JP2008290692A - Vehicular brake fluid pressure control device - Google Patents

Vehicular brake fluid pressure control device Download PDF

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JP2008290692A
JP2008290692A JP2007191193A JP2007191193A JP2008290692A JP 2008290692 A JP2008290692 A JP 2008290692A JP 2007191193 A JP2007191193 A JP 2007191193A JP 2007191193 A JP2007191193 A JP 2007191193A JP 2008290692 A JP2008290692 A JP 2008290692A
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hydraulic pressure
pump
hydraulic
brake
reservoir
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Japanese (ja)
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Hiromi Inagaki
裕巳 稲垣
Takayuki Omori
貴之 大森
Takehiro Horiuchi
雄大 堀内
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To reduce cost by reducing the number of solenoid valves in a vehicular brake fluid pressure control device comprising a hydraulic pressure generating means, a reservoir, a pump with its suction side connected to the reservoir, a normally-opened solenoid valve interposed between a hydraulic passage connected to the discharge side of the pump and the hydraulic pressure generating means, a wheel brake, and a directional control valve for changing the connection state of the wheel brake to the hydraulic pressure generating means and the reservoir. <P>SOLUTION: First one-way valves 11A, 11B for permitting the distribution of a brake fluid to a pump 10 side are interposed between reservoirs 8A, 8B and the pump 10. Second one-way valves 12A, 12B for permitting the distribution of the brake fluid from the pump 10 are interposed between hydraulic pressure passages 5A, 5B and the pump 10. A third one-way valve 14 for permitting the distribution of the brake fluid to the pump 10 side is interposed in a suction passage 13 with one end connected to an external reservoir R and the other end connected to the suction side of the pump 10 on the downstream side of the first one-way valves 11A, 11B. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、ブレーキ操作に応じた液圧を出力する液圧発生手段と、リザーバと、吸入側が前記リザーバに接続されるポンプと、該ポンプの吐出側に接続される液圧路および前記液圧発生手段間に介設される常開型電磁弁と、車輪ブレーキと、前記液圧路および前記車輪ブレーキ間を接続するとともに前記車輪ブレーキおよび前記リザーバ間を遮断する状態ならびに前記液圧路および前記車輪ブレーキ間を遮断するとともに前記車輪ブレーキおよび前記リザーバ間を接続する状態を切換可能な切換弁手段とを備える車両用ブレーキ液圧制御装置に関する。   The present invention includes a hydraulic pressure generating means for outputting a hydraulic pressure corresponding to a brake operation, a reservoir, a pump whose suction side is connected to the reservoir, a hydraulic pressure path connected to the discharge side of the pump, and the hydraulic pressure A normally open solenoid valve interposed between the generating means, a wheel brake, a state in which the hydraulic pressure path and the wheel brake are connected, and a state in which the wheel brake and the reservoir are disconnected, and the hydraulic pressure path and the The present invention relates to a vehicular brake hydraulic pressure control device that includes switching valve means that cuts off a wheel brake and can switch a state of connecting the wheel brake and the reservoir.

このような車両用ブレーキ液圧制御装置は、たとえば特許文献１等で既に良く知られている。
特開２００４−３４１８３３号公報 Such a vehicle brake hydraulic pressure control device is already well known, for example, in Patent Document 1 and the like.
JP 2004-341833 A

ところが、上記特許文献１で開示されたブレーキ液圧制御装置では、液圧系統を２系統とした４輪車両用ブレーキ装置の場合には、各車輪ブレーキ毎の切換弁手段と、各液圧系統に個別に対応した一対のポンプと、マスタシリンダに付設された外部リザーバおよび両ポンプの吸入側間にそれぞれ介設される常閉型電磁弁と、両ポンプの吐出側が個別に接続される液圧路およびマスタシリンダ間にそれぞれ介設される常開型電磁弁とが必要であり、電磁弁の個数が多くなり、コストの増大にもつながっている。   However, in the brake hydraulic pressure control device disclosed in Patent Document 1, in the case of a four-wheel vehicle brake device having two hydraulic systems, the switching valve means for each wheel brake and each hydraulic system are provided. A pair of pumps individually corresponding to each other, an external reservoir attached to the master cylinder, a normally closed solenoid valve interposed between the suction sides of both pumps, and a hydraulic pressure at which the discharge sides of both pumps are individually connected A normally-open solenoid valve interposed between the passage and the master cylinder is required, which increases the number of solenoid valves, leading to an increase in cost.

本発明は、かかる事情に鑑みてなされたものであり、電磁弁の個数を少なくしてコスト低減を可能とした車両用ブレーキ液圧制御装置を提供することを目的とする。   The present invention has been made in view of such circumstances, and an object of the present invention is to provide a vehicular brake hydraulic pressure control device capable of reducing the cost by reducing the number of solenoid valves.

上記目的を達成するために、請求項１記載の発明は、ブレーキ操作に応じた液圧を出力する液圧発生手段と、リザーバと、吸入側が前記リザーバに接続されるポンプと、該ポンプの吐出側に接続される液圧路および前記液圧発生手段間に介設される常開型電磁弁と、車輪ブレーキと、前記液圧路および前記車輪ブレーキ間を接続するとともに前記車輪ブレーキおよび前記リザーバ間を遮断する状態ならびに前記液圧路および前記車輪ブレーキ間を遮断するとともに前記車輪ブレーキおよび前記リザーバ間を接続する状態を切換可能な切換弁手段とを備える車両用ブレーキ液圧制御装置において、前記ポンプ側へのブレーキ液の流通を許容するようにして前記リザーバおよび前記ポンプの吸入側間に介設される第１一方向弁と、前記ポンプからのブレーキ液の流通を許容するようにして前記液圧路および前記ポンプの吐出側間に介設される第２一方向弁と、前記液圧発生手段に付設される外部リザーバと、該外部リザーバに一端が接続されるとともに第１一方向弁よりも下流側で前記ポンプの吸入側に他端が接続される吸入路に介設されて前記ポンプ側へのブレーキ液の流通を許容する第３一方向弁とを含むことを特徴とする。   In order to achieve the above object, the invention described in claim 1 is a fluid pressure generating means for outputting a fluid pressure corresponding to a brake operation, a reservoir, a pump whose suction side is connected to the reservoir, and a discharge of the pump. A hydraulic pressure path connected to the side and a normally open solenoid valve interposed between the hydraulic pressure generating means, a wheel brake, and the hydraulic pressure path and the wheel brake, and the wheel brake and the reservoir In a vehicle brake hydraulic pressure control device, comprising: a switching valve means capable of switching between a state of shutting off and a state of shutting off between the hydraulic pressure path and the wheel brake and connecting between the wheel brake and the reservoir; A first one-way valve interposed between the reservoir and the suction side of the pump so as to allow the brake fluid to flow to the pump side; A second one-way valve interposed between the hydraulic pressure passage and the discharge side of the pump so as to allow a brake fluid to flow, an external reservoir attached to the hydraulic pressure generating means, and an external reservoir A third one is connected to one end of the suction passage and connected to the suction side of the pump on the downstream side of the first one-way valve and allows the brake fluid to flow to the pump side. And a directional valve.

また請求項２記載の発明は、請求項１記載の発明の構成に加えて、前記第２一方向弁および前記液圧路間に常閉型電磁弁が介設され、該常閉型電磁弁および前記第２一方向弁間に蓄圧器が接続されることを特徴とする。   According to a second aspect of the invention, in addition to the configuration of the first aspect of the invention, a normally closed electromagnetic valve is interposed between the second one-way valve and the hydraulic pressure path, and the normally closed electromagnetic valve A pressure accumulator is connected between the second one-way valve.

請求項３記載の発明は、請求項１または２記載の発明の構成に加えて、前記液圧発生手段が備える一対の出力ポートにそれぞれ連なる一対の液圧系統に、前記リザーバ、前記常開型電磁弁、前記切換弁手段、第１一方向弁および第２一方向弁がそれぞれ設けられ、前記両液圧系統に共通な単一の前記第３一方向弁が前記吸入路に介設されることを特徴とする。   According to a third aspect of the present invention, in addition to the configuration of the first or second aspect of the invention, the reservoir, the normally open type are connected to a pair of hydraulic systems respectively connected to a pair of output ports provided in the hydraulic pressure generating means. An electromagnetic valve, the switching valve means, a first one-way valve, and a second one-way valve are provided, respectively, and the single third one-way valve common to both the hydraulic systems is interposed in the suction passage. It is characterized by that.

請求項４記載の発明は、請求項１〜３のいずれかに記載の発明の構成に加えて、共通な単一の電動モータで駆動されるとともに出力タイミングの位相がずれた複数の前記ポンプが並列接続されることを特徴とする。   According to a fourth aspect of the invention, in addition to the configuration of the first aspect of the invention, a plurality of the pumps driven by a common single electric motor and whose output timing phases are shifted are provided. It is characterized by being connected in parallel.

請求項５記載の発明は、請求項１記載の発明の構成に加えて、前記第１一方向弁、前記第２一方向弁および前記第３一方向弁間の液圧を検出する液圧検出手段を備えることを特徴とする。   According to a fifth aspect of the invention, in addition to the configuration of the first aspect of the invention, a hydraulic pressure detection for detecting a hydraulic pressure between the first one-way valve, the second one-way valve and the third one-way valve. Means are provided.

さらに請求項６記載の発明は、請求項３記載の発明の構成に加えて、一対の前記液圧系統に個別に対応した一対の前記ポンプの吐出側に個別の第２一方向弁を介して接続されるとともに前記両液圧系統の前記液圧路に個別に通じる２つの液圧室に両端を臨ませたフリーピストンがストロークを制限されつつシリンダボディに摺動可能に嵌合されて成る脈動緩和手段を含むことを特徴とする。   In addition to the configuration of the invention described in claim 3, the invention described in claim 6 is provided via an individual second one-way valve on the discharge side of the pair of pumps individually corresponding to the pair of hydraulic systems. A pulsation formed by a free piston having both ends facing two hydraulic chambers that are connected to each other and individually connected to the hydraulic pressure paths of the both hydraulic systems and slidably fitted to the cylinder body while limiting the stroke. A mitigation means is included.

なお実施例のマスタシリンダＭが本発明の液圧発生手段に対応する。   The master cylinder M of the embodiment corresponds to the hydraulic pressure generating means of the present invention.

請求項１記載の発明によれば、非ブレーキ操作時にポンプを作動せしめるとともに常開型電磁弁の作動を制御して液圧路の液圧を調圧し、切換弁手段によって車輪ブレーキの液圧を制御することによって車両の運動を制御する際に、前記ポンプの作動開始時には外部リザーバから第３一方向弁を介してブレーキ液を直ちに吸入することが可能であり、外部リザーバおよびポンプの吸入側間に常閉型電磁弁が介設されていた従来のものと比べると、応答性を高めるとともに吸入抵抗を小さく抑えることができるとともに電磁弁の個数を低減することでコスト低減を図ることができる。また切換弁手段が車輪ブレーキおよびリザーバ間を接続したまま故障したとしても吸入路に介設されている第３一方向弁の働きによって車輪ブレーキからのブレーキ液が外部リザーバ側に流れることが阻止されるので、車輪ブレーキのブレーキ液圧が「０」となってしまうことは回避される。   According to the first aspect of the present invention, the pump is operated during non-brake operation, the operation of the normally open solenoid valve is controlled to adjust the hydraulic pressure in the hydraulic pressure path, and the hydraulic pressure of the wheel brake is adjusted by the switching valve means. When controlling the movement of the vehicle by controlling, it is possible to immediately suck the brake fluid from the external reservoir through the third one-way valve at the start of operation of the pump, and between the external reservoir and the suction side of the pump. Compared with the conventional one in which a normally closed solenoid valve is interposed, the responsiveness can be improved and the suction resistance can be kept small, and the number of solenoid valves can be reduced to reduce the cost. Even if the switching valve means fails with the wheel brake and the reservoir connected, the third one-way valve provided in the suction passage prevents the brake fluid from the wheel brake from flowing to the external reservoir side. Therefore, it is avoided that the brake fluid pressure of the wheel brake becomes “0”.

また請求項２記載の発明によれば、ポンプの吐出圧を蓄圧器に蓄圧しておき、自動ブレーキ時に常閉型電磁弁を開弁することで蓄圧器で蓄された液圧を液圧路に作用せしめるようにして、自動ブレーキ時の初期応答性を高めることができる。   According to the second aspect of the invention, the discharge pressure of the pump is stored in the accumulator, and the normally closed electromagnetic valve is opened during automatic braking so that the hydraulic pressure stored in the accumulator is supplied to the hydraulic path. It is possible to improve the initial response during automatic braking.

請求項３記載の発明によれば、２系統の液圧系統にもかかわらず、第３一方向弁を単一とするとともに、ポンプを両系統に共通なものとして部品点数を少なくすることができる。   According to the invention described in claim 3, in spite of the two hydraulic systems, the third one-way valve can be made single and the number of parts can be reduced by making the pump common to both systems. .

請求項４記載の発明によれば、出力タイミングの位相がずれた複数のポンプが並列接続されるので、液圧路に作用する液圧の脈動を低減することができる。   According to the fourth aspect of the present invention, since the plurality of pumps whose output timing phases are shifted are connected in parallel, the pulsation of the hydraulic pressure acting on the hydraulic pressure path can be reduced.

請求項５記載の発明によれば、第１一方向弁、前記第２一方向弁および前記第３一方向弁間の液圧を液圧検出手段で検出することによって、リザーバへの貯留液量を推定することが可能であり、それによりリザーバの貯留液量が大きくなったときにポンプを作動せしめるようにしてポンプの無駄な作動を回避することができ、ポンプを駆動することによる消費エネルギーを低減することが可能となるとともにポンプの作動音を静粛にしつつ良好なブレーキ操作フィーリングを得ることができる。また第２一方向弁で漏れが生じているときにも液圧発生手段の検出値変化をみることでその漏れを検出することができる。   According to the fifth aspect of the present invention, the amount of liquid stored in the reservoir is detected by detecting the hydraulic pressure among the first one-way valve, the second one-way valve, and the third one-way valve by the hydraulic pressure detecting means. Therefore, it is possible to avoid unnecessary operation of the pump by operating the pump when the amount of liquid stored in the reservoir becomes large, and the energy consumed by driving the pump can be reduced. It is possible to reduce the noise, and it is possible to obtain a good brake operation feeling while quietly operating the pump. Even when a leak occurs in the second one-way valve, the leak can be detected by looking at the change in the detection value of the hydraulic pressure generating means.

さらに請求項６記載の発明によれば、一対の液圧路にそれぞれ通じるとともに一対のポンプの吐出側に第２一方向弁をそれぞれ介して接続される２つの液圧室に、シリンダボディに摺動可能に嵌合されるフリーピストンの両端が臨むので、２つの液圧系統を分離した上で両ポンプの吐出脈動を緩和することができる。   According to the sixth aspect of the present invention, the cylinder body is slid onto the two hydraulic chambers respectively connected to the discharge sides of the pair of pumps via the second one-way valves. Since both ends of the free piston that is movably fitted face each other, the discharge pulsation of both pumps can be reduced after separating the two hydraulic systems.

以下、本発明の実施の形態を、添付の図面に示した本発明の実施例に基づいて説明する。   DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on examples of the present invention shown in the accompanying drawings.

本発明の第１実施例について図１を参照しながら説明すると、たとえば四輪車両に搭載される液圧発生手段としてのマスタシリンダＭは、ブレーキペダル１のブレーキ操作量に応じた液圧を出力可能な第１および第２出力ポート２Ａ，２Ｂを有してタンデム型に構成されるものであり、このマスタシリンダＭには外部リザーバＲが付設される。   The first embodiment of the present invention will be described with reference to FIG. 1. For example, a master cylinder M as a hydraulic pressure generating means mounted on a four-wheel vehicle outputs a hydraulic pressure corresponding to the brake operation amount of the brake pedal 1. The master cylinder M has a first and second output ports 2A and 2B that can be configured, and an external reservoir R is attached to the master cylinder M.

第１出力ポート２Ａには、左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲに対応した第１液圧系統３Ａが接続され、第２出力ポート２Ｂには、右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬに対応した第２液圧系統３Ｂが接続される。   A first hydraulic system 3A corresponding to the left front wheel brake BFL and the right rear wheel brake BRR is connected to the first output port 2A, and the right front wheel brake BFR and the second output port 2B are connected to the first output port 2A. A second hydraulic system 3B corresponding to the left rear wheel brake BRL is connected.

第１液圧系統３Ａは、第１出力ポート２Ａに接続される第１出力液圧路４Ａと、第１出力液圧路４Ａに接続される第１液圧路５Ａと、第１液圧路５Ａから分岐した分岐液圧路６Ａ，６Ｂとを有しており、両分岐液圧路６Ａ，６Ｂは、左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲにそれぞれ接続される。第２液圧系統３Ｂは、第２出力ポート２Ｂに接続される第２出力液圧路４Ｂと、第２出力液圧路４Ｂに接続される第２液圧路５Ｂと、第２液圧路５Ｂから分岐した分岐液圧路６Ｃ，６Ｄとを有しており、両分岐液圧路６Ｃ，６Ｄは、右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬにそれぞれ接続される。   The first hydraulic system 3A includes a first output hydraulic path 4A connected to the first output port 2A, a first hydraulic path 5A connected to the first output hydraulic path 4A, and a first hydraulic path Branch hydraulic pressure paths 6A and 6B branched from 5A are connected to the left front wheel brake BFL and the right rear wheel brake BRR, respectively. The second hydraulic system 3B includes a second output hydraulic path 4B connected to the second output port 2B, a second hydraulic path 5B connected to the second output hydraulic path 4B, and a second hydraulic path. Branch hydraulic pressure paths 6C and 6D branched from 5B are connected to the right front wheel brake BFR and the left rear wheel brake BRL, respectively.

第１および第２液圧路５Ａ，５Ｂには、電動モータ９で駆動されるとともに第１および第２液圧系統３Ａ，３Ｂにそれぞれ対応した第１および第２リザーバ８Ａ，８Ｂに吸入側が接続されるポンプ１０の吐出側が接続されるものであり、第１および第２リザーバ８Ａ，８Ｂと前記ポンプ１０の吸入側との間には、前記ポンプ１０側へのブレーキ液の流通を許容する第１一方向弁１１Ａ，１１Ｂがそれぞれ介設され、第１および第２液圧路５Ａ，５Ｂと前記ポンプ１０の吐出側との間には、前記ポンプ１０からのブレーキ液の流通を許容する第２一方向弁１２Ａ，１２Ｂがそれぞれ介設される。   The first and second hydraulic pressure paths 5A and 5B are connected to the first and second reservoirs 8A and 8B respectively driven by the electric motor 9 and corresponding to the first and second hydraulic pressure systems 3A and 3B, respectively. The discharge side of the pump 10 is connected, and between the first and second reservoirs 8A, 8B and the suction side of the pump 10, a brake fluid is allowed to flow to the pump 10 side. 1 one-way valves 11A and 11B are interposed, respectively, between the first and second hydraulic pressure passages 5A and 5B and the discharge side of the pump 10 to allow the brake fluid to flow from the pump 10. 2 One-way valves 12A and 12B are interposed.

また前記マスタシリンダＭに付設される外部リザーバＲに一端が接続されるとともに第１一方向弁１１Ａ，１１Ｂよりも下流側で前記ポンプ１０の吸入側に他端が接続される吸入路１３には、前記ポンプ１０側へのブレーキ液の流通を許容する第３一方向弁１４が介設される。   One end is connected to an external reservoir R attached to the master cylinder M, and the other end is connected to the suction side of the pump 10 on the downstream side of the first one-way valves 11A and 11B. A third one-way valve 14 that allows the brake fluid to flow to the pump 10 side is interposed.

第１出力液圧路４Ａには、リニアソレノイド弁である第１常開型電磁弁１５Ａが介設され、第２出力液圧路４Ｂには、リニアソレノイド弁である第２常開型電磁弁１５Ｂが介設され、第１および第２常開型電磁弁１５Ａ，１５Ｂには、マスタシリンダＭからのブレーキ液の流通を許容する第４一方向弁１６Ａ，１６Ｂが並列に接続される。   A first normally open solenoid valve 15A, which is a linear solenoid valve, is interposed in the first output hydraulic pressure path 4A, and a second normally open solenoid valve, which is a linear solenoid valve, is interposed in the second output hydraulic pressure path 4B. 15B is interposed, and the first and second normally open electromagnetic valves 15A and 15B are connected in parallel with fourth one-way valves 16A and 16B that permit the flow of the brake fluid from the master cylinder M.

第１液圧系統３Ａには、左前輪用車輪ブレーキＢＦＬに対応した切換弁手段１７Ａならびに右後輪用車輪ブレーキＢＲＲに対応した切換弁手段１７Ｂが設けられ、第２液圧系統３Ｂには、右前輪用車輪ブレーキＢＦＲに対応した切換弁手段１７Ｃならびに左後輪用車輪ブレーキＢＲＬに対応した切換弁手段１７Ｄが設けられる。   The first hydraulic system 3A is provided with switching valve means 17A corresponding to the left front wheel brake BFL and switching valve means 17B corresponding to the right rear wheel brake BRR, and the second hydraulic system 3B includes A switching valve means 17C corresponding to the right front wheel brake BFR and a switching valve means 17D corresponding to the left rear wheel brake BRL are provided.

第１液圧系統３Ａの切換弁手段１７Ａ，１７Ｂは、常開型電磁弁であって分岐液圧路６Ａ，６Ｂに介設される入口弁１８Ａ，１８Ｂと、入口弁１８Ａ，１８Ｂに並列に接続される第５一方向弁１９Ａ，１９Ｂと、常閉型電磁弁であって前記入口弁１８Ａ，１８Ｂよりも下流側の分岐液圧路６Ａ，６Ｂおよび第１リザーバ８Ａ間に介設される出口弁２０Ａ，２０Ｂとで構成される。   The switching valve means 17A, 17B of the first hydraulic system 3A are normally open solenoid valves, and are parallel to the inlet valves 18A, 18B and the inlet valves 18A, 18B provided in the branch hydraulic pressure paths 6A, 6B. The fifth one-way valve 19A, 19B to be connected, and a normally closed electromagnetic valve, which is interposed between the branch hydraulic pressure passages 6A, 6B and the first reservoir 8A downstream of the inlet valves 18A, 18B. It consists of outlet valves 20A and 20B.

このような切換弁手段１７Ａ，１７Ｂにおいては、入口弁１８Ａ，１８Ｂを開弁するとともに出口弁２０Ａ，２０Ｂを閉弁することで第１液圧路５Ａならびに左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲ間を接続するとともに第１リザーバ８Ａならびに左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲ間を遮断して第１液圧路５Ａの液圧を左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲに作用せしめる状態と、入口弁１８Ａ，１８Ｂを閉弁するとともに出口弁２０Ａ，２０Ｂを開弁することで第１液圧路５Ａならびに左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲ間を遮断するとともに第１リザーバ８Ａならびに左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲ間を接続して左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲの液圧を第１リザーバ８Ａに解放する状態と、入口弁１８Ａ，１８Ｂおよび出口弁２０Ａ，２０Ｂをともに閉弁することで左前輪用車輪ブレーキＢＦＬおよび右後輪用車輪ブレーキＢＲＲの液圧を保持する状態とを切換可能である。   In such switching valve means 17A and 17B, the inlet valves 18A and 18B are opened, and the outlet valves 20A and 20B are closed, whereby the first hydraulic pressure passage 5A, the left front wheel brake BFL and the right rear wheel are closed. The first brake 8A and the left front wheel brake BFL and the right rear wheel brake BRR are disconnected and the hydraulic pressure in the first hydraulic passage 5A is reduced to the left front wheel brake BFL and The state of acting on the right rear wheel wheel brake BRR, and closing the inlet valves 18A and 18B and opening the outlet valves 20A and 20B, the first hydraulic path 5A and the left front wheel brake BFL and the right rear The wheel brake BRR for the wheel is disconnected, and the first reservoir 8A, the left front wheel brake BFL, and the right rear wheel brake The state in which the hydraulic pressures of the left front wheel brake BFL and the right rear wheel brake BRR are released to the first reservoir 8A by connecting the RRs, and the inlet valves 18A and 18B and the outlet valves 20A and 20B are closed. Thus, it is possible to switch between the state in which the hydraulic pressure of the left front wheel brake BFL and the right rear wheel brake BRR is maintained.

第２液圧系統３Ｂの切換弁手段１７Ｃ，１７Ｄは、常開型電磁弁であって分岐液圧路６Ｃ，６Ｄに介設される入口弁１８Ｃ，１８Ｄと、入口弁１８Ｃ，１８Ｄに並列に接続される第５一方向弁１９Ｃ，１９Ｄと、常閉型電磁弁であって前記入口弁１８Ｃ，１８Ｄよりも下流側の分岐液圧路６Ｃ，６Ｄおよび第２リザーバ８Ｂ間に介設される出口弁２０Ｃ，２０Ｄとで構成される。   The switching valve means 17C and 17D of the second hydraulic system 3B are normally open solenoid valves, and are parallel to the inlet valves 18C and 18D and the inlet valves 18C and 18D provided in the branch hydraulic pressure paths 6C and 6D. The fifth one-way valves 19C, 19D to be connected, and the normally closed electromagnetic valves, which are interposed between the branch hydraulic pressure paths 6C, 6D downstream of the inlet valves 18C, 18D and the second reservoir 8B. It is comprised by outlet valve 20C, 20D.

このような切換弁手段１７Ｃ，１７Ｄにおいては、入口弁１８Ｃ，１８Ｄを開弁するとともに出口弁２０Ｃ，２０Ｄを閉弁することで第２液圧路５Ｂならびに右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬ間を接続するとともに第２リザーバ８Ｃならびに右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬ間を遮断して第２液圧路５Ｂの液圧を右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬに作用せしめる状態と、入口弁１８Ｃ，１８Ｄを閉弁するとともに出口弁２０Ｃ，２０Ｄを開弁することで第２液圧路５Ｂならびに右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬ間を遮断するとともに第２リザーバ８Ｂならびに右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬ間を接続して右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬの液圧を第２リザーバ８Ｂに解放する状態と、入口弁１８Ｃ，１８Ｄおよび出口弁２０Ｃ，２０Ｄをともに閉弁することで右前輪用車輪ブレーキＢＦＲおよび左後輪用車輪ブレーキＢＲＬの液圧を保持する状態とを切換可能である。   In such switching valve means 17C, 17D, the inlet valves 18C, 18D are opened and the outlet valves 20C, 20D are closed, whereby the second hydraulic pressure passage 5B, the right front wheel brake BFR, and the left rear wheel are closed. And the second reservoir 8C and the right front wheel brake BFR and the left rear wheel brake BRL are disconnected to reduce the hydraulic pressure in the second hydraulic pressure path 5B to the right front wheel brake BFR and A state of acting on the left rear wheel brake BRL, and closing the inlet valves 18C and 18D and opening the outlet valves 20C and 20D to open the second hydraulic path 5B and the right front wheel brake BFR and the left rear The wheel brake BRL for the wheel is cut off, and the second reservoir 8B, the wheel brake BFR for the right front wheel, and the wheel brake for the left rear wheel A state in which the hydraulic pressures of the right front wheel brake BFR and the left rear wheel brake BRL are released to the second reservoir 8B by connecting the RLs, and the inlet valves 18C and 18D and the outlet valves 20C and 20D are closed. Thus, it is possible to switch between the state in which the hydraulic pressure of the right front wheel brake BFR and the left rear wheel brake BRL is maintained.

ところでポンプ１０は、ブレーキペダル１をブレーキ操作したブレーキ操作状態でのアンチロックブレーキ制御時ならびにブレーキペダル１をブレーキ操作しない非ブレーキ操作状態での自動ブレーキ制御時に電動モータ９で駆動されるものであり、アンチロックブレーキ制御時に前記各切換弁手段１７Ａ〜１７Ｄが作動することで第１および第２リザーバ８Ａ，８Ｂに貯留されたブレーキ液はポンプ１０で第１および第２液圧路５Ａ，５Ｂに還流され、自動ブレーキ制御時には、外部リザーバＲから吸入したブレーキ液はポンプ１０で第１および第２液圧５Ａ，５Ｂに供給され、常開型電磁弁１５Ａ，１５Ｂの開閉作動によって第１および第２液圧路５Ａ，５Ｂの液圧が調圧されることになる。   By the way, the pump 10 is driven by the electric motor 9 at the time of anti-lock brake control in the brake operation state where the brake pedal 1 is braked and at the time of automatic brake control in the non-brake operation state where the brake pedal 1 is not operated. The brake fluid stored in the first and second reservoirs 8A and 8B is moved to the first and second hydraulic pressure passages 5A and 5B by the pump 10 by operating the switching valve means 17A to 17D during the anti-lock brake control. At the time of automatic brake control, the brake fluid sucked from the external reservoir R is supplied to the first and second hydraulic pressures 5A and 5B by the pump 10, and the first and first hydraulic valves 15A and 15B are opened and closed to open and close the first and second hydraulic pressures. The hydraulic pressures in the two hydraulic pressure paths 5A and 5B are adjusted.

次にこの第１実施例の作用について説明すると、ポンプ１０側へのブレーキ液の流通を許容する第１一方向弁１１Ａ，１１Ｂが第１および第２リザーバ８Ａ，８Ｂとポンプ１０の吸入側との間に介設され、ポンプ１０からのブレーキ液の流通を許容する第１一方向弁１２Ａ，１２Ｂが、第１および第２液圧路５Ａ，５Ｂとポンプ１０の吐出側との間に介設され、マスタシリンダＭに付設される外部リザーバＲに一端が接続されるとともに第１一方向弁１１Ａ，１１Ｂよりも下流側でポンプ１０の吸入側に他端が接続される吸入路１３にポンプ１０側へのブレーキ液の流通を許容する第３一方向弁１４が介設されている。   Next, the operation of the first embodiment will be described. The first one-way valves 11A and 11B that allow the flow of the brake fluid to the pump 10 side include the first and second reservoirs 8A and 8B, the suction side of the pump 10, and Between the first and second hydraulic pressure passages 5A and 5B and the discharge side of the pump 10 are interposed between the first and second one-way valves 12A and 12B. One end is connected to the external reservoir R attached to the master cylinder M, and the other end is connected to the suction passage 13 downstream of the first one-way valves 11A and 11B and the other end is connected to the suction side of the pump 10. A third one-way valve 14 that allows the brake fluid to flow to the 10 side is interposed.

したがって非ブレーキ操作時にポンプ１０を作動せしめるとともに常開型電磁弁１５Ａ，１５Ｂの作動を制御して第１および第２液圧路５Ａ，５Ｂの液圧を調圧し、切換弁手段１７Ａ〜１７Ｄによって各車輪ブレーキＢＦＬ，ＢＲＲ；ＢＦＲ，ＢＲＬの液圧を制御するようにして車両の運動を制御する際に、前記ポンプ１０の作動開始時には外部リザーバＲから第３一方向弁１４を介してブレーキ液を直ちに吸入することが可能であり、外部リザーバＲおよびポンプ１０の吸入側間に常閉型電磁弁が介設されていた従来のものと比べると、応答性を高めるとともに吸入抵抗を小さく抑えることができるとともに電磁弁の個数を低減することでコスト低減を図ることができる。   Accordingly, the pump 10 is operated at the time of non-braking operation, and the operation of the normally open type electromagnetic valves 15A and 15B is controlled to adjust the hydraulic pressure in the first and second hydraulic pressure paths 5A and 5B, and the switching valve means 17A to 17D are used. When controlling the vehicle movement by controlling the hydraulic pressure of each wheel brake BFL, BRR; BFR, BRL, the brake fluid is supplied from the external reservoir R through the third one-way valve 14 when the pump 10 is started. Compared with the conventional type in which a normally closed solenoid valve is interposed between the external reservoir R and the suction side of the pump 10, the responsiveness is enhanced and the suction resistance is kept small. In addition, the cost can be reduced by reducing the number of solenoid valves.

また切換弁手段１７Ａ〜１７Ｄにおける出口弁２０Ａ〜２０Ｄが車輪ブレーキＢＦＬ，ＢＲＲ；ＢＦＲ，ＢＲＬと第１および第２リザーバ８Ａ，８Ｂとの間を接続したまま故障したとしても吸入路１３に介設されている第３一方向弁１４の働きによって車輪ブレーキＢＦＬ，ＢＲＲ；ＢＦＲ，ＢＲＬからのブレーキ液が外部リザーバＲ側に流れることが阻止されるので、車輪ブレーキＢＦＬ，ＢＲＲ；ＢＦＲ，ＢＲＬのブレーキ液圧が「０」となってしまうことは回避される。   Even if the outlet valves 20A to 20D in the switching valve means 17A to 17D fail while the wheel brakes BFL and BRR; BFR and BRL are connected to the first and second reservoirs 8A and 8B, they are interposed in the suction passage 13. Since the brake fluid from the wheel brakes BFL, BRR; BFR, BRL is prevented from flowing to the external reservoir R side by the action of the third one-way valve 14 that has been performed, the brakes of the wheel brakes BFL, BRR; BFR, BRL It is avoided that the hydraulic pressure becomes “0”.

しかもマスタシリンダＭが備える第１および第２出力ポート２Ａ，２Ｂにそれぞれ連なる第１および第２液圧系統３Ａ，３Ｂに、第１および第２リザーバ８Ａ，８Ｂ、常開型電磁弁１５Ａ，１５Ｂ、切換弁手段１７Ａ，１７Ｂ；１７Ｃ，１７Ｄ、第１一方向弁１１Ａ，１１Ｂおよび第２一方向弁１２Ａ，１２Ｂがそれぞれ設けられるのに対して、両液圧系統３Ａ，３Ｂに共通な単一の前記第３一方向弁１４が前記吸入路１３に介設されるので、２系統の液圧系統にもかかわらず、第３一方向弁１４を単一とするとともに、ポンプ１０を両系統３Ａ，３Ｂに共通なものとして部品点数を少なくすることができる。   Moreover, the first and second hydraulic systems 3A and 3B connected to the first and second output ports 2A and 2B of the master cylinder M are respectively connected to the first and second reservoirs 8A and 8B and the normally open solenoid valves 15A and 15B. , The switching valve means 17A, 17B; 17C, 17D, the first one-way valves 11A, 11B and the second one-way valves 12A, 12B are provided respectively, whereas the single common to both hydraulic systems 3A, 3B Since the third one-way valve 14 is interposed in the suction passage 13, the third one-way valve 14 is single and the pump 10 is connected to both systems 3A regardless of the two hydraulic systems. , 3B, the number of parts can be reduced.

図２は本発明の第２実施例を示すものであり、上記第１実施例に対応する部分には同一の参照符号を付して図示するのみで詳細な説明は省略する。   FIG. 2 shows a second embodiment of the present invention. The parts corresponding to the first embodiment are indicated by the same reference numerals, and the detailed description is omitted.

第１および第２液圧系統３Ａ，３Ｂにそれぞれ対応した第１および第２リザーバ８Ａ，８Ｂには、出力タイミングの位相がずれるとともに並列接続された複数たとえば一対のポンプ１０Ａ，１０Ｂの吸入側が第１一方向弁１１Ａ，１１Ｂを介して接続され、両ポンプ１０，１０Ｂの吐出側は第２一方向弁１２Ａ，１２Ｂを介して第１および第２液圧路５Ａ，５Ｂに接続される。しかも両ポンプ１０Ａ，１０Ｂは共通な単一の電動モータ９で駆動される。   The first and second reservoirs 8A and 8B corresponding to the first and second hydraulic systems 3A and 3B have the output timing out of phase and the suction sides of a plurality of, for example, a pair of pumps 10A and 10B connected in parallel are first. 1 are connected via one-way valves 11A and 11B, and the discharge sides of both pumps 10 and 10B are connected to first and second hydraulic pressure passages 5A and 5B via second one-way valves 12A and 12B. Moreover, both pumps 10A and 10B are driven by a common single electric motor 9.

この第２実施例によれば、出力タイミングの位相がずれた一対のポンプ１０Ａ，１０Ｂが並列接続されるので、第１および第２液圧路５Ａ，５Ｂに作用する液圧の脈動を低減することができる。   According to the second embodiment, since the pair of pumps 10A and 10B whose output timing phases are shifted are connected in parallel, the pulsation of the hydraulic pressure acting on the first and second hydraulic pressure paths 5A and 5B is reduced. be able to.

図３は本発明の第３実施例を示すものであり、上記第１実施例に対応する部分には同一の参照符号を付して図示するのみで詳細な説明は省略する。   FIG. 3 shows a third embodiment of the present invention. The parts corresponding to those of the first embodiment are indicated by the same reference numerals and are not described in detail.

ポンプ１０の吐出側と第１および第２液圧路５Ａ，５Ｂ間に介設される第２一方向弁１２Ａ，１２Ｂと、第１および第２液圧路５Ａ，５Ｂとの間にはリニアソレノイド弁である常閉型電磁弁２１Ａ，２１Ｂが介設され、該常閉型電磁弁２１Ａ，２１Ｂおよび前記第２一方向弁１２Ａ，１２Ｂ間には蓄圧器２２Ａ，２２Ｂが接続される。   Linear between the discharge side of the pump 10 and the second one-way valves 12A and 12B interposed between the first and second hydraulic pressure paths 5A and 5B and the first and second hydraulic pressure paths 5A and 5B. Normally closed solenoid valves 21A and 21B, which are solenoid valves, are interposed, and accumulators 22A and 22B are connected between the normally closed solenoid valves 21A and 21B and the second one-way valves 12A and 12B.

この第３実施例によれば、ポンプ１０の吐出圧を蓄圧器２２Ａ，２２Ｂに蓄圧しておき、自動ブレーキ時に常閉型電磁弁２１Ａ，２１Ｂを開弁することで蓄圧器２２Ａ，２２Ｂで蓄圧された液圧を第１および第２液圧路５Ａ，５Ｂに作用せしめるようにして、自動ブレーキ時の初期応答性を高めることができる。   According to the third embodiment, the discharge pressure of the pump 10 is stored in the pressure accumulators 22A and 22B, and the normally closed electromagnetic valves 21A and 21B are opened during automatic braking, whereby the pressure accumulators 22A and 22B store the pressure. It is possible to improve the initial responsiveness during automatic braking by applying the hydraulic pressure to the first and second hydraulic pressure paths 5A and 5B.

また車輪ブレーキＢＦＬ，ＢＦＲ；ＢＦＲ，ＢＲＬが、車輪とともに回転する被制動部材に液圧シリンダ内の制動ピストンの作動によって摩擦部材を摺接させることで制動するように構成され、摩擦部材のひきずりを防止するために制動ピストンまたは摩擦部材が後退方向にばね付勢されるものであるときには、制動ピストンの前進開始時に常閉型電磁弁２１Ａ，２１Ｂを開弁して蓄圧器２２Ａ，２２Ｂに蓄圧された液圧を第１および第２液圧路５Ａ，５Ｂに作用せしめることにより、制動ピストンまたは摩擦部材が後退方向にばね付勢されていることによるブレーキ操作初期の液損を補償することができる。   Further, the wheel brakes BFL, BFR; BFR, BRL are configured to brake the friction member by rotating the brake piston in the hydraulic cylinder against the member to be braked that rotates together with the wheel, and the friction member is dragged. In order to prevent this, when the braking piston or the friction member is spring-biased in the reverse direction, the normally closed electromagnetic valves 21A and 21B are opened and accumulated in the pressure accumulators 22A and 22B when the braking piston starts to advance. By causing the hydraulic pressure to act on the first and second hydraulic pressure paths 5A and 5B, it is possible to compensate for the liquid loss at the initial stage of the brake operation due to the spring biasing of the brake piston or the friction member in the backward direction. .

図４は本発明の第４実施例を示すものであり、上記第１〜第３実施例に対応する部分には同一の参照符号を付して図示するのみで詳細な説明は省略する。   FIG. 4 shows a fourth embodiment of the present invention. The portions corresponding to the first to third embodiments are indicated by the same reference numerals, and detailed description thereof is omitted.

第１および第２液圧路５Ａ，５Ｂには、電動モータ９で駆動されるとともに第１および第２液圧系統３Ａ，３Ｂにそれぞれ対応した第１および第２リザーバ８Ａ，８Ｂに吸入側が接続されるポンプ１０の吐出側が接続されるものであり、第１および第２リザーバ８Ａ，８Ｂと前記ポンプ１０の吸入側との間には、前記ポンプ１０側へのブレーキ液の流通を許容する第１一方向弁１１Ａ，１１Ｂがそれぞれ介設され、第１および第２液圧路５Ａ，５Ｂと前記ポンプ１０の吐出側との間には、前記ポンプ１０からのブレーキ液の流通を許容する第２一方向弁１２Ａ，１２Ｂがそれぞれ介設される。   The first and second hydraulic pressure paths 5A and 5B are connected to the first and second reservoirs 8A and 8B respectively driven by the electric motor 9 and corresponding to the first and second hydraulic pressure systems 3A and 3B, respectively. The discharge side of the pump 10 is connected, and between the first and second reservoirs 8A, 8B and the suction side of the pump 10, a brake fluid is allowed to flow to the pump 10 side. 1 one-way valves 11A and 11B are interposed, respectively, between the first and second hydraulic pressure passages 5A and 5B and the discharge side of the pump 10 to allow the brake fluid to flow from the pump 10. 2 One-way valves 12A and 12B are interposed.

またマスタシリンダＭに付設される外部リザーバＲに一端が接続されるとともに第１一方向弁１１Ａ，１１Ｂよりも下流側で前記ポンプ１０の吸入側に他端が接続される吸入路１３には、前記ポンプ１０側へのブレーキ液の流通を許容する第３一方向弁１４が介設される。   A suction path 13 having one end connected to the external reservoir R attached to the master cylinder M and connected to the suction side of the pump 10 on the downstream side of the first one-way valves 11A and 11B, A third one-way valve 14 that allows the brake fluid to flow to the pump 10 side is interposed.

しかも第１一方向弁１１Ａ，１１Ｂ、第２一方向弁１２Ａ，１２Ｂおよび第３一方向弁１４間の液圧が、液圧検出手段２３で検出される。而してポンプ１０は、その非作動時に吐出側および吸入側を同一液圧とするものであり、この第４実施例では、前記液圧検出手段２３が、第２一方向弁１２Ａ，１２Ｂおよびポンプ１０の吐出側間に接続される。   Moreover, the hydraulic pressure between the first one-way valves 11A and 11B, the second one-way valves 12A and 12B, and the third one-way valve 14 is detected by the hydraulic pressure detecting means 23. Thus, when the pump 10 is not in operation, the discharge side and the suction side are set to the same hydraulic pressure. In the fourth embodiment, the hydraulic pressure detecting means 23 includes the second one-way valves 12A, 12B and Connected between the discharge sides of the pump 10.

この第４実施例によれば、第１一方向弁１１Ａ，１１Ｂ、第２一方向弁１２Ａ，１２Ｂおよび第３一方向弁１３間の液圧を液圧検出手段２３で検出することによって、リザーバ８Ａ，８Ｂへの貯留液量を推定することが可能であり、それによりリザーバ８Ａ，８Ｂの貯留液量が大きくなったときにポンプ１０を作動せしめるようにしてポンプ１０の無駄な作動を回避することができ、ポンプ１０を駆動することによる消費エネルギーを低減することが可能となるとともにポンプ１０およびモータ９の作動音を静粛にしつつ、ブレーキペダル１の良好な操作フィーリングを得ることができる。   According to the fourth embodiment, the hydraulic pressure between the first one-way valves 11A and 11B, the second one-way valves 12A and 12B, and the third one-way valve 13 is detected by the hydraulic pressure detecting means 23, whereby the reservoir It is possible to estimate the amount of liquid stored in 8A and 8B, thereby avoiding useless operation of the pump 10 by operating the pump 10 when the amount of liquid stored in the reservoirs 8A and 8B increases. Thus, it is possible to reduce the energy consumed by driving the pump 10, and to obtain a favorable operation feeling of the brake pedal 1 while quietly operating the pump 10 and the motor 9.

また第２一方向弁１２Ａ，１２Ｂで漏れが生じているときにも液圧発生手段２３の検出値変化をみることでその漏れを検出することができる。   Further, even when leakage occurs in the second one-way valves 12A and 12B, the leakage can be detected by looking at the change in the detection value of the hydraulic pressure generating means 23.

なお第２実施例における第１一方向弁１１Ａ，１１Ｂ、第２一方向弁１２Ａ，１２Ｂおよび第３一方向弁１４間の液圧を液圧検出手段２３で検出することによっても、上記第４実施例と同様の効果を奏することができる。   It is noted that the above-described fourth method can also be realized by detecting the hydraulic pressure between the first one-way valves 11A, 11B, the second one-way valves 12A, 12B and the third one-way valve 14 in the second embodiment by the hydraulic pressure detecting means 23. The same effects as in the embodiment can be obtained.

図５は本発明の第５実施例を示すものであり、上記第１〜第４実施例に対応する部分には同一の参照符号を付して図示するのみで詳細な説明は省略する。   FIG. 5 shows a fifth embodiment of the present invention. The parts corresponding to those of the first to fourth embodiments are indicated by the same reference numerals and are not described in detail.

第１および第２液圧系統３Ａ，３Ｂにそれぞれ対応した第１および第２リザーバ８Ａ，８Ｂには一対のポンプ１０Ａ，１０Ｂの吸入側が一方向弁１１Ａ，１１Ｂを介して接続され、両ポンプ１０Ａ，１０Ｂは共通な単一の電動モータ９で駆動される。   The suction sides of the pair of pumps 10A and 10B are connected to the first and second reservoirs 8A and 8B corresponding to the first and second hydraulic systems 3A and 3B, respectively, via one-way valves 11A and 11B. , 10B are driven by a common single electric motor 9.

またマスタシリンダＭに付設される外部リザーバＲに一端が接続されるとともに前記一方向弁１１Ａ，１１Ｂよりも下流側で前記ポンプ１０Ａ，１０Ｂの吸入側に他端が接続される吸入路１３には、前記ポンプ１０Ａ，１０Ｂ側へのブレーキ液の流通を許容する第３一方向弁１４が介設される。   One end is connected to the external reservoir R attached to the master cylinder M, and the other end is connected to the suction side of the pumps 10A and 10B on the downstream side of the one-way valves 11A and 11B. A third one-way valve 14 that allows the brake fluid to flow to the pumps 10A and 10B is interposed.

両ポンプ１０，１０Ｂの吐出側は、脈動緩和手段２４が備える一対の液圧室２６Ａ，２６Ｂに個別の第２一方向弁１２Ａ，１２Ｂを介して接続されており、また両液圧室２６Ａ，２６Ｂは、一対の液圧系統３Ａ，３Ｂの前記液圧路５Ａ，５Ｂにそれぞれ個別に連通する。   The discharge sides of both pumps 10 and 10B are connected to a pair of hydraulic chambers 26A and 26B provided in the pulsation mitigating means 24 via individual second one-way valves 12A and 12B. 26B communicates with the hydraulic pressure paths 5A and 5B of the pair of hydraulic systems 3A and 3B, respectively.

前記脈動緩和手段２４は、前記両液圧室２５Ａ，２５Ｂに両端を臨ませたフリーピストン２７がストロークを制限されつつシリンダボディ２８に摺動可能に嵌合されて成るものであり、前記両液圧室２５Ａ，２５Ｂには、フリーピストン２７の両端およびシリンダボディ２８の両端壁間に縮設されるばね２６Ａ，２６Ｂが収容される。   The pulsation mitigating means 24 is configured by a free piston 27 having both ends facing the both hydraulic pressure chambers 25A and 25B and is slidably fitted to a cylinder body 28 with its stroke limited. The pressure chambers 25A and 25B accommodate springs 26A and 26B that are contracted between both ends of the free piston 27 and both end walls of the cylinder body 28, respectively.

この第５実施例によれば、一対のポンプ１０Ａ，１０Ｂの吐出側に第２一方向弁１２Ａ，１２Ｂをそれぞれ介して接続される２つの液圧室２５Ａ，２５Ｂに、シリンダボディ２８に摺動可能に嵌合されるフリーピストン２７の両端が臨むので、２つの液圧系統３Ａ，３Ｂを分離した上で両ポンプ１０Ａ，１０Ｂの吐出脈動を緩和することができる。   According to the fifth embodiment, the cylinder body 28 slides on the two hydraulic chambers 25A and 25B connected to the discharge sides of the pair of pumps 10A and 10B via the second one-way valves 12A and 12B, respectively. Since both ends of the free piston 27 that can be fitted face each other, the discharge pulsations of both the pumps 10A and 10B can be reduced after separating the two hydraulic systems 3A and 3B.

以上、本発明の実施例を説明したが、本発明は上記実施例に限定されるものではなく、特許請求の範囲に記載された本発明を逸脱することなく種々の設計変更を行うことが可能である。   Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. It is.

第１実施例の車両用ブレーキ液圧制御装置の液圧系統図である。1 is a hydraulic system diagram of a vehicle brake hydraulic pressure control apparatus according to a first embodiment. 第２実施例の車両用ブレーキ液圧制御装置の液圧系統図である。It is a hydraulic-system figure of the brake hydraulic-pressure control apparatus for vehicles of 2nd Example. 第３実施例の車両用ブレーキ液圧制御装置の液圧系統図である。It is a hydraulic-system figure of the brake hydraulic-pressure control apparatus for vehicles of 3rd Example. 第４実施例の車両用ブレーキ液圧制御装置の液圧系統図である。It is a hydraulic-system figure of the brake hydraulic-pressure control apparatus for vehicles of 4th Example. 第５実施例の車両用ブレーキ液圧制御装置の液圧系統図である。It is a hydraulic-system figure of the brake hydraulic-pressure control apparatus for vehicles of 5th Example.

符号の説明Explanation of symbols

２Ａ，２Ｂ・・・出力ポート
３Ａ，３Ｂ・・・液圧系統
５Ａ，５Ｂ・・・液圧路
８Ａ，８Ｂ・・・リザーバ
９・・・電動モータ
１０，１０Ａ，１０Ｂ・・・ポンプ
１１Ａ，１１Ｂ・・・第１一方向弁
１２Ａ，１２Ｂ・・・第２一方向弁
１３・・・吸入路
１４・・・第３一方向弁
１５Ａ，１５Ｂ・・・常開型電磁弁
１７Ａ，１７Ｂ，１７Ｃ，１７Ｄ・・・切換弁手段
２１Ａ，２１Ｂ・・・常閉型電磁弁
２２Ａ，２２Ｂ・・・蓄圧器
２４・・・脈動緩和手段
２５Ａ，２５Ｂ・・・液圧室
２７・・・フリーピストン
２８・・・シリンダボディ
ＢＦＬ，ＢＦＲ，ＢＲＲ，ＢＲＬ・・・車輪ブレーキ
Ｍ・・・液圧発生手段であるマスタシリンダ
Ｒ・・・外部リザーバ 2A, 2B ... Output ports 3A, 3B ... Hydraulic systems 5A, 5B ... Hydraulic passages 8A, 8B ... Reservoir 9 ... Electric motors 10, 10A, 10B ... Pump 11A, 11B ... 1st one way valve 12A, 12B ... 2nd one way valve 13 ... Suction way 14 ... 3rd one way valve 15A, 15B ... Normally open type solenoid valve 17A, 17B, 17C, 17D ... Switching valve means 21A, 21B ... Normally closed solenoid valves 22A, 22B ... Accumulator 24 ... Pulsation mitigation means 25A, 25B ... Hydraulic pressure chamber 27 ... Free piston 28 ... Cylinder body BFL, BFR, BRR, BRL ... Wheel brake M ... Master cylinder R as hydraulic pressure generating means ... External reservoir

Claims (6)

ブレーキ操作に応じた液圧を出力する液圧発生手段（Ｍ）と、リザーバ（８Ａ，８Ｂ）と、吸入側が前記リザーバ（８Ａ，８Ｂ）に接続されるポンプ（１０，１０Ａ，１０Ｂ）と、該ポンプ（１０，１０Ａ，１０Ｂ）の吐出側に接続される液圧路（５Ａ，５Ｂ）および前記液圧発生手段（Ｍ）間に介設される常開型電磁弁（１５Ａ，１５Ｂ）と、車輪ブレーキ（ＢＦＬ，ＢＲＲ，ＢＦＲ，ＢＲＬ）と、前記液圧路（５Ａ，５Ｂ）および前記車輪ブレーキ（ＢＦＬ，ＢＲＲ，ＢＦＲ，ＢＲＬ）間を接続するとともに前記車輪ブレーキ（ＢＦＬ，ＢＲＲ，ＢＦＲ，ＢＲＬ）および前記リザーバ（８Ａ，８Ｂ）間を遮断する状態ならびに前記液圧路（５Ａ，５Ｂ）および前記車輪ブレーキ（ＢＦＬ，ＢＲＲ，ＢＦＲ，ＢＲＬ）間を遮断するとともに前記車輪ブレーキ（ＢＦＬ，ＢＲＲ，ＢＦＲ，ＢＲＬ）および前記リザーバ（８Ａ，８Ｂ）間を接続する状態を切換可能な切換弁手段（１７Ａ，１７Ｂ，１７Ｃ，１７Ｄ）とを備える車両用ブレーキ液圧制御装置において、前記ポンプ（１０，１０Ａ，１０Ｂ）側へのブレーキ液の流通を許容するようにして前記リザーバ（８Ａ，８Ｂ）および前記ポンプ（１０，１０Ａ，１０Ｂ）の吸入側間に介設される第１一方向弁（１１Ａ，１１Ｂ）と、前記ポンプ（１０，１０Ａ，１０Ｂ）からのブレーキ液の流通を許容するようにして前記液圧路（５Ａ，５Ｂ）および前記ポンプ（１０，１０Ａ，１０Ｂ）の吐出側間に介設される第２一方向弁（１２Ａ，１２Ｂ）と、前記液圧発生手段（Ｍ）に付設される外部リザーバ（Ｒ）と、該外部リザーバ（Ｒ）に一端が接続されるとともに第１一方向弁（１１Ａ，１１Ｂ）よりも下流側で前記ポンプ（１０，１０Ａ，１０Ｂ）の吸入側に他端が接続される吸入路（１３）に介設されて前記ポンプ（１０，１０Ａ，１０Ｂ）側へのブレーキ液の流通を許容する第３一方向弁（１４）とを含むことを特徴とする車両用ブレーキ液圧制御装置。   A hydraulic pressure generating means (M) for outputting a hydraulic pressure corresponding to a brake operation, a reservoir (8A, 8B), a pump (10, 10A, 10B) whose suction side is connected to the reservoir (8A, 8B), A hydraulic path (5A, 5B) connected to the discharge side of the pump (10, 10A, 10B) and a normally open solenoid valve (15A, 15B) interposed between the hydraulic pressure generating means (M); The wheel brakes (BFL, BRR, BFR, BRL) are connected to the hydraulic pressure paths (5A, 5B) and the wheel brakes (BFL, BRR, BFR, BRL) and the wheel brakes (BFL, BRR, BFR). , BRL) and the reservoir (8A, 8B) are shut off, and the hydraulic path (5A, 5B) and the wheel brake (BFL, BRR, BFR, BRL) are shut off. Brake hydraulic pressure control for a vehicle comprising wheel brakes (BFL, BRR, BFR, BRL) and switching valve means (17A, 17B, 17C, 17D) capable of switching the state of connecting the reservoirs (8A, 8B). In the device, it is interposed between the reservoir (8A, 8B) and the suction side of the pump (10, 10A, 10B) so as to allow the brake fluid to flow to the pump (10, 10A, 10B) side. The hydraulic pressure passages (5A, 5B) and the pumps (10, 10A) are allowed to allow the brake fluid to flow from the first one-way valves (11A, 11B) and the pumps (10, 10A, 10B). , 10B), a second one-way valve (12A, 12B) interposed between the discharge sides, an external reservoir (R) attached to the hydraulic pressure generating means (M), and the external reservoir ( ) And one end connected to a suction passage (13) connected to the suction side of the pump (10, 10A, 10B) on the downstream side of the first one-way valve (11A, 11B). And a third one-way valve (14) that allows the brake fluid to flow to the pump (10, 10A, 10B) side. 前記第２一方向弁（１２Ａ，１２Ｂ）および前記液圧路（５Ａ，５Ｂ）間に常閉型電磁弁（２１Ａ，２１Ｂ）が介設され、該常閉型電磁弁（２１Ａ，２１Ｂ）および前記第２一方向弁（１２Ａ，１２Ｂ）間に蓄圧器（２２Ａ，２２Ｂ）が接続されることを特徴とする請求項１記載の車両用ブレーキ液圧制御装置。   A normally closed solenoid valve (21A, 21B) is interposed between the second one-way valve (12A, 12B) and the hydraulic pressure path (5A, 5B), and the normally closed solenoid valve (21A, 21B) and The vehicular brake hydraulic pressure control apparatus according to claim 1, wherein a pressure accumulator (22A, 22B) is connected between the second one-way valves (12A, 12B). 前記液圧発生手段（Ｍ）が備える一対の出力ポート（２Ａ，２Ｂ）にそれぞれ連なる一対の液圧系統（３Ａ，３Ｂ）に、前記リザーバ（８Ａ，８Ｂ）、前記常開型電磁弁（１５Ａ，１５Ｂ）、前記切換弁手段（１７Ａ〜１７Ｄ）、第１一方向弁（１１Ａ，１１Ｂ）および第２一方向弁（１２Ａ，１２Ｂ）がそれぞれ設けられ、前記両液圧系統（３Ａ，３Ｂ）に共通な単一の前記第３一方向弁（１４）が前記吸入路（１３）に介設されることを特徴とする請求項１または２記載の車両用ブレーキ液圧制御装置。   The reservoir (8A, 8B), the normally open solenoid valve (15A) are connected to a pair of hydraulic systems (3A, 3B) respectively connected to a pair of output ports (2A, 2B) provided in the hydraulic pressure generating means (M). 15B), the switching valve means (17A-17D), the first one-way valve (11A, 11B) and the second one-way valve (12A, 12B), respectively, and the both hydraulic systems (3A, 3B). The vehicular brake hydraulic pressure control device according to claim 1 or 2, wherein the single third one-way valve (14) common to the vehicle is interposed in the suction passage (13). 共通な単一の電動モータ（９）で駆動されるとともに出力タイミングの位相がずれた複数の前記ポンプ（１０Ａ，１０Ｂ）が並列接続されることを特徴とする請求項１〜３のいずれかに記載の車両用ブレーキ液圧制御装置。   A plurality of pumps (10A, 10B) driven by a common single electric motor (9) and whose output timing phase is shifted are connected in parallel. The brake fluid pressure control apparatus for vehicles as described. 前記第１一方向弁（１１Ａ，１１Ｂ）、前記第２一方向弁（１２Ａ，１２Ｂ）および前記第３一方向弁（１４）間の液圧を検出する液圧検出手段（２３）を備えることを特徴とする請求項１記載の車両用ブレーキ液圧制御装置。   Fluid pressure detecting means (23) for detecting fluid pressure between the first one-way valve (11A, 11B), the second one-way valve (12A, 12B) and the third one-way valve (14). The vehicle brake hydraulic pressure control device according to claim 1. 一対の前記液圧系統（３Ａ，３Ｂ）に個別に対応した一対の前記ポンプ（１０Ａ，１０Ｂ）の吐出側に個別の第２一方向弁（１２Ａ，１２Ｂ）を介して接続されるとともに前記両液圧系統（３Ａ，３Ｂ）の前記液圧路（５Ａ，５Ｂ）に個別に通じる２つの液圧室（２５Ａ，２５Ｂ）に両端を臨ませたフリーピストン（２７）がストロークを制限されつつシリンダボディ（２８）に摺動可能に嵌合されて成る脈動緩和手段（２４）を含むことを特徴とする請求項３記載の車両用ブレーキ液圧制御装置。   Connected to the discharge sides of the pair of pumps (10A, 10B) individually corresponding to the pair of hydraulic systems (3A, 3B) via individual second one-way valves (12A, 12B) and the both The free piston (27) facing both ends of the two hydraulic chambers (25A, 25B) individually communicating with the hydraulic pressure paths (5A, 5B) of the hydraulic system (3A, 3B) 4. The vehicle brake hydraulic pressure control device according to claim 3, further comprising pulsation mitigation means (24) slidably fitted to the body (28).
JP2007191193A 2007-04-23 2007-07-23 Vehicular brake fluid pressure control device Pending JP2008290692A (en)

Priority Applications (1)

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JP2014024388A (en) * 2012-07-25 2014-02-06 Bosch Corp Brake fluid pressure control device
CN107445093A (en) * 2017-08-24 2017-12-08 四川宏华石油设备有限公司 A kind of gas drive hydrodynamic pressure disc brake device

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JPH1170864A (en) * 1997-08-28 1999-03-16 Mitsubishi Motors Corp Brake system and brake pressure generating device for vehicle
JPH11301443A (en) * 1998-04-22 1999-11-02 Aisin Seiki Co Ltd Two-system hydraulic brake device for vehicle
JP2000071967A (en) * 1998-06-15 2000-03-07 Denso Corp Brake device for vehicle
JP2000025597A (en) * 1998-07-09 2000-01-25 Toyota Motor Corp Braking force control device for vehicle
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Publication number Priority date Publication date Assignee Title
JP2014024388A (en) * 2012-07-25 2014-02-06 Bosch Corp Brake fluid pressure control device
CN107445093A (en) * 2017-08-24 2017-12-08 四川宏华石油设备有限公司 A kind of gas drive hydrodynamic pressure disc brake device

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