
状前端部（２０ａ）を首振り可能にかしめ結合すると共
に，そのかしめ結合部（１９ａ）を前記弁ピストン（３
３）で覆い，この弁ピストン（３３）の後端に形成した
大気導入弁座（３１）と，この大気導入弁座（３１）を
環状通路（３２）を挟んで囲繞するように前記弁筒（１
０）に形成した負圧導入弁座（３０）と，前記弁筒（１
０）に前後動可能に取付けられて前記負圧導入弁座（３
０）及び大気導入弁座（３１）に前端の弁部（３４ａ）
を対向させる弁体（３４）と，この弁体（３４）の弁部
（３４ａ）を前記両弁座（３０，３１）との着座方向へ
付勢する弁ばね（３６）とから前記制御弁（３８）を構
成すると共に，前記弁体（３４）の内側を大気に連通
し，前記負圧導入弁座（３０）を前記負圧室（２ａ，３
ａ）に連通する第１ポート（２９ａ）と，前記環状通路
（３２）を前記作動室（２ｂ，３ｂ）に連通する第２ポ
ート（２９ｂ）とを前記弁筒（１０）に設け，前記弁ピ
ストン（３３）の，前記環状通路（３２）に臨む外周面
（３２ａ）を後端に向かって小径となるテーパ状に形成
したことを特徴とする，負圧ブースタ。2. The negative pressure booster according to claim 1,
The spherical front end portion (20a) of the input rod (20) is swaged to the input plunger (18) so as to swing, and the swaged connection portion (19a) is connected to the valve piston (3).
3) and an air introduction valve seat (31) formed at the rear end of the valve piston (33), and the valve cylinder so as to surround the air introduction valve seat (31) with an annular passage (32) interposed therebetween. (1
0) and the valve cylinder (1).
0) so as to be able to move back and forth, and the negative pressure introduction valve seat (3)
0) and the valve part (34a) at the front end on the air introduction valve seat (31).
And a valve spring (36) for urging the valve portion (34a) of the valve body (34) in the seating direction of the two valve seats (30, 31). (38), the inside of the valve body (34) communicates with the atmosphere, and the negative pressure introducing valve seat (30) is connected to the negative pressure chambers (2a, 3).
a) a first port (29a) communicating with the working chamber (2b, 3b), and a second port (29b) communicating with the working chamber (2b, 3b). A negative pressure booster characterized in that an outer peripheral surface (32a) of the piston (33) facing the annular passage (32) is formed in a tapered shape having a smaller diameter toward a rear end.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23888199A JP4167353B2 (en) | 1999-08-25 | 1999-08-25 | Negative pressure booster |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23888199A JP4167353B2 (en) | 1999-08-25 | 1999-08-25 | Negative pressure booster |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001063549A true JP2001063549A (en) | 2001-03-13 |
| JP4167353B2 JP4167353B2 (en) | 2008-10-15 |
Family
ID=17036663
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23888199A Expired - Lifetime JP4167353B2 (en) | 1999-08-25 | 1999-08-25 | Negative pressure booster |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4167353B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002337681A (en) * | 2001-03-15 | 2002-11-27 | Bosch Automotive Systems Corp | Brake booster |
| JP2007099277A (en) * | 2002-01-31 | 2007-04-19 | Hitachi Ltd | Pneumatic booster |
| JP2007099276A (en) * | 2002-01-31 | 2007-04-19 | Hitachi Ltd | Pneumatic booster |
| CN101003272B (en) * | 2002-01-31 | 2010-05-26 | 株式会社日立制作所 | Pneumatic booster |
| DE102010034828A1 (en) * | 2010-08-19 | 2012-02-23 | Lucas Automotive Gmbh | Vacuum brake booster with reduced noise emission and method for producing such a vacuum brake booster |
| CN102501845A (en) * | 2011-10-28 | 2012-06-20 | 江苏九龙汽车制造有限公司 | Auxiliary device of vacuum booster |
-
1999
- 1999-08-25 JP JP23888199A patent/JP4167353B2/en not_active Expired - Lifetime
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002337681A (en) * | 2001-03-15 | 2002-11-27 | Bosch Automotive Systems Corp | Brake booster |
| JP2007099277A (en) * | 2002-01-31 | 2007-04-19 | Hitachi Ltd | Pneumatic booster |
| JP2007099276A (en) * | 2002-01-31 | 2007-04-19 | Hitachi Ltd | Pneumatic booster |
| CN101003272B (en) * | 2002-01-31 | 2010-05-26 | 株式会社日立制作所 | Pneumatic booster |
| JP4626773B2 (en) * | 2002-01-31 | 2011-02-09 | 日立オートモティブシステムズ株式会社 | Pneumatic booster |
| JP4626772B2 (en) * | 2002-01-31 | 2011-02-09 | 日立オートモティブシステムズ株式会社 | Pneumatic booster |
| DE102010034828A1 (en) * | 2010-08-19 | 2012-02-23 | Lucas Automotive Gmbh | Vacuum brake booster with reduced noise emission and method for producing such a vacuum brake booster |
| US9446751B2 (en) | 2010-08-19 | 2016-09-20 | Lucas Automotive Gmbh | Vacuum brake force booster with reduced noise emission and method for manufacturing a vacuum brake force booster of said type |
| CN102501845A (en) * | 2011-10-28 | 2012-06-20 | 江苏九龙汽车制造有限公司 | Auxiliary device of vacuum booster |
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| Publication number | Publication date |
|---|---|
| JP4167353B2 (en) | 2008-10-15 |
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