JPH043902Y2 - - Google Patents
Info
- Publication number
- JPH043902Y2 JPH043902Y2 JP1985198839U JP19883985U JPH043902Y2 JP H043902 Y2 JPH043902 Y2 JP H043902Y2 JP 1985198839 U JP1985198839 U JP 1985198839U JP 19883985 U JP19883985 U JP 19883985U JP H043902 Y2 JPH043902 Y2 JP H043902Y2
- Authority
- JP
- Japan
- Prior art keywords
- booster
- booster piston
- disk portion
- working chamber
- connecting plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000002093 peripheral effect Effects 0.000 claims description 26
- 239000011324 bead Substances 0.000 claims description 20
- 229910000831 Steel Inorganic materials 0.000 description 5
- 239000010959 steel Substances 0.000 description 5
- 238000003466 welding Methods 0.000 description 4
- 238000007789 sealing Methods 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 229920003002 synthetic resin Polymers 0.000 description 2
- 239000000057 synthetic resin Substances 0.000 description 2
- 210000000078 claw Anatomy 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000006116 polymerization reaction Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Landscapes
- Braking Systems And Boosters (AREA)
Description
【考案の詳細な説明】
Ａ 考案の目的
(1) 産業上の利用分野
本考案は、主として自動車のブレーキマスタシ
リンダを負圧力を以て倍力作動する負圧式倍力装
置、特にブースタシエルの内部を、それに前後往
復動自在に収容したブースタピストンと、該ブー
スタピストンの後面に重合して内周ビードを該ブ
ースタピストンに結着すると共に外周ビードを前
記ブースタシエルの周壁に結着したダイヤフラム
とにより、負圧源に連なる前部の第１作動室と、
入力部材に連動する制御弁を介して前記第１作動
室または大気に選択的に連通される後部の第２作
動室とに区画し、前記ブースタピストンを円板部
と該円板部の中心に貫通するボス部により構成
し、該ボス部と一体の連結フランジの後面に前記
円板部の前面を、また前記連結フランジの前面に
連結板の後面をそれぞれ重合して、前記連結フラ
ンジの外周縁近傍で前記円板部と前記連結板とを
重合結合したものの改良に関する。[Detailed description of the invention] A. Purpose of the invention (1) Industrial application field The present invention mainly uses a negative pressure booster that boosts the brake master cylinder of an automobile with negative pressure, especially the inside of the booster shell. A booster piston is housed in the booster piston so as to be able to reciprocate back and forth, and a diaphragm overlaps the rear surface of the booster piston to connect the inner peripheral bead to the booster piston and the outer peripheral bead to the peripheral wall of the booster shell. a first working chamber at the front connected to the pressure source;
partitioned into the first working chamber or a second working chamber at the rear which is selectively communicated with the atmosphere through a control valve interlocked with an input member, and the booster piston is located between a disk portion and the center of the disk portion. The outer peripheral edge of the connecting flange is formed by a penetrating boss portion, and the front surface of the disc portion is superimposed on the rear surface of the connecting flange that is integrated with the boss portion, and the rear surface of the connecting plate is overlapped with the front surface of the connecting flange. The present invention relates to an improvement in a structure in which the disk portion and the connecting plate are polymerized and bonded in the vicinity.
(2) 従来の技術
従来、ブースタピストンの円板部は薄肉鋼板よ
り構成されているので、第１および第２作動室間
に生じる気圧差が大きい場合、連結板との重合結
合部を支点とした円板部の第１作動室側への撓み
量が多くなるが、従来の負圧式倍力装置は円板部
の撓みを防止する手段を備えていない。(2) Conventional technology Conventionally, the disc part of the booster piston is made of a thin steel plate, so when the pressure difference between the first and second working chambers is large, the disc part of the booster piston is made of a thin steel plate. However, the conventional negative pressure booster does not have a means for preventing the disc from deflecting.
(3) 考案が解決しようとする問題点
そのため過大な撓み量に起因して円板部の重合
結合部に永久歪が発生するおそれがある。(3) Problems to be solved by the invention Therefore, there is a risk that permanent strain will occur in the overlapping joint of the disc part due to the excessive amount of deflection.
また斯かる問題を解決すべく、例えば円板部と
連結板との重合結合部を径方向外方へ偏位させて
円板部の撓みを極力抑えることが考えられるが、
その場合には、該重合連結部が上記連結フランジ
外周縁より径方向外方に離れてしまい、円板部及
び連結板間での該連結フランジの挟持が的確には
行い得なくなる問題がある。 In addition, in order to solve this problem, it is conceivable to suppress the deflection of the disc part as much as possible by, for example, deviating the overlapping joint between the disc part and the connecting plate radially outward.
In that case, there is a problem in that the overlapping connecting portion is separated radially outward from the outer peripheral edge of the connecting flange, and the connecting flange cannot be accurately held between the disk portion and the connecting plate.
本考案は前記に鑑み提案されたもので、円板部
と連結板との重合結合部を連結フランジの外周縁
近傍に設置しながらも、極めて簡単な手段により
円板部の前記撓みを極力抑え得るようにして、前
記問題を一挙に解決した前記負圧式倍力装置を提
供することを目的とする。 The present invention was proposed in view of the above, and while the overlapping joint between the disc part and the connecting plate is installed near the outer peripheral edge of the connecting flange, the above-mentioned deflection of the disc part is suppressed as much as possible by extremely simple means. It is an object of the present invention to provide the negative pressure booster which solves the above problems at once.
Ｂ 考案の構成
(1) 問題点を解決するための手段
上記目的を達成するために本考案によれば、第
１および第２作動室間に生じる気圧差に伴うブー
スタピストン円板部の撓みを防止すべく、連結板
は、それと前記円板部との重合結合部より半径方
向外方へ延出して前記円板部前面に衝合する環状
支承部を備え、その環状支承部の前記円板部に対
する衝合面は、横断面が該円板部側に凸の円弧状
に形成される。B. Structure of the device (1) Means for solving the problem In order to achieve the above object, the present invention solves the deflection of the booster piston disc due to the pressure difference occurring between the first and second working chambers. In order to prevent this, the connecting plate includes an annular bearing portion that extends radially outward from the overlapping joint between the connecting plate and the disc portion and abuts against the front surface of the disc portion, and the connecting plate includes an annular bearing portion that abuts against the front surface of the disc portion. The abutment surface with respect to the disk portion has a cross section formed in the shape of an arc convex toward the disk portion.
(2) 作用
円板部及び連結板間での連結フランジの挟持を
的確に行わせるべく前記重合結合部を連結フラン
ジ外周縁近傍へ設置しても、その重合結合部より
半径方向外方に離間した位置で円板部前面を上記
環状支承部に支承させることができるから、その
重合結合部を支点とした円板部の撓みが抑制され
る。(2) Effect Even if the overlapping joint is installed near the outer periphery of the connecting flange in order to accurately hold the connecting flange between the disc portion and the connecting plate, the overlapping joint may be spaced radially outward from the overlapping joint. Since the front surface of the disk portion can be supported by the annular support portion at this position, the bending of the disk portion about the overlapping joint portion as a fulcrum is suppressed.
また環状支承部の円板部に対する衝合面が上記
のように円弧面に形成されるので、円板部が環状
支承部を支点として多少とも撓み変形する際には
上記円弧面に沿つて変形し、環状支承部による円
板部の支承面積が増大して円板部における応力集
中が抑制される。 In addition, since the abutting surface of the annular support against the disc part is formed into an arcuate surface as described above, when the disc part bends and deforms to some extent using the annular support part as a fulcrum, it deforms along the arcuate surface. However, the supporting area of the disk portion by the annular support portion increases, and stress concentration in the disk portion is suppressed.
(3)実施例
第１図においてＷは自動車のエンジンルーム後
側壁を構成する支持壁で、その前面にブレーキ用
マスタシリンダＭを前端に結合した負圧式倍力装
置Ｓが取付けられる。(3) Embodiment In FIG. 1, reference numeral W denotes a support wall constituting the rear side wall of an engine room of an automobile, and a negative pressure booster S having a brake master cylinder M coupled to its front end is attached to the front surface of the support wall.
倍力装置Ｓのブースタシエル１は軸方向に分割
された前部シエル１Ａ及び後部シエル１Ｂとより
構成され、これらは薄肉鋼板または合成樹脂より
成形されている。このブースタシエル１内に前後
往復動自在に収容されたブースタピストン２は薄
肉鋼板製円板部２ａと、その円板部２ａの中心を
貫通する合成樹脂製ボス部２ｂとより構成され、
その円板部２ａの後面に弾性を有するローリング
型ゴム製ダイヤフラム７が重合されている。この
ダイヤフラム７の内周ビード７ａは、円板部２ａ
の内周端に結着されると共にボス部２ｂの外周に
気密に嵌合され、一方、外周ビード７ｂは前、後
部シエル１Ａ，１Ｂの突合わせ端部に結着され
る。 The booster shell 1 of the booster S is composed of a front shell 1A and a rear shell 1B that are divided in the axial direction, and these are molded from a thin steel plate or synthetic resin. The booster piston 2, which is housed in the booster shell 1 so as to be able to reciprocate back and forth, is composed of a thin-walled steel disk portion 2a and a synthetic resin boss portion 2b passing through the center of the disk portion 2a.
An elastic rolling rubber diaphragm 7 is superimposed on the rear surface of the disc portion 2a. The inner peripheral bead 7a of this diaphragm 7 is a disc portion 2a.
The outer peripheral bead 7b is connected to the inner peripheral end of the boss portion 2b and hermetically fitted to the outer peripheral edge of the boss portion 2b, while the outer peripheral bead 7b is connected to the abutting ends of the front and rear shells 1A and 1B.
上記ブースタピストン２及びダイヤフラム７は
ブースタシエル１内部を前部の第１作動室Ａと後
部の第２作動室Ｂとに区画し、第１作動室Ａは負
圧導入管８を介して負圧源たる機関の吸気マニホ
ールド（図示せず）内と常時連通し、また第２作
動室Ｂは、入力部材としての入力杆９の前、後動
により操作される図示しない制御弁により第１作
動室Ａまたは大気との連通を交互に切り換えられ
るようになつている。而して、第１作動室Ａが負
圧を蓄えているとき、ブレーキペダル１０の操作
により入力杆９を前進させて第２作動室Ｂを大気
に連通すれば、両作動室Ａ，Ｂ間に生じる気圧差
によりブースタピストン２に推力が与えられ、こ
のブースタピストン２の前進により出力杆１１を
介してマスタシリンダＭの作動ピストン１２を前
方に駆動することができる。 The booster piston 2 and the diaphragm 7 divide the inside of the booster shell 1 into a first working chamber A at the front and a second working chamber B at the rear, and the first working chamber A receives negative pressure through a negative pressure introduction pipe 8. The second working chamber B is always in communication with the intake manifold (not shown) of the engine which is the source, and the second working chamber B is connected to the first working chamber by a control valve (not shown) operated by the front and rear movement of the input rod 9 as an input member. Communication with A or the atmosphere can be switched alternately. Therefore, when the first working chamber A stores negative pressure, if the input rod 9 is advanced by operating the brake pedal 10 and the second working chamber B is communicated with the atmosphere, the gap between the two working chambers A and B is increased. A thrust is applied to the booster piston 2 due to the pressure difference generated between the two, and the forward movement of the booster piston 2 can drive the working piston 12 of the master cylinder M forward via the output rod 11.
前記ブースタピストン２において、その円板部
２ａはボス部２ｂと一体の連結フランジ３の後面
に重合され、また薄肉鋼板製連結板６の後面が連
結フランジ３の前面に重合される。円板部２ａに
おいて連結フランジ３の外周縁近傍には、前方へ
突出する４個の重合座４２（第２図参照）が円周
上等間隔にプレス成形され、各重合座４２にねじ
部を前方に突出させた溶接ボルト４が設けられ
る。連結板６に各溶接ボルト４に対応してねじ挿
通孔４３が形成され、各ねじ挿通孔４３に各溶接
ボルト４を挿通させて各溶接ボルト４に座金４４
を介してナツト５を螺着すると、円板部２ａと連
結板６とが重合結合され、それら２ａ，６により
連結フランジ３が強く挟着される。これにより円
板部２ａとボス部２ｂとが強固に連結される。 In the booster piston 2, the disk portion 2a is superimposed on the rear surface of the connecting flange 3 integral with the boss portion 2b, and the rear surface of the thin steel plate connecting plate 6 is overlapped on the front surface of the connecting flange 3. In the disk portion 2a, near the outer peripheral edge of the connecting flange 3, four overlapping seats 42 (see Fig. 2) projecting forward are press-molded at equal intervals on the circumference, and each overlapping seat 42 has a threaded portion. A welding bolt 4 is provided that projects forward. A screw insertion hole 43 is formed in the connecting plate 6 to correspond to each welding bolt 4, and each welding bolt 4 is inserted into each screw insertion hole 43, and a washer 44 is attached to each welding bolt 4.
When the nut 5 is screwed in through the nut 5, the disc portion 2a and the connecting plate 6 are polymerized and bonded, and the connecting flange 3 is tightly sandwiched between the disk portion 2a and the connecting plate 6. Thereby, the disk portion 2a and the boss portion 2b are firmly connected.
連結板６は、それと円板部２ａとの重合結合部
ｄより半径方向外方に延出する環状支承部６ａを
備え、その支承部６ａの外周縁は後方へ突出する
横断面略半円状をなす環状突条４５に形成され
る。 The connecting plate 6 includes an annular bearing part 6a extending radially outward from the overlapping joint part d between the connecting plate 6 and the disk part 2a, and the outer peripheral edge of the bearing part 6a has a substantially semicircular cross section projecting rearward. It is formed into an annular protrusion 45 having a shape.
円板部２ａと連結板６との重合結合状態下にて
支承部６ａの突条４５後面が円板部２ａの前面に
当接し、前記支承部６ａにより、第１および第２
作動室Ａ，Ｂ間に生じる気圧差に伴う重合結合部
ｄを支点とした円板部２ａの第１作動室Ａ側への
撓みが防止される。 When the disk portion 2a and the connecting plate 6 are in an overlapping state, the rear surface of the protrusion 45 of the support portion 6a comes into contact with the front surface of the disk portion 2a, and the support portion 6a allows the first and second
This prevents the disk portion 2a from deflecting toward the first working chamber A using the overlapping joint portion d as a fulcrum due to the pressure difference occurring between the working chambers A and B.
前、後部シエル１Ａ，１Ｂの各端壁、ブースタ
ピストン２における円板部２ａの透孔１３及びダ
イヤフラム７の透孔１４を、それらの中心軸線を
挟んでそれと平行に延びる２本のタイロツド１５
（第１図には１本のみ示す。）が貫通する。 Two tie rods 15 extend parallel to each end wall of the front and rear shells 1A, 1B, the through hole 13 of the disk portion 2a of the booster piston 2, and the through hole 14 of the diaphragm 7 with their central axes interposed therebetween.
(Only one is shown in FIG. 1) penetrates.
後部シエル１Ｂの端壁内面には、タイロツド１
５に貫通される支筒１６が溶接され、これにタイ
ロツド１５外周に一体に突設した段付フランジ１
７が嵌入される。その際、段付フランジ１７、支
筒１６及び後部シエル１Ｂの端壁により画成され
る環状ハウジング１８に、後部シエル１Ｂのタイ
ロツド貫通孔１９を封緘するシール部材２０が嵌
装される。このシール部材２０と協働して段付フ
ランジ１７の大径部を挟持する止環２１が支筒１
６の内周壁に係止される。かくして、タイロツド
１５は後部シエル１Ｂの端壁に固着される。 Tie rod 1 is installed on the inner surface of the end wall of rear shell 1B.
A support tube 16 is welded to the tie rod 15, and a stepped flange 1 integrally protrudes from the outer circumference of the tie rod 15.
7 is inserted. At this time, a sealing member 20 for sealing the tie rod through hole 19 of the rear shell 1B is fitted into the annular housing 18 defined by the stepped flange 17, the support tube 16, and the end wall of the rear shell 1B. A stop ring 21 that cooperates with this seal member 20 to clamp the large diameter portion of the stepped flange 17 is attached to the support tube 1.
It is locked to the inner circumferential wall of 6. Thus, the tie rod 15 is fixed to the end wall of the rear shell 1B.
前部シエル１Ａの端壁内面には挟持板２２が重
合され、これによりブースタピストン２を後退方
向に弾発する戻しばね２３の固定端が支承され
る。この挟持板２２の両端には一対のボス２４
（第１図には１個のみ示す。）が一体が形成されて
おり、これらのボス２４に２本のタイロツド１５
が貫通して挟持板２２の回り止めをなしている。
また、ボス２４の内側端面には欠円状凹孔２５が
設けられており、これにタイロツド１５上の欠円
状フランジ２６が嵌合してそのタイロツド１５の
回り止めをなしている。さらに、ボス２４の外側
端面にはシールハウジング２７が凹設されてお
り、このハウジング２７に前部シエル１Ａのタイ
ロツド貫通孔２８を封緘するシール部材２９が嵌
着される。 A clamping plate 22 is superimposed on the inner surface of the end wall of the front shell 1A, and supports a fixed end of a return spring 23 that urges the booster piston 2 in the backward direction. A pair of bosses 24 are provided at both ends of this clamping plate 22.
(Only one is shown in FIG. 1) are integrally formed, and two tie rods 15 are attached to these bosses 24.
is passed through to prevent the holding plate 22 from rotating.
Further, a notched circular concave hole 25 is provided on the inner end surface of the boss 24, into which a notched circular flange 26 on the tie rod 15 is fitted to prevent the tie rod 15 from rotating. Furthermore, a seal housing 27 is recessed in the outer end surface of the boss 24, and a seal member 29 that seals the tie rod through hole 28 of the front shell 1A is fitted into the housing 27.
タイロツド１５はブースタシエル１の前後に突
出する両端部をボルト１５ａ，１５ｂに形成され
ており、前部のボルト１５ａの基部に前部シエル
１Ａの抜け止め用サークリツプ３０が係止され
る。このボルト１５ａはマスタシリンダＭのシリ
ンダ本体３１後端に形成した取付フランジ３２を
貫通してその先端にナツト３３が螺合され、これ
によりマスタシリンダＭは、タイロツド１５を介
してブースタシエル１の前面に取付けられると共
に、挟持板２２と協働して前部シエル１Ａの端壁
を挟持補強する。かくして、前、後部シエル１
Ａ，１Ｂはタイロツド１５を介して一体に結合さ
れる。 The tie rod 15 is formed with bolts 15a and 15b at both ends projecting forward and backward of the booster shell 1, and a circlip 30 for preventing the front shell 1A from coming off is locked at the base of the front bolt 15a. This bolt 15a passes through a mounting flange 32 formed at the rear end of the cylinder body 31 of the master cylinder M, and a nut 33 is screwed onto its tip. At the same time, it cooperates with the clamping plate 22 to clamp and reinforce the end wall of the front shell 1A. Thus, front and rear shell 1
A and 1B are integrally connected via a tie rod 15.
また、後部のボルト１５ｂは支持壁Ｗを貫通し
てその先端にナツト３４を螺合され、これにより
ブースタシエル１はタイロツド１５を介して支持
壁Ｗに固着される。 Further, the rear bolt 15b passes through the support wall W and has a nut 34 screwed onto its tip, thereby fixing the booster shell 1 to the support wall W via the tie rod 15.
タイロツド１５に貫通されるブースタピストン
２の透孔１３の周辺には次のようなシール手段が
施される。 The following sealing means is provided around the through hole 13 of the booster piston 2 that is penetrated by the tie rod 15.
第５図に明示するようにブースタピストン２の
透孔１３には筒体３５が設けられる。その筒体３
５は大径部３５ａとそれに連設され、透孔１３を
囲繞する小径部３５ｂとよりなり、その大径部３
５ａの口縁に抜止めフランジ３６が一体に設けら
れる。筒体３５は、大径部３５ａを第２作動室Ｂ
側に突出させ、また小径部３５ｂを透孔１３に貫
通させて配設され、両部３５ａ，３５ｂ間の段部
３５ｃがブースタピストン２の透孔周辺部に溶着
される。第２図に明示するように抜止めフランジ
３６は、その外周の一部に大径部３５ａの外周の
一部が内接すると共にその内接部ａから大径部３
５ａの外周に沿つてその大径部３５ａ外周からの
突出量が漸増するような形状を有し、筒体３５は
それをブースタピストン２に溶着する際内接部ａ
がダイヤフラム７の内周ビード７ａ側に位置する
ように配設される。 As clearly shown in FIG. 5, a cylindrical body 35 is provided in the through hole 13 of the booster piston 2. The cylinder body 3
5 consists of a large diameter part 35a and a small diameter part 35b connected thereto and surrounding the through hole 13, and the large diameter part 3
A retaining flange 36 is integrally provided on the edge of 5a. The cylinder body 35 has a large diameter portion 35a as a second working chamber B.
The small diameter portion 35b is arranged to protrude to the side and pass through the through hole 13, and a stepped portion 35c between both portions 35a and 35b is welded to the peripheral portion of the through hole of the booster piston 2. As clearly shown in FIG. 2, the retaining flange 36 has a part of its outer periphery inscribed with a part of the outer periphery of the large diameter part 35a, and extends from the inscribed part a to the large diameter part 35a.
The cylindrical body 35 has a shape such that the amount of protrusion from the outer periphery of the large diameter portion 35a gradually increases along the outer periphery of the cylindrical body 35, and when it is welded to the booster piston 2, the inner part a
is arranged so as to be located on the inner peripheral bead 7a side of the diaphragm 7.
タイロツド１５は第１作動室Ａにおいて、蛇腹
状の伸縮性ブーツ３７に囲繞され、このブーツ３
７の前端部３７ａがタイロツド１５外周に、また
その厚肉の後端部３７ｂが筒体３５の小径部３５
ｂ外周にそれぞれ気密に嵌着される。したがつ
て、ブーツ３７はその伸縮性によりブースタピス
トン２の前後動を妨げることなく筒体３５内、し
たがつて透孔１３を封緘することができる。 The tie rod 15 is surrounded by a bellows-shaped elastic boot 37 in the first working chamber A.
The front end 37a of 7 is connected to the outer periphery of the tie rod 15, and the thick rear end 37b is connected to the small diameter portion 35 of the cylinder 35.
b are hermetically fitted to the outer periphery of each. Therefore, the boot 37 can seal the inside of the cylinder 35 and therefore the through hole 13 without interfering with the back and forth movement of the booster piston 2 due to its elasticity.
またタイロツド１５に貫通されるダイヤフラム
７の透孔周辺部７ｃは厚肉に形成され、その透孔
１４は筒体３５の大径部３５ａ外周に気密に嵌合
される。これにより透孔周辺部７ｃの内周ビード
近傍部分ｂを除く外周ビード側ｃが抜止めフラン
ジ３６と円板部２ａ間に挟着され、また内周ビー
ド近傍部分ｂはマニユアル作動時に排気弁として
機能し得るように解放状態に保持される。 Further, the peripheral portion 7c of the through hole of the diaphragm 7 penetrated by the tie rod 15 is formed thick, and the through hole 14 is hermetically fitted to the outer periphery of the large diameter portion 35a of the cylindrical body 35. As a result, the outer bead side c of the through-hole peripheral portion 7c, excluding the inner bead vicinity portion b, is sandwiched between the retaining flange 36 and the disc portion 2a, and the inner bead vicinity portion b functions as an exhaust valve during manual operation. It is kept open so that it can function.
ブースタピストン２の透孔１３及びダイヤフラ
ム７の透孔１４は筒体３５を介してタイロツド１
５と同心上に配置される。またブースタシエル１
における前、後部シエル１Ａ，１Ｂは、第１、第
３図に示すように前部シエル１Ａ及び後部シエル
１Ｂの連接端部に設けられた互いに係合する切欠
３８及び爪３９により位置決めされ、さらにブー
スタシエル１とダイヤフラム７は第１、第４図に
示すように後部シエル１Ｂ及びダイヤフラム７の
外周ビード７ｂの連接部に設けられた互いに係合
する切欠４０及び突起４１により位置決めされ
る。 The through hole 13 of the booster piston 2 and the through hole 14 of the diaphragm 7 are connected to the tie rod 1 through the cylindrical body 35.
It is placed concentrically with 5. Also Booster Ciel 1
The front and rear shells 1A and 1B are positioned by mutually engaging notches 38 and claws 39 provided at the connecting ends of the front shell 1A and rear shell 1B, as shown in FIGS. 1 and 3, and As shown in FIGS. 1 and 4, the booster shell 1 and the diaphragm 7 are positioned by a notch 40 and a protrusion 41 that engage with each other, which are provided at the joint between the rear shell 1B and the outer peripheral bead 7b of the diaphragm 7.
上記構成において、第１作動室Ａに高い負圧が
蓄えられたとき、その負圧による大なる吸引力が
前部シエル１Ａの特に剛性の弱い端壁に作用して
も、その吸引力は挟持板２２及びタイロツド１５
を介して支持壁Ｗに伝達して支承され、しかも、
前部シエル１Ａの端壁は、挟持板２２及びマスタ
シリンダＭの取付フランジ３２に挟持されて補強
されているから、内方への変形を生じることはな
い。また、挟持板２２は、戻しばね２３の固定端
を支承しているので、戻しばね２３の弾発力をも
タイロツド１５に伝達して前部シエル１Ａには負
担させない。 In the above configuration, when a high negative pressure is accumulated in the first working chamber A, even if a large suction force due to the negative pressure acts on the particularly weak end wall of the front shell 1A, the suction force is Plate 22 and tie rod 15
is transmitted to and supported by the support wall W via the
The end wall of the front shell 1A is held and reinforced by the holding plate 22 and the mounting flange 32 of the master cylinder M, so that no inward deformation occurs. Further, since the clamping plate 22 supports the fixed end of the return spring 23, the elastic force of the return spring 23 is also transmitted to the tie rod 15, so that the front shell 1A is not burdened with it.
ブレーキペダル１０による入力杆９の前進操作
により第２作動室Ｂを大気に連通して両作動室
Ａ，Ｂ間に生じる気圧差によつてブースタピスト
ン２が前進すれば、マスタシリンダＭの作動ピス
トン１２を前方に押動して図示しない油圧室に油
圧を発生し、これにより車輪ブレーキを作動させ
る。このとき、作動ピストン１２の前方押圧力は
上記油圧を介してマスタシリンダＭのシリンダ本
体３１に前向きのスラスト荷重として作用する
が、この荷重は取付フランジ３２及びタイロツド
１５を介して支持壁Ｗに伝達して支承される。し
たがつてブースタシエル１には上記荷重を負担さ
せず、その荷重によるブースタシエル１の変形が
防止される。 When the input rod 9 is operated forward by the brake pedal 10, the second working chamber B is communicated with the atmosphere and the booster piston 2 moves forward due to the pressure difference generated between the two working chambers A and B. 12 is pushed forward to generate hydraulic pressure in a hydraulic chamber (not shown), thereby operating the wheel brakes. At this time, the forward pressing force of the actuating piston 12 acts as a forward thrust load on the cylinder body 31 of the master cylinder M via the above-mentioned hydraulic pressure, but this load is transmitted to the support wall W via the mounting flange 32 and tie rod 15. will be supported. Therefore, the booster shell 1 is not burdened with the above load, and deformation of the booster shell 1 due to the load is prevented.
また入力杆９による高入力に起因して両作動室
Ａ，Ｂ間に生じる気圧差が大きいときには、円板
部２ａに第１作動室Ａ側への大きな押圧力が作用
するが、重合結合部ｄよりも半径方向外方におい
て、円板部２ａは支承部６ａにより支承されてい
るので、円板部２ａが重合結合部ｄを支点として
撓みことがなく、したがつて円板部２ａの重合結
合部における永久歪の発生が防止される。 Furthermore, when there is a large pressure difference between the working chambers A and B due to a high input from the input rod 9, a large pressing force acts on the disc portion 2a toward the first working chamber A, but the overlapped joint Since the disc part 2a is supported by the support part 6a in the radial direction outward from d, the disc part 2a does not bend about the overlapping joint part d as a fulcrum, so that the overlapping of the disc part 2a is prevented. Permanent deformation at the joint is prevented.
また円板部２ａにおける環状突条４５の半径方
向外方部分が第１作動室Ａ側へ撓んだ場合には、
突条４５の外周面が円弧面になつている関係で該
円板部２ａの半径方向外方部分が上記円弧面に沿
つて変形し、環状支承部６ａによる円板部２ａの
支承面積が増大して円板部２ａにおける応力集中
が抑制される。 Further, when the radially outward portion of the annular protrusion 45 in the disc portion 2a is bent toward the first working chamber A,
Since the outer circumferential surface of the protrusion 45 is an arcuate surface, the radially outer portion of the disc portion 2a deforms along the arcuate surface, increasing the bearing area of the disc portion 2a by the annular support portion 6a. Thus, stress concentration in the disc portion 2a is suppressed.
次に、負圧源に負圧が無く、したがつて第１作
動室Ａに負圧が蓄えられていない場合に、入力杆
９の前進操作によりブースタピストン２を前方へ
押動すれば、図示しない制御弁により第２作動室
Ｂは第１作動室Ａとの連通を断たれて大気と連通
するので、第１作動室Ａ内の空気は圧縮されて負
圧導入管８から負圧源側に排出されようとする
が、その排出抵抗によりその室Ａの気圧が一定値
以上高くなると、第５図に示すように両作動室
Ａ，Ｂ間に生じる気圧差によりダイヤフラム７
の、円板部２ｂ後面との重合部分がその後面より
離間するので、前記重合部分と円板部２ｂ間の間
隙g1を通つた空気により透孔周辺部７ｃの内周ビ
ード近傍部分ｂが押圧され、排気弁として機能す
べく第２作動室Ｂ側へ撓む。これにより筒体３５
と内周ビード近傍部分ｂとの間に間隙g2が生じる
ので、その間隙g2を通じて第１作動室Ａの空気が
第２作動室Ｂに排出され、第１作動室Ａ内の空気
排出抵抗が殆どなくなつてブースタピストン２を
軽快にマニユアル作動することができる。 Next, when there is no negative pressure in the negative pressure source and therefore no negative pressure is stored in the first working chamber A, if the booster piston 2 is pushed forward by forward operation of the input rod 9, as shown in the figure. Since the second working chamber B is disconnected from the first working chamber A and communicated with the atmosphere by the control valve that does not operate, the air in the first working chamber A is compressed and flows from the negative pressure introduction pipe 8 to the negative pressure source side. However, when the air pressure in chamber A becomes higher than a certain value due to the evacuation resistance, the diaphragm 7
Since the overlapping portion with the rear surface of the disk portion 2b is separated from the rear surface, the portion b near the inner peripheral bead of the through-hole peripheral portion 7c is caused by air passing through the gap g1 between the overlapping portion and the disk portion 2b When pressed, it bends toward the second working chamber B to function as an exhaust valve. As a result, the cylindrical body 35
Since a gap g2 is created between the inner bead and the inner bead vicinity part b, the air in the first working chamber A is discharged to the second working chamber B through the gap g2 , and the air discharge resistance in the first working chamber A is reduced. The booster piston 2 can be manually operated with ease.
前記ダイヤフラム７の重合部分が円板部後面よ
り離間し、また内周ビード近傍部分ｂが第２作動
室Ｂ側へ撓んでも、内周ビード７ａがブースタピ
ストン２に結着され、また透孔周辺部７ｃの、内
周ビード近傍部分ｂを除いた外周ビード側ｃは抜
止めフランジ３６により挟着されるようになつて
いるので、透孔周辺部７ｃが筒体３５より外れる
ことはない。 Even if the overlapping portion of the diaphragm 7 is separated from the rear surface of the disk portion, and the portion b near the inner bead is bent toward the second working chamber B, the inner bead 7a is bonded to the booster piston 2 and the through hole is Since the outer peripheral bead side c of the peripheral portion 7c excluding the inner peripheral bead vicinity portion b is sandwiched by the retaining flange 36, the through-hole peripheral portion 7c does not come off from the cylindrical body 35.
Ｃ 考案の効果
本考案によれば、ブースタピストンの円板部
を、重合結合部よりも半径方向外方において、連
結板の環状支承部により支承したので、円板部及
び連結板間での連結フランジの挟持を的確に行わ
せるべく前記重合結合部を連結フランジ外周縁近
傍へ設置しても、その重合結合部より半径方向外
方に離間した位置に於いて円板部前面を上記環状
支承部に支承させることができ、これにより、上
記重合結合部を支点とした円板部の撓みが抑制さ
れ、円板部の重合結合部における永久歪の発生を
回避することができる。C. Effects of the invention According to the invention, the disc part of the booster piston is supported by the annular support part of the connecting plate radially outward from the overlapping joint part, so that the connection between the disc part and the connecting plate is improved. Even if the overlapping joint is installed near the outer periphery of the connecting flange in order to accurately hold the flange, the front surface of the disk portion is attached to the annular support at a position radially outward from the overlapping joint. As a result, the bending of the disc portion about the overlapping joint portion as a fulcrum can be suppressed, and generation of permanent strain at the overlapping joint portion of the disc portion can be avoided.
また環状支承部の円板部に対する衝合面は、横
断面が該円板部側に凸の円弧状に形成されるの
で、円板部が環状支承部を支点として多少とも撓
み変形する際には上記円弧面に沿つて変形し、環
状支承部による円板部の支承面積が増大して円板
部における応力集中が抑制され、従つて円板部の
撓みに因る耐久性低下を極力抑えることができ
る。 In addition, since the cross section of the abutment surface of the annular support against the disc part is formed in an arc shape convex toward the disc part, when the disc part bends and deforms more or less with the annular support part as a fulcrum, is deformed along the circular arc surface, the bearing area of the disc part by the annular bearing part increases, and stress concentration in the disc part is suppressed, thus minimizing the decrease in durability due to deflection of the disc part. be able to.
図面は本考案の一実施例を示し、第１図は全体
の縦断面図で、第２図−線断面に相当し、第
２図は第１図−線断面図、第３、第４図は第
１図および矢視図、第５図は排気弁の作動説
明図である。
Ａ，Ｂ……第１、第２作動室、ｄ……重合結合
部、１……ブースタシエル、２……ブースタピス
トン、２ａ……円板部、２ｂ……ボス部、３……
連結フランジ、６……連結板、６ａ……環状支承
部、７……ダイヤフラム、７ａ，７ｂ……内、外
周ビード、９……入力部材としての入力杆。
The drawings show one embodiment of the present invention, and FIG. 1 is a longitudinal cross-sectional view of the whole, which corresponds to a cross-sectional view taken along the line in FIG. 2; FIG. FIG. 1 is an arrow-direction view, and FIG. 5 is an explanatory diagram of the operation of the exhaust valve. A, B...First and second working chambers, d...Polymerization joint portion, 1...Booster shell, 2...Booster piston, 2a...Disk portion, 2b...Boss portion, 3...
Connection flange, 6... Connection plate, 6a... Annular support portion, 7... Diaphragm, 7a, 7b... Inner and outer peripheral beads, 9... Input rod as input member.
Claims (1)
自在に収容したブースタピストン２と、該ブース
タピストン２の後面に重合して内周ビード７ａを
該ブースタピストン２に結着すると共に外周ビー
ド７ｂを前記ブースタシエル１の周壁に結着した
ダイヤフラム７とにより、負圧源に連なる前部の
第１作動室Ａと、入力部材９に連動する制御弁を
介して前記第１作動室Ａまたは大気に選択的に連
通される後部の第２作動室Ｂとに区画し、前記ブ
ースタピストン２を円板部２ａと該円板部２ａの
中心を貫通するボス部２ｂとより構成し、該ボス
部２ｂと一体の連結フランジ３の後面に前記円板
部２ａの前面を、また前記連結フランジ３の前面
に連結板６の後面をそれぞれ重合して、前記連結
フランジ３の外周縁近傍で前記円板部２ａと前記
連結板６とを重合結合した負圧式倍力装置におい
て、前記第１および第２作動室Ａ，Ｂ間に生じる
気圧差に伴う前記円板部２ａの撓みを防止すべ
く、前記連結板６は、それと前記円板部２ａとの
重合結合部ｄより半径方向外方へ延出して前記円
板部２ａ前面に衝合する環状支承部６ａを備え、
その環状支承部６ａの前記円板部２ａに対する衝
合面は、横断面が該円板部２ａ側に凸の円弧状に
形成されることを特徴とする負圧式倍力装置。 A booster piston 2 is housed inside the booster shell 1 so as to be able to reciprocate back and forth, and the booster piston 2 overlaps the rear surface of the booster piston 2 to bond the inner bead 7a to the booster piston 2 and connect the outer bead 7b to the booster piston 2. A diaphragm 7 connected to the peripheral wall of the shell 1 selectively connects a first working chamber A at the front connected to a negative pressure source and the first working chamber A or the atmosphere via a control valve linked to an input member 9. The booster piston 2 is composed of a disk portion 2a and a boss portion 2b passing through the center of the disk portion 2a, and is integral with the boss portion 2b. The front surface of the disk portion 2a is overlapped with the rear surface of the connection flange 3, and the rear surface of the connection plate 6 is overlapped with the front surface of the connection flange 3. In a negative pressure booster in which the connecting plate 6 is bonded to the connecting plate 6, the connecting plate 6 is provided with an annular support portion 6a extending radially outward from an overlapping joint portion d between the annular support portion 6a and the disk portion 2a and abutting against the front surface of the disk portion 2a;
A negative pressure booster characterized in that the abutment surface of the annular support portion 6a against the disk portion 2a has a cross section formed in an arc shape convex toward the disk portion 2a side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985198839U JPH043902Y2 (en) | 1985-12-24 | 1985-12-24 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985198839U JPH043902Y2 (en) | 1985-12-24 | 1985-12-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62105070U JPS62105070U (en) | 1987-07-04 |
| JPH043902Y2 true JPH043902Y2 (en) | 1992-02-05 |
Family
ID=31159903
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1985198839U Expired JPH043902Y2 (en) | 1985-12-24 | 1985-12-24 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH043902Y2 (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56120442A (en) * | 1980-02-27 | 1981-09-21 | Aisin Seiki Co Ltd | Brake booster for automobile |
-
1985
- 1985-12-24 JP JP1985198839U patent/JPH043902Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56120442A (en) * | 1980-02-27 | 1981-09-21 | Aisin Seiki Co Ltd | Brake booster for automobile |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62105070U (en) | 1987-07-04 |
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