JPS6025839A - Pneumatic booster - Google Patents
Pneumatic boosterInfo
- Publication number
- JPS6025839A JPS6025839A JP58132474A JP13247483A JPS6025839A JP S6025839 A JPS6025839 A JP S6025839A JP 58132474 A JP58132474 A JP 58132474A JP 13247483 A JP13247483 A JP 13247483A JP S6025839 A JPS6025839 A JP S6025839A
- Authority
- JP
- Japan
- Prior art keywords
- pressure chamber
- piston
- shell
- working
- working pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/24—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being gaseous
- B60T13/46—Vacuum systems
- B60T13/52—Vacuum systems indirect, i.e. vacuum booster units
- B60T13/563—Vacuum systems indirect, i.e. vacuum booster units with multiple booster units, e.g. tandem booster units
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Braking Systems And Boosters (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、車両等のブレーキ装置、クラッチ装置等にお
いて使用される気圧倍力装置、より詳しくはシェル内に
複数のピストンを直列に配置したタンデム型気圧倍力装
置に関する。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a pressure booster used in brake devices, clutch devices, etc. of vehicles, and more specifically, a pressure booster device in which a plurality of pistons are arranged in series in a shell. This invention relates to a tandem pressure booster.
（従来技術）
従来のタンデム型気圧倍力装置は、第１図に示すような
一般的構造を有していた。すなわち、前方シェル１と後
方シェル２で構成される密閉容器（シェル）内には、第
１のダイアフラム３と第２のダイアフラム４とが張設さ
れ、両ダイアフラム３，４にはそれぞれ第１のピストン
５と第２のピストン６とが取付けられている。そして、
前記両ピストン５．６Ｆｉ筒状部材７によって連結され
ると共に、両ピストン５．６間には該第１のピストン５
側罠小室を画成するセンターグレート （隔壁）８が設
けられ、前記筒状部材７はセンタープレート８に対し気
密を保持して摺動できるものとなっている。(Prior Art) A conventional tandem type pressure booster had a general structure as shown in FIG. That is, a first diaphragm 3 and a second diaphragm 4 are stretched in a closed container (shell) composed of a front shell 1 and a rear shell 2, and both diaphragms 3 and 4 have a first diaphragm 3 and a second diaphragm 4, respectively. A piston 5 and a second piston 6 are attached. and,
The two pistons 5.6 are connected by the cylindrical member 7, and the first piston 5 is connected between the two pistons 5.6.
A center grate (partition wall) 8 defining a side trap chamber is provided, and the cylindrical member 7 can slide against the center plate 8 in an airtight manner.
かくして、第１、第２のピストン５，６の前後部には、
４つの圧力室Ａ、 Ｂ、 Ｃ，Ｄが画成され、このうち
、圧力室ＡとＣとは、第１、第２の定圧室として、内部
通路９により相互に連通ずると共に、圧力導入口１１介
して車両エンジンの負圧発生部に連通し、一方圧力室Ｂ
とＤとは、第１、第２の足動圧室として、第２のダイア
フラム４の通路１１により相互に連通している。Thus, at the front and rear of the first and second pistons 5 and 6,
Four pressure chambers A, B, C, and D are defined, and among these, pressure chambers A and C serve as first and second constant pressure chambers and communicate with each other through an internal passage 9. 11 to the negative pressure generating section of the vehicle engine, while the pressure chamber B
and D communicate with each other through a passage 11 of the second diaphragm 4 as first and second foot dynamic pressure chambers.
１２は第１のピストン５側がら筒状部材７の軸部に挿入
され、後端に７ランク部１３ヲ有して成る被動杆であっ
て、その先端を、図示を略したマスクシリンダに係合さ
せ、かつ前記フランジ部１３ヲ第２のピストン６に固設
された収納体１４内に嵌入している。１５は図示を略し
たペダルに連動する操作杆で、弁プランジャ１６を介し
て前記収納体１４と係合している。そして、前記弁プラ
ンジャ１６を含む周知の弁機構１７が第２のビス変位に
応じて第２の定圧室Ｃと第２の作動圧室りとの間の連通
遮断の役割をなす。A driven rod 12 is inserted into the shaft of the cylindrical member 7 from the side of the first piston 5 and has a seven-rank portion 13 at its rear end, the tip of which is connected to a mask cylinder (not shown). The flange portion 13 is fitted into a storage body 14 fixed to the second piston 6. Reference numeral 15 denotes an operating rod that is linked to a pedal (not shown) and is engaged with the storage body 14 via a valve plunger 16. A well-known valve mechanism 17 including the valve plunger 16 serves to interrupt communication between the second constant pressure chamber C and the second operating pressure chamber in response to the displacement of the second screw.
なお、１８は被動杆１２のフランジ部１３とプランジャ
１６との間に介装された弾性を有する加圧変形部材で、
反力を伝達する中間部品となる。また、第１、第２のピ
ストン５．６は第１のピストン５の前方に介装したリタ
ーンスプリング１９により、戻り位置に付勢されている
。Note that 18 is an elastic pressure deformation member interposed between the flange portion 13 of the driven rod 12 and the plunger 16;
It becomes an intermediate part that transmits reaction force. Further, the first and second pistons 5.6 are urged to the return position by a return spring 19 interposed in front of the first piston 5.
か＼る構成により、ペダルに踏力が加えられずに操作杆
１２が変位しない状態では、弁機構１７が第２の定圧室
Ｃと第２の作動圧室１）とを連通させるので圧力室Ａ、
Ｂ、 Ｃ，Ｄがすべて同圧に保たれ、第１、第２のピ
ストン５．６は変位しない。With this configuration, when no pedal force is applied to the pedal and the operating rod 12 is not displaced, the valve mechanism 17 connects the second constant pressure chamber C and the second operating pressure chamber 1), so that the pressure chamber A ,
B, C, and D are all kept at the same pressure, and the first and second pistons 5.6 are not displaced.
これに対し、操作杆１５が図の左方に変位する操作時に
は、弁機構１７が第２の定圧室Ｃと第２の作動圧室りと
の連通を断つと共に、第２の作動圧室りに大気を導入す
る。前記したように、第１、第２の定圧室Ａ、Ｃ問およ
び第１、第２の作動圧室Ｂ、Ｄ間は相互に連通している
ので、前記弁機構１７の作動により大気の導入される第
１、第２の作動圧室Ｂ、Ｄと負圧源に連通している第１
、第２の定圧室Ａ、Ｃとの間には圧力差が発生し、この
圧力差によって第１、第２のピストン５．６が変位する
ことになる。この結果、第１゜第２のピストン５．６の
推力を受ける被動杆１２がマスクシリンダを作動させる
。このとき、反カバ披動杆１２、加圧変形部材１８およ
び弁プランジャ１６を介して操作杆１５に伝達される。On the other hand, when the operating rod 15 is displaced to the left in the figure, the valve mechanism 17 cuts off the communication between the second constant pressure chamber C and the second working pressure chamber, and also closes the second working pressure chamber. Introduce the atmosphere into the As mentioned above, since the first and second constant pressure chambers A and C and the first and second working pressure chambers B and D are in communication with each other, the operation of the valve mechanism 17 prevents the introduction of atmospheric air. The first and second working pressure chambers B, D and the first chamber are connected to a negative pressure source.
, and the second constant pressure chambers A and C, and this pressure difference causes the first and second pistons 5.6 to be displaced. As a result, the driven rod 12 receiving the thrust of the first and second pistons 5.6 actuates the mask cylinder. At this time, the force is transmitted to the operating rod 15 via the anti-cover sliding rod 12, the pressurizing deformation member 18, and the valve plunger 16.
しかして、上記構成の気圧倍力装置においては、その入
出力特性が第２図に示すようになる。The input/output characteristics of the air pressure booster having the above configuration are as shown in FIG. 2.
すなわち、入力Ｆｉが一定にて出力Ｆθがジャンプイン
する初期特性（Ａ）と、入力Ｆｉに対して出力Ｆθが所
定の勾配、ｔａｎθで増大する中期特性（１１）と、出
力Ｆθの増大が緩和される終期特性（Ｃ）との３つのｌ
ｉｊ性を有している。こ＼で、初期特性（Ａ）は反力が
操作杆１５に伝達されるまでに発生するもので、具体的
には加圧変形部材１８が弁プランジャ１６とのクリアラ
ンスδだけはみ出すのに必要な出力を表わす。また、中
期特性（ＩＪ）は、反力が弁プランジャ１８ヲ介して操
作杆に伝達している間に発生するもので、その出力Ｆθ
と入力ＦｉＯ比すなわちｔａｎθがいわゆるサーボ比と
なり、具体的には、被動杆１２のフランジ部１３の外径
ｉＤｘ、弁プランジャ１６の先端外径ｉＤ２とすれば、
（Ｄ１／Ｄ２）２ で表わされる。In other words, there is an initial characteristic (A) in which the output Fθ jumps in when the input Fi is constant, a medium-term characteristic (11) in which the output Fθ increases with a predetermined slope, tanθ, with respect to the input Fi, and an increase in the output Fθ is moderated. The three l with the terminal characteristic (C) to be
It has ij characteristics. Here, the initial characteristic (A) occurs before the reaction force is transmitted to the operating rod 15, and specifically, the initial characteristic (A) is the one that occurs before the reaction force is transmitted to the operating rod 15. represents the output. In addition, the medium-term characteristic (IJ) occurs while the reaction force is being transmitted to the operating rod via the valve plunger 18, and its output Fθ
The input FiO ratio, that is, tanθ, becomes the so-called servo ratio. Specifically, if the outer diameter iDx of the flange portion 13 of the driven rod 12 and the outer diameter iD2 of the tip of the valve plunger 16 are:
It is expressed as (D1/D2)2.
しかるに、上記したごとくサーボ比は、被動杆１２のフ
ランジ部１３の外径Ｄ１と弁プランジャ１６の先端外径
Ｄ２の部品寸法だけで一義的に決定し、このため、サー
ボ比を大きくとりたいとしても寸法的に一定の値以上に
設定できず、かつ使用中、サーボ比を任意選択したいと
してもその変更は不可能なものとなっていた。また、ジ
ャンプ・イン特性の変更も前記δの値を変える以外に適
宜手段が無く、さらには、第１、第２のピストンが一体
的連結されているため、強度的に余裕を持った設計がで
きず、総じて、従来の気圧倍力装置は用途すなわち使用
条件に応じて大巾な設計変更をやり直さなければならな
いという制約を有するものであった。However, as mentioned above, the servo ratio is uniquely determined by only the outer diameter D1 of the flange portion 13 of the driven rod 12 and the outer diameter D2 of the tip end of the valve plunger 16. Therefore, if you want to increase the servo ratio, The servo ratio cannot be set above a certain value due to dimensions, and even if one wishes to arbitrarily select the servo ratio during use, it is impossible to change the servo ratio. In addition, there is no other way to change the jump-in characteristics other than changing the value of δ, and furthermore, since the first and second pistons are integrally connected, the design has sufficient strength. Generally speaking, conventional air pressure boosters have been limited in that they require extensive design changes depending on the application, that is, the conditions of use.
（発明の目的）
本発明は上記従来技術の問題点に鑑み大きなサーボ比衾
イ■ることができると共に該サーボ比の任意選択が可能
で、かつジャンプ・イン特性の変更も容易に行うことが
でき、全体として設計余裕を持った気圧倍力装置を提供
することを目的とする。(Object of the Invention) In view of the above-mentioned problems of the prior art, the present invention is capable of greatly increasing the servo ratio, allowing arbitrary selection of the servo ratio, and easily changing the jump-in characteristic. The purpose of the present invention is to provide an air pressure booster that can be used as a whole and has a design margin as a whole.
（発明の構成）
ぞして、この目的は、前方に位置する第１のピストンに
シェル外に突出する第１の被動杆を設け、後方に位置す
る第２のピスト：／に前記第１の被動杆に先端を当接さ
せる第２の被動杆を設け、該第２の被動杆の後端には反
力機構を介して操作杆を連結し、かつ第１の作動圧室と
第１の定圧窓とを連通した状態か第１の作動圧室と第２
の作動圧室とを連通した状態のいづれか一方を選択でき
る弁機構？設けて成る気圧倍力装置によって達成される
。(Structure of the Invention) This object is to provide a first driven rod that protrudes outside the shell on a first piston located at the front, and to provide a first driven rod that protrudes outside the shell on a first piston located at the front, and to attach the first driven rod to a second piston located at the rear. A second driven rod is provided whose tip abuts the driven rod, an operating rod is connected to the rear end of the second driven rod via a reaction force mechanism, and a first working pressure chamber and a first working pressure chamber are connected to each other. Either the first working pressure chamber and the second working pressure chamber are in communication with the constant pressure window.
A valve mechanism that allows you to select either state in communication with the operating pressure chamber? This is achieved by means of a pressure booster provided.
（実施例）
以下、本発明の実施例を添付図面にもとづいて説明する
。(Example) Hereinafter, an example of the present invention will be described based on the accompanying drawings.
第３図は本発明にか＼る気圧倍力装置の構造を示したも
のである。なお、第１図に示した部分と同一構成要素に
は同一符号を付し、その作用の説明は省略する。本実施
例においては、センタープレート８に対し気密を保持し
て摺動できる筒状部材２１が第１のピストン５にのみ固
定されている。一方、推力を伝達する被動杆は、第１の
ピストン５に固鷲された第１の被動杆２２と第２のピス
トン６の収納体１４にフランジ部２３ａを嵌合する第２
の被動杆２３とから成り、第２の被動杆２３の先端を第
１の被動杆２２の後端に設けた凹部２２ａに当接させる
ようにしている。また、従来のものにおける第１と第２
の作動圧室ＢとＤと全連通する通路１１（第１図）が廃
されている。FIG. 3 shows the structure of a pressure booster according to the present invention. Note that the same components as those shown in FIG. 1 are denoted by the same reference numerals, and explanations of their functions will be omitted. In this embodiment, a cylindrical member 21 that can slide on the center plate 8 in an airtight manner is fixed only to the first piston 5. On the other hand, the driven rod that transmits the thrust is a first driven rod 22 fixed to the first piston 5 and a second driven rod whose flange portion 23a is fitted into the storage body 14 of the second piston 6.
The tip of the second driven rod 23 is brought into contact with a recess 22a provided at the rear end of the first driven rod 22. In addition, the first and second
The passage 11 (FIG. 1) that completely communicates with the working pressure chambers B and D has been eliminated.
すなわち、本発明における気圧倍力装置は、シェル内に
、第１のピストン５と第２のピストン６とを独立的に配
置すると共に、該第１のピストン５の後部および第２の
ピストン６の後部には独立的な室Ｈ，Ｃ２画成するよう
にしている。That is, in the air pressure booster according to the present invention, the first piston 5 and the second piston 6 are arranged independently in the shell, and the rear part of the first piston 5 and the second piston 6 are arranged separately. At the rear, independent chambers H and C2 are defined.
しがして、第１の定圧ｉＡと、第１の作動圧室Ｊ３と、
第２の作動圧室りとには、それぞれ第１、第２、第３の
圧力導入口２４．２５．２６が設けられ、外部の切換弁
２７に接続される。切換弁２７は、第１の定圧室Ａと、
氾１の作動圧室Ｂとが連通した状態か、あるいは第１の
作動圧室Ｂと第２の作動圧室りがノル１「６シた状態の
どちらかを任意に選択できる構造になっている。However, the first constant pressure iA and the first working pressure chamber J3,
The second working pressure chamber is provided with first, second, and third pressure inlets 24, 25, and 26, respectively, and is connected to an external switching valve 27. The switching valve 27 has a first constant pressure chamber A,
The structure allows you to arbitrarily select either a state where the first working pressure chamber B and the second working pressure chamber B are in communication, or a state where the first working pressure chamber B and the second working pressure chamber B are connected to each other. There is.
か＼る構成により、いま、切換弁２７が第１の定圧室Ａ
と第１の作動圧室Ｂとを連通した場合において、先ず、
ベグルに踏力が加えられずに操作杆１５が変位１〜ない
状態では、弁機構１７が第２の定圧室Ｃと第２の作動圧
室りとを連通させるので、圧力室Ａ、 Ｂ、 Ｃ，Ｄが
すべて同圧に保たれ、第１、第２のピストン５．６は変
位しない。With this configuration, the switching valve 27 is now connected to the first constant pressure chamber A.
When communicating with the first working pressure chamber B, first,
When no pedal force is applied to the beggle and the operating rod 15 is not displaced from 1 to 1, the valve mechanism 17 connects the second constant pressure chamber C and the second operating pressure chamber, so that the pressure chambers A, B, and C are connected to each other. , D are all kept at the same pressure, and the first and second pistons 5.6 are not displaced.
これに対し、操作杆１５が（図の左方に変位する操作時
には、弁機構１７が第２の定圧室Ｃと第２の作動圧室り
との連通を遮断すると共に、作動圧室りに大気を導入す
る。すなわち、圧力室Ａ。On the other hand, when the operating rod 15 is displaced to the left in the figure, the valve mechanism 17 cuts off the communication between the second constant pressure chamber C and the second working pressure chamber, and Introduce atmosphere, ie pressure chamber A.
Ｂ、 Ｃ，Ｄのうち第２の作動圧室りにのみ大気が導入
するため、第２の定圧室Ｃと第２の作動圧室りとの間に
圧力差が発生し、この圧力差によつ２て第２のピストン
６が変位する結果、第１の被動杆２２が第２のピストン
６の推力を第２の被動杆２３を介して受けてマスクシリ
ンダを作動させる。このとき反力は第１、第２の被動杆
２２．２３、加圧変形部材１８および弁プランジャ１６
ヲ介して操作杆１５に伝達され、したがって、サーボ比
は（Ｄ見／Ｄ２） となる。Since the atmosphere is introduced only into the second working pressure chamber among B, C, and D, a pressure difference occurs between the second constant pressure chamber C and the second working pressure chamber, and this pressure difference As a result of the displacement of the second piston 6, the first driven rod 22 receives the thrust of the second piston 6 via the second driven rod 23, thereby operating the mask cylinder. At this time, the reaction force is applied to the first and second driven rods 22, 23, the pressurizing deformation member 18, and the valve plunger 16.
The signal is transmitted to the operating rod 15 via the servo ratio, so the servo ratio is (D/D2).
次に、切換弁２７により第１の作動圧室Ｂと第２の作動
圧室りとを連通した場合は、操作杆１５を操作すると、
第１、第２の作動圧室１３．Ｄ両方に大気が導入され、
これにより、第１の定圧室Ａと第１の作動圧室Ｂおよび
第２の定圧室Ｃと第２の作動圧室りの両方に圧力差が発
生し、この圧力差によって第１、第２のピストン５．６
が変位する結果、第１の被動杆２２が前記両ピストン５
．６の推力金受けてマスクシリンダを作動させる。この
ときのサーボ比は、いま第１のダイアフラム３と第２の
ダイアフラム４の有効径をそれぞれｄｘ、 ｄ２とする
と、略（（ｄ１２＋ ｄ２”）／ｄ２）（Ｄｉ／Ｄ２
） ＋ １となる。Next, when the first working pressure chamber B and the second working pressure chamber are communicated with each other by the switching valve 27, when the operating rod 15 is operated,
First and second working pressure chambers 13. D Atmosphere is introduced into both,
As a result, a pressure difference is generated between the first constant pressure chamber A and the first working pressure chamber B, and between the second constant pressure chamber C and the second working pressure chamber, and this pressure difference causes a pressure difference between the first and second working pressure chambers. piston 5.6
As a result of the displacement, the first driven rod 22 moves toward both pistons 5.
．． The mask cylinder is operated by receiving the thrust of step 6. The servo ratio at this time is approximately ((d12+d2'')/d2)(Di/D2), where the effective diameters of the first diaphragm 3 and the second diaphragm 4 are dx and d2, respectively.
) +1.
第４図は、本気圧倍力装置の入出力特性を示したもので
、図中、Ｐ ｔｉｌｌ線は第１の定圧室Ａと４′Ｖ１の
作動圧室Ｂとを連通した場合、へ曲線は第１の作動圧室
Ｂと第２の作動圧室りとを連通した場合の結果を表わし
ている。これより、本気圧倍力装置道においてはサーボ
比を２段に切換λ−ることか可能となり、しかも、従来
にも増して旨いサーボ比ヲ得ることも可能となっている
。Figure 4 shows the input/output characteristics of this pressure booster. represents the result when the first working pressure chamber B and the second working pressure chamber are communicated with each other. As a result, in this pressure booster, it is possible to switch the servo ratio in two stages, and it is also possible to obtain a better servo ratio than before.
才た、本気圧倍力装置においては、リターンスプリング
１９の荷重が第１、第２の被動杆２２．２３を介して加
圧変形部材１８に作用するようになっているため、ジャ
ンプ・イン特性Ａは、前記リターンスプリング１９の設
定荷＠を変えれば、容易に変更できるものとなる。In this pressure booster, the load of the return spring 19 acts on the pressurized deformable member 18 via the first and second driven rods 22 and 23, so that the jump-in characteristic is improved. A can be easily changed by changing the set load of the return spring 19.
設し、これに：ｌｌ１４宜弁機構を設けて、前記のごと
き切換え動作ができるようにしても良い。A switching operation as described above may be performed by providing a switching mechanism.
また、上記実施例においては、２ピストンタイプについ
て説明ｌ−タが、より多数のピストンを有するものに適
用できることはもちろんである。Further, in the above embodiments, the two-piston type is described, but it goes without saying that it can be applied to a type having a larger number of pistons.
さらに、例えば第１の作動圧室Ｂｌ独立して設け、これ
への人伝の導入をコントロールすることによって、サー
ボ比を連続的に変更することも可能となる。Furthermore, for example, by independently providing the first working pressure chamber Bl and controlling the introduction of the pressure into it, it is also possible to continuously change the servo ratio.
（発明の効果）
以上、詳細に説明したように、本発明Ｋか＼る気圧倍力
装置は、シェル内に２つのピストンを直列に独立して配
置し、かつシェル内に画成された圧力室を任童切倹えで
きるようにしたもので、これにより、以下に記すような
効果が得られた。(Effects of the Invention) As explained above in detail, the air pressure booster according to the present invention has two pistons arranged independently in series in a shell, and a pressure booster defined in the shell. This made it possible to save the room, and as a result, the following effects were obtained.
■ 従来の気圧発生装置のように、２つのピストンの締
結部が無いため、強度的に余裕を持った設計が可能であ
る。■ Unlike conventional air pressure generators, there is no connecting part between the two pistons, so it is possible to design with sufficient strength.
■ サーボ比を手動あるいは自動的に変更でき、ｆた、
従来より大きいサーボ比を得ることができる。したがっ
て、例えば荷物積載車両において空荷時と積載時Ａとで
同じ減速度が得られるようにすることができる。■ You can change the servo ratio manually or automatically,
A larger servo ratio than before can be obtained. Therefore, for example, in a loaded vehicle, the same deceleration can be obtained when the vehicle is unladen and when it is loaded.
■ ジャンプ・イン特性をターンスプリングの設定荷重
の変更により容易に変えることができる。■ Jump-in characteristics can be easily changed by changing the set load of the turn spring.
第１図は従来の気圧倍力装置の構造を示す断面図、第２
図は従来の気圧倍力装置の入出力特性を示す相関図、第
３図は本発明にか＼る気圧倍力装置の構造を示す断面図
、第４図は本気圧倍力装置の入出力特性を示す相関図で
ある。
１ ・・・・・・前方シェル
２ ・・・・・・後方シェル
３．４ ・・・ダイアフラム
５ ・−・・・・第１のピストン
６ ・・・・・・第２のピストン
８ ・・・・・・センタープレート （隔壁）１５・・
・・・・操作杆
１６・・・・・１・・…弁プランジャ
１８・・・・・・・・・・・・加圧変形部材１９・・・
・・・・・・・・・ターンスフリング２２・・・・・・
・・・・・・第１の被動杆２３・・・・・・・・・・・
・第２の被動杆２４、２５．２６・・・圧力導入口
２７・・・・・・・・・・・・切換弁
特許出願人 トキコ株式会社
イＡFigure 1 is a sectional view showing the structure of a conventional pressure booster;
The figure is a correlation diagram showing the input/output characteristics of a conventional air pressure booster, Figure 3 is a sectional view showing the structure of the air pressure booster according to the present invention, and Figure 4 is the input/output of this air pressure booster. It is a correlation diagram showing characteristics. 1...Front shell 2...Back shell 3.4...Diaphragm 5...First piston 6...Second piston 8... ...Center plate (bulkhead) 15...
......Operating rod 16...1...Valve plunger 18......Press deformation member 19...
......Turnsfring 22...
・・・・・・First driven rod 23・・・・・・・・・・・・
・Second driven rod 24, 25.26...Pressure inlet 27...Switching valve patent applicant Tokico Co., Ltd. IA
Claims (1)
に取付けられｆｃ２つのピストンと、該２つのピストン
間に装着された隔壁と、により４つの圧力室全画成して
成る気圧倍力装置において、前方に位置する第１のピス
トンにシェル外に突出するＷＪｌの被動杆を設け、後方
に位置する第２のピストンに前記第１の被動杆に先端を
当接させる第２の被動杆を設け、該第２の被動杆の後端
には反力機構を介して操作杆を連結し、前記第１、第２
のピストン′！ｉｌ−戻り位置に付勢する付勢手段を設
け、かつ前記第１のピストンの後部１則の第１の作動圧
室と前記第１のピストンの前部側の第１の定圧室とが連
通した状態か前記第１の作動圧室と第２のピストンの後
部側の第２の作動圧室とが連通した状態のｂづれか一方
を選択できる切換弁機構を設けたことを特徴とする気圧
倍力装置。(1) In an air pressure booster comprising four pressure chambers all defined in a shell by a diaphragm, two fc pistons attached to the diaphragm, and a partition installed between the two pistons, the front A first piston located at is provided with a WJl driven rod that protrudes outside the shell, a second piston located at the rear is provided with a second driven rod whose tip abuts the first driven rod, An operating rod is connected to the rear end of the second driven rod via a reaction force mechanism, and
's piston'! il- A biasing means for biasing the first piston to the return position is provided, and a first working pressure chamber in the rear part of the first piston and a first constant pressure chamber on the front side of the first piston communicate with each other. or a state in which the first working pressure chamber and the second working pressure chamber on the rear side of the second piston communicate with each other. booster.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58132474A JPS6025839A (en) | 1983-07-20 | 1983-07-20 | Pneumatic booster |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58132474A JPS6025839A (en) | 1983-07-20 | 1983-07-20 | Pneumatic booster |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6025839A true JPS6025839A (en) | 1985-02-08 |
| JPH038982B2 JPH038982B2 (en) | 1991-02-07 |
Family
ID=15082216
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58132474A Granted JPS6025839A (en) | 1983-07-20 | 1983-07-20 | Pneumatic booster |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6025839A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60166553A (en) * | 1983-11-07 | 1985-08-29 | Jidosha Kiki Co Ltd | Booster device for tandem brake |
| US6446537B1 (en) | 1999-09-30 | 2002-09-10 | Aisin Seiki Kabushiki Kaisha | Vacuum brake booster |
| US6554374B1 (en) | 1999-05-12 | 2003-04-29 | ZF Lemförder Metallwaren AG | Tandem brake booster for automobiles |
-
1983
- 1983-07-20 JP JP58132474A patent/JPS6025839A/en active Granted
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60166553A (en) * | 1983-11-07 | 1985-08-29 | Jidosha Kiki Co Ltd | Booster device for tandem brake |
| US6554374B1 (en) | 1999-05-12 | 2003-04-29 | ZF Lemförder Metallwaren AG | Tandem brake booster for automobiles |
| US6446537B1 (en) | 1999-09-30 | 2002-09-10 | Aisin Seiki Kabushiki Kaisha | Vacuum brake booster |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH038982B2 (en) | 1991-02-07 |
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