JP2000006785A - Hydraulic brake system for vehicle - Google Patents
Hydraulic brake system for vehicleInfo
- Publication number
- JP2000006785A JP2000006785A JP10177696A JP17769698A JP2000006785A JP 2000006785 A JP2000006785 A JP 2000006785A JP 10177696 A JP10177696 A JP 10177696A JP 17769698 A JP17769698 A JP 17769698A JP 2000006785 A JP2000006785 A JP 2000006785A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- piston
- hydraulic
- regulator
- 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
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
- B60T8/4072—Systems in which a driver input signal is used as a control signal for the additional fluid circuit which is normally used for braking
- B60T8/4081—Systems with stroke simulating devices for driver input
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/66—Electrical control in fluid-pressure brake systems
- B60T13/68—Electrical control in fluid-pressure brake systems by electrically-controlled valves
- B60T13/686—Electrical control in fluid-pressure brake systems by electrically-controlled valves in hydraulic systems or parts thereof
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T7/00—Brake-action initiating means
- B60T7/02—Brake-action initiating means for personal initiation
- B60T7/04—Brake-action initiating means for personal initiation foot actuated
- B60T7/042—Brake-action initiating means for personal initiation foot actuated by electrical means, e.g. using travel or force sensors
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/321—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration deceleration
- B60T8/3255—Systems in which the braking action is dependent on brake pedal data
- B60T8/326—Hydraulic systems
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
- B60T8/4072—Systems in which a driver input signal is used as a control signal for the additional fluid circuit which is normally used for braking
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Regulating Braking Force (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、少なくとも通常ブ
レーキ時に、ホイールシリンダをマスタシリンダから遮
断し、液圧源のパワー液圧を調圧したレギュレータ液圧
に応じた液圧をホイールシリンダに供給する車両用液圧
ブレーキ装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a brake system in which a wheel cylinder is disconnected from a master cylinder at least during normal braking, and a hydraulic pressure corresponding to a regulator hydraulic pressure obtained by adjusting a power hydraulic pressure of a hydraulic pressure source is supplied to the wheel cylinder. The present invention relates to a hydraulic brake device for a vehicle.
【0002】[0002]
【従来の技術】従来のこの種の車両用液圧ブレーキ装置
としては、例えば1996年9月に出版された「Automo
tive industry 」の第118〜119頁に示される「el
ectro-hydraulic brake systems 」(Kelsey-Hayes社)
が知られている。このものでは、マスタシリンダ及びホ
イールシリンダ間に電磁切換弁が設けられ、アキュムレ
ータがレギュレータ(比例制御弁)及び増圧器を介して
ホイールシリンダに接続されている。2. Description of the Related Art A conventional hydraulic brake system for a vehicle of this type is disclosed in, for example, "Automo
tive industry "on pages 118-119
ectro-hydraulic brake systems "(Kelsey-Hayes)
It has been known. In this device, an electromagnetic switching valve is provided between a master cylinder and a wheel cylinder, and an accumulator is connected to a wheel cylinder via a regulator (proportional control valve) and a pressure intensifier.
【0003】電磁切換弁は、常態ではマスタシリンダを
ホイールシリンダに連通しており、少なくとも運転者が
ブレーキペダルを操作した場合にソレノイドに通電され
て、マスタシリンダ及びホイールシリンダ間の連通を遮
断すると共にマスタシリンダをストロークシュミレータ
に連通する。ストロークシュミレータは、ピストン及び
スプリングで構成され、マスタシリンダ及びホイールシ
リンダ間の連通を遮断している間、ブレーキペダルの操
作量に対応したストロークを与える。レギュレータは、
アキュムレータ内に蓄圧された高液圧を少なくともブレ
ーキペダルの操作量に応じたレギュレータ液圧に調整す
る。増圧器は、シリンダ内に摺動自在に配設されたピス
トンを有する。このピストンにより、ホイールシリンダ
に連通する圧力室とレギュレータ液圧を入力する入力室
とが液密的に分離形成されている。圧力室内にスプリン
グが配設され、圧力室の容積を増大させる方向にピスト
ンを付勢している。従って、レギュレータ液圧によりピ
ストンがスプリングの付勢力に抗して摺動し、圧力室を
圧縮してホイールシリンダのブレーキ液圧を増圧する。An electromagnetic switching valve normally communicates a master cylinder with a wheel cylinder, and at least when a driver operates a brake pedal, the solenoid is energized to cut off communication between the master cylinder and the wheel cylinder. Connect the master cylinder to the stroke simulator. The stroke simulator includes a piston and a spring, and gives a stroke corresponding to the operation amount of the brake pedal while the communication between the master cylinder and the wheel cylinder is interrupted. The regulator is
The high hydraulic pressure accumulated in the accumulator is adjusted to a regulator hydraulic pressure corresponding to at least the operation amount of the brake pedal. The pressure intensifier has a piston slidably disposed in the cylinder. With this piston, the pressure chamber communicating with the wheel cylinder and the input chamber for inputting the regulator hydraulic pressure are formed in a liquid-tight manner. A spring is disposed in the pressure chamber and urges the piston in a direction to increase the volume of the pressure chamber. Therefore, the piston slides against the urging force of the spring by the regulator hydraulic pressure, compressing the pressure chamber and increasing the brake hydraulic pressure of the wheel cylinder.
【0004】[0004]
【発明が解決しようとする課題】ところが、この装置で
は、少なくともブレーキペダルの操作に応じてマスタシ
リンダ及びホイールシリンダ間の連通を遮断するため
に、電磁切換弁を用いているため、ソレノイドが不可欠
になり、その分コスト的に不利になると共に大型化す
る。However, in this device, an electromagnetic switching valve is used to cut off the communication between the master cylinder and the wheel cylinder at least in accordance with the operation of the brake pedal, so that the solenoid is indispensable. As a result, it is disadvantageous in terms of cost and the size is increased.
【0005】また、ストロークシュミレータをピストン
及びスプリングで構成しているため、コスト的に更に不
利となる。[0005] Further, since the stroke simulator is constituted by the piston and the spring, the cost is further disadvantageous.
【0006】故に、本発明は、電磁切換弁のソレノイド
を廃止できる車両用液圧ブレーキ装置を提供すること
を、第1の技術的課題とする。Accordingly, it is a first technical object of the present invention to provide a vehicle hydraulic brake device that can eliminate the solenoid of an electromagnetic switching valve.
【0007】また、本発明は、ストロークシュミレータ
を安価に構成できる車両用液圧ブレーキ装置を提供する
ことを、第2の技術的課題とする。A second technical object of the present invention is to provide a hydraulic brake device for a vehicle in which a stroke simulator can be constructed at a low cost.
【0008】[0008]
【課題を解決するための手段】上記第1の技術的課題を
解決するため、請求項1の発明の車両用液圧ブレーキ装
置は、車両の車輪に装着され前記車輪を制動するホイー
ルシリンダと、ブレーキ液を貯蔵するリザーバと、ブレ
ーキペダルの操作量に応じて前記リザーバのブレーキ液
を昇圧しマスタシリンダ液圧を出力するマスタシリンダ
と、前記リザーバ内のブレーキ液を所定の圧力に昇圧し
てパワー液圧を出力する液圧源と、前記液圧源の出力パ
ワー液圧を少なくとも前記ブレーキペダルの操作量に応
じたレギュレータ液圧に調圧するレギュレータと、前記
マスタシリンダ及び前記ホイールシリンダ間の液圧路に
配設され前記液圧路を開閉する切換弁と、前記レギュレ
ータ及び前記ホイールシリンダ間を液密的に分離するピ
ストンを有し、前記レギュレータの出力レギュレータ液
圧に応じて前記ピストンを作動させてレギュレータ液圧
に応じた液圧を前記ホイールシリンダに供給する増圧器
とを備えた車両用液圧ブレーキ装置において、前記切換
弁を、前記ピストンに機械的に連動して前記液圧路を開
閉するように構成したものである。To solve the first technical problem, a vehicle hydraulic brake device according to the first aspect of the present invention includes a wheel cylinder mounted on wheels of a vehicle and braking the wheels. A reservoir that stores brake fluid, a master cylinder that boosts the brake fluid in the reservoir according to the operation amount of a brake pedal and outputs a master cylinder fluid pressure, and boosts the brake fluid in the reservoir to a predetermined pressure to power A hydraulic pressure source that outputs hydraulic pressure, a regulator that regulates an output power hydraulic pressure of the hydraulic pressure source to a regulator hydraulic pressure corresponding to at least an operation amount of the brake pedal, and a hydraulic pressure between the master cylinder and the wheel cylinder. A switching valve disposed in the passage for opening and closing the hydraulic passage, and a piston for liquid-tightly separating the regulator and the wheel cylinder, An intensifier for operating the piston in accordance with the output regulator hydraulic pressure of a regulator to supply a hydraulic pressure according to the regulator hydraulic pressure to the wheel cylinder. The hydraulic passage is configured to be opened and closed mechanically in conjunction with a piston.
【0009】請求項1の発明によれば、切換弁がピスト
ンに機械的に連動してマスタシリンダ及びホイールシリ
ンダ間の液圧路を開閉するので、切換弁を駆動するため
のソレノイドを廃止でき、結果、安価になると共に小型
化する。According to the first aspect of the present invention, the switching valve opens and closes the hydraulic passage between the master cylinder and the wheel cylinder in mechanical linkage with the piston, so that the solenoid for driving the switching valve can be eliminated. As a result, the cost is reduced and the size is reduced.
【0010】請求項1において、請求項2の発明に示す
ように、前記ピストンは、ハウジング内に摺動自在に配
設され、一端側に前記ホイールシリンダに連通する圧力
室を形成すると共に他端側にレギュレータ液圧を入力す
る第1入力室を形成し、前記切換弁は、前記第1入力室に
レギュレータ液圧が供給されていないときは、前記マス
タシリンダを前記圧力室に連通し、前記第1入力室にレ
ギュレータ液圧が供給されて前記ピストンが前記圧力室
の容積を小さくする方向に摺動したときに、前記ピスト
ンに機械的に連動して前記マスタシリンダ及び前記圧力
室間の連通を遮断するように構成されていると、好まし
い。[0010] In the first aspect of the present invention, the piston is slidably disposed in the housing, and has a pressure chamber communicating with the wheel cylinder at one end and another end. Forming a first input chamber for inputting a regulator hydraulic pressure on the side, wherein the switching valve communicates the master cylinder with the pressure chamber when the regulator hydraulic pressure is not supplied to the first input chamber; When the regulator hydraulic pressure is supplied to the first input chamber and the piston slides in a direction to reduce the volume of the pressure chamber, communication between the master cylinder and the pressure chamber is mechanically interlocked with the piston. It is preferable to be configured so as to block the light.
【0011】請求項2において、第1の技術的課題に加
えて第2の技術的課題を解決するために、請求項3の発
明に示すように、前記増圧器が、前記マスタシリンダに
常時連通し前記ピストンの作動に伴い容積が変化する第
2入力室を有すると、好ましい。この構成によれば、マ
スタシリンダに常時連通しピストンの作動に伴い容積が
変化する第2入力室を増圧器に設けたので、簡単な構成
でブレーキペダルのストロークシュミレータ機能を発揮
でき、結果、一層安価になる。According to a second aspect of the present invention, in order to solve the second technical problem in addition to the first technical problem, the pressure intensifier is always in communication with the master cylinder. It is preferable to have a second input chamber whose volume changes with the operation of the piston. According to this configuration, the second input chamber, which is always in communication with the master cylinder and changes in volume with the operation of the piston, is provided in the pressure intensifier, so that the stroke simulator function of the brake pedal can be exhibited with a simple configuration, and as a result, Become cheap.
【0012】請求項3において、請求項4の発明に示す
ように、前記ハウジングは段付シリンダを有し、前記ピ
ストンは、前記段付シリンダに摺動自在に配設され、前
記圧力室の圧力を受ける受圧面積が前記第1入力室の圧
力を受ける受圧面積よりも大きい段付ピストンであり、
前記第2入力室は、前記ピストンの外周に形成された段
付環状室であり、前記段付環状室は、前記ピストンが前
記圧力室の容積を小さくする方向に摺動するに伴いその
容積が増加するように構成されていると、好ましい。こ
の構成によれば、ブレーキペダルが操作されると、レギ
ュレータ液圧に応じてピストンが圧力室の容積を小さく
する方向に摺動し、それに伴い段付環状室の容積が増加
する。つまり、段付環状室がストロークシュミレータと
して機能する。According to a third aspect of the present invention, the housing has a stepped cylinder, the piston is slidably disposed on the stepped cylinder, and the pressure of the pressure chamber is increased. A stepped piston whose receiving pressure area is larger than the receiving pressure area that receives the pressure of the first input chamber,
The second input chamber is a stepped annular chamber formed on the outer periphery of the piston. The volume of the stepped annular chamber increases as the piston slides in a direction to reduce the volume of the pressure chamber. It is preferable that it is configured to increase. According to this configuration, when the brake pedal is operated, the piston slides in a direction to reduce the volume of the pressure chamber according to the regulator hydraulic pressure, and accordingly, the volume of the stepped annular chamber increases. That is, the stepped annular chamber functions as a stroke simulator.
【0013】請求項1において、請求項5の発明に示す
ように、前記切換弁は、前記増圧器の内部に設けられて
いると、好ましい。この構成によれば、増圧器の外部に
設ける場合に比べて、小型化できる。According to the first aspect of the present invention, it is preferable that the switching valve be provided inside the pressure intensifier. According to this configuration, the size can be reduced as compared with the case where the pressure booster is provided outside.
【0014】請求項5において、請求項6の発明に示す
ように、前記ピストンは、ハウジング内に摺動自在に配
設され、一端側に前記ホイールシリンダに連通する圧力
室を形成すると共に他端側にレギュレータ液圧を入力す
る第1入力室を形成し、前記切換弁は、前記ピストンの
一端に固定された弁体と、前記圧力室に前記弁体に着脱
可能に配置された弁座とを有し、前記ピストンが前記圧
力室の容積を小さくする方向に摺動して前記弁体が前記
弁座に着座した後、前記弁体及び弁座は前記ピストンと
共に一体移動するように構成されていると、好ましい。According to a fifth aspect of the present invention, as set forth in the sixth aspect of the present invention, the piston is slidably disposed in the housing, and has a pressure chamber communicating with the wheel cylinder at one end and another end. Forming a first input chamber for inputting a regulator hydraulic pressure on the side, wherein the switching valve has a valve body fixed to one end of the piston, and a valve seat removably mounted on the valve body in the pressure chamber. After the piston slides in a direction to reduce the volume of the pressure chamber and the valve body is seated on the valve seat, the valve body and the valve seat are configured to move together with the piston. Is preferable.
【0015】[0015]
【発明の実施の形態】以下、本発明の望ましい実施の形
態を図面を参照して説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings.
【0016】図1は本実施形態に係る液圧ブレーキ装置
を示すもので、マスタシリンダ1は、負圧式ブースタ2
を介してブレーキペダル3に連結されていると共に、マ
スタリザーバ(リザーバ)4に接続されている。このマ
スタシリンダ1は、2つの圧力室1a,1bが形成され
たダンデムマスタシリンダで、ブレーキペダル3の操作
量に応じてマスタリザーバ4内に貯蔵されたブレーキ液
を圧力室1a,1bにて加圧し、マスタシリンダ液圧を
出力する。マスタシリンダ1の圧力室1a,1bは、そ
れぞれ主液圧路(液圧路)P1,P1’を介して車両前
方の車輪FL,FRのホイールシリンダWfl,Wfr
に接続され、主液圧路P1,P1’には後述する増圧器
7,7’が配設されている。FIG. 1 shows a hydraulic brake system according to the present embodiment, in which a master cylinder 1 includes a negative pressure type booster 2.
Is connected to the brake pedal 3 and to a master reservoir (reservoir) 4. The master cylinder 1 is a dandem master cylinder in which two pressure chambers 1a and 1b are formed, and the brake fluid stored in the master reservoir 4 is added in the pressure chambers 1a and 1b in accordance with the operation amount of the brake pedal 3. And output the master cylinder pressure. The pressure chambers 1a and 1b of the master cylinder 1 are respectively connected to the wheel cylinders Wfl and Wfr of the wheels FL and FR in front of the vehicle via main hydraulic paths (hydraulic paths) P1 and P1 '.
, And pressure intensifiers 7 and 7 ', which will be described later, are provided in the main hydraulic pressure paths P1 and P1'.
【0017】マスタリザーバ4には、パワー液圧を生成
する補助液圧源(液圧源)5の入力側が接続されてい
る。補助液圧源5の出力側は、レギュレータ6及び増圧
器7,7’を介して前輪ホイールシリンダWfl,Wf
rに接続されると共に、レギュレータ6を介して車両後
方の車輪RL,RRのホイールシリンダに接続されてい
る。The input side of an auxiliary hydraulic pressure source (hydraulic pressure source) 5 for generating power hydraulic pressure is connected to the master reservoir 4. The output side of the auxiliary hydraulic pressure source 5 is connected to front wheel cylinders Wfl, Wf via a regulator 6 and pressure intensifiers 7, 7 '.
r and connected via a regulator 6 to the wheel cylinders of the wheels RL, RR behind the vehicle.
【0018】補助液圧源5は、モータ駆動の液圧ポンプ
51と、アキュムレータ52と、逆止弁53と、リリー
フ弁54とから構成されている。液圧ポンプ51は、マ
スタリザーバ4内のブレーキ液を吸入昇圧し、それをア
キュムレータ52に吐出する。アキュムレータ52は、
液圧ポンプ51による昇圧ブレーキ液を蓄え、レギュレ
ータ6にパワー液圧を出力する。逆止弁53は、液圧ポ
ンプ51及びアキュムレータ52間に配設され、液圧ポ
ンプ側へのブレーキ液の流れを阻止する。リリーフ弁5
4は、アキュムレータ52内の液圧が所定の上限値を越
えた場合にアキュムレータ52内の蓄圧ブレーキ液をマ
スタリザーバ4に逃がす。The auxiliary hydraulic pressure source 5 comprises a motor-driven hydraulic pump 51, an accumulator 52, a check valve 53, and a relief valve 54. The hydraulic pump 51 suctions and pressurizes the brake fluid in the master reservoir 4 and discharges it to the accumulator 52. The accumulator 52
The booster brake fluid by the hydraulic pump 51 is stored, and the power fluid pressure is output to the regulator 6. The check valve 53 is disposed between the hydraulic pump 51 and the accumulator 52, and blocks the flow of the brake fluid to the hydraulic pump. Relief valve 5
4 releases the accumulated brake fluid in the accumulator 52 to the master reservoir 4 when the fluid pressure in the accumulator 52 exceeds a predetermined upper limit.
【0019】レギュレータ6は、アキュムレータ52及
び増圧器7,7’(又は後輪ホイールシリンダWrl,
Wrr)間に配設された常閉型の2ポート比例電磁弁6
1と、増圧器7,7’(又は後輪ホイールシリンダWr
l,Wrr)及びマスタリザーバ4間に配設された常開
型の2ポート比例電磁弁62とから構成されている。主
液圧路P1’には、マスタシリンダ1の圧力室1bの圧
力(即ちマスタシリンダ液圧)を検出する圧力センサP
Sが接続されている。この圧力センサPSの検出信号は
電子制御装置ECUに入力され、電子制御装置ECUは
圧力センサPSの検出信号に応じた電流値を演算し、比
例電磁弁61,62に出力する。つまり、比例電磁弁6
1,62は、アキュムレータ52のパワー圧をマスタシ
リンダ液圧に応じたレギュレータ液圧に調圧する。The regulator 6 includes an accumulator 52 and pressure intensifiers 7, 7 '(or a rear wheel cylinder Wrl,
Wrr), a normally closed 2-port proportional solenoid valve 6
1 and the pressure intensifiers 7, 7 '(or the rear wheel cylinder Wr
1, Wrr) and a normally open two-port proportional solenoid valve 62 disposed between the master reservoir 4. A pressure sensor P for detecting the pressure of the pressure chamber 1b of the master cylinder 1 (that is, the master cylinder pressure) is provided in the main hydraulic pressure path P1 '.
S is connected. The detection signal of the pressure sensor PS is input to the electronic control unit ECU. The electronic control unit ECU calculates a current value according to the detection signal of the pressure sensor PS and outputs the current value to the proportional solenoid valves 61 and 62. That is, the proportional solenoid valve 6
Reference numerals 1 and 62 regulate the power pressure of the accumulator 52 to a regulator fluid pressure corresponding to the master cylinder fluid pressure.
【0020】尚、レギュレータ6を2つの2ポート比例
電磁弁で構成したが、アキュムレータ52に接続される
第1ポート、増圧器7,7’(又は後輪ホイールシリン
ダWrl,Wrr)に接続される第2ポート、及びマス
タリザーバ4に接続される第3ポートをもつ1つの3ポ
ート比例電磁弁で構成しても良く、マスタシリンダに機
械的に連動する機械式レギュレータで構成しても良い。
また、圧力センサPSに代えてペダルストロークセンサ
や踏力センサを設けても良い。更に、電子制御装置は、
荷重センサ、車輪速度センサ、ヨーレートセンサ、横加
速度センサ、操舵角センサ等の検出信号を入力し、荷重
に応じた制御、アンチスキッド制御、前後制動力配分制
御、トラクション制御、オーバーステア抑制制御、アン
ダーステア抑制制御、ブレーキアシスト制御、自動ブレ
ーキ制御等の各種制御を行うことができる。Although the regulator 6 is composed of two 2-port proportional solenoid valves, it is connected to the first port connected to the accumulator 52 and the pressure intensifiers 7, 7 '(or the rear wheel cylinders Wrl, Wrr). It may be constituted by one 3-port proportional solenoid valve having the second port and the third port connected to the master reservoir 4, or may be constituted by a mechanical regulator mechanically linked to the master cylinder.
Further, a pedal stroke sensor or a pedaling force sensor may be provided instead of the pressure sensor PS. In addition, the electronic control unit
Input detection signals from load sensor, wheel speed sensor, yaw rate sensor, lateral acceleration sensor, steering angle sensor, etc., and control according to load, anti-skid control, longitudinal braking force distribution control, traction control, oversteer suppression control, understeer Various controls such as suppression control, brake assist control, and automatic brake control can be performed.
【0021】図2は図1における増圧器7の具体的構成
を示す拡大断面図である。尚、他方の増圧器7’の構成
も増圧器7と同一であるので、その説明を省略する。FIG. 2 is an enlarged sectional view showing a specific configuration of the pressure intensifier 7 in FIG. Note that the configuration of the other pressure intensifier 7 'is the same as that of the pressure intensifier 7, and the description thereof is omitted.
【0022】増圧器7のハウジング71には、第1入力
ポート71a、第2入力ポート71b、出力ポート71
c及び段付シリンダ孔71dが形成されている。第1入
力ポート71aは、レギュレータ6に接続されてレギュ
レータ6の出力レギュレータ液圧を入力する。第2入力
ポート71bは、マスタシリンダ1の圧力室1aに接続
されてマスタシリンダ液圧を入力する。出力ポート71
cは、左前輪ホイールシリンダWflに接続される。The housing 71 of the pressure intensifier 7 has a first input port 71a, a second input port 71b, and an output port 71.
c and a stepped cylinder hole 71d are formed. The first input port 71 a is connected to the regulator 6 and inputs the output regulator hydraulic pressure of the regulator 6. The second input port 71b is connected to the pressure chamber 1a of the master cylinder 1 and inputs a master cylinder hydraulic pressure. Output port 71
c is connected to the left front wheel cylinder Wfl.
【0023】段付シリンダ孔71dには、一端側(図示
右端側)のシール径(シール面積)が他端側(図示左端
側)のシール径(シール面積)よりも大の円柱状の段付
ピストン72が摺動自在に配設されている。段付ピスト
ン72の大径端とハウジング71との間には出力ポート
71cに連通する圧力室72aが形成され、段付ピスト
ン72の小径端とハウジング71との間には第1入力ポ
ート71aに連通する第1入力室72bが形成されてい
る。これにより、圧力室72aは第1入力室72bより
も小径とされ、段付ピストン72の大径端が圧力室72
aの液圧から受ける受圧面積S1は、段付ピストン72
の小径端が第1入力室72bのレギュレータ液圧から受
ける受圧面積S2よりも大とされている。In the stepped cylinder hole 71d, a cylindrical stepped seal whose seal diameter (seal area) at one end (right end in the drawing) is larger than the seal diameter (seal area) at the other end (left end in the drawing). A piston 72 is slidably disposed. A pressure chamber 72a communicating with the output port 71c is formed between the large diameter end of the stepped piston 72 and the housing 71, and a first input port 71a is provided between the small diameter end of the stepped piston 72 and the housing 71. A communicating first input chamber 72b is formed. Thus, the pressure chamber 72a has a smaller diameter than the first input chamber 72b, and the large-diameter end of the stepped piston 72 is
The pressure receiving area S1 received from the hydraulic pressure of a
Is smaller than the pressure receiving area S2 received from the regulator hydraulic pressure in the first input chamber 72b.
【0024】段付ピストン72の外周部には、圧力室7
2a及び第1入力室72b間に位置するよう段付環状室
72cが形成され、第2入力ポート71bに連通してい
る。この段付環状室72cは、段付ピストン72の大径
端が圧力室72aの液圧から受ける受圧面積S1と段付
ピストン72の小径端が第1入力室72bのレギュレー
タ液圧から受ける受圧面積S2との差に等しい受圧面積
をもっており、段付ピストン72の圧力室72aの容積
を減少させる方向への移動に伴いその容積が増大するよ
うに構成されている。段付ピストン72の外周部には、
第1入力室72b及び段付環状室72c間に位置するよ
うにシールリング72dが配設され、両者間が液密的に
分離されている。また、段付ピストン72の外周部に
は、段付環状室72c及び圧力室72a間に位置するよ
うにシールリング72eが配設され、ピストン外周部を
介する段付環状室72c及び圧力室72a間の連通を遮
断している。A pressure chamber 7 is provided around the outer periphery of the stepped piston 72.
A stepped annular chamber 72c is formed between the first input chamber 72b and the second input chamber 72b, and communicates with the second input port 71b. The stepped annular chamber 72c has a pressure receiving area S1 where the large diameter end of the stepped piston 72 receives from the hydraulic pressure of the pressure chamber 72a and a pressure receiving area where the small diameter end of the stepped piston 72 receives from the regulator hydraulic pressure of the first input chamber 72b. It has a pressure receiving area equal to the difference from S2, and is configured such that the volume of the stepped piston 72 increases as the pressure chamber 72a moves in the direction of decreasing the volume. On the outer periphery of the stepped piston 72,
A seal ring 72d is provided so as to be located between the first input chamber 72b and the stepped annular chamber 72c, and the two are separated in a liquid-tight manner. A seal ring 72e is disposed on the outer periphery of the stepped piston 72 so as to be located between the stepped annular chamber 72c and the pressure chamber 72a, and between the stepped annular chamber 72c and the pressure chamber 72a via the piston outer periphery. Communication is blocked.
【0025】ハウジング71には、段付シリンダ孔71
dの図示右端に位置するようにリテーナ部材73が固定
されている。段付ピストン72の右端部には円筒部72
fが形成され、円筒部72fの先端にはその開口部を塞
ぐようにリテーナ74が対向配置されている。このリテ
ーナ74とリテーナ部材73との間には、スプリング7
5が配設され、リテーナ74を段付ピストン72の円筒
部72fの先端に押圧している。即ち、段付ピストン7
2は、スプリング75により、圧力室72aの容積を増
加する方向に付勢されており、第1入力室72bにレギ
ュレータ液圧が入力されていないときは図示するように
段付ピストン72の左端面は段付シリンダ孔の左端面に
当接している。The housing 71 has a stepped cylinder hole 71.
The retainer member 73 is fixed so as to be located at the right end in the drawing of FIG. A cylindrical portion 72 is provided at the right end of the stepped piston 72.
f is formed, and a retainer 74 is opposed to the tip of the cylindrical portion 72f so as to close the opening. A spring 7 is provided between the retainer 74 and the retainer member 73.
5, which presses the retainer 74 against the tip of the cylindrical portion 72 f of the stepped piston 72. That is, the stepped piston 7
2 is urged by a spring 75 in a direction to increase the volume of the pressure chamber 72a, and when regulator fluid pressure is not input to the first input chamber 72b, the left end face of the stepped piston 72 as shown in the drawing. Is in contact with the left end face of the stepped cylinder hole.
【0026】段付ピストン72の円筒部72f内には、
常開型の開閉弁(切換弁)8が配設されている。開閉弁
8は、円筒状の弁体81と、弁体81に着脱可能な弁座
部材82と、弁座部材82を弁体81に着座する方向に
付勢するスプリング83とから構成されている。弁体8
1は、段付ピストン72の円筒部72fの底面側端部に
圧入固定されており、段付ピストン72と共に一体移動
可能である。この弁体81は、本体81aと、本体81
aの外周部に固定された弾性体81bとから構成されて
おり、弾性体81bが弁座部材82に着脱可能になって
いる。常態(図示状態)では弾性体81bは弁座82か
ら離脱しており、段付環状室72cは段付ピストン72
に形成された通路72g,72hを介して圧力室72a
に連通している。スプリング83は、リテーナ74と弁
座部材82の間に配設され、このスプリング83によ
り、段付ピストン72が図示右方に移動したときに弁体
81が弁座部材82に着座し、その状態が維持される。In the cylindrical portion 72f of the stepped piston 72,
A normally open on-off valve (switching valve) 8 is provided. The on-off valve 8 includes a cylindrical valve body 81, a valve seat member 82 detachable from the valve body 81, and a spring 83 for urging the valve seat member 82 in a direction in which the valve seat member 82 is seated on the valve body 81. . Valve 8
1 is press-fitted and fixed to the bottom end of the cylindrical portion 72f of the stepped piston 72, and can move together with the stepped piston 72. The valve body 81 includes a main body 81a and a main body 81a.
The elastic body 81b is fixed to the outer peripheral portion of the valve seat a, and the elastic body 81b is detachable from the valve seat member 82. In a normal state (shown), the elastic body 81b is separated from the valve seat 82, and the stepped annular chamber 72c is
Pressure chamber 72a through passages 72g and 72h formed in
Is in communication with The spring 83 is disposed between the retainer 74 and the valve seat member 82, and when the stepped piston 72 moves rightward in the drawing, the valve body 81 is seated on the valve seat member 82 by this spring 83, Is maintained.
【0027】弁座部材82にはロッド76が一体的に設
けられている。ロッド76は、弁座部材82の左端から
リテーナ74を貫通してリテーナ部材73に向かって延
び、その先端(右端)はリテーナ部材73内に取付けら
れた保持部材77によりリテーナ部材73から外れない
ように支持されている。尚、段付ピストン72の円筒部
72fの外周には、カップ状シール部材78が配設され
ている。A rod 76 is provided integrally with the valve seat member 82. The rod 76 extends from the left end of the valve seat member 82 through the retainer 74 toward the retainer member 73, and its tip (right end) is not detached from the retainer member 73 by the holding member 77 attached to the retainer member 73. It is supported by. A cup-shaped seal member 78 is provided on the outer periphery of the cylindrical portion 72f of the stepped piston 72.
【0028】上記の如く構成された液圧ブレーキ装置の
作動を説明する。The operation of the hydraulic brake device configured as described above will be described.
【0029】ブレーキペダル3の非操作時には、増圧器
7内に設けられた開閉弁8が開放しているため、マスタ
シリンダ1の一方の圧力室1aが増圧器7の圧力室72
aを介して左前輪ホイールシリンダWflに連通してい
る。また同様に、マスタシリンダ1の他方の圧力室1b
も増圧器7’を介して右前輪ホイールシリンダWfrに
連通している。When the brake pedal 3 is not operated, the on-off valve 8 provided in the pressure intensifier 7 is open, so that one pressure chamber 1a of the master cylinder 1 is connected to the pressure chamber 72 of the pressure intensifier 7.
a, and communicates with the front left wheel cylinder Wfl. Similarly, the other pressure chamber 1b of the master cylinder 1
Also communicates with the right front wheel cylinder Wfr via the pressure intensifier 7 '.
【0030】運転者がブレーキペダル3を操作すると、
マスタシリンダ液圧が増圧器7,7’に出力されると共
に、電子制御装置ECUによりマスタシリンダ液圧に応
じてレギュレータ6が制御される。結果、レギュレータ
6によりアキュムレータ52のパワー液圧がマスタシリ
ンダ液圧に略比例するレギュレータ液圧に調圧される。
このレギュレータ液圧が増圧器7の入力室72bに入力
され、段付ピストン72がスプリング75の付勢力に抗
して圧力室72aの容積を減少させる方向に摺動する。
すると、段付ピストン72と連動する開閉弁8の弁体8
1が弁座部材82に着座し、マスタシリンダ1の圧力室
1a(つまり段付環状室72c)及び圧力室72a(つ
まりホイールシリンダWfl)間の連通が遮断される。
この状態で更に段付ピストン72が摺動すると、圧力室
72aのブレーキ液圧が増圧され、このブレーキ液圧が
左前輪ホイールシリンダWflに供給される。即ち、レ
ギュレータ液圧が左前輪ホイールシリンダWflに供給
される。尚、同様な作動により、レギュレータ液圧が右
前輪ホイールシリンダWfrに供給される。When the driver operates the brake pedal 3,
The master cylinder hydraulic pressure is output to the pressure intensifiers 7 and 7 ', and the electronic control unit ECU controls the regulator 6 according to the master cylinder hydraulic pressure. As a result, the regulator 6 regulates the power hydraulic pressure of the accumulator 52 to a regulator hydraulic pressure that is substantially proportional to the master cylinder hydraulic pressure.
This regulator fluid pressure is input to the input chamber 72b of the pressure intensifier 7, and the stepped piston 72 slides in a direction to reduce the volume of the pressure chamber 72a against the urging force of the spring 75.
Then, the valve element 8 of the opening / closing valve 8 interlocked with the stepped piston 72
1 is seated on the valve seat member 82, and the communication between the pressure chamber 1a (that is, the stepped annular chamber 72c) and the pressure chamber 72a (that is, the wheel cylinder Wfl) of the master cylinder 1 is cut off.
When the stepped piston 72 further slides in this state, the brake fluid pressure in the pressure chamber 72a is increased, and this brake fluid pressure is supplied to the left front wheel cylinder Wfl. That is, the regulator hydraulic pressure is supplied to the front left wheel cylinder Wfl. Note that, by the same operation, the regulator hydraulic pressure is supplied to the right front wheel cylinder Wfr.
【0031】上記作動中、ブレーキペダル操作量即ち段
付ピストン72の移動量に応じた分だけ段付環状室72
cの容積が増加する。結果、マスタシリンダ液圧が段付
環状室72cに流入し、ブレーキペダル3は確実にスト
ロークする。つまり、段付環状室72cがブレーキペダ
ル3のストロークシュミレータとして機能する。During the above operation, the stepped annular chamber 72 has an amount corresponding to the operation amount of the brake pedal, that is, the movement amount of the stepped piston 72.
The volume of c increases. As a result, the master cylinder hydraulic pressure flows into the stepped annular chamber 72c, and the brake pedal 3 reliably strokes. That is, the stepped annular chamber 72c functions as a stroke simulator of the brake pedal 3.
【0032】また上記作動と同時に、レギュレータ6の
出力レギュレータ液圧が後輪ホイールシリンダWrl,
Wrrに供給される。Simultaneously with the above operation, the output regulator hydraulic pressure of the regulator 6 is changed to the rear wheel cylinder Wrl,
Wrr.
【0033】一方、運転者がブレーキペダル3を解放す
ると、マスタシリンダ液圧が減圧されるので、それに応
じてレギュレータ6が図1の状態に切り換わる。する
と、スプリング75の付勢力により増圧器7の段付ピス
トン72が圧力室72aの容積を増加させる方向に移動
し、開閉弁8の弁体81が弁座部材82から離脱する。
その結果、左前輪ホイールシリンダWflのブレーキ液
圧はマスタシリンダ1の圧力室1a(ひいてはマスタリ
ザーバ4)に戻され、同様に右前輪ホイールシリンダW
flのブレーキ液圧もマスタシリンダ1の圧力室1b
(ひいてはマスタリザーバ4)に戻される。また、後輪
ホイールシリンダWrl,Wrrのブレーキ液圧はレギ
ュレータ6を介してマスタリザーバ4に戻される。On the other hand, when the driver releases the brake pedal 3, the master cylinder hydraulic pressure is reduced, and accordingly, the regulator 6 switches to the state shown in FIG. Then, the stepped piston 72 of the pressure intensifier 7 moves in the direction of increasing the volume of the pressure chamber 72 a by the urging force of the spring 75, and the valve body 81 of the on-off valve 8 is separated from the valve seat member 82.
As a result, the brake fluid pressure of the left front wheel cylinder Wfl is returned to the pressure chamber 1a of the master cylinder 1 (therefore, the master reservoir 4).
The brake fluid pressure of fl is also the pressure chamber 1b of the master cylinder 1.
(Consequently, it is returned to the master reservoir 4). The brake fluid pressure in the rear wheel cylinders Wrl and Wrr is returned to the master reservoir 4 via the regulator 6.
【0034】[0034]
【発明の効果】請求項1の発明によれば、切換弁がピス
トンに機械的に連動してマスタシリンダ及びホイールシ
リンダ間の液圧路を開閉するので、切換弁を駆動するた
めのソレノイドを廃止でき、結果、安価になると共に小
型化する。According to the first aspect of the present invention, the switching valve opens and closes the hydraulic path between the master cylinder and the wheel cylinder in mechanical linkage with the piston, so that the solenoid for driving the switching valve is eliminated. As a result, it becomes cheaper and smaller.
【0035】また、請求項3の発明によれば、マスタシ
リンダに常時連通しピストンの作動に伴い容積が変化す
る第2入力室を増圧器に設けたので、簡単な構成でブレ
ーキペダルのストロークシュミレータ機能を発揮でき、
結果、一層安価になる。According to the third aspect of the present invention, since the second input chamber which is always in communication with the master cylinder and whose volume changes with the operation of the piston is provided in the pressure intensifier, the stroke simulator of the brake pedal has a simple structure. Function.
As a result, it becomes even cheaper.
【図1】本発明の一実施形態に係る車両用液圧ブレーキ
装置の全体構成図である。FIG. 1 is an overall configuration diagram of a vehicle hydraulic brake device according to an embodiment of the present invention.
【図2】図1の増圧器の拡大断面図である。FIG. 2 is an enlarged sectional view of the pressure intensifier of FIG.
FL,FR,RL,RR 車輪 Wfl,Wfr,Wrl,Wrr ホイールシリンダ 1 マスタシリンダ 1a,1b マスタシリンダの圧力室 3 ブレーキペダル 4 マスタリザーバ(リザーバ) P1 液圧路 5 補助液圧源(液圧源) 6 レギュレータ 7 増圧器 71 ハウジング 71d 段付シリンダ孔 72 段付ピストン 72a 圧力室 72b 入力室(第1入力室) 72c 段付環状室(第2入力室) 75 スプリング 8 開閉弁(切換弁) 81 弁体 82 弁座部材(弁座) 83 スプリング FL, FR, RL, RR Wheels Wfl, Wfr, Wrl, Wrr Wheel cylinder 1 Master cylinder 1a, 1b Pressure chamber of master cylinder 3 Brake pedal 4 Master reservoir (reservoir) P1 Hydraulic pressure path 5 Auxiliary hydraulic pressure source (hydraulic pressure source) 6) Regulator 7 Booster 71 Housing 71d Stepped cylinder hole 72 Stepped piston 72a Pressure chamber 72b Input chamber (first input chamber) 72c Stepped annular chamber (second input chamber) 75 Spring 8 Opening / closing valve (switching valve) 81 Valve body 82 Valve seat member (valve seat) 83 Spring
Claims (6)
るホイールシリンダと、ブレーキ液を貯蔵するリザーバ
と、ブレーキペダルの操作量に応じて前記リザーバのブ
レーキ液を昇圧しマスタシリンダ液圧を出力するマスタ
シリンダと、前記リザーバ内のブレーキ液を所定の圧力
に昇圧してパワー液圧を出力する液圧源と、前記液圧源
の出力パワー液圧を少なくとも前記ブレーキペダルの操
作量に応じたレギュレータ液圧に調圧するレギュレータ
と、前記マスタシリンダ及び前記ホイールシリンダ間の
液圧路に配設され前記液圧路を開閉する切換弁と、前記
レギュレータ及び前記ホイールシリンダ間を液密的に分
離するピストンを有し、前記レギュレータの出力レギュ
レータ液圧に応じて前記ピストンを作動させてレギュレ
ータ液圧に応じた液圧を前記ホイールシリンダに供給す
る増圧器とを備えた車両用液圧ブレーキ装置において、 前記切換弁は、前記ピストンに機械的に連動して前記液
圧路を開閉するように構成されていることを特徴とする
車両用液圧ブレーキ装置。1. A wheel cylinder mounted on a vehicle wheel for braking the wheel, a reservoir for storing brake fluid, and a brake fluid in the reservoir is boosted according to an operation amount of a brake pedal to output a master cylinder fluid pressure. A master cylinder, a hydraulic pressure source for increasing the brake fluid in the reservoir to a predetermined pressure and outputting a power hydraulic pressure, and an output power hydraulic pressure of the hydraulic pressure source at least according to an operation amount of the brake pedal. A regulator that regulates a regulator hydraulic pressure, a switching valve that is provided in a hydraulic passage between the master cylinder and the wheel cylinder and opens and closes the hydraulic passage, and liquid-tightly separates the regulator and the wheel cylinder. A fluid having a piston and actuating the piston in accordance with the output regulator fluid pressure of the regulator to operate the piston in accordance with the regulator fluid pressure; A hydraulic brake device for a vehicle, comprising: a pressure intensifier that supplies pressure to the wheel cylinder. The switching valve is configured to open and close the hydraulic pressure path mechanically in association with the piston. A hydraulic brake device for a vehicle, comprising:
一端側に前記ホイールシリンダに連通する圧力室を形成
すると共に他端側にレギュレータ液圧を入力する第1入
力室を形成し、 前記切換弁は、前記第1入力室にレギュレータ液圧が供
給されていないときは、前記マスタシリンダを前記圧力
室に連通し、前記第1入力室にレギュレータ液圧が供給
されて前記ピストンが前記圧力室の容積を小さくする方
向に摺動したときに、前記ピストンに機械的に連動して
前記マスタシリンダ及び前記圧力室間の連通を遮断する
ように構成されていることを特徴とする車両用液圧ブレ
ーキ装置。2. The method according to claim 1, wherein the piston is slidably disposed in the housing.
A pressure chamber communicating with the wheel cylinder is formed on one end side, and a first input chamber for inputting regulator fluid pressure is formed on the other end side. The switching valve is configured such that the regulator fluid pressure is supplied to the first input chamber. When not, the master cylinder is communicated with the pressure chamber, and when the regulator hydraulic pressure is supplied to the first input chamber and the piston slides in a direction to reduce the volume of the pressure chamber, the piston moves. A hydraulic brake device for a vehicle, wherein the hydraulic brake device is configured to mechanically interlock with the hydraulic cylinder to cut off communication between the master cylinder and the pressure chamber.
ストンの作動に伴い容積が変化する第2入力室を有する
ことを特徴とする車両用液圧ブレーキ装置。3. The hydraulic brake system for a vehicle according to claim 2, wherein the pressure intensifier has a second input chamber which is always in communication with the master cylinder and whose volume changes with the operation of the piston.
れ、前記圧力室の圧力を受ける受圧面積が前記第1入力
室の圧力を受ける受圧面積よりも大きい段付ピストンで
あり、 前記第2入力室は、前記ピストンの外周に形成された段
付環状室であり、前記段付環状室は、前記ピストンが前
記圧力室の容積を小さくする方向に摺動するに伴いその
容積が増加するように構成されていることを特徴とする
車両用液圧ブレーキ装置。4. The housing according to claim 3, wherein the housing has a stepped cylinder, the piston is slidably disposed on the stepped cylinder, and a pressure receiving area for receiving a pressure of the pressure chamber is the first pressure receiving area. A stepped piston larger than a pressure receiving area receiving the pressure of the input chamber; the second input chamber is a stepped annular chamber formed on the outer periphery of the piston; A hydraulic brake device for a vehicle, characterized in that the pressure chamber is configured to increase in volume as the pressure chamber slides in a direction to reduce the volume.
を特徴とする車両用液圧ブレーキ装置。5. The hydraulic brake device for a vehicle according to claim 1, wherein the switching valve is provided inside the pressure intensifier.
一端側に前記ホイールシリンダに連通する圧力室を形成
すると共に他端側にレギュレータ液圧を入力する第1入
力室を形成し、 前記切換弁は、前記ピストンの一端に固定された弁体
と、前記圧力室に前記弁体に着脱可能に配置された弁座
とを有し、前記ピストンが前記圧力室の容積を小さくす
る方向に摺動して前記弁体が前記弁座に着座した後、前
記弁体及び弁座は前記ピストンと共に一体移動するよう
に構成されていることを特徴とする車両用液圧ブレーキ
装置。6. The piston according to claim 5, wherein the piston is slidably disposed in the housing.
A pressure chamber communicating with the wheel cylinder is formed on one end side, and a first input chamber for inputting regulator fluid pressure is formed on the other end side, wherein the switching valve is a valve body fixed to one end of the piston, Having a valve seat removably disposed on the valve body in the pressure chamber, after the piston slides in a direction to reduce the volume of the pressure chamber and the valve body is seated on the valve seat, A hydraulic brake device for a vehicle, wherein the valve element and the valve seat are configured to move together with the piston.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10177696A JP2000006785A (en) | 1998-06-24 | 1998-06-24 | Hydraulic brake system for vehicle |
DE1999128756 DE19928756A1 (en) | 1998-06-24 | 1999-06-23 | Hydraulic brake apparatus for vehicle |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10177696A JP2000006785A (en) | 1998-06-24 | 1998-06-24 | Hydraulic brake system for vehicle |
Publications (1)
Publication Number | Publication Date |
---|---|
JP2000006785A true JP2000006785A (en) | 2000-01-11 |
Family
ID=16035517
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP10177696A Pending JP2000006785A (en) | 1998-06-24 | 1998-06-24 | Hydraulic brake system for vehicle |
Country Status (2)
Country | Link |
---|---|
JP (1) | JP2000006785A (en) |
DE (1) | DE19928756A1 (en) |
-
1998
- 1998-06-24 JP JP10177696A patent/JP2000006785A/en active Pending
-
1999
- 1999-06-23 DE DE1999128756 patent/DE19928756A1/en not_active Ceased
Also Published As
Publication number | Publication date |
---|---|
DE19928756A1 (en) | 1999-12-30 |
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