JPS6114926Y2 - - Google Patents
Info
- Publication number
- JPS6114926Y2 JPS6114926Y2 JP1977176204U JP17620477U JPS6114926Y2 JP S6114926 Y2 JPS6114926 Y2 JP S6114926Y2 JP 1977176204 U JP1977176204 U JP 1977176204U JP 17620477 U JP17620477 U JP 17620477U JP S6114926 Y2 JPS6114926 Y2 JP S6114926Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve plunger
- brake
- piston
- valve
- elastic body
- 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
- 239000012530 fluid Substances 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 230000009191 jumping Effects 0.000 description 7
- 238000003780 insertion Methods 0.000 description 4
- 230000037431 insertion Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000013013 elastic material Substances 0.000 description 3
- 239000000853 adhesive Substances 0.000 description 2
- 230000001070 adhesive effect Effects 0.000 description 2
- 206010020751 Hypersensitivity Diseases 0.000 description 1
- 238000004026 adhesive bonding Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000012790 confirmation Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
Landscapes
- Braking Systems And Boosters (AREA)
Description
【考案の詳細な説明】
本考案はブレーキ倍力装置、特に自動車の動力
制動装置に用いられる倍力装置において、制動時
にマスターシリンダに発生したブレーキ液圧を反
力としてブレーキペタル側に伝える反力機構に関
し、この反力機構を構成する加圧変形部材の耐久
性を向上させることを目的とするものである。[Detailed description of the invention] This invention is a brake booster, especially a booster used in the power braking system of automobiles, which uses the brake fluid pressure generated in the master cylinder during braking as a reaction force that is transmitted to the brake pedal side. Regarding the mechanism, the purpose is to improve the durability of the pressurized deformation member that constitutes this reaction force mechanism.
従来、ブレーキ倍力装置においては、ブレーキ
ペタルに連動する操作杆により弁機構を作動して
ピストンに加わる流体差圧を変化させ、ピストン
に嵌合したブレーキ側被動杆に作動圧力を発生さ
せてマスターシリンダを駆動し、ブレーキシリン
ダへ制動液圧を供給するようにしているが、この
マスターシリンダに生じた液圧反力をブレーキペ
タル側へ伝える反力機構としては、上記ピストン
における被動杆の嵌入部と上記操作杆先端の弁プ
ランジヤとの間にゴム等の加圧変形部材を介装す
るようにしていた。 Conventionally, in a brake booster, a valve mechanism is actuated by an operating rod linked to a brake pedal to change the fluid pressure differential applied to the piston, and an operating pressure is generated in the brake-side driven rod fitted with the piston. The cylinder is driven and braking hydraulic pressure is supplied to the brake cylinder.The reaction force mechanism that transmits the hydraulic reaction force generated in the master cylinder to the brake pedal side is the insertion part of the driven rod in the piston. A pressure deformable member such as rubber is interposed between the valve plunger and the valve plunger at the tip of the operating rod.
そして、この加圧変形部材は、わずかな液圧反
力でも、該加圧変形部材が嵌合するピストンの段
部状内径部に沿つて変形して、その反力をブレー
キペタル側へ伝えることができるようにするため
に、充分に柔軟なものを使用する必要がある。 The pressure deformation member deforms along the stepped inner diameter portion of the piston into which it is fitted even with a slight hydraulic reaction force, and transmits the reaction force to the brake pedal side. It is necessary to use one that is sufficiently flexible to allow for this.
しかしながら、柔軟な加圧変形部材を使用する
と、特に液圧反力が大きくなつて場合には、反力
機構を構成する被動杆および弁プランジヤとピス
トンの内壁面とのわずかな間隙にも上記加圧変形
部材の一部が喰込み易く、特に弁プランジヤ端面
と加圧変形部材との接触部分の脆化が甚しく、そ
の耐久性が著しく低下するという欠点があつた。
このため既に加圧変形部材の弁プランジヤ側端面
に加圧変形部材より高強度の弾性体を粘着し、金
属等の剛体からなる弁プランジヤが直接加圧変形
部材を押圧する状態をなくしてこれの耐久性向上
を図つた装置（実開昭50−138493号公報）が知ら
れているが、この装置では加圧変形部材と弾性体
の接着作業が不可欠であるのみならず、弾性体の
接着により加圧変形部材はピストンへの装置に当
たりその挿入方向の確認を要するという方向性の
問題が生じるため組立作業性が悪くなり、さらに
弁プランジヤの径に応じた外径の弾性体を備えた
加圧変形部材を多数揃えねばならない、等の問題
点があつた。 However, when a flexible pressure deformation member is used, especially when the hydraulic reaction force becomes large, the above-mentioned pressure is applied even to the small gap between the driven rod and valve plunger that constitute the reaction force mechanism and the inner wall surface of the piston. A part of the pressurized deformable member tends to bite, and in particular, the contact portion between the end face of the valve plunger and the pressurized deformable member becomes extremely brittle, resulting in a disadvantage that its durability is significantly reduced.
For this purpose, an elastic body with higher strength than the pressure deformation member is already attached to the end face of the pressure deformation member on the valve plunger side to eliminate the situation in which the valve plunger made of a rigid body such as metal directly presses the pressure deformation member. A device designed to improve durability (Japanese Utility Model Publication No. 50-138493) is known, but this device not only requires bonding work between the pressurized deformation member and the elastic body, but also the bonding of the elastic body. The pressurized deformable member is a device that is inserted into the piston, so there is a problem with the directionality of the device, which requires confirmation of its insertion direction, which makes assembly work difficult. There were problems such as the need to prepare a large number of deformable members.
また、弁プランジヤはこれにより大径の加圧変
形部材に対向して軸方向の隙間を介して上記ピス
トンに摺動自在に嵌合され、したがつて加圧変形
部材の嵌合部と弁プランジヤの嵌入部には段部が
形成されており、補強弾性体を有しない従来の加
圧変形部材の変形時には、この段部側に膨出した
加圧変形部材の一部が弁プランジヤとその嵌入部
との嵌合隙間にも入り込み上述した加圧変形部材
の著しい噛りおよび脆化の問題を生じさせている
ものであるが、更にこの加圧変形部材と弁プラン
ジヤとの間の上記隙間は、ブレーキフイーリング
の良否に直接関わる支配的影響力を及ぼすもので
あり、これがブレーキ倍力装置のジヤンピング特
性（ブレーキ作動開始時に加圧変形部材を介して
反力が入力側に伝達させるまでに生ずる出力の立
上がり現象）を規制し、たとえば前述の加圧変形
部材に高強度の弾性体を粘着した場合にこれのピ
ストンへの装着方向を誤ち上記隙間を増大させた
ときには、上記ジヤンピグ特性のジヤンピング荷
重が著しく増大したガクンと加わる衝撃的ブレー
キフイーリングを生じさせる惧れがあつた。そし
て、上述した加圧変形部材の噛りや脆化変形は上
記隙間の保持にも影響を及ぼしてブレーキフイー
リングの維持を保ち難くする原因となつていた。
また上記加圧変形部材に粘着された高強度の弾性
体は、通常作動時にも弁プランジヤ側への変動が
柔軟性を欠き変形し難く上記ジヤンピング特性に
過敏の反応を及ぼし、その製造誤差によりブレー
キ倍力装置のジヤンピング特性に関してバラツキ
を大きくする欠点を有していた。 Further, the valve plunger is thereby slidably fitted to the piston through an axial gap in opposition to the large-diameter pressure deformation member, so that the fitting portion of the pressure deformation member and the valve plunger A stepped portion is formed in the fitting portion of the valve plunger, and when a conventional pressurized deformable member that does not have a reinforcing elastic body is deformed, a portion of the pressurized deformable member that bulges toward the stepped portion is connected to the valve plunger and its fitting portion. It also enters the fitting gap between the valve plunger and the valve plunger, causing the above-mentioned problem of severe jamming and embrittlement of the pressure deformation member. , which exerts a dominant influence directly related to the quality of the brake feeling, and this is the jumping characteristic of the brake booster (the output generated until the reaction force is transmitted to the input side through the pressurized deformation member at the start of brake operation) For example, if a high-strength elastic body is attached to the above-mentioned pressurized deformation member, and the above-mentioned gap is increased due to the incorrect mounting direction of the pressurized deformation member, the above-mentioned jumping load of the above-mentioned jumping characteristic There was a risk that this would result in an impactful brake feeling that was significantly increased. The above-mentioned jamming and brittle deformation of the pressurized deformation member also affects the maintenance of the above-mentioned gap, making it difficult to maintain the brake feeling.
In addition, the high-strength elastic body adhered to the pressurized deformation member lacks flexibility and is difficult to deform when it moves toward the valve plunger even during normal operation, causing a hypersensitive response to the jumping characteristics, and manufacturing errors may cause brake failure. This has the drawback of increasing variations in the jumping characteristics of the booster.
本考案は叙上の問題点を解消するためになされ
たものであつて、上記弁プランジヤをこれより大
径の上記加圧変形部材に対向して隙間を介して摺
動自在に嵌合させるとともに、上記弁プランジヤ
の加圧変形部材と対向する端面部に環状段部を形
成し、この段部に上記加圧変形部材より高強度の
弾性体を一体的に嵌着して該弾性体により上記弁
プランジヤ端面部の少なくとも周縁部を構成させ
るようにすることにより、弾性体と加圧変形部材
との接着作業の要をなしかつ加圧変形部材の方向
性をなくして、組立作業性を向上させるととも
に、弁プランジヤに対向する加圧変形部材の接触
端面の噛りをなくし、該加圧変形部材と弁プラン
ジヤとの間の隙間管理すなわちジヤンピング特性
の維持を容易ならしめて良好なブレーキフイーリ
ングを得られるようにしたものである。 The present invention has been made in order to solve the above-mentioned problems, and the above-mentioned valve plunger is slidably fitted to the above-mentioned pressure deformation member having a larger diameter through a gap, and , an annular step is formed on the end face of the valve plunger facing the pressure deformation member, an elastic body having higher strength than the pressure deformation member is integrally fitted into the step, and the elastic body allows the pressure deformation member to By configuring at least the peripheral edge of the end face of the valve plunger, there is no need for bonding work between the elastic body and the pressure deformation member, and the directionality of the pressure deformation member is eliminated, thereby improving assembly workability. At the same time, it is possible to eliminate the engagement of the contact end surface of the pressurizing deformable member facing the valve plunger, making it easier to manage the gap between the pressurizing deformable member and the valve plunger, that is, maintain the jumping characteristic, and obtain a good brake feeling. This is how it was done.
以下図示実施例について本考案を説明すると、
１は前殻体２と後殻体３とを衝合させ、それらの
間にダイヤフラム４を挾着支持した密閉殻体、５
はこの殻体内に挿入して背部周面に上記ダイヤフ
ラム４の内周縁を定着したピストンで、このピス
トンおよびダイヤフラム４で殻体１内部を前部室
６と後部室７とに区画するとともに、このピスト
ン後方筒部８を上記後殻体３の開口部からシール
９を介して摺動可能に突出させている。１０はこ
のピストンの前面と前部室６の端壁との間に張設
してピストン５を、その背面におけるダイヤフラ
ム４のスポツト状突起１１を介して後殻体３の段
部に圧接した戻しばね、１２はピストン５の前面
中央に設けた嵌合孔、１３はこの嵌合孔内に基端
嵌入部１４を摺動自在に嵌合した被動杆で、先端
部は前部室６の端壁をシール１５を介して気密に
貫通して図示されてないマスターシリンダに出力
を伝達するようにしている。１６は前部室６の端
壁に開口させたエンジン吸気管等の負圧源に連な
る負圧管、１７は上記ピストン５の内部を貫ぬい
て筒部８内部に開口させた連通路、１８はピスト
ン５における上記嵌合孔１２に通ずる内部室１９
と上記後部室７とを連通して設けた他の連通路で
ある。 The present invention will be explained below with reference to the illustrated embodiments.
1 is a closed shell body in which a front shell body 2 and a rear shell body 3 are brought into contact with each other, and a diaphragm 4 is clamped and supported between them;
is a piston that is inserted into this shell and has the inner circumferential edge of the diaphragm 4 fixed on its back circumferential surface, and this piston and diaphragm 4 partition the inside of the shell 1 into a front chamber 6 and a rear chamber 7, and A rear cylindrical portion 8 is slidably projected from the opening of the rear shell 3 via a seal 9. A return spring 10 is stretched between the front surface of the piston and the end wall of the front chamber 6, and presses the piston 5 against the stepped portion of the rear shell 3 via the spot-like protrusion 11 of the diaphragm 4 on the back surface thereof. , 12 is a fitting hole provided at the center of the front surface of the piston 5; 13 is a driven rod having a base end fitting portion 14 slidably fitted into the fitting hole; The output is transmitted through the seal 15 in an airtight manner to a master cylinder (not shown). 16 is a negative pressure pipe opened in the end wall of the front chamber 6 and connected to a negative pressure source such as an engine intake pipe; 17 is a communication passage that penetrates the inside of the piston 5 and opens inside the cylindrical portion 8; and 18 is a piston. An internal chamber 19 communicating with the fitting hole 12 in 5
This is another communication path provided to communicate the rear chamber 7 and the rear chamber 7.
然して、２０は上記筒部８の後部開口からエア
クリーナ２１を介して挿通した操作杆で、先端球
状部２２にはピストン５の上記内部室１９に摺動
自在に嵌合させた弁プランジヤ２３の後端をカシ
メ付けて設け、後端部は図示しないブレーキペタ
ルに連動させるようにしている。２４はこの操作
杆を囲み上記球状部２３の後方に設けた弁部材
で、筒状の板部材をゴム等の弾性部材で覆つた構
成を備え、後縁拡大部２５を上記筒部８の中間内
周位置に固定している。２６は上記操作杆２０の
中間鍔部２７に取付けた受部２８と上記弁部材２
４の拡大部２５との間に設けた弁戻しばね、２９
は上記受部２８の前縁と弁部材２４の後方段部と
の間に設けた弁偏倚ばね、３０は上記嵌合孔１２
の内部において弁プランジヤ２３と被動杆入部１
４との間に嵌めたゴム等の加圧変形部材であつ
て、上記弁プランジヤ２３の加圧変形部材３０側
側端面外周には、本考案の特徴とする弾性体３１
が冠着されている。弾性体３１は加圧変形部材３
０よりも強度（硬度）の大きなゴム、プラスチツ
ク等の弾性材料から環状に形成したもので、その
内径は弁プランジヤ２３の環状段部２３ａに対し
締め代をもつて嵌着されるように定められてお
り、またその外径は弁プランジヤ２３の先端の径
とほぼ同一に形成されている。そしてこの弾性体
３１の端面は弁プランジヤ２３端面と面一、すな
わち両端面が同一平面に位置するようになつてい
る。３２はこの弁プランジヤ２３の中間縮径部に
その遊動間隔を残して跨架したキー部材、３３は
上記筒部８と後殻体３のそれぞれ開口端を覆つて
設けたベローズを示している。 The operating rod 20 is inserted through the air cleaner 21 from the rear opening of the cylindrical portion 8, and the spherical tip 22 has a valve plunger 23 slidably fitted into the internal chamber 19 of the piston 5. The end is caulked, and the rear end is linked to a brake pedal (not shown). Reference numeral 24 denotes a valve member surrounding this operating rod and provided at the rear of the spherical portion 23, which has a configuration in which a cylindrical plate member is covered with an elastic member such as rubber, and the rear edge enlarged portion 25 is located in the middle of the cylindrical portion 8. It is fixed at the inner circumference position. Reference numeral 26 indicates a receiving portion 28 attached to the intermediate flange portion 27 of the operating rod 20 and the valve member 2.
A valve return spring provided between the enlarged portion 25 of 4, 29
30 is a valve biasing spring provided between the front edge of the receiving portion 28 and the rear step portion of the valve member 24; 30 is the fitting hole 12;
Inside the valve plunger 23 and the driven rod insertion part 1
An elastic body 31, which is a pressure deformation member such as rubber, fitted between the valve plunger 23 and the pressure deformation member 30, is provided on the outer periphery of the end surface of the valve plunger 23 on the pressure deformation member 30 side.
is crowned. The elastic body 31 is the pressurized deformation member 3
It is formed into an annular shape from an elastic material such as rubber or plastic having a strength (hardness) greater than zero, and its inner diameter is determined so that it can be fitted onto the annular stepped portion 23a of the valve plunger 23 with a tightness. The outer diameter of the valve plunger 23 is approximately the same as the diameter of the tip of the valve plunger 23. The end face of the elastic body 31 is flush with the end face of the valve plunger 23, that is, both end faces are located on the same plane. Reference numeral 32 indicates a key member that spans the intermediate reduced diameter portion of the valve plunger 23 with a free movement interval left, and reference numeral 33 indicates a bellows provided to cover the respective open ends of the cylinder portion 8 and the rear shell body 3.
上述のような構成を有するため、この倍力装置
は非作動時において図示のように、弁戻しばね２
６により弁プランジヤ２３が操作杆２０とともに
後方に弾圧され弁プランジヤ２３の縮径部前縁を
キー部材３１に当接させた後退位置にあり、弁部
材２４は弁偏倚ばね２９に付勢されてその前縁を
弁プランジヤ２３の後縁に圧接させるとともに、
またこの位置ではピストン内部室１９の開口縁３
４と弁部材２４の前縁とは離隔位置になつてい
る。したがつて、負圧は前部室６、連通路１７、
内部室１９、他の連通路１８を経て後部室７に通
じ、ピストン５は戻しばね１０により付勢されて
図示後退位置を占め、一方大気圧はエアクリーナ
２１を介して弁プランジヤ２３の内部位置まで達
しここで閉塞されている。そして、ブレーキペタ
ルが踏まれ操作杆２０が弁戻しばね２６に抗して
前進すると、先ず弁部材２４が内部室１９の開口
縁３４に当接して連通路１７と内部室１９との連
絡を断ち、次いでこの弁部材２４の前縁から弁プ
ランジヤ２３の後縁が離間して空気が内部室１９
および他の連通路１８を介して後部室７内に進入
するから、ピストン５は戻しばね１０に抗して前
進し、被動杆１３がマスターシリンダを作動させ
て制動液圧ブレーキシリンダに給送するに至る。 Since it has the above-mentioned configuration, when this booster is not in operation, the valve return spring 2 is activated as shown in the figure.
6, the valve plunger 23 is pressed rearward together with the operating rod 20 and is in a retracted position where the front edge of the reduced diameter portion of the valve plunger 23 is brought into contact with the key member 31, and the valve member 24 is biased by the valve biasing spring 29. While pressing its leading edge against the trailing edge of the valve plunger 23,
Also, in this position, the opening edge 3 of the piston internal chamber 19
4 and the front edge of the valve member 24 are separated from each other. Therefore, negative pressure is generated in the front chamber 6, the communication passage 17,
The inner chamber 19 communicates with the rear chamber 7 via another communication passage 18 , and the piston 5 is biased by the return spring 10 into the retracted position shown, while the atmospheric pressure is supplied via the air cleaner 21 to the inner position of the valve plunger 23 . Reached here is blocked. Then, when the brake pedal is stepped on and the operating rod 20 moves forward against the valve return spring 26, the valve member 24 first comes into contact with the opening edge 34 of the internal chamber 19, cutting off communication between the communication passage 17 and the internal chamber 19. Then, the rear edge of the valve plunger 23 is separated from the front edge of the valve member 24, and air flows into the internal chamber 19.
and another communication passage 18 into the rear chamber 7, the piston 5 moves forward against the return spring 10, and the driven rod 13 actuates the master cylinder and feeds the brake hydraulic pressure to the brake cylinder. leading to.
ブレーキペタルから踏力が除かれると、前述の
作動は逆に、弁プランジヤ２３により大気側が閉
じられるとともに、弁部材２４の前縁が内部室１
９の開口縁３４から離れ、後部室７が再び前部室
６と通じて後部室７内の空気はエンジン側に吸出
され、ピストン５および操作杆２０等が図示作動
位置に復帰する。 When the pedal force is removed from the brake pedal, the above-mentioned operation is reversed, and the valve plunger 23 closes the atmosphere side, and the leading edge of the valve member 24 closes the inner chamber 1.
9, the rear chamber 7 communicates with the front chamber 6 again, the air in the rear chamber 7 is sucked out to the engine side, and the piston 5, operating rod 20, etc. return to the operating position shown.
そして上述のブレーキ操作時には、マスターシ
リンダの液圧反力により被動杆１３の嵌入部１４
が加圧変形部材３０を圧縮変形させ、この圧縮変
形により弁プランジヤ２３に反力が伝達されて操
作杆２０を介してブレーキ操作者にブレーキの反
力感覚を与えることになる。ところで、柔軟な加
圧変形部材３０はこの圧縮変形時に前述のように
弁プランジヤ２３周囲の微妙な隙間に喰い込んで
噛られる傾向となるのであるが、本考案では弁プ
ランジヤ２３の端面外周に弾性体３１を設けてい
るので、上記のような加圧変形部材３０の局部的
な変形は防止される。すなわち弾性体３１は加圧
変形部材３０より硬度、強度が大きい弾性材料か
ら構成されているので、加圧変形部材３０の変形
を受けてこの弾性体３１も同時に圧縮変形し、加
圧変形部材３０の上記局部的変形を吸収すること
ができる。したがつて加圧変形部材３０の噛りや
脆化が防がれ、また弾性体３１自身は加圧変形部
材３０より硬度が大で弁プランジヤ２３に一体に
設けられているため局部的な変形を生じることが
なく、このため、加圧変形部材３０、弾性体３１
とも、繰返し使用しても初期の性能を長時間持続
できる。 During the above-mentioned brake operation, the hydraulic reaction force of the master cylinder causes the fitting part 14 of the driven rod 13 to
compressively deforms the pressurized deformable member 30, and this compressive deformation transmits a reaction force to the valve plunger 23, giving the brake operator a feeling of brake reaction force via the operating rod 20. By the way, the flexible pressurizing deformation member 30 has a tendency to get stuck in the delicate gap around the valve plunger 23 during this compression deformation as described above, but in the present invention, the outer periphery of the end face of the valve plunger 23 is made of elastic material. Since the body 31 is provided, local deformation of the pressure deformation member 30 as described above is prevented. That is, since the elastic body 31 is made of an elastic material having higher hardness and strength than the pressure deformation member 30, when the pressure deformation member 30 is deformed, the elastic body 31 is also compressed and deformed at the same time, and the pressure deformation member 30 The above local deformation of can be absorbed. Therefore, the pressurized deformable member 30 is prevented from becoming jammed or brittle, and since the elastic body 31 itself is harder than the pressurized deformable member 30 and is integrally provided with the valve plunger 23, local deformation is prevented. Therefore, the pressure deformation member 30 and the elastic body 31
Both can maintain their initial performance for a long time even after repeated use.
第２図ａないしｃは、弁プランジヤ２３端面に
設けられる弾性体３１の種々の形状例を示すもの
で、同図ａは環状の弾性体３１の内径部および弁
プランジヤ２３の段部２３ａをテーパ状として抜
け止め完全を期したものを示している。これに対
し同図ｂないしｃは、弁プランジヤ２３の端面全
体に弾性体に適当な締め代を与え、あるいは図示
のようなテーパ面を利用することにより容易に弾
性体３１と弁プランジヤ２３とを一体にすること
ができ、かつ、上記と同様の効果を得ることがで
きる。なお接着剤により、または接着剤を併用し
て弾性体３１を弁プランジヤ２３に設けることが
できるのは勿論である。 2A to 2C show various examples of shapes of the elastic body 31 provided on the end face of the valve plunger 23, and FIG. The figure shows a product that is designed to completely prevent it from coming off. On the other hand, in FIGS. 2-3B to 3-C, the elastic body 31 and the valve plunger 23 can be easily connected by providing an appropriate tightening margin to the elastic body over the entire end face of the valve plunger 23, or by using a tapered surface as shown in the figure. They can be integrated, and the same effects as above can be obtained. It goes without saying that the elastic body 31 can be provided on the valve plunger 23 by using an adhesive or by using an adhesive together.
以上のように本考案によれば、加圧変形部材の
弁プランジヤ周囲への局部的変形を防止して耐久
性を向上させることができ、しかも弾性体は予め
弁プランジヤと一体に設けることができるので、
組立作業性を向上させ、コストダウンを図ること
ができる効果がある。 As described above, according to the present invention, it is possible to prevent local deformation of the pressure deformation member around the valve plunger and improve durability, and the elastic body can be provided integrally with the valve plunger in advance. So,
This has the effect of improving assembly workability and reducing costs.
そして、本考案においては、弁プランジヤの加
圧変形部材と対向する端面部に環状段部を形成
し、この段部に高強度の弾性体を一体的に嵌着し
て該弾性体により上記弁プランジヤ端面部の少く
とも周縁部分を構成させるようにしたものである
から、弁プランジヤと弾性体との正確かつ確実な
一体的結合を容易に達成し得られるのみならず、
該弾性体により取扱い操作上傷つき易い弁プラン
ジヤの端面部周縁を充分被覆保護することができ
るとともに、弁プランジヤ先端部の仕上寸法精度
を緩やかなものとすることのできる利点がある。
特に、本考案において、加圧変形部材そのものに
は何等の改変を加えることなくそれの弁プランジ
ヤ周辺における局部的変形を阻止し得ることは、
加圧変形部材に挿着の方向性を与えず、作動時そ
れに従来のものと変わることのない自由変形を許
容してしかも耐久性を可久的に向上し得られる点
で顕著な効用を奏するものと言うことができる。
しかも本考案においては弾性体は弁プランジヤ側
に設けられるため、従来のような加圧変形部材と
弾性体との接着作業をなくし得るとともに、弁プ
ランジヤと加圧変形部材との間の隙間管理を良好
に維持させてジヤンピング特性のバラツキを抑え
る所期のブレーキフイーリングを得させ得る効果
がある。 In the present invention, an annular step is formed on the end face of the valve plunger facing the pressurizing deformation member, and a high-strength elastic body is integrally fitted into this step, and the elastic body causes the above-mentioned valve to open. Since at least the peripheral portion of the end face of the plunger is configured, not only can accurate and reliable integral connection between the valve plunger and the elastic body be easily achieved, but also
The elastic body can sufficiently cover and protect the periphery of the end face of the valve plunger, which is easily damaged during handling, and has the advantage that the finished dimensional accuracy of the tip end of the valve plunger can be made gentle.
In particular, in the present invention, local deformation around the valve plunger can be prevented without making any changes to the pressurized deformation member itself.
It is extremely effective in that it does not impose a direction of insertion on the pressure deformable member, allows free deformation during operation and is unchanged from conventional ones, and can permanently improve durability. It can be said that it is a thing.
Moreover, in the present invention, since the elastic body is provided on the valve plunger side, it is possible to eliminate the conventional work of gluing the pressurized deformation member and the elastic body, and also to manage the gap between the valve plunger and the pressurization deformation member. This has the effect of making it possible to obtain the desired brake feeling that is well maintained and suppresses variations in the jumping characteristics.
第１図は本考案のブレーキ倍力装置の一実施例
を示す縦断面図、第２図ａないしｃはそれぞれ本
考案の他の実施例を示す要部の断面図である。
５・・ピストン、１３・・被動杆、１４・・嵌
入部、２０・・操作杆、２３・・弁プランジヤ、
３０・・加圧変形部材、３１・・弾性体。
FIG. 1 is a longitudinal cross-sectional view showing one embodiment of the brake booster according to the present invention, and FIGS. 2A to 2C are cross-sectional views of essential parts showing other embodiments of the present invention. 5. Piston, 13. Driven rod, 14. Fitting part, 20. Operating rod, 23. Valve plunger.
30... Pressure deformation member, 31... Elastic body.
Claims (1)
を作動してピストンに加わる流体圧力を制御し、
このピストンに嵌合したブレーキ側被動杆に作動
圧力を発生させ、かつ該被動杆に生じるブレーキ
反力を、該被動杆の嵌入部と上記操作杆先端の弁
プランジヤとの間に介装した弾性体からなる加圧
変形部分を介して上記ブレーキペタルに伝達する
ブレーキ倍力装置において、上記弁プランジヤを
これより大径の上記加圧変形部材に対向して隙間
を介し上記ピストンに摺動自在に嵌合させるとと
もに、上記弁プランジヤの加圧変形部材と対向す
る端面部に環状段部を形成し、この段部に上記加
圧変形部材より高強度の弾性体を一体的に嵌着し
た該弾性体により上記弁プランジヤ端面部の少な
くとも周縁部分を構成させたことを特徴とするブ
レーキ倍力装置の反力機構。 A valve mechanism is actuated by an operating lever linked to the brake pedal to control the fluid pressure applied to the piston.
An elastic member interposed between the fitting part of the driven rod and the valve plunger at the tip of the operating rod generates operating pressure in the brake-side driven rod fitted with this piston and absorbs the brake reaction force generated in the driven rod. In the brake booster that transmits pressure to the brake pedal via a pressurizing deformable portion consisting of a body, the valve plunger is slidably slidable on the piston through a gap facing the pressurizing deformable member having a larger diameter. At the same time, an annular stepped portion is formed on the end face of the valve plunger facing the pressurized deformable member, and an elastic body having a higher strength than the pressurized deformable member is integrally fitted into the stepped portion. A reaction force mechanism for a brake booster, characterized in that at least a peripheral edge portion of the end face portion of the valve plunger is formed by a body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1977176204U JPS6114926Y2 (en) | 1977-12-29 | 1977-12-29 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1977176204U JPS6114926Y2 (en) | 1977-12-29 | 1977-12-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS54103491U JPS54103491U (en) | 1979-07-20 |
| JPS6114926Y2 true JPS6114926Y2 (en) | 1986-05-09 |
Family
ID=29184507
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1977176204U Expired JPS6114926Y2 (en) | 1977-12-29 | 1977-12-29 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6114926Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5011236B2 (en) * | 2007-08-29 | 2012-08-29 | 本田技研工業株式会社 | Brake device stroke simulator |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5340617Y2 (en) * | 1974-05-02 | 1978-09-30 |
-
1977
- 1977-12-29 JP JP1977176204U patent/JPS6114926Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS54103491U (en) | 1979-07-20 |
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