JPH02185846A - Antilock device - Google Patents
Antilock deviceInfo
- Publication number
- JPH02185846A JPH02185846A JP426789A JP426789A JPH02185846A JP H02185846 A JPH02185846 A JP H02185846A JP 426789 A JP426789 A JP 426789A JP 426789 A JP426789 A JP 426789A JP H02185846 A JPH02185846 A JP H02185846A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- pressure
- valve
- liquid chamber
- chamber
- 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.)
- Pending
Links
- 239000012530 fluid Substances 0.000 claims abstract description 80
- 239000007788 liquid Substances 0.000 claims abstract description 50
- 238000010586 diagram Methods 0.000 description 6
- 230000006837 decompression Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 1
Landscapes
- Regulating Braking Force (AREA)
Abstract
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は車輌のアンチロック装置に関する。[Detailed description of the invention] [Industrial application field] The present invention relates to an anti-lock device for a vehicle.
従来、第３図に示すようなアンチロック装置が知られて
いる。Conventionally, an anti-lock device as shown in FIG. 3 has been known.
このアンチロック装置は、レギュレータ５１に、ピスト
ン５２を嵌入し、ピストン５２後面の液圧室５を、マス
ターシリンダＭ／Ｃの第２液室に接続し、ピストン５２
前面の制御液室１０を、球形の弁１２を介挿した圧液路
１１でアキュムレータ１９に接続し、ピストン５２の前
進で球形の弁１２を押圧して圧液路１１を開き、ピスト
ン５２の後退で圧液路１１を閉ざし、さらに、前記後退
に続くピストン５２の後退で、ピストン５２の前端部が
球形の弁１２から離れて、制御液室１０とリザーバ２５
を接続する液排出路２３を開くように形成しである。In this anti-lock device, a piston 52 is fitted into a regulator 51, a hydraulic chamber 5 on the rear surface of the piston 52 is connected to a second hydraulic chamber of a master cylinder M/C, and the piston 52 is connected to a second hydraulic chamber of a master cylinder M/C.
The control fluid chamber 10 on the front side is connected to the accumulator 19 through a pressure fluid path 11 with a spherical valve 12 inserted therein, and when the piston 52 advances, the spherical valve 12 is pressed to open the pressure fluid path 11. The pressure fluid path 11 is closed by the retraction, and further, the front end of the piston 52 is separated from the spherical valve 12 by the retraction of the piston 52 following the retraction, and the control fluid chamber 10 and the reservoir 25 are closed.
It is formed so as to open a liquid discharge path 23 connecting the two.
そして、マスターシリンダＭ／Ｃの第１液室をプロボー
シタニングバルブＰ−Ｃ−Ｖと第１カット弁２８を順次
介挿したブレーキ液路２９でリヤ側のホイールシリンダ
Ｗ／Ｃ−Ｒｒに接続し、第１カット弁２８を第１減圧ピ
ストン３３の前進で押し開くように形成し、第１減圧ピ
ストン３３前面の前部液室３４を、リヤ側のホイールシ
リンダＷ／Ｃ−Ｒｒに接続し、第１減圧ピストン３３後
面の後部液室３５を、常開型電磁弁よりなる第１ホール
ドバルブ３９を介して第１レギュレータｌの制御液室１
０に接続すると共に、常閉型電磁弁よりなる第１ディケ
イバルブ４０を介してリザーバ２５に接続しである。Then, the first fluid chamber of the master cylinder M/C is connected to the rear wheel cylinder W/C-Rr through the brake fluid path 29 in which the Probos tanning valve P-C-V and the first cut valve 28 are sequentially inserted. The first cut valve 28 is formed to be pushed open by the forward movement of the first pressure reducing piston 33, and the front liquid chamber 34 in front of the first pressure reducing piston 33 is connected to the rear wheel cylinder W/C-Rr. The rear liquid chamber 35 on the rear surface of the first pressure reducing piston 33 is connected to the control liquid chamber 1 of the first regulator l via the first hold valve 39 which is a normally open type solenoid valve.
0 and is also connected to the reservoir 25 via a first decay valve 40 which is a normally closed electromagnetic valve.
また、マスターシリンダＭ／Ｃの第２液室をカット弁７
８を介挿したブレーキ液路２９でフロント側のホイール
シリンダＷ／Ｃ−Ｆｔに接続し、カット弁７８を減圧ピ
ストン８３の前進で押し開くように形成し、減圧ピスト
ン８３前面の前部液室３４を、フロント側のホイールシ
リンダＷ／Ｃ−Ｆｒに接続し、減圧ピストン８３後面の
後部液室３５を、常開型電磁弁よりなるホールドバルブ
８９を介してレギュレータ５１の制御液室１０に接続す
ると共に、常閉型電磁弁よりなるディケイバルブ９０を
介してリザーバ２５に接続したアンチロック装置である
。Also, the second liquid chamber of the master cylinder M/C is connected to the cut valve 7.
The cut valve 78 is connected to the front wheel cylinder W/C-Ft by a brake fluid path 29 inserted with a brake fluid passage 8 inserted therein, and the cut valve 78 is formed so as to be pushed open by the forward movement of the pressure reducing piston 83. 34 is connected to the front wheel cylinder W/C-Fr, and the rear liquid chamber 35 on the rear surface of the pressure reducing piston 83 is connected to the control liquid chamber 10 of the regulator 51 via a hold valve 89 which is a normally open electromagnetic valve. In addition, the anti-lock device is connected to the reservoir 25 via a decay valve 90 which is a normally closed solenoid valve.
また、このようなレギュレータを備えたアンチロック装
置として特開昭６２−１８７６４５号公報がある。Further, there is an anti-lock device equipped with such a regulator in Japanese Patent Laid-Open No. 187645/1983.
第３図に示すアンチロック装置は、レギュレータ５１の
液圧室５に、マスターシリンダＭ／Ｃより導入されてい
る液圧が、制御液室ｌＧの制御液圧よりも高くなるとピ
ストン５２が前進して弁１２を開き、制御液室１０にア
キュムレータ１９から圧液を供給し、制御液室１０の制
御液圧が液圧室５の液圧よりも高くなると弁１２が閉ざ
される。In the anti-lock device shown in FIG. 3, when the hydraulic pressure introduced from the master cylinder M/C into the hydraulic pressure chamber 5 of the regulator 51 becomes higher than the control hydraulic pressure in the control liquid chamber lG, the piston 52 moves forward. The valve 12 is opened to supply pressure fluid from the accumulator 19 to the control fluid chamber 10, and when the control fluid pressure in the control fluid chamber 10 becomes higher than the fluid pressure in the fluid pressure chamber 5, the valve 12 is closed.
したがって、フロント側のホイールシリンダＷ／Ｃ−Ｆ
ｔのブレーキ液圧と制御液圧は、第４図に示すようにバ
ランスしており、アンチロック制御時に、後部液室３５
の減圧に対応して減圧ピストン８３が直ちに後退し、ブ
レーキ液圧の減圧遅れは発生しない。Therefore, the front wheel cylinder W/C-F
The brake fluid pressure at t and the control fluid pressure are balanced as shown in Figure 4, and during anti-lock control, the rear fluid chamber 35
The pressure reducing piston 83 immediately retreats in response to the pressure reduction, and no delay in reducing the brake fluid pressure occurs.
しかしながら、リヤ側のホイールシリンダＷ／Ｃ−Ｒｒ
に供給されるブレーキ液圧は、プロボーシジニングバル
ブｐ−ｃ−ｖを経て供給されているので、ピストンスプ
リング６の押圧力である規定圧Ｐｋ以上になると、第４
図に示すように、制御液圧よりも減圧された液圧となり
、制御液圧とリヤ側のブレーキ液圧との間に圧力差ΔＰ
は生じる。However, the rear wheel cylinder W/C-Rr
Since the brake fluid pressure supplied to
As shown in the figure, the hydraulic pressure is lower than the control hydraulic pressure, and there is a pressure difference ΔP between the control hydraulic pressure and the rear brake hydraulic pressure.
occurs.
したがって、アンチロック制御時に、後部液室３５の減
圧を開始しても、圧力差ΔＰの減圧に要する時間だけ第
１減圧ピストン３３の後退が遅れる。Therefore, even if pressure reduction of the rear liquid chamber 35 is started during anti-lock control, the retreat of the first pressure reduction piston 33 is delayed by the time required to reduce the pressure difference ΔP.
本発明は前記事項に鑑みなされたものであり、マスター
シリンダＭ／Ｃの液圧に対して、ブレーキ液圧を減圧し
て供給する装置において、アンチロック制御時の減圧遅
れを防止できるようにすることを技術的課題とする。The present invention has been made in view of the above-mentioned problems, and is intended to prevent a delay in pressure reduction during anti-lock control in a device that supplies brake fluid pressure after reducing it with respect to the fluid pressure of a master cylinder M/C. This is a technical issue.
本発明は、第１レギュレータｌに、小径ピストン３と大
径ピストン４を連結した段付ピストン２を嵌入し、小径
ピストン３後而の液圧室５を、マスターシリンダＭ／Ｃ
の第１液室に接続し、大径ピストン４前而の制御液室１
０を、弁１２を介挿した圧液路１１で圧液源１７に接続
し、段付ピストン２の前進で弁１２を押圧して圧液路１
１を開き、段付ピストン２の後退で圧液路１１を閉ざし
、さらに、前記後退に続く段付ピストン２の後退で制御
液室１０とリザーバ２５を接続する液排出路２３を開く
ように形成し、そして、マスターシリンダＭ／Ｃの第１
液室を、第１カット弁２８を介挿したブレーキ液路２９
でホイールシリンダＷ／Ｃに接続し、第１カット弁２８
を第１減圧ピストン３３の前進で押し開くように形成し
、第１減圧ピストン３３前面の前部液室３４を、ホイー
ルシリンダＷ／Ｃに接続するブレーキ液路２９に接続し
、第１減圧ピストン３３後面の後部液室３５を、第１ホ
ールドバルブ３９を介して第１レギュレータｌの制御液
室１０に接続すると共に、第１ディケイバルブ４０を介
してリザーバ２５に接続したアンチロック装置とした。In the present invention, a stepped piston 2 connecting a small-diameter piston 3 and a large-diameter piston 4 is fitted into a first regulator l, and a hydraulic chamber 5 behind the small-diameter piston 3 is connected to a master cylinder M/C.
control liquid chamber 1 in front of the large diameter piston 4.
0 is connected to a pressure fluid source 17 through a pressure fluid path 11 with a valve 12 inserted therein, and the valve 12 is pressed by the forward movement of the stepped piston 2 to open the pressure fluid path 1.
1 is opened, the pressure fluid path 11 is closed when the stepped piston 2 retreats, and the fluid discharge path 23 connecting the control fluid chamber 10 and the reservoir 25 is opened when the stepped piston 2 retreats following the retreat. Then, the first of the master cylinder M/C
The fluid chamber is connected to a brake fluid path 29 with a first cut valve 28 inserted therein.
Connect to the wheel cylinder W/C with the first cut valve 28.
The front fluid chamber 34 on the front surface of the first pressure reducing piston 33 is connected to the brake fluid path 29 connected to the wheel cylinder W/C, and the first pressure reducing piston A rear liquid chamber 35 on the rear surface of 33 is connected to the control liquid chamber 10 of the first regulator 1 via a first hold valve 39 and connected to the reservoir 25 via a first decay valve 40, forming an anti-lock device.
本発明は、ブレーキの非作動時には、第１レギュレータ
１の弁１２が閉じ、圧液源１７の圧力ＰＡは制御液室１
０に作用せず、ピストンスプリング６によって決定され
る規定圧Ｐｋが制御液室１０に残っている。In the present invention, when the brake is not operated, the valve 12 of the first regulator 1 is closed, and the pressure PA of the pressure fluid source 17 is reduced to the control fluid chamber 1.
0, and the specified pressure Pk determined by the piston spring 6 remains in the control liquid chamber 10.
ブレーキ制動時に、マスターシリンダＭ／Ｃの液圧ＰＭ
と、小径ピストン３の断面積ＡＳの積である押圧力が、
規定圧Ｐｋと大径ピストン４の断面積ＡＬの積である押
圧力以上になると、第１レギュレータｌの段付ピストン
２は前進して弁１２を開き、圧液源１７の圧液が制御液
室１０に導入され、制御液圧が第２図に示すように上昇
する。When applying the brake, the hydraulic pressure PM of the master cylinder M/C
The pressing force, which is the product of the cross-sectional area AS of the small diameter piston 3, is
When the pressing force exceeds the product of the specified pressure Pk and the cross-sectional area AL of the large-diameter piston 4, the stepped piston 2 of the first regulator 1 advances to open the valve 12, and the pressure fluid in the pressure fluid source 17 flows into the control fluid. is introduced into the chamber 10, and the control fluid pressure increases as shown in FIG.
制御液圧が上昇し、小径ピストン３を押圧するマスター
シリンダＭ／Ｃの液圧と、ピストンスプリング６とによ
る押圧力が、大径ピストン４を押圧する制御液圧による
押圧力とバランスすると、弁１２は閉状態となり、圧液
源１７からの圧液の導入は停止する。When the control hydraulic pressure increases and the hydraulic pressure of the master cylinder M/C that presses the small diameter piston 3 and the pressing force of the piston spring 6 are balanced with the pressing force of the control hydraulic pressure that presses the large diameter piston 4, the valve 12 is in a closed state, and the introduction of pressure liquid from the pressure liquid source 17 is stopped.
さらに、この動作を繰り返し行なうことにより、制御液
圧は、マスターシリンダＭ／Ｃの液圧ＰＭに対して、小
径ピストン３の断面積ＡＳと大径ピストン４の断面積Ａ
Ｌの比によって減圧された圧力となる。Furthermore, by repeating this operation, the controlled hydraulic pressure is adjusted to the cross-sectional area AS of the small-diameter piston 3 and the cross-sectional area A of the large-diameter piston 4 with respect to the hydraulic pressure PM of the master cylinder M/C.
The pressure is reduced depending on the ratio of L.
この関係は次式で表わされる。This relationship is expressed by the following equation.
ここでＰＭ≧Ｐｋであり、
ＰＣは制御液圧、ＡＳは小径ピストン２の断面積、ＡＬ
は大径ピストン３の断面積、ＰＭはマスターシリンダＭ
／Ｃの液圧、ｆはピストンスプリング６の押圧力、Ｐ＾
は圧液源１９の液圧、ＡＶは弁１２の断面積である。Here, PM≧Pk, PC is the control hydraulic pressure, AS is the cross-sectional area of the small diameter piston 2, and AL
is the cross-sectional area of the large diameter piston 3, PM is the master cylinder M
/C hydraulic pressure, f is the pressing force of the piston spring 6, P^
is the hydraulic pressure of the pressure liquid source 19, and AV is the cross-sectional area of the valve 12.
そして、この系統のブレーキ液圧は、第１レギュレータ
ｌの制御液圧と同圧力でコントロールされるので、ブレ
ーキ液圧は、規定圧Ｐｋを折点とし、ある減圧比ｔａｎ
θ を持った液圧となり、ブロポーショニングバルブＰ
−ＣＩＩ■の作用も同時に行なう。Since the brake fluid pressure in this system is controlled at the same pressure as the control fluid pressure of the first regulator l, the brake fluid pressure has the specified pressure Pk as the turning point and a certain pressure reduction ratio tan.
The liquid pressure becomes θ, and the blow-portioning valve P
The action of -CII■ also takes place at the same time.
第１図は本発明の一実施例を示す系統図で第２図はその
液圧線図である。FIG. 1 is a system diagram showing one embodiment of the present invention, and FIG. 2 is a hydraulic pressure diagram thereof.
この実施例は、マスターシリンダＭ／Ｃの第１液室から
リヤ側のホイールシリンダＷ／Ｃ−Ｒｒに接続する一方
の系統と、他方の第２液室からフロント側のホイールシ
リンダＷ／Ｃ−Ｆｒに接続する他方の系統を有するアン
チロック装置である。In this embodiment, one system connects the first fluid chamber of the master cylinder M/C to the rear wheel cylinder W/C-Rr, and the other system connects the second fluid chamber to the front wheel cylinder W/C-Rr. This is an anti-lock device that has the other system connected to Fr.
この実施例は、一方の系統に設置された第１レギュレー
タ１に、小径ピストン３と大径ピストン４を連結した段
付ピストン２を嵌入し、小径ピストン３後面を、ピスト
ンスプリング６で押圧付勢すると共に、後面に形成され
た液圧室５を、マスターシリンダＭ／Ｃの第１液室に接
続し、大径ピストン４前面の制御液室ＩＯを、球形の弁
１２を介挿した圧液路１１で、ポンプ１８とアキュムレ
ータ１９とからなる圧液源１７に接続し、段付ピストン
２の前進で弁用スプリング１３に抗して弁１２を押圧し
て圧液路１１を開き、段付ピストン２の後退で圧液路１
１を閉ざし、さらに、前記後退に続く段付ピストン２の
後退で、大径ピストン４の前面が弁１２から離れ、制御
液室１０とリザーバ２５を接続する液排出路２３を開き
、制御液室１０の液をリザーバ２５に排出できるように
形成しである。In this embodiment, a stepped piston 2 in which a small-diameter piston 3 and a large-diameter piston 4 are connected is fitted into a first regulator 1 installed in one system, and the rear surface of the small-diameter piston 3 is pressed and biased by a piston spring 6. At the same time, the hydraulic pressure chamber 5 formed on the rear surface is connected to the first fluid chamber of the master cylinder M/C, and the control fluid chamber IO on the front surface of the large diameter piston 4 is connected to the pressure fluid chamber 5 formed on the rear surface with a spherical valve 12 inserted. The passage 11 is connected to a pressure fluid source 17 consisting of a pump 18 and an accumulator 19, and the forward movement of the stepped piston 2 pushes the valve 12 against the valve spring 13 to open the pressure fluid passage 11. Pressure fluid path 1 opens when piston 2 retreats.
Further, as the stepped piston 2 retreats following the aforementioned retreat, the front surface of the large diameter piston 4 separates from the valve 12, opening the fluid discharge path 23 connecting the control fluid chamber 10 and the reservoir 25, and opening the fluid discharge path 23 connecting the control fluid chamber 10 and the reservoir 25. 10 liquids can be discharged into the reservoir 25.
そして、マスターシリンダＭ／Ｃの第１液室を、第１カ
ット弁２８を介挿したブレーキ液路２９でリヤ側のホイ
ールシリンダＷ／Ｃ−Ｒｒに接続し、第１カット弁２８
を第１減圧ピストン３３の前進で押し開くように形成し
、第１減圧ピストン３３前面の前部液室３４を、リヤ側
のホイールシリンダＷ／Ｃ・Ｒｒに接続するブレーキ液
路２９に接続し、第１減圧ピストン３３後面に形成した
後部液室３５を、第１ホールドバルブ３９を介して第１
レギュレータｌの制御液室１０に接続すると共に、第１
ディケイバルブ４０を介してリザーバ２５に接続しであ
る。Then, the first fluid chamber of the master cylinder M/C is connected to the rear wheel cylinder W/C-Rr through the brake fluid path 29 in which the first cut valve 28 is inserted.
The front fluid chamber 34 on the front surface of the first pressure reducing piston 33 is connected to the brake fluid path 29 connected to the rear wheel cylinder W/C/Rr. , the rear liquid chamber 35 formed on the rear surface of the first pressure reducing piston 33 is connected to the first pressure reducing piston 33 via the first hold valve 39.
It is connected to the control liquid chamber 10 of the regulator l, and the first
It is connected to the reservoir 25 via a decay valve 40.
そして、他方の系統に設置されたレギュレータ５１には
、ピストン５２を嵌入し、ピストン５２後面を、ピスト
ンスプリング６で押圧付勢すると共に、後面に形成され
た液圧室５を、マスターシリンダＭ／Ｃの他方の第２液
室に接続し、ピストン５２前面の制御液室１０を、球形
の弁１２を介挿した圧液路１１で、ポンプ１Ｂとアキュ
ムレータ１９に接続し、ピストン５２の前進で、弁用ス
プリング１３に抗して弁１２を押圧して圧液路！１を開
き、ピストン５２の後退で圧液路Ｕを閉ざし、さらに、
前記後退に続くピストン５２の後退で、ピストン５２の
前面が弁１２から離れて、制御液室１０の液をリザーバ
２５に排出できるように形成しである。A piston 52 is fitted into the regulator 51 installed in the other system, and the rear surface of the piston 52 is pressed and biased by the piston spring 6, and the hydraulic chamber 5 formed on the rear surface is connected to the master cylinder M/ The control liquid chamber 10 on the front side of the piston 52 is connected to the pump 1B and the accumulator 19 through a pressure liquid passage 11 with a spherical valve 12 inserted therein. , press the valve 12 against the valve spring 13 to open the pressure fluid path! 1 is opened, the pressure fluid path U is closed by the retreat of the piston 52, and further,
When the piston 52 retreats following the aforementioned retreat, the front surface of the piston 52 separates from the valve 12, so that the liquid in the control liquid chamber 10 can be discharged into the reservoir 25.
そして、マスターシリンダＭ／Ｃの他方の第２液室は、
カット弁７８を介挿したブレーキ液路２９でフロント側
の中イールシリンダＷ／Ｃ−Ｐｉに接続し、カット弁７
８を減圧ピストン８３の前進で押し開くように形成し、
減圧ピストン８３前面の前部液室３４を、フロント側の
ホイールシリンダＷ／Ｃ・Ｆｔに接続するブレーキ液路
２９に接続し、減圧ピストン８３後面に形成した後部液
室３５を、ホールドバルブ８９を介してレギュレータ５
１の制御液室１０に接続すると共に、ディケイバルブ９
０を介してリザーバ２５に接続した。The other second liquid chamber of the master cylinder M/C is
A brake fluid path 29 with a cut valve 78 inserted therein is connected to the front middle eel cylinder W/C-Pi, and the cut valve 7
8 is formed to be pushed open by the advancement of the decompression piston 83,
The front fluid chamber 34 on the front surface of the pressure reducing piston 83 is connected to the brake fluid path 29 that connects to the front wheel cylinder W/C・Ft, and the rear fluid chamber 35 formed on the rear surface of the pressure reducing piston 83 is connected to the hold valve 89. via regulator 5
1 and the decay valve 9.
0 to the reservoir 25.
本発明は、第１レギユレータ１に、段付ピストン２を嵌
入し、制御液室１０の制御液圧を、大径ピストン４と小
径ピストン３の断面積の比に比例して減圧した制御液圧
とし、この減圧した制御液圧を、第１減圧ピストン３３
後面の後部液室３５に導入し、この後部液室３５の液圧
と、前部液室３４に作用するホイールシリンダＷ／Ｃの
ブレーキ液圧との圧力差によりカット弁２８を開閉する
ので、前部液室３４と後部液室３５の液圧が路間−圧力
となり、液圧差が存在しない。したがって、アンチロッ
ク制御時に、後部液室３５の減圧に対応して直ちに第１
減圧ピストン８３が後退し、第１カット弁２８を閉鎖す
るので、アンチロック制御時の減圧遅れを防止できる。In the present invention, a stepped piston 2 is fitted into the first regulator 1, and the control fluid pressure in the control fluid chamber 10 is reduced in proportion to the ratio of the cross-sectional areas of the large-diameter piston 4 and the small-diameter piston 3. This reduced control fluid pressure is applied to the first pressure reducing piston 33.
The cut valve 28 is opened and closed by the pressure difference between the hydraulic pressure in the rear liquid chamber 35 and the brake hydraulic pressure of the wheel cylinder W/C acting on the front liquid chamber 34. The hydraulic pressures in the front liquid chamber 34 and the rear liquid chamber 35 are equal to the road pressure, and there is no difference in liquid pressure. Therefore, during anti-lock control, the first
Since the pressure reducing piston 83 retreats and closes the first cut valve 28, a delay in pressure reduction during anti-lock control can be prevented.
また、前記の如く、第１減圧ピストン３３の後部液室３
５に作用する第１レギユレータｌの制御液室１０の制御
液圧を減圧した液圧とし、前部液室３４の液圧が後部液
室３５と同一圧力となっているので、マスターシリンダ
Ｍ／Ｃと第１カット弁２８を接続する液路にプロボーシ
ジニングバルブＰ−Ｃ・■を介挿する必要もなくなった
。Further, as described above, the rear liquid chamber 3 of the first decompression piston 33
The control fluid pressure in the control fluid chamber 10 of the first regulator L acting on the first regulator L is a reduced fluid pressure, and the fluid pressure in the front fluid chamber 34 is the same as that of the rear fluid chamber 35, so that the master cylinder M/ It is no longer necessary to insert the provosizing valve P-C into the liquid path connecting C and the first cut valve 28.
第１図は本発明の一実施例の系統図、第２図はその液圧
線図、第３図は従来例の系統図、第４図はその液圧線図
である。
１・・第ルギュレー夕、
２・・段付ピストン、 ３・
４・・大径ピストン、 ５・
１０・・制御液室、 １１・
１２・・弁、 １７・
２３・・液排出路、 ２５・
２８・・第１カット弁、 ２９・
３３・・第１減圧ピストン、
３４・・前部液室、 ３５・・後部液室、３９・・
第１ホールドバルブ、
４０・・第１ディケイバルブ。
小径ピストン、
液圧室、
圧液路、
圧液源、
リザーバ、
ブレーキ液路、
第２図
Ｍ／Ｃ圧（ＰＭ）
第４図
Ｍ／Ｃ反FIG. 1 is a system diagram of an embodiment of the present invention, FIG. 2 is a hydraulic pressure diagram thereof, FIG. 3 is a system diagram of a conventional example, and FIG. 4 is a hydraulic pressure diagram thereof. 1. 1st regulation valve, 2. Stepped piston, 3. 4. Large diameter piston, 5. 10. Control liquid chamber, 11. 12. Valve, 17. 23. Liquid discharge path, 25. 28...First cut valve, 29...33...First pressure reducing piston, 34...Front liquid chamber, 35...Rear liquid chamber, 39...
1st hold valve, 40... 1st decay valve. Small diameter piston, hydraulic chamber, pressure fluid path, pressure fluid source, reservoir, brake fluid path, Fig. 2 M/C pressure (PM) Fig. 4 M/C counter
Claims (1)
ストン４を連結した段付ピストン２を嵌入し、小径ピス
トン３後面の液圧室５を、マスターシリンダＭ／Ｃの第
１液室に接続し、大径ピストン４前面の制御液室１０を
、弁１２を介挿した圧液路１１で圧液源１７に接続し、
段付ピストン２の前進で弁１２を押圧して圧液路１１を
開き、段付ピストン２の後退で圧液路１１を閉ざし、さ
らに、前記後退に続く段付ピストン２の後退で制御液室
１０とリザーバ２５を接続する液排出路２３を開くよう
に形成し、そして、マスターシリンダＭ／Ｃの第１液室
を、第１カット弁２８を介挿したブレーキ液路２９でホ
ィールシリンダＷ／Ｃに接続し、第１カット弁２８を第
１減圧ピストン３３の前進で押し開くように形成し、第
１減圧ピストン３３前面の前部液室３４を、ホィールシ
リンダＷ／Ｃに接続するブレーキ液路２９に接続し、第
１減圧ピストン３３後面の後部液室３５を、第１ホール
ドバルブ３９を介して第１レギュレータ１の制御液室１
０に接続すると共に、第１ディケイバルブ４０を介して
リザーバ２５に接続したアンチロック装置。(1) Fit the stepped piston 2, which connects the small-diameter piston 3 and the large-diameter piston 4, into the first regulator 1, and connect the hydraulic chamber 5 on the rear surface of the small-diameter piston 3 to the first hydraulic chamber of the master cylinder M/C. and connect the control liquid chamber 10 on the front side of the large diameter piston 4 to the pressure liquid source 17 through a pressure liquid path 11 with a valve 12 inserted therein.
The forward movement of the stepped piston 2 presses the valve 12 to open the pressure fluid passage 11, the retreat of the stepped piston 2 closes the pressure fluid passage 11, and the subsequent retreat of the stepped piston 2 opens the control liquid chamber. 10 and the reservoir 25, and the first liquid chamber of the master cylinder M/C is connected to the wheel cylinder W/C by the brake fluid path 29 in which the first cut valve 28 is inserted. The brake fluid is connected to C, the first cut valve 28 is formed to be pushed open by the advance of the first pressure reducing piston 33, and the front liquid chamber 34 in front of the first pressure reducing piston 33 is connected to the wheel cylinder W/C. 29 and connects the rear liquid chamber 35 on the rear surface of the first pressure reducing piston 33 to the control liquid chamber 1 of the first regulator 1 via the first hold valve 39.
0 and connected to the reservoir 25 via the first decay valve 40.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP426789A JPH02185846A (en) | 1989-01-11 | 1989-01-11 | Antilock device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP426789A JPH02185846A (en) | 1989-01-11 | 1989-01-11 | Antilock device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02185846A true JPH02185846A (en) | 1990-07-20 |
Family
ID=11579767
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP426789A Pending JPH02185846A (en) | 1989-01-11 | 1989-01-11 | Antilock device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH02185846A (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5313066A (en) * | 1976-07-22 | 1978-02-06 | Aisin Seiki Co Ltd | Anti-skid control system |
| JPS6053452A (en) * | 1983-09-01 | 1985-03-27 | Akebono Brake Ind Co Ltd | Hydraulic controller used for antilock control |
-
1989
- 1989-01-11 JP JP426789A patent/JPH02185846A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5313066A (en) * | 1976-07-22 | 1978-02-06 | Aisin Seiki Co Ltd | Anti-skid control system |
| JPS6053452A (en) * | 1983-09-01 | 1985-03-27 | Akebono Brake Ind Co Ltd | Hydraulic controller used for antilock control |
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