JPH0236772Y2 - - Google Patents
Info
- Publication number
- JPH0236772Y2 JPH0236772Y2 JP1984088840U JP8884084U JPH0236772Y2 JP H0236772 Y2 JPH0236772 Y2 JP H0236772Y2 JP 1984088840 U JP1984088840 U JP 1984088840U JP 8884084 U JP8884084 U JP 8884084U JP H0236772 Y2 JPH0236772 Y2 JP H0236772Y2
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic pressure
- receiving surface
- hydraulic
- valve body
- pressure receiving
- 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 22
- 230000007423 decrease Effects 0.000 description 5
- 238000012856 packing Methods 0.000 description 4
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000005856 abnormality Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 1
Landscapes
- Hydraulic Control Valves For Brake Systems (AREA)
Description
【考案の詳細な説明】
（産業上の利用分野）
本考案は、プロポーシヨンニングバルブの改良
に関する。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to an improvement of a proportioning valve.
（従来技術）
一般に、プロポーシヨンニングバルブは、第４
図に示す如く、液圧入口１と液圧出口２を有する
シリンダ状のバルブ本体３内に、液圧入口１側が
小径受圧面４ａに、液圧出口２側が大径受圧面４
ｂにそれぞれ形成され、軸方向に流体通孔５を有
する主ピストン４が嵌合され、該主ピストン４
は、大径受圧面４ｂ側にばね６で付勢されるとと
もに、該主ピストン４の小径受圧面４ａ側に、主
ピストン４の流体通孔５の開口５ａと所定の隙間
ｔを隔てて対向するバルブ体７が設けられて構成
されている。(Prior art) Generally, the proportioning valve has a fourth
As shown in the figure, inside a cylindrical valve body 3 having a hydraulic pressure inlet 1 and a hydraulic pressure outlet 2, the hydraulic pressure inlet 1 side is a small diameter pressure receiving surface 4a, and the hydraulic pressure outlet 2 side is a large diameter pressure receiving surface 4a.
A main piston 4 having a fluid passage hole 5 in the axial direction is fitted into the main piston 4.
is urged by a spring 6 toward the large-diameter pressure-receiving surface 4b, and faces the small-diameter pressure-receiving surface 4a of the main piston 4 with a predetermined gap t from the opening 5a of the fluid passage hole 5 of the main piston 4. The valve body 7 is provided with a valve body 7 to perform the operation.
そして、液圧入口１から入口液圧Ｐ（IN）を、
バルブ体７の隙間ｔ、主ピストン４の流体通孔５
を介して液圧出口２に作用させる一方、入口液圧
Ｐ（IN）が折点液圧Pk（第５図参照）以上になる
と、主ピストン４の大径受圧面４ｂに作用する出
口液圧Ｐ（OUT）で主ピストン４をばね６の付勢
力に抗してバルブ体７側に変位させ、隙間ｔを減
少させて入口液圧Ｐ（IN）に対して出口液圧Ｐ
（OUT）を減少させるように作用する。 Then, the inlet hydraulic pressure P (IN) from the hydraulic pressure inlet 1 is
Gap t of valve body 7, fluid passage hole 5 of main piston 4
On the other hand, when the inlet hydraulic pressure P (IN) exceeds the turning point hydraulic pressure Pk (see Fig. 5), the outlet hydraulic pressure acts on the large diameter pressure receiving surface 4b of the main piston 4. P (OUT), the main piston 4 is displaced toward the valve body 7 against the urging force of the spring 6, the gap t is reduced, and the outlet hydraulic pressure P is increased relative to the inlet hydraulic pressure P (IN).
(OUT).
上記のような構成、作用のプロポーシヨンニン
グバルブ８は、例えば第６図ａまたは第６図ｂに
示すような自動車の液圧ブレーキシステムに採用
される。 The proportioning valve 8 having the structure and operation as described above is employed, for example, in a hydraulic brake system of an automobile as shown in FIG. 6a or FIG. 6b.
第６図ａは、FR車用のFR配管の例を示し、プ
ロポーシヨンニングバルブ８は、マスターシリン
ダ９と後輪ブレーキシリンダRl，Rrとの間に介
設され、急ブレーキを踏んだときに、上述の如
く、入口液圧Ｐ（IN）が折点液圧Pk以上になる
と、出口液圧Ｐ（OUT）を減少させて、後輪ブレ
ーキの効きすぎをコントロールし、自動車のスキ
ツド現象を抑制させるのである。 Figure 6a shows an example of FR piping for an FR vehicle, and the proportioning valve 8 is interposed between the master cylinder 9 and the rear brake cylinders Rl and Rr, and is As mentioned above, when the inlet hydraulic pressure P (IN) becomes equal to or higher than the turning point hydraulic pressure Pk, the outlet hydraulic pressure P (OUT) is decreased to control the rear wheel brakes from being too effective and suppress the car skid phenomenon. Let it happen.
第６図ｂは、FF車用のＸ配管の例を示し、そ
の作用は第６図ａの場合と同様である。 FIG. 6b shows an example of an X-piping for a front-wheel-drive vehicle, and its operation is the same as that shown in FIG. 6a.
ところで、近年では二系統ブレーキシステムが
法定化されており、一方のブレーキシステムが配
管の破損等で故障した場合でも他方のブレーキシ
ステムが効くようになつている。 Incidentally, in recent years, dual brake systems have been legalized, and even if one brake system fails due to damage to piping or the like, the other brake system remains effective.
このような二系統ブレーキシステムにプロポー
シヨンニングバルブ８を採用した場合、正常時に
は、プロポーシヨンニングバルブ８により後輪ブ
レーキの効きすぎがコントロールされるので有用
であるというものの、一方のブレーキシステムが
故障した異常時にも、正常時と同じようにプロポ
ーシヨンニングバルブ８により他方のブレーキの
効きすぎがコントロールされると、全体のブレー
キ力が不足するので危険であるという問題があつ
た。 When the proportioning valve 8 is used in such a dual brake system, it is useful because it controls the rear wheel brakes from being too effective during normal operation, but if one brake system breaks down, the proportioning valve 8 is useful. Even in such an abnormal situation, if the over-effectiveness of the other brake is controlled by the proportioning valve 8 in the same way as in normal situations, there is a problem in that the overall braking force is insufficient, which is dangerous.
このため、特公昭49−38237号公報では、一方
の入口室の流体圧力が他方の入口室の流体圧力よ
り低くなると、可動弁部材が流体通路を閉止しな
いようにして、一方のブレーキ流体系の故障時は
他方のブレーキ装置にその最大のブレーキ効果を
与えるようにした流体圧力分配弁が提案されてい
る。 For this reason, in Japanese Patent Publication No. 49-38237, when the fluid pressure in one inlet chamber becomes lower than the fluid pressure in the other inlet chamber, the movable valve member prevents the fluid passage from closing. A fluid pressure distribution valve has been proposed that, in the event of a failure, provides the maximum braking effect to the other brake device.
しかしながら、上記従来技術では、通常は生じ
るマスターシリンダ（液圧発生装置）の差圧によ
る差動ピストンの微少振動を防止するために、ば
ね部材が別に必要となり、構成が複雑となる。 However, in the above-mentioned prior art, a separate spring member is required in order to prevent minute vibrations of the differential piston due to the differential pressure of the master cylinder (hydraulic pressure generating device) that normally occurs, resulting in a complicated configuration.
（考案の目的）
本考案は、上記従来のような問題を解決するた
めになされたもので、とくに自動車の二系統ブレ
ーキシステムに採用した場合に、一方のブレーキ
システムの異常時（失陥時）には他方のブレーキ
が強力に効くように作用するとともに、差動ピス
トンの微少振動を有効に防止できるプロポーシヨ
ンニングバルブを提供することを目的とするもの
である。(Purpose of the invention) The present invention was made in order to solve the above-mentioned conventional problems, and is particularly applicable when one of the brake systems is abnormal (failure) when applied to a dual-brake system of an automobile. It is an object of the present invention to provide a proportioning valve that can act so that the other brake is strongly effective, and can effectively prevent minute vibrations of the differential piston.
（考案の構成）
このため本考案は、液圧入口と液圧出口とを有
するシリンダ状のバルブ本体内に、液圧入口側が
小径受圧面に、液圧出口側が大径受圧面にそれぞ
れ形成され、軸方向に流体通孔を有する主ピスト
ンが嵌合され、該主ピストンは、大径受圧面側に
ばねで付勢されるとともに、該主ピストンの小径
受圧面側に、主ピストンの流体通孔の開口と、所
定の隙間を隔てて対向するバルブ体が設けられた
プロポーシヨンニングバルブにおいて、上記バル
ブ本体の液圧入口側に、液圧作用口を設ける一
方、該バルブ本体内に、液圧入口側が小径受圧面
に、液圧作用口側が大径受圧面にそれぞれ形成さ
れた差動ピストンを嵌合するとともに、誤差動ピ
ストンと上記バルブ体とを連結して構成したもの
である。(Structure of the invention) For this reason, the present invention has a cylindrical valve body having a hydraulic inlet and a hydraulic outlet, in which a small diameter pressure receiving surface is formed on the hydraulic pressure inlet side and a large diameter pressure receiving surface is formed on the hydraulic outlet side. , a main piston having a fluid passage hole in the axial direction is fitted, the main piston is urged by a spring toward the large diameter pressure receiving surface side, and the fluid passage hole of the main piston is biased toward the small diameter pressure receiving surface side of the main piston. In a proportioning valve that is provided with a valve body that faces the opening of a hole with a predetermined gap in between, a hydraulic pressure application port is provided on the hydraulic pressure inlet side of the valve body, and a liquid A differential piston having a pressure inlet side formed on a small-diameter pressure receiving surface and a hydraulic pressure application port side formed on a large-diameter pressure receiving surface is fitted, and the differential piston is connected to the valve body.
そして、液圧作用口から、例えば一方のブレー
キシステムの正常な作用液圧が差動ピストンの大
径受圧面に作用している間は、バルブ体を所定位
置に保持して、上記従来と同様の作用を行なわせ
る一方、一方のブレーキシステムの異常で液圧作
用口からの作用液圧が異常に減少したとき、差動
ピストンの小径受圧面に作用する入口液圧で差動
ピストンを液圧作用口側に変位させ、隙間を増加
させて出口液圧を増加させ、他方のブレーキシス
テムを強力に作用させる。 Then, while the normal working hydraulic pressure of one brake system is acting from the hydraulic pressure application port on the large diameter pressure receiving surface of the differential piston, the valve body is held in a predetermined position and the valve body is held in a predetermined position. On the other hand, when the working hydraulic pressure from the hydraulic pressure application port decreases abnormally due to an abnormality in one of the brake systems, the differential piston is hydraulically operated by the inlet hydraulic pressure acting on the small diameter pressure receiving surface of the differential piston. The brake system is moved toward the action port side, increasing the gap and increasing the outlet hydraulic pressure, making the other brake system work more strongly.
（考案の効果）
本考案によれば、液圧作用口からの作用液圧が
異常に減少したときには、バルブ体とピストンの
開口との間の隙間が増加されるので、自動車の二
系統ブレーキシステムに採用した場合、一方のブ
レーキシステムの失陥時には他方のブレーキシス
テムが強力に作用するようになり、全体のブレー
キ力が不足するという危険がなくなる。(Effect of the invention) According to the invention, when the hydraulic pressure from the hydraulic pressure application port abnormally decreases, the gap between the valve body and the opening of the piston is increased, so that the two-system brake system of the automobile If this is adopted, when one brake system fails, the other brake system will work more strongly, eliminating the risk that the overall braking force will be insufficient.
また、差動ピストンの液圧入口側を小径受圧面
に、液圧作用口側を大径受圧面にそれぞれ形成し
ているから、この面積差によりマスターシリンダ
の差圧による差動ピストンの微少振動を有効に防
止することができ、従来技術のようなばねが不要
となつて構成が簡素化できる。 In addition, since the hydraulic inlet side of the differential piston is formed as a small-diameter pressure receiving surface, and the hydraulic pressure application side is formed as a large-diameter pressure receiving surface, this area difference causes minute vibrations of the differential piston due to the differential pressure of the master cylinder. It is possible to effectively prevent this, and the configuration can be simplified since a spring as in the prior art is not required.
（実施例）
第１図に示すように、プロポーシヨンニングバ
ルブ１０は、シリンダ状のバルブ本体１１の右側
開口部にプラグ１２が螺着されて液圧作用口１３
が形成され、左側開口部にプラグ１４が螺着され
て液圧出口１５が形成され、該バルブ本体１１の
側上部に液圧入口１６が形成されている。(Example) As shown in FIG. 1, the proportioning valve 10 has a plug 12 screwed into the right opening of a cylindrical valve body 11, and a hydraulic pressure application port 13.
A plug 14 is screwed into the left opening to form a hydraulic outlet 15, and a hydraulic inlet 16 is formed at the upper side of the valve body 11.
上記液圧入口１６には、後述するマスターシリ
ンダ９により後輪ブレーキシリンダRl，Rrへ供
給される液圧が、また、液圧作用口１３には、同
マスターシリンダ９により前輪ブレーキシリンダ
Fl，Frへ供給される液圧が、それぞれ別個の経
路で加えられている。 The hydraulic pressure inlet 16 receives hydraulic pressure supplied to the rear brake cylinders Rl and Rr by a master cylinder 9, which will be described later.
The hydraulic pressure supplied to Fl and Fr is applied through separate routes.
上記液圧出口１５は、後輪ブレーキシリンダ
Rl，Rrに接続される。 The hydraulic outlet 15 is connected to the rear wheel brake cylinder.
Connected to Rl and Rr.
上記液圧入口１６側が小径受圧面１７ａに、液
圧出口１５側が大径受圧面１７ｂにそれぞれ形成
され、軸方向に流体通孔１８を有する主ピストン
１７を設け、該主ピストン１７の大径受圧面１７
ｂ側を、上記左側のプラグ１４に形成されたシリ
ンダ部１４ａにパツキンリング１９を介して摺動
自在に嵌合するとともに、小径受圧面１７ａ側
を、上記バルブ本体１１に形成されたガイド孔１
１ａにパツキンリング２０を介して摺動自在に嵌
合する。 A main piston 17 is provided, which has a small diameter pressure receiving surface 17a on the hydraulic pressure inlet 16 side and a large diameter pressure receiving surface 17b on the hydraulic pressure outlet 15 side, and has a fluid passage hole 18 in the axial direction. Surface 17
The b side is slidably fitted into the cylinder portion 14a formed in the left plug 14 via a packing ring 19, and the small diameter pressure receiving surface 17a side is fitted into the guide hole 1 formed in the valve body 11.
1a through a packing ring 20 so as to be slidable.
上記左側のプラグ１４とガイド孔１１ａとの間
のバルブ本体１１の大気開放室２１には、主ピス
トン１７を大径受圧面１７ｂ側に付勢するコイル
ばね２２を設け、主ピストン１７は、このコイル
ばね２２により付勢された状態で、フランジ部１
７ｃがプラグ１４で当て止められる復動位置に定
位する。この復動位置において、プラグ１４のシ
リンダ部１４ａと主ピストン１７の大径受圧面１
７ｂとの間には、大径受圧面１７ｂに出口液圧Ｐ
（OUT）を作用させるための間隙２３が形成され
る。 A coil spring 22 for biasing the main piston 17 toward the large diameter pressure receiving surface 17b is provided in the atmosphere open chamber 21 of the valve body 11 between the left plug 14 and the guide hole 11a. While being biased by the coil spring 22, the flange portion 1
7c is positioned at the return position where it is stopped by the plug 14. In this return position, the cylinder portion 14a of the plug 14 and the large diameter pressure receiving surface 1 of the main piston 17
7b, there is an outlet hydraulic pressure P on the large diameter pressure receiving surface 17b.
A gap 23 is formed for applying (OUT).
一方、液圧入口１６側が小径受圧面２５ａに、
液圧作用口１３側が大径受圧面２５ｂにそれぞれ
形成された差動ピストン２５を設け、該差動ピス
トン２５の大径受圧面２５ｂ側をバルブ本体１１
の右側のプラグ１２側に形成された大径シリンダ
部１１ｂにパツキンリング２６を介して摺動自在
に嵌合するとともに、小径受圧面２５ａ側をバル
ブ本体１１の液圧入口１６に対応して形成された
小径シリンダ部１１ｃにパツキンリング２７を介
して摺動自在に嵌合する。 On the other hand, the hydraulic inlet 16 side is the small diameter pressure receiving surface 25a,
A differential piston 25 is provided in which the hydraulic pressure operation port 13 side is formed on the large diameter pressure receiving surface 25b, and the large diameter pressure receiving surface 25b side of the differential piston 25 is formed on the valve body 11.
It is slidably fitted into the large diameter cylinder portion 11b formed on the right side of the plug 12 through the packing ring 26, and the small diameter pressure receiving surface 25a side is formed corresponding to the hydraulic pressure inlet 16 of the valve body 11. It is slidably fitted into the small diameter cylinder portion 11c via a packing ring 27.
上記バルブ本体１１の小径シリンダ部１１ｃ内
には、上記主ピストン１７の流体通孔１８のテー
パ状開口１８ａと所定の間隙ｔを隔てて対向する
半球状のバルブ体２８が配設され、該バルブ体２
８は差動ピストン２５の凹部２５ｃ内に設けられ
たコイルばね２９で開口１８ａ側に付勢された状
態でフランジ２８ａが差動ピストン２５の係止溝
２５ｄで保持された位置決めリング３０で当て止
められて定位する。 A hemispherical valve body 28 is disposed within the small diameter cylinder portion 11c of the valve body 11 and faces the tapered opening 18a of the fluid passage hole 18 of the main piston 17 with a predetermined gap t therebetween. body 2
8 is a state in which the flange 28a is pressed toward the opening 18a by a coil spring 29 provided in the recess 25c of the differential piston 25, and the flange 28a is stopped by the positioning ring 30 held in the locking groove 25d of the differential piston 25. Orient yourself.
上記のようにプロポーシヨンニングバルブ１０
を構成すれば、液圧作用口１３から所定の作用液
圧Ｐ（Ｆ）が差動ピストン２５の大径受圧面２５
ｂに作用していると、差動ピストン２５は左動さ
れて大径シリンダ部１１ｂと小径シリンダ部１１
ｃの段部１１ｄで当て止められ、バルブ体２８を
定位置に保持する。 Proportioning valve 10 as above
If configured, a predetermined working hydraulic pressure P (F) is applied from the hydraulic working port 13 to the large diameter pressure receiving surface 25 of the differential piston 25.
b, the differential piston 25 is moved to the left to separate the large diameter cylinder portion 11b and the small diameter cylinder portion 11.
The valve body 28 is held in place by being abutted by the stepped portion 11d of c.
従つて、液圧入口１６から入口液圧Ｐ（IN）
を、バルブ体２８と主ピストン１７の開口１８ａ
との隙間ｔ、主ピストン１７の流体通孔１８を介
して液圧出口１５に作用させることができる。 Therefore, the inlet hydraulic pressure P(IN) from the hydraulic inlet 16
, the valve body 28 and the opening 18a of the main piston 17
The hydraulic pressure can be applied to the hydraulic outlet 15 through the fluid passage hole 18 of the main piston 17.
そして、入口液圧Ｐ（IN）が折点液圧Pk（第２
図参照）以上になると、主ピストン１７の大径受
圧面１７ｂに作用する出口液圧Ｐ（OUT）で主ピ
ストン１７がコイルばね２２の付勢力に抗してバ
ルブ体１８側に右動され、隙間ｔが減少して、入
口液圧Ｐ（IN）に対して出口液圧Ｐ（OUT）が減
少するようになる（第２図の実線参照）。 Then, the inlet hydraulic pressure P (IN) is the turning point hydraulic pressure Pk (second
(see figure), the main piston 17 is moved to the right toward the valve body 18 by the outlet hydraulic pressure P (OUT) acting on the large diameter pressure receiving surface 17b of the main piston 17 against the biasing force of the coil spring 22. As the gap t decreases, the outlet hydraulic pressure P(OUT) decreases relative to the inlet hydraulic pressure P(IN) (see the solid line in FIG. 2).
一方、液圧作用口１３からの作用液圧Ｐ（Ｆ）
が異常に減少すると、差動ピストン２５の小径受
圧面２５ａに作用する入口液圧Ｐ（IN）で差動ピ
ストン２５が液圧作用口１３側に右動され、この
右動に連動してバルブ体１８も定位置から右動す
るので、隙間ｔが増加して、出口液圧Ｐ（OUT）
が増加するようになる（第２図の点線参照）。 On the other hand, the working hydraulic pressure P(F) from the hydraulic working port 13
When the differential piston 25 decreases abnormally, the inlet hydraulic pressure P (IN) acting on the small diameter pressure receiving surface 25a of the differential piston 25 moves the differential piston 25 to the right toward the hydraulic pressure application port 13, and in conjunction with this rightward movement, the valve Since the body 18 also moves to the right from the fixed position, the gap t increases and the outlet fluid pressure P(OUT)
(see the dotted line in Figure 2).
しかして、上記プロポーシヨンニングバルブ１
０を自動車の液圧ブレーキシステムに採用した例
を第３図ａまたは第３図ｂに示す。 However, the above proportioning valve 1
3a or 3b shows an example in which 0 is applied to a hydraulic brake system of an automobile.
第３図ａはFR車用のFR配管の例を示し、プロ
ポーシヨンニングバルブ１０とマスターシリンダ
９を、前輪ブレーキシリンダFl，Frと後輪ブレ
ーキシリンダRl，Rrに対して図示のように配管
する。 Figure 3a shows an example of FR piping for an FR vehicle, in which the proportioning valve 10 and master cylinder 9 are connected to the front brake cylinders Fl, Fr and the rear brake cylinders Rl, Rr as shown. .
従つて、前輪ブレーキシステムが正常であれ
ば、差動ピストン２５でバルブ体２８が定位置に
保持されているので、急ブレーキを踏んだときに
入口液圧Ｐ（IN）が折点液圧Pk以上になると、
出口液圧Ｐ（OUT）が減少して、後輪ブレーキの
効きすぎがコントロールされ、スキツド現象が抑
制される。 Therefore, if the front wheel brake system is normal, the valve body 28 is held in place by the differential piston 25, so that when the brake is suddenly pressed, the inlet hydraulic pressure P (IN) reaches the corner hydraulic pressure Pk. If it becomes more than that,
The outlet hydraulic pressure P (OUT) is reduced, the over-effectiveness of the rear wheel brake is controlled, and the skid phenomenon is suppressed.
一方、前輪ブレーキシステムに異常が発生して
作動液圧Ｐ（Ｆ）が異常に小さくなると、入口液
圧Ｐ（IN）＞作動液圧Ｐ（Ｆ）となつて、差動ピス
トン２５がバルブ体２８との隙間ｔを増加する方
向に移動されるので、急ブレーキを踏んだときで
も、マスターシリンダから供給される高い入口液
圧Ｐ（IN）がそのまま出口液圧Ｐ（OUT）として
出力されるので、出口液圧Ｐ（OUT）が減少する
ことなく増加するから、後輪ブレーキシステムが
強力に作用するようになり、全体のブレーキ力が
不足することがなくなる。 On the other hand, if an abnormality occurs in the front wheel brake system and the working fluid pressure P (F) becomes abnormally small, the inlet fluid pressure P (IN) > the working fluid pressure P (F), and the differential piston 25 moves to the valve body. Since it is moved in the direction of increasing the gap t with 28, even when the brake is suddenly applied, the high inlet hydraulic pressure P (IN) supplied from the master cylinder is output as the outlet hydraulic pressure P (OUT). Therefore, the outlet hydraulic pressure P(OUT) increases without decreasing, so the rear wheel brake system works more strongly, and the overall braking force is not insufficient.
また、差動ピストン２５の液圧入口１６側が小
径受圧面２５ａに、液圧作用口１３側が大径受圧
面２５ｂに形成されているから、この面積差によ
り、マスターシリンダ９の差圧による差動ピスト
ン２５の微少振動が有効に防止できる。 In addition, since the hydraulic pressure inlet 16 side of the differential piston 25 is formed as a small diameter pressure receiving surface 25a, and the hydraulic pressure operation port 13 side is formed as a large diameter pressure receiving surface 25b, this area difference allows the differential pressure due to the differential pressure of the master cylinder 9 to Minute vibrations of the piston 25 can be effectively prevented.
第３図ｂは、FF車用のＸ配管の例を示し、そ
の作用は第３図ａの場合とほぼ同様である。 FIG. 3b shows an example of an X-piping for a front-wheel drive vehicle, and its operation is almost the same as that shown in FIG. 3a.
第１図は本考案に係るプロポーシヨンニングバ
ルブの断面図、第２図は第１図のバルブの液圧変
化を示すグラフ、第３図ａはFR配管を示す平面
図、第３図ｂはＸ配管を示す平面図、第４図は従
来のプロポーシヨンニングバルブの断面図、第５
図は第４図のバルブの液圧変化を示すグラフ、第
６図ａはFR配管を示す平面図、第６図ｂはＸ配
管を示す平面図である。
１０……プロポーシヨンニングバルブ、１１…
…バルブ本体、１３……液圧作用口、１５……液
圧入口、１６……液圧出口、１７……主ピスト
ン、１７ａ……小径受圧面、１７ｂ……大径受圧
面、１８……流体通孔、２２……コイルばね、２
５……差動ピストン、２５ａ……小径受圧面、２
５ｂ……大径受圧面、２８……バルブ体、Ｐ
（IN）……入口液圧、Ｐ（OUT）……出口液圧、
Ｐ（Ｆ）……作用液圧、ｔ……隙間。
Fig. 1 is a sectional view of the proportioning valve according to the present invention, Fig. 2 is a graph showing changes in hydraulic pressure of the valve in Fig. 1, Fig. 3a is a plan view showing the FR piping, and Fig. 3b is A plan view showing the X piping, Figure 4 is a sectional view of a conventional proportioning valve, and Figure 5 is a sectional view of a conventional proportioning valve.
The figures are graphs showing changes in the hydraulic pressure of the valve in Fig. 4, Fig. 6a is a plan view showing the FR piping, and Fig. 6b is a plan view showing the X piping. 10...proportioning valve, 11...
...Valve body, 13...Hydraulic pressure acting port, 15...Hydraulic pressure inlet, 16...Hydraulic pressure outlet, 17...Main piston, 17a...Small diameter pressure receiving surface, 17b...Large diameter pressure receiving surface, 18... Fluid hole, 22...Coil spring, 2
5...Differential piston, 25a...Small diameter pressure receiving surface, 2
5b...Large diameter pressure receiving surface, 28...Valve body, P
(IN)...Inlet fluid pressure, P(OUT)...Outlet fluid pressure,
P(F)... Working fluid pressure, t... Gap.
Claims (1)
ブ本体内に、液圧入口側が小径受圧面に、液圧出
口側が大径受圧面にそれぞれ形成され、軸方向に
流体通孔を有する主ピストンが嵌合され、該主ピ
ストンは、大径受圧面側にばねで付勢されるとと
もに、該主ピストンの小径受圧面側に、主ピスト
ンの流体通孔の開口と所定の隙間を隔てて対向す
るバルブ体が設けられたプロポーシヨンニングバ
ルブにおいて、 上記バルブ本体の液圧入口側に、液圧作用口を
設ける一方、該バルブ本体内に、液圧入口側が小
径受圧面に、液圧作用口側が大径受圧面にそれぞ
れ形成された差動ピストンを嵌合するとともに、
該差動ピストンと上記バルブ体とを連結したこと
を特徴とするプロポーシヨンニングバルブ。[Claim for Utility Model Registration] Inside the cylindrical valve body having a hydraulic inlet and a hydraulic outlet, the hydraulic inlet side is formed as a small-diameter pressure receiving surface, and the hydraulic pressure outlet side is formed as a large-diameter pressure receiving surface, and the valve body is formed in the axial direction. A main piston having a fluid passage hole is fitted, and the main piston is urged by a spring toward the large diameter pressure receiving surface side, and has an opening of the fluid passage hole of the main piston on the small diameter pressure receiving surface side of the main piston. In a proportioning valve having valve bodies facing each other with a predetermined gap, a hydraulic pressure acting port is provided on the hydraulic inlet side of the valve body, and a small diameter pressure receiving port is provided in the valve body on the hydraulic inlet side. A differential piston whose hydraulic pressure application port side is formed on the large-diameter pressure receiving surface is fitted to the surface, and
A proportioning valve characterized in that the differential piston and the valve body are connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8884084U JPS613769U (en) | 1984-06-14 | 1984-06-14 | Proportioning valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8884084U JPS613769U (en) | 1984-06-14 | 1984-06-14 | Proportioning valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS613769U JPS613769U (en) | 1986-01-10 |
| JPH0236772Y2 true JPH0236772Y2 (en) | 1990-10-05 |
Family
ID=30642361
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8884084U Granted JPS613769U (en) | 1984-06-14 | 1984-06-14 | Proportioning valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS613769U (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10088850B2 (en) * | 2017-01-25 | 2018-10-02 | Goodrich Corporation | Brake pressure reducer valve with input pressure change compensation |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4938237A (en) * | 1972-08-18 | 1974-04-09 | ||
| JPS55123554A (en) * | 1979-03-16 | 1980-09-24 | Sumitomo Electric Ind Ltd | Follow-up valve |
-
1984
- 1984-06-14 JP JP8884084U patent/JPS613769U/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4938237A (en) * | 1972-08-18 | 1974-04-09 | ||
| JPS55123554A (en) * | 1979-03-16 | 1980-09-24 | Sumitomo Electric Ind Ltd | Follow-up valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS613769U (en) | 1986-01-10 |
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