JPH04212664A - Fluid pressure brake system - Google Patents
Fluid pressure brake systemInfo
- Publication number
- JPH04212664A JPH04212664A JP271291A JP271291A JPH04212664A JP H04212664 A JPH04212664 A JP H04212664A JP 271291 A JP271291 A JP 271291A JP 271291 A JP271291 A JP 271291A JP H04212664 A JPH04212664 A JP H04212664A
- Authority
- JP
- Japan
- Prior art keywords
- brake
- valve
- pump
- conduit
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 34
- 238000000926 separation method Methods 0.000 claims description 6
- 238000002955 isolation Methods 0.000 claims description 4
- 230000000903 blocking effect Effects 0.000 claims 1
- 241000931526 Acer campestre Species 0.000 abstract 1
- 230000002349 favourable effect Effects 0.000 abstract 1
- 238000009423 ventilation Methods 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
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
- B60T8/48—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 connecting the brake actuator to an alternative or additional source of fluid pressure, e.g. traction control systems
- B60T8/4809—Traction control, stability control, using both the wheel brakes and other automatic braking systems
- B60T8/4827—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems
- B60T8/4863—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems
- B60T8/4872—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems pump-back 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
- 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
- B60T13/12—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 the fluid being liquid
- B60T13/16—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 the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs
-
- 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
- B60T8/343—Systems characterised by their lay-out
- B60T8/344—Hydraulic systems
- B60T8/347—3 Channel 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
-
- 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
- B60T8/4018—Pump units characterised by their drive mechanisms
- B60T8/4022—Pump units driven by an individual electric motor
-
- 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
- B60T8/4031—Pump units characterised by their construction or mounting
-
- 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
- B60T8/404—Control of the pump unit
- B60T8/405—Control of the pump unit involving the start-up phase
-
- 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
- B60T8/42—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 having expanding chambers for controlling pressure, i.e. closed systems
- B60T8/4275—Pump-back systems
- B60T8/4291—Pump-back systems having means to reduce or eliminate pedal kick-back
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Regulating Braking Force (AREA)
- Braking Systems And Boosters (AREA)
Abstract
Description
【0001】0001
【産業上の利用分野】本発明は流体圧ブレーキシステム
に関し、少なくとも1個のホイールブレーキがブレーキ
導管を介してマスタシリンダと連通し、ペダルが作動す
ると、圧力流体がマスタブレーキシリンダからブレーキ
導管を介してホイールブレーキシリンダに移動するペダ
ル作動マスタシリンダと、油圧ポンプとで構成されるブ
レーキスリップ/トラクションスリップ制御装置付きの
流体圧ブレーキシステムに関する。TECHNICAL FIELD The present invention relates to a hydraulic brake system, in which at least one wheel brake communicates with a master cylinder through a brake conduit, and when a pedal is actuated, pressure fluid is transferred from the master brake cylinder through the brake conduit. The present invention relates to a hydraulic brake system with a brake slip/traction slip control device comprising a pedal actuated master cylinder that moves to a wheel brake cylinder and a hydraulic pump.
【0002】0002
【従来の技術】上記の型のブレーキシステムは、例えば
DE OS 3,831,426に開示されている
。ポンプは、制御時に,吐出される圧力流体をホイール
ブレーキからブレーキ導管に送るための機能を備えてい
る。
そのためポンプの吸込側は、ホイールブレーキに接続可
能な圧力流体コレクタ装置に結合し、ポンプの圧力側は
マスタブレーキシリンダに接続している。従ってポンプ
はブレーキ導管の分岐路に配置されているので、非制御
減速時に圧力流体がそこから流出することはない。吸込
側とマスタブレーキシリンダとの接続は、トラクション
スリップ制御時にのみなされる。この場合、ポンプはマ
スタブレーキシリンダに接続するリザーバから圧力を吸
収し、この圧力をホイールブレーキに送る。ただし、こ
うして圧力が送られるのは、マスタブレーキシリンダが
動作していない時、つまり非加圧状態の時に限られる。BACKGROUND OF THE INVENTION A brake system of the above type is disclosed, for example, in DE OS 3,831,426. The pump has the function of conveying the discharged pressurized fluid from the wheel brake to the brake conduit when controlled. For this purpose, the suction side of the pump is connected to a pressure fluid collector device connectable to the wheel brake, and the pressure side of the pump is connected to the master brake cylinder. The pump is therefore arranged in a branch of the brake conduit, so that no pressure fluid can escape there during uncontrolled deceleration. The connection between the suction side and the master brake cylinder is made only during traction slip control. In this case, the pump absorbs pressure from a reservoir connected to the master brake cylinder and sends this pressure to the wheel brakes. However, pressure is sent in this way only when the master brake cylinder is not operating, that is, when it is in a non-pressurized state.
【0003】上記の型の回路には、本質的に2つの短所
がある。先ず,ブレーキスリップ制御においてポンプは
、非加圧状態の圧力流体収集装置からマスタシリンダの
圧力により吐出を行う。従ってブレーキ流体が低温で粘
度が高い時、ポンプは始動段階が延長されなければ最大
出力に達しないので、制御は質的に低下する。もう一つ
の短所は、自動吸込ポンプがその吸込側に適当な圧力流
体がない場合、真空を生成することである。対応する封
止が破損した場合、空気はこの真空部分に流入しやすく
なる。ポンプはブレーキ導管の分岐路に配置されている
ので、流入した空気を除去することは難しく、ブレーキ
システム内の空胴部によってブレーキシステムの故障が
生じやすくなる。There are essentially two disadvantages to circuits of the above type. First, in brake slip control, the pump discharges fluid from the non-pressurized pressure fluid collection device using the pressure of the master cylinder. Therefore, when the brake fluid is cold and viscous, the control quality is degraded because the pump will not reach its maximum output unless the starting phase is extended. Another disadvantage is that automatic suction pumps create a vacuum in the absence of suitable pressure fluid on their suction side. Air tends to enter this vacuum section if the corresponding seal is broken. Since the pump is located in a branch of the brake conduit, it is difficult to remove the incoming air, and cavities within the brake system are susceptible to failure of the brake system.
【0004】0004
【発明が解決しようとする課題】従って本発明は、周囲
温度に左右されず永続的に高度な制御を保証し、故障の
可能性が少なく、特に換気が容易な流体圧ブレーキシス
テムを提供することにある。SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a hydraulic brake system that permanently guarantees a high degree of control regardless of the ambient temperature, has a low possibility of failure, and is particularly easy to ventilate. It is in.
【0005】[0005]
【課題を解決するための手段】本発明の上記課題は、請
求項1記載の手段,即ち少なくとも1個のホイールブレ
ーキ(3)がブレーキ導管(2)を介してマスタブレー
キシリンダ(1)に連通し、ペダル作動時,圧力流体が
マスタブレーキシリンダから上記ブレーキ導管を介して
上記ホイールブレーキ内に移動するペダル作動マスタシ
リンダ(1)と、流体圧ポンプ(4)とで構成され、上
記ポンプは、その吸込側Sが上記マスタブレーキシリン
ダ(1)に連通し、その圧力側Dがホイールブレーキシ
リンダと連通するように,上記ブレーキ導管(2)内に
挿入されている流体圧ブレーキシステムによって解決さ
れる。The object of the invention is achieved by the means according to claim 1, in which at least one wheel brake (3) is connected via a brake conduit (2) to a master brake cylinder (1). and comprises a pedal actuation master cylinder (1) through which pressurized fluid moves from the master brake cylinder through the brake conduit into the wheel brake when the pedal is actuated, and a fluid pressure pump (4), the pump comprising: solved by a hydraulic brake system inserted into said brake conduit (2) such that its suction side S communicates with said master brake cylinder (1) and its pressure side D communicates with said wheel brake cylinder. .
【0006】[0006]
【作用】上述の構成において、ブレーキ導管にポンプが
装備されているので、ポンプが始動するとポンプの吸込
側と圧力側に圧力の平衡が生じ、特に低温の場合,ポン
プの機能は著しく改善され、減速過程で避け難いエァポ
ケットがポンプからなくなり、ポンプの効率が維持され
る。[Operation] In the above configuration, the brake conduit is equipped with a pump, so when the pump starts, there is a pressure equilibrium between the suction side and the pressure side of the pump, and the function of the pump is significantly improved, especially at low temperatures. Air pockets that are unavoidable during the deceleration process are removed from the pump and the efficiency of the pump is maintained.
【0007】ブレーキ圧調整装置は通常、ホイールブレ
ーキに対する圧力流体の供給を制御する吸込弁と吐出弁
とで構成される。これらの弁は電磁作動し、電子分析器
による制御信号が使用可能であり、車輪の回転パターン
を決定するセンサの信号が評価される。[0007] Brake pressure regulators typically consist of a suction valve and a discharge valve that control the supply of pressurized fluid to the wheel brakes. These valves are electromagnetically actuated and control signals by an electronic analyzer are available to evaluate the sensor signals that determine the rotation pattern of the wheels.
【0008】マスタシリンダとポンプの吸込側とを分離
する弁は、ブレーキのスリップ制御が行われる際,ブレ
ーキ回路から遮断されるので、システム内の圧力変動は
マスタシリンダに対して影響を及ぼさない。The valve separating the master cylinder from the suction side of the pump is isolated from the brake circuit when brake slip control is performed, so that pressure fluctuations within the system have no effect on the master cylinder.
【0009】ポンプ圧力側の高圧アキュムレータは、ポ
ンプが吐出する圧力流体を吸収し、マスタシリンダの代
わりに圧力発生装置として作用する。圧力流体が通常の
減速過程で,早々と圧力流体を吸収するのを防ぐため、
アキュムレータのばねを偏らせて、車輪がロックしない
程度の圧力ではアキュムレータが圧力流体を吸収しない
ようにする。The high-pressure accumulator on the pump pressure side absorbs the pressure fluid delivered by the pump and acts as a pressure generator instead of the master cylinder. In order to prevent pressure fluid from absorbing pressure fluid prematurely during the normal deceleration process,
The accumulator spring is biased to prevent the accumulator from absorbing pressure fluid at pressures that would prevent the wheels from locking.
【0010】直接導管は、ホイールブレーキとマスタシ
リンダとの間に逆止弁が装備されているので、ホイール
ブレーキ内の圧力がマスタシリンダ内の圧力より高くな
るのを防ぐ。その結果、運転者は、ペダルに対する踏圧
を加減する制御減速をしないでよい。また、非制御減速
時の圧力の減少は、直接導管を介して行われる。The direct conduit is equipped with a check valve between the wheel brake and the master cylinder, which prevents the pressure in the wheel brake from becoming higher than the pressure in the master cylinder. As a result, the driver does not need to perform controlled deceleration by increasing or decreasing the pressure applied to the pedal. Also, the pressure reduction during uncontrolled deceleration takes place directly via the conduit.
【0011】トラクションスリップ制御で必要なように
、ペダルが作動しなくてもホイールブレーキに圧力を生
成するために、直接導管には、トラクションスリップ制
御の際に直接導管を遮断する電磁作動弁を装備する。In order to generate pressure on the wheel brakes even without pedal activation, as required for traction slip control, the direct conduit is equipped with an electromagnetically actuated valve that shuts off the direct conduit during traction slip control. do.
【0012】ポンプの吸込側と圧力側との間にある放出
弁は、ポンプの圧力側の圧力が過度に上昇するのを防ぐ
。A release valve between the suction side and the pressure side of the pump prevents the pressure on the pressure side of the pump from increasing too much.
【0013】又ブレーキ導管の分離弁は、機械的にも作
動できることが望ましい。この場合分離弁とアキュムレ
ータとを機械的に結合し、アキュムレータのピストンが
移動する際に分離弁が閉じるようにすると都合がよい。It is also desirable that the brake conduit isolation valve be mechanically actuable. In this case it is advantageous to mechanically couple the separating valve and the accumulator so that the separating valve closes when the piston of the accumulator moves.
【0014】放出弁はアキュムレータ内でも作動でき、
そのためにアキュムレータのピストンには弁が装備され
ている。この弁は、アキュムレータのピストンが予め決
められた距離だけ移動すると、プランジャを介してばね
の力により押し開かれる。アキュムレータのチャンバ内
の圧力流体は、接続導管を介してポンプの吸込側と連通
する背圧チャンバに流入することができる。従ってアキ
ュムレータにロードする際のエネルギー需要が減少する
。同様に、背圧チャンバの容積に対応する圧力流体の追
加の量を高圧に保つことができるので、制御過程でポン
プが故障した場合でも、ポンプは作動し続ける。[0014] The release valve can also operate within the accumulator;
For this purpose, the piston of the accumulator is equipped with a valve. This valve is forced open by the force of a spring via a plunger when the piston of the accumulator moves a predetermined distance. Pressure fluid in the chamber of the accumulator can flow via a connecting conduit into a backpressure chamber that communicates with the suction side of the pump. The energy demand when loading the accumulator is therefore reduced. Similarly, an additional amount of pressurized fluid corresponding to the volume of the backpressure chamber can be kept at high pressure, so that even if the pump fails during the control process, the pump will continue to operate.
【0015】ポンプの吸込側と圧力側に連通する制御可
能なスロットルも、ポンプの効率に良い影響を及ぼし得
る。Controllable throttles communicating with the suction and pressure sides of the pump can also positively influence the efficiency of the pump.
【0016】このシステムにより可能なもう一つの長所
は、ブースト効果が得られることである。この効果を得
るには、ポンプは、ペダル力に比例して制御されなけれ
ばならない。Another advantage possible with this system is that it provides a boosting effect. To obtain this effect, the pump must be controlled proportionally to the pedal force.
【0017】[0017]
【実施例】本発明の原理、その展開および用途について
、4枚の図面を参照して詳しく説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS The principle of the present invention, its development and application will be explained in detail with reference to four drawings.
【0018】先ず、本発明の基本的な原理を表す図1に
ついて説明する。このブレーキシステムは、1個または
複数のホイールブレーキ3が、ブレーキ導管2を介して
,接続されるマスタブレーキシリンダを備えている。
以下で詳しく説明するポンプ4はブレーキ導管内に装備
され、その吸込側Sは第1のブレーキ導管5を介してマ
スタブレーキシリンダ1と連通し、圧力側Dは第2のブ
レーキ導管6を介してホイールブレーキと連通する。上
記第2のブレーキ導管6には、電磁作動する吸込弁が装
備されている。この弁は、定位置で導管を開き、切換位
置では導管を遮断する。ホイールブレーキ3は、戻り導
管9を介して圧力流体コレクター装置10と連通し、戻
り導管9には吐出弁8が装備されている。この吐出弁8
は同じく電磁作動するが、定位置では戻り導管を遮断し
、切換位置では戻り導管を開く。上記圧力流体コレクタ
ー装置10は、受け入れ容量が限られている低圧のアキ
ュムレータである。この装置は、逆止弁11を介して第
1ブレーキ導管5部分(吐出点E)に連通する。吐出点
Eとマスタブレーキシリンダ1との間には分離弁12が
装備されている。上記弁12はこの実施例では電磁的に
作動し、定位置ではブレーキ導管を開き続け、切換位置
ではブレーキ導管を遮断する。First, FIG. 1, which represents the basic principle of the present invention, will be explained. The brake system comprises a master brake cylinder to which one or more wheel brakes 3 are connected via brake conduits 2 . A pump 4, which will be explained in more detail below, is installed in the brake conduit, the suction side S of which communicates with the master brake cylinder 1 via a first brake conduit 5, and the pressure side D communicated with the master brake cylinder 1 via a second brake conduit 6. Communicates with the wheel brake. The second brake conduit 6 is equipped with an electromagnetically operated suction valve. The valve opens the conduit in the home position and blocks the conduit in the switched position. The wheel brake 3 communicates with a pressure fluid collector device 10 via a return conduit 9, which is equipped with a discharge valve 8. This discharge valve 8
is also electromagnetically operated, but in the home position it blocks the return conduit and in the switched position it opens the return conduit. The pressure fluid collector device 10 is a low pressure accumulator with limited capacity. This device communicates via a check valve 11 with the first brake conduit 5 section (discharge point E). A separation valve 12 is provided between the discharge point E and the master brake cylinder 1. The valve 12 is actuated electromagnetically in this embodiment and keeps the brake line open in the home position and shuts it off in the switched position.
【0019】ホイールブレーキ3は、直接導管13を介
してマスタブレーキシリンダ1と連通し、直接導管13
にはマスタブレーキシリンダ方向に開く逆止弁14が装
備されている。この直接導管には、その他締切弁15が
装備されている。この弁については、その機能上、以下
,ASR弁と言うが、定位置では直接導管を開き続け、
トラクションスリップ制御の際の切換位置においては直
接導管を遮断する。ポンプの圧力側Dは、高圧アキュム
レータ16に連通する。このアキュムレータは、この実
施例ではピストン型のアキュムレータである。アキュム
レータのピストン17は、アキュムレータチャンバの容
量が最小になるように強力なばねにより荷重が加えられ
ている。ばね型のアキュムレータ18は、ポンプの圧力
側Dの圧力が最小になり、アキュムレータが容量を吸収
するようにプレストレスが加えられている。The wheel brake 3 communicates with the master brake cylinder 1 via a direct conduit 13;
is equipped with a check valve 14 that opens toward the master brake cylinder. This direct conduit is further equipped with a shutoff valve 15. Due to its function, this valve is hereinafter referred to as the ASR valve, but in its normal position, it continues to directly open the conduit.
In the switching position for traction slip control, the direct line is shut off. The pressure side D of the pump communicates with a high pressure accumulator 16 . This accumulator is a piston-type accumulator in this embodiment. The accumulator piston 17 is loaded with a strong spring so that the volume of the accumulator chamber is minimized. The spring-type accumulator 18 is prestressed so that the pressure on the pressure side D of the pump is at a minimum and the accumulator absorbs the volume.
【0020】この実施例に基くポンプ4はピストン型の
ポンプで、ポンプピストン19は電動の偏心板20によ
り移動する。ポンプピストン19の先にあるポンプチャ
ンバ21は、各1個の逆止弁22と23を介してそれぞ
れポンプ4の吸込側Sと圧力側Dに連通する。逆止弁2
2はポンプチャンバ方向が開き、逆止弁23はポンプチ
ャンバ方向が閉じている。放出弁24は、ポンプの圧力
側と吸込側に連通し、圧力アキュムレータ16に過負荷
が生じるのを防ぐ。The pump 4 based on this embodiment is a piston type pump, and the pump piston 19 is moved by an electric eccentric plate 20. A pump chamber 21 at the end of the pump piston 19 communicates with the suction side S and the pressure side D of the pump 4 via one check valve 22 and 23, respectively. Check valve 2
2 is open toward the pump chamber, and the check valve 23 is closed toward the pump chamber. The discharge valve 24 communicates with the pressure and suction sides of the pump and prevents the pressure accumulator 16 from being overloaded.
【0021】図示のブレーキシステムは、以下のパター
ンで動作する。The illustrated braking system operates in the following pattern.
【0022】1.非制御減速
ペダルが作動すると、圧力流体はマスタブレーキシリン
ダ1からホイールブレーキ3内に移動する。圧力経路は
、開放分離弁12、第1逆止弁22、ポンプチャンバ2
1、第2逆止弁23、開放吸込弁7に至る。ホイールブ
レーキ3内に圧力が生成され、その結果車輪が減速して
、自動車の減速が起こる。ペダルが解放されると、圧力
流体はホイールブレーキ3から開放逆止弁14、直接導
管13、開放ASR弁を介してマスタブレーキシリンダ
内に戻る。圧力生成経路が、通常の減速時,ポンプチャ
ンバ21まで続いていることは重要である。1. When the uncontrolled reduction pedal is actuated, pressure fluid moves from the master brake cylinder 1 into the wheel brake 3. The pressure path includes the open separation valve 12, the first check valve 22, and the pump chamber 2.
1, the second check valve 23, and the open suction valve 7. Pressure is created in the wheel brake 3, resulting in a deceleration of the wheels and a deceleration of the vehicle. When the pedal is released, pressure fluid returns from the wheel brake 3 to the master brake cylinder via the open check valve 14, the direct conduit 13 and the open ASR valve. It is important that the pressure generation path continues up to the pump chamber 21 during normal deceleration.
【0023】2.ブレーキスリップ制御減速される車輪
のブレーキ作動パターンは、図示されていないセンサで
常時,監視される。従って電子分析器は車輪がロックし
そうになると直ちにそれを検出することができる。車輪
がロックすると上記分析器は以下の段階を開始する。2. Brake slip control The brake operation pattern of the wheels being decelerated is constantly monitored by a sensor (not shown). The electronic analyzer can therefore detect as soon as the wheels are about to lock up. When the wheels lock, the analyzer begins the following steps.
【0024】先ず,吸込弁7が切り換えられてブレーキ
導管を遮断する。吐出弁8が開き、その結果圧力流体は
ホイールブレーキから低圧アキュムレータ10に流入す
る。弁12が閉じて、マスタブレーキシリンダがブレー
キ回路から遮断される。ポンプ駆動装置Mが作動し、ポ
ンプは圧力流体を低圧アキュムレータ10から高圧アキ
ュムレータ16に送る。ピストン17はばね18の力に
抗して移動するので、ポンプDの出口の圧力はばねの力
に対応する。吸気弁7と吐出弁8が順に切り換えられる
ので、圧力流体はホイールブレーキに供給され、ホイー
ルブレーキから排出される。これは一定のアルゴリズム
に従って行われるので、車輪のスリップの値を最適に調
節することが可能である。ホイールブレーキ内の圧力は
、直接導管13を介して、マスタブレーキシリンダ内の
圧力の範囲内に制限される。運転者の踏圧が減少すると
、ホイールブレーキ内の圧力も減少し、減速または制御
過程が夫々終了する。First, the intake valve 7 is switched over to shut off the brake line. The discharge valve 8 opens, so that pressure fluid flows from the wheel brake into the low-pressure accumulator 10. Valve 12 closes, disconnecting the master brake cylinder from the brake circuit. Pump drive M is activated and the pump delivers pressurized fluid from low pressure accumulator 10 to high pressure accumulator 16 . Since the piston 17 moves against the force of the spring 18, the pressure at the outlet of the pump D corresponds to the force of the spring. Inlet valve 7 and outlet valve 8 are switched in sequence so that pressure fluid is supplied to and discharged from the wheel brake. This is done according to a certain algorithm, so that it is possible to optimally adjust the value of the wheel slip. The pressure in the wheel brake is limited via the direct line 13 to the extent of the pressure in the master brake cylinder. When the driver's pedal pressure decreases, the pressure in the wheel brake also decreases and the deceleration or control process is respectively terminated.
【0025】3.トラクションスリップ制御車輪が駆動
車輪である場合、自動車のエンジンにより伝達されるト
ルクはタイヤと道路間で伝達し得るトルクを超え、車輪
のスピンが生じる可能性がある。こうした車輪のスピン
を防ぐには、ブレーキ装置は、残っているトルクがブレ
ーキのトルクによって、タイヤと道路間で伝達され得る
力と一致するように、駆動トルクを補正すればよい。前
述のセンサは、空転の傾向も検出することができる。電
子分析器は、次の段階を開始する。ポンプのモータが作
動して、ポンプは圧力流体をマスタブレーキシリンダに
対応するリザーバからマスタブレーキシリンダと開放分
離弁を介してホイールブレーキに送る。ASR弁15が
閉じ、ホイールブレーキに送られる圧力流体は、直接導
管からマスタブレーキシリンダに逆流できなくなる。ブ
レーキスリップ制御の場合のように、弁7と弁8の切換
によって、ホイールブレーキ内で最適なブレーキ圧に調
節することができる。このようなブレーキシステムでは
、トラクションスリップ制御の場合のように、ポンプの
吸込側に静圧が存在しないので、ポンプは自動吸収タイ
プでなければならない。放出弁24は、ポンプの圧力側
に過圧が生成されるのを防ぐ。3. When the traction slip control wheel is a drive wheel, the torque transmitted by the vehicle's engine exceeds the torque that can be transmitted between the tires and the road, potentially resulting in wheel spin. To prevent such wheel spin, the braking system should correct the drive torque so that the remaining torque matches the force that can be transmitted between the tires and the road by the brake torque. The aforementioned sensors can also detect a tendency to slip. The electronic analyzer initiates the next stage. The pump motor is activated and the pump directs pressurized fluid from the reservoir corresponding to the master brake cylinder through the master brake cylinder and the open isolation valve to the wheel brake. The ASR valve 15 is closed and the pressure fluid sent to the wheel brakes cannot flow back from the direct conduit to the master brake cylinder. As in the case of brake slip control, an optimum brake pressure can be set in the wheel brake by switching valves 7 and 8. In such brake systems, the pump must be of the self-absorbing type, since there is no static pressure on the suction side of the pump, as in the case of traction slip control. The release valve 24 prevents overpressure from being created on the pressure side of the pump.
【0026】次に、図2に基く実施例について説明する
。Next, an embodiment based on FIG. 2 will be described.
【0027】図2に基く実施例は、本質的には図1の実
施例と同じである。ただし、図1と異なり,分離弁は電
磁作動せず、高圧アキュムレータ16の充填レベルに応
じて機械的に作動する。The embodiment according to FIG. 2 is essentially the same as the embodiment according to FIG. However, unlike FIG. 1, the separation valve is not electromagnetically operated, but is mechanically operated depending on the filling level of the high pressure accumulator 16.
【0028】従ってピストン17と弁12は共通ハウジ
ング内に配置されている。アキュムレータのピストン1
7は、端部がアキュムレータチャンバの方向に面し、ア
キュムレータピストン17よりも直径が小さい延長部3
0を具備する。この延長部30は封止されてボア内に案
内され、アキュムレータピストンの反対側の端部には、
ボア32を通過できるプランジャ31がある。このボア
は吸込チャンバ36と吐出チャンバ37を接続し、吸込
チャンバ36はマスタブレーキシリンダに連通し、吐出
チャンバ37はポンプの圧力側に連通している。吐出チ
ャンバ37は、延長部30の前面によって範囲が制限さ
れる。分離弁は、吸気チャンバ36内のボール弁34と
、ボア32上の弁座33とで構成される。弁ばね35は
ボール弁を弁座33方向に押す。ピストン17が定位置
にある場合,即ちアキュムレータチャンバの容積が最小
になる位置では、プランジャ31はボア32を通過し、
ボール弁34は弁座33から離れる。Piston 17 and valve 12 are therefore arranged in a common housing. Accumulator piston 1
7 is an extension 3 whose end faces towards the accumulator chamber and which has a smaller diameter than the accumulator piston 17;
0. This extension 30 is sealed and guided into the bore, and at the end opposite the accumulator piston is
There is a plunger 31 that can pass through a bore 32. This bore connects a suction chamber 36 and a discharge chamber 37, the suction chamber 36 communicating with the master brake cylinder and the discharge chamber 37 communicating with the pressure side of the pump. The discharge chamber 37 is delimited by the front surface of the extension 30 . The isolation valve consists of a ball valve 34 in the intake chamber 36 and a valve seat 33 on the bore 32. The valve spring 35 pushes the ball valve towards the valve seat 33. When the piston 17 is in the home position, i.e. in the position where the volume of the accumulator chamber is at a minimum, the plunger 31 passes through the bore 32;
The ball valve 34 is separated from the valve seat 33.
【0029】圧力流体は、マスタブレーキシリンダ1か
らポンプまで自由に流れる。ブレーキスリップまたはト
ラクションスリップ制御時には、前述の通り,アキュム
レータは充填され、図示のアキュムレータピストン17
は、ポンプの圧力側に適当な圧力が生じると直ちに右に
移動する。プランジャ31はボア32から引き抜かれ、
ボ−ル弁36が弁座33に収まり、ブレーキ導管が遮断
される。ブレーキシステムにおけるその他の動作は、図
1に基くブレーキシステムの動作と同じである。 図
3は、図1に基くブレーキシステムのもう一つの実施例
であるが、放出弁がアキュムレータ内にある点が重要で
ある。そのために、アキュムレータピストン17は弁4
3を具備する。このアキュムレータピストン17は、チ
ャンバ40を背圧チャンバ41から分離する。弁43は
、2つのチャンバ40,41間のピストン17に設けら
れた接続ボアを有しており、弁部材はアキュムレータチ
ャンバ40内に位置し、接続ボア上に取り付けることが
できる。アキュムレータピストンが図示の右方向に移動
すると、プランジャ44はボア内に移動し、弁43のボ
ール弁がボアから上がり、アキュムレータチャンバ40
と背圧チャンバ41の間に圧力流体が流れる。背圧チャ
ンバ41は、接続導管42を介してポンプの吸込側と連
通している。アキュムレータが予め決められた充填レベ
ルに達し、その結果、ばね18の圧縮に応じて貯蔵チャ
ンバ内の圧力が予め決められたレベルに達すると、弁4
3が開き、圧力流体はさらにアキュムレータチャンバ内
に入り、背圧チャンバを介してポンプの吸込側に戻る。
このブレーキシステムのその他の構造および機能は、図
1のブレーキシステムと同じである。Pressure fluid flows freely from the master brake cylinder 1 to the pump. During brake slip or traction slip control, the accumulator is filled as described above and the illustrated accumulator piston 17
moves to the right as soon as a suitable pressure is created on the pressure side of the pump. The plunger 31 is pulled out from the bore 32,
The ball valve 36 is seated in the valve seat 33 and the brake conduit is shut off. The other operations in the brake system are the same as the operation of the brake system based on FIG. FIG. 3 shows another embodiment of the brake system according to FIG. 1, but importantly, the release valve is in the accumulator. For this purpose, the accumulator piston 17 is connected to the valve 4
3. This accumulator piston 17 separates the chamber 40 from the backpressure chamber 41. The valve 43 has a connecting bore in the piston 17 between the two chambers 40, 41, the valve member being located in the accumulator chamber 40 and can be mounted on the connecting bore. As the accumulator piston moves to the right as shown, the plunger 44 moves into the bore and the ball valve of valve 43 rises out of the bore, causing the accumulator chamber 40
Pressure fluid flows between the back pressure chamber 41 and the back pressure chamber 41 . The backpressure chamber 41 communicates with the suction side of the pump via a connecting conduit 42. When the accumulator reaches a predetermined filling level and, as a result, the pressure in the storage chamber reaches a predetermined level in response to the compression of the spring 18, the valve 4
3 is opened and the pressure fluid further enters the accumulator chamber and returns to the suction side of the pump via the back pressure chamber. The rest of the structure and function of this brake system are the same as the brake system of FIG.
【0030】第4図は、車輪64、65、66、67を
具備する4輪車の完全なブレーキシステムを表し、HR
、HL、VL、VRはそれぞれ次の車輪を指す。FIG. 4 represents the complete braking system of a four-wheeled vehicle comprising wheels 64, 65, 66, 67,
, HL, VL, and VR each refer to the next wheel.
【0031】
HR=右後輪
HL=左後輪
VL=左前輪
VR=右前輪
マスタシリンダ1は、それぞれが1本のブレーキ回路を
構成する2つのチャンバ60、61から成る。チャンバ
60には、ブレーキ導管2′を介して、車輪HRとHL
のホイールブレーキが接続されている。この2つのホイ
ールブレーキ内のブレーキ圧は、通常、図2に示すよう
な制御システムにより制御される。車輪VLとVRのブ
レーキは、それぞれブレーキ導管2″の分岐回路62,
63を介して、マスタブレーキシリンダのチャンバ61
と連通している。分岐回路62,63には、夫々図2に
示すような制御システムが装備されている。HR = Rear right wheel HL = Rear left wheel VL = Front left wheel VR = Front right wheel The master cylinder 1 consists of two chambers 60 and 61, each of which constitutes one brake circuit. The chamber 60 is connected to the wheels HR and HL via the brake conduit 2'.
The wheel brake is connected. The brake pressure in the two wheel brakes is typically controlled by a control system as shown in FIG. The brakes for wheels VL and VR are provided by branch circuits 62 and 62 of the brake conduit 2'', respectively.
63 to the chamber 61 of the master brake cylinder.
It communicates with The branch circuits 62 and 63 are each equipped with a control system as shown in FIG.
【0032】従ってこのブレーキシステムには3つの制
御回路が装備され、それぞれの回路にポンプ4′,4″
,4′′′が装備されている。この点についての制御シ
ステムは、図1と図3に示す位置に配置することもでき
る点に注意されたい。This brake system is therefore equipped with three control circuits, each with a pump 4', 4''.
, 4''' are equipped. It should be noted that the control system in this regard can also be placed in the positions shown in FIGS. 1 and 3.
【0033】特に強調したい点は、ポンプ4′,4″,
4′′′は共通の駆動装置、つまり電動モータEMで作
動するという事実である。もう一つの特徴は、個々の吸
気弁と吐出弁が3方/2位置弁68、69、70の形態
であるという点である。従ってシステムは単純になるが
、しかしブレーキ導管と戻り導管の両方が遮断される圧
力維持段階を実現できないという欠点がある。[0033] The point I would like to particularly emphasize is that the pumps 4', 4'',
4''' is the fact that they operate with a common drive, namely the electric motor EM. Another feature is that the individual intake and discharge valves are in the form of 3-way/2-position valves 68, 69, 70. The system is therefore simple, but has the disadvantage that it is not possible to implement a pressure maintenance phase in which both the brake conduit and the return conduit are shut off.
【0034】各々の制御システムは前述の原理で動作す
るので、当然、各制御導管のホイールブレーキ内の圧力
は個別に調節することが可能である。Since each control system operates on the principle described above, it is naturally possible to adjust the pressure in the wheel brake of each control conduit individually.
【図1】本発明の1実施例であるブレーキシステムの構
成図。FIG. 1 is a configuration diagram of a brake system that is an embodiment of the present invention.
【図2】本発明の他の実施例であるブレーキシステムの
構成図。FIG. 2 is a configuration diagram of a brake system according to another embodiment of the present invention.
【図3】本発明の他の実施例であるブレーキシステムの
構成図。FIG. 3 is a configuration diagram of a brake system according to another embodiment of the present invention.
【図4】本発明の他の実施例であるブレーキシステムの
構成図。FIG. 4 is a configuration diagram of a brake system according to another embodiment of the present invention.
1…マスタブレーキシリンダ,2…ブレーキ導管,3…
ホイールブレーキ,4…ポンプ,7…吸込弁,8…吐出
弁,10…低圧アキュムレータ,12…分離弁,15…
締切弁,16…高圧アキュムレータ。1...Master brake cylinder, 2...Brake conduit, 3...
Wheel brake, 4...Pump, 7...Suction valve, 8...Discharge valve, 10...Low pressure accumulator, 12...Separation valve, 15...
Shutoff valve, 16...high pressure accumulator.
Claims (16)
ップ制御装置を具備し、少なくとも1個のホイールブレ
ーキ(3)がブレーキ導管(2)を介してマスタブレー
キシリンダ(1)に連通し、ペダル作動時,圧力流体が
マスタブレーキシリンダから上記ブレーキ導管を介して
上記ホイールブレーキ内に移動するペダル作動マスタシ
リンダ(1)と、流体圧ポンプ(4)とで構成され、上
記ポンプは、その吸込側Sが上記マスタブレーキシリン
ダ(1)に連通し、その圧力側Dがホイールブレーキシ
リンダと連通するように,上記ブレーキ導管(2)内に
挿入されていることを特徴とする流体圧ブレーキシステ
ム。1. A brake slip/traction slip control device, wherein at least one wheel brake (3) communicates with a master brake cylinder (1) via a brake conduit (2), and when the pedal is actuated, pressurized fluid consists of a pedal actuated master cylinder (1), which moves from the master brake cylinder into the wheel brake via the brake conduit, and a hydraulic pump (4), the pump having a suction side S connected to the master brake. Hydraulic brake system, characterized in that it is inserted into said brake conduit (2) in such a way that it communicates with the cylinder (1) and its pressure side D communicates with the wheel brake cylinder.
ホイールブレーキシリンダとの間に吸込弁(7)が装備
され、この弁が定位置ではブレーキ導管を開放し、切換
位置では遮断し、また、ホイールブレーキ(3)が戻り
導管(9)を介して圧力流体コレクター装置(10)と
連通し、吐出弁(8)が戻り導管(9)に挿入されて、
この弁の定位置で戻り導管を遮断し、切換位置で導管を
開放することを特徴とする請求項1に記載の流体圧ブレ
ーキシステム。2. A suction valve (7) is provided between the pump (4) of the brake line (6) and the wheel brake cylinder, which opens the brake line in the home position and blocks it in the switching position; The wheel brake (3) also communicates with the pressure fluid collector device (10) via the return conduit (9), and the discharge valve (8) is inserted into the return conduit (9).
Hydraulic brake system according to claim 1, characterized in that in the home position of this valve the return conduit is blocked and in the switching position the conduit is opened.
止弁(11)を介して、ブレーキ導管(5)のポンプ(
4)とマスタブレーキシリンダ(1)間のE点と連通し
、開放点Eとマスタブレーキシリンダ間に分離弁(12
)が挿入され、この弁が定位置でブレーキ導管を開放し
、切換位置では遮断することを特徴とする請求項2に記
載の流体圧ブレーキシステム。3. The pressure fluid collector device (10) connects the pump (5) of the brake conduit (5) via the check valve (11) with
4) and the master brake cylinder (1), and a separation valve (12) is connected between the release point E and the master brake cylinder (1).
3. Hydraulic brake system according to claim 2, characterized in that a valve is inserted, which opens the brake conduit in the home position and blocks it in the switching position.
(4)の圧力側Dに連通していることを特徴とする請求
項2に記載のブレーキシステム。4. Brake system according to claim 2, characterized in that the high-pressure accumulator (16) communicates with the pressure side D of the pump (4).
圧力側Dが最小圧力の場合にのみ充填されることを特徴
とする請求項4に記載のブレーキシステム。5. Brake system according to claim 4, characterized in that the accumulator (16) is filled only when the pressure side D of the pump is at a minimum pressure.
(13)を介してマスタブレーキシリンダ(1)と直接
連通し、直接導管(13)に逆止弁(14)が挿入され
、マスタブレーキシリンダ(1)方向に開いていること
を特徴とする請求項2に記載の流体圧ブレーキシステム
。6. The wheel brake (3) is in direct communication with the master brake cylinder (1) via a direct conduit (13), a check valve (14) is inserted into the direct conduit (13), and the master brake cylinder The hydraulic brake system according to claim 2, wherein the hydraulic brake system is open in the (1) direction.
13)に挿入され、定位置では導管を開き、切換位置で
は導管を遮断することを特徴とする請求項6に記載の流
体圧ブレーキシステム。[Claim 7] The shutoff valve (ASR valve 15) is directly connected to the conduit (
13), opening the conduit in the home position and blocking the conduit in the switching position.
4)であり、そのポンプチャンバ(21)が各1個の逆
止弁(22、23)を介して吸込側Sと圧力側Dに連通
することを特徴とする請求項1に記載の流体圧ブレーキ
システム。[Claim 8] The pump is a reciprocating piston type pump (
4), the pump chamber (21) communicating with the suction side S and the pressure side D via one check valve (22, 23) in each case. brake system.
弁(24)を介して相互に連通することを特徴とする請
求項1に記載の流体圧ブレーキシステム。9. Hydraulic brake system according to claim 1, characterized in that the suction side S and the pressure side D of the pump communicate with each other via a discharge valve (24).
ータ(16)のピストン(17)により機械的に作動す
ることを特徴とする請求項3乃至4に記載の流体圧ブレ
ーキシステム。10. Hydraulic brake system according to claim 3, characterized in that the isolation valve (12) is mechanically actuated by a piston (17) of the high-pressure accumulator (16).
式で、弁体(34)が、ピストン(17)に装備されて
いるプランジャ(31)により起動し、弁(12)がア
キュムレータ(16)の充填の際に閉じることを特徴と
する請求項10に記載の流体圧ブレーキシステム。11. The separation valve (12) is in the form of a seated valve, the valve body (34) is actuated by a plunger (31) mounted on the piston (17), and the valve (12) is connected to the accumulator (16). 11. The hydraulic brake system according to claim 10, wherein the hydraulic brake system closes upon filling of the hydraulic brake system.
ピストン(17)がアキュムレータチャンバ(40)を
背圧チャンバから分離し、弁(43)が分離ピストン(
17)に配置され、この弁(43)がプランジャにより
起動し、アキュムレータチャンバ(40)内が予め決め
られた充填レベルに達すると、アキュムレータチャンバ
(40)と背圧チャンバ(41)間が連通することを特
徴とする請求項5に記載の流体圧ブレーキシステム。12. A separating piston (17) of the high pressure accumulator (16) separates the accumulator chamber (40) from the back pressure chamber, and a valve (43) separates the separating piston (
17), and when this valve (43) is actuated by a plunger and the inside of the accumulator chamber (40) reaches a predetermined filling level, the accumulator chamber (40) and the back pressure chamber (41) communicate with each other. 6. The hydraulic brake system according to claim 5.
42)を介してポンプ(4)の吸込側Sと連通すること
を特徴とする請求項12に記載の記載の流体圧ブレーキ
システム。13. The back pressure chamber (41) is connected to the connecting conduit (
13. Hydraulic brake system according to claim 12, characterized in that it communicates with the suction side S of the pump (4) via the pump (42).
との間に制御可能なスロットルが接続され、その断面が
、ポンプの吸込側Sと圧力側Dとの圧力差により決定さ
れることを特徴とする請求項1に記載の流体圧ブレーキ
システム。[Claim 14] Suction side S and pressure side D of the pump (4)
Hydraulic brake system according to claim 1, characterized in that a controllable throttle is connected between the pumps, the cross section of which is determined by the pressure difference between the suction side S and the pressure side D of the pump.
され、リヤアクスルのホイールブレーキと各1個のフロ
ントアクスルのホイールブレーキが1つの回路を構成し
、各制御回路に装備されているポンプ(4′、4″、4
′′′)に共通の駆動装置が装備されていることを特徴
とする上記請求項1〜14の何れか1つに記載の流体圧
ブレーキシステム。15. A triple circuit system is provided for a four-wheeled vehicle, in which a rear axle wheel brake and a front axle wheel brake constitute one circuit, and each control circuit is equipped with a pump ( 4′, 4″, 4
15. Hydraulic brake system according to claim 1, characterized in that a common drive device is provided for the hydraulic brake systems ``'').
/2位置弁の形態であることを特徴とする上記請求項1
〜15の何れか1つに記載の流体圧ブレーキシステム。16. The above-mentioned claim 1, wherein the intake valve (7) and the discharge valve (8) are in the form of a 3-way/2-position valve.
16. The hydraulic brake system according to any one of items 1 to 15.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19904000837 DE4000837B4 (en) | 1990-01-13 | 1990-01-13 | Hydraulic brake system with a device for braking and / or traction control |
DE4000837 | 1990-01-13 |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH04212664A true JPH04212664A (en) | 1992-08-04 |
Family
ID=6398021
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP271291A Pending JPH04212664A (en) | 1990-01-13 | 1991-01-14 | Fluid pressure brake system |
Country Status (4)
Country | Link |
---|---|
JP (1) | JPH04212664A (en) |
DE (1) | DE4000837B4 (en) |
FR (1) | FR2657059B1 (en) |
GB (1) | GB2239913B (en) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4108756A1 (en) * | 1990-10-05 | 1992-09-24 | Teves Gmbh Alfred | MOTOR VEHICLE BRAKE SYSTEM WITH SLIP-RELATED REGULATION OF THE BRAKE PRESSURE |
DE4104069C2 (en) * | 1991-02-11 | 2000-08-17 | Continental Teves Ag & Co Ohg | Brake system with devices for regulating both the brake slip and the drive slip |
DE4118951A1 (en) * | 1991-06-08 | 1992-12-10 | Teves Gmbh Alfred | HYDRAULIC BRAKE SYSTEM WITH ANTI-BLOCK CONTROL |
JP3115909B2 (en) * | 1991-07-05 | 2000-12-11 | 曙ブレーキ工業株式会社 | Hydraulic modulator for anti-lock brake and traction control system for vehicles |
DE4127040B4 (en) * | 1991-08-16 | 2005-06-23 | Continental Teves Ag & Co. Ohg | Slip-controlled brake system |
DE4134459A1 (en) * | 1991-10-18 | 1993-04-22 | Teves Gmbh Alfred | BLOCK-PROTECTED HYDRAULIC BRAKE SYSTEM |
US5628550A (en) * | 1991-10-18 | 1997-05-13 | Itt Automotive Europe Gmbh | Anti-lock hydraulic brake system |
DE4135062A1 (en) * | 1991-10-24 | 1993-04-29 | Bosch Gmbh Robert | METHOD FOR ACCELERATING BRAKE INTERVENTION IN DRIVE-SLIP REGULATION AND HYDRAULIC BRAKE SYSTEM FOR CARRYING OUT THE METHOD |
US5374112A (en) * | 1991-10-30 | 1994-12-20 | Sumitomo Electric Industries, Ltd. | Brake fluid pressure control device |
JPH05116607A (en) * | 1991-10-30 | 1993-05-14 | Sumitomo Electric Ind Ltd | Hydraulic pressure control device for brake |
DE4201732A1 (en) * | 1992-01-23 | 1993-07-29 | Teves Gmbh Alfred | BRAKE PRESSURE CONTROL DEVICE, IN PARTICULAR TO CONTROL THE DRIVE SLIP OF DRIVED WHEELS |
DE4213199A1 (en) * | 1992-04-22 | 1993-10-28 | Teves Gmbh Alfred | Hydraulic brake system with brake slip and traction control |
DE4230088A1 (en) * | 1992-09-09 | 1994-03-10 | Teves Gmbh Alfred | Hydraulic brake installation with antislip regulation - has self-priming pump drawing on pressure medium container via main brake cylinder with suction connection following flow chamber of brake circuit |
DE4427799A1 (en) * | 1994-08-05 | 1996-02-08 | Teves Gmbh Alfred | Hydraulic motor vehicle brake system |
JPH09286314A (en) * | 1996-02-21 | 1997-11-04 | Aisin Seiki Co Ltd | Brake power control device for vehicle |
DE19638920A1 (en) | 1996-09-23 | 1998-03-26 | Teves Gmbh Alfred | Hydraulic brake system with brake booster |
WO2000034097A1 (en) * | 1998-12-09 | 2000-06-15 | Continental Teves Ag & Co. Ohg | Hydraulic intensifier operating as a pressure intensifier |
JP5070750B2 (en) * | 2006-05-31 | 2012-11-14 | トヨタ自動車株式会社 | Brake device for vehicle and reservoir thereof |
DE102007004494A1 (en) * | 2006-07-12 | 2008-01-17 | Continental Teves Ag & Co. Ohg | Electrohydraulic control system for actuating an actuator in a motor vehicle |
CN101749295A (en) * | 2008-12-18 | 2010-06-23 | 卡特彼勒公司 | Pressure regulating system and method for working machine |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4046214A (en) * | 1976-08-13 | 1977-09-06 | Aspro, Inc. | Brake pressure modulator and system |
GB2057613B (en) * | 1979-08-14 | 1983-03-30 | Lucas Industries Ltd | Hydraulic anti-skid braking systems for vehicles |
DE3137287C2 (en) * | 1981-09-18 | 1986-04-03 | Daimler-Benz Ag, 7000 Stuttgart | Device for charging a pressure accumulator provided for a propulsion control device on a motor vehicle, which is also equipped with an anti-lock system, as part of an auxiliary pressure source |
JPS6150860A (en) * | 1984-08-15 | 1986-03-13 | Toyota Motor Corp | Antiskid type hydraulic braking device for automobile |
JPS61160343A (en) * | 1985-01-07 | 1986-07-21 | Toyota Motor Corp | Kick-back prevention type anti-skid hydraulic brake device |
DE3538330A1 (en) * | 1985-10-28 | 1987-04-30 | Teves Gmbh Alfred | Hydraulic brake system for motor vehicles |
DE3540366A1 (en) * | 1985-11-14 | 1987-05-21 | Teves Gmbh Alfred | METHOD AND BRAKE SYSTEM FOR CONTROLLING THE DRIVE SLIP |
DE3602430A1 (en) * | 1986-01-28 | 1987-07-30 | Teves Gmbh Alfred | BLOCK-PROTECTED HYDRAULIC BRAKE SYSTEM |
DE3605220A1 (en) * | 1986-02-19 | 1987-08-20 | Teves Gmbh Alfred | SLIP-CONTROLLED BRAKE SYSTEM |
DE3717237C2 (en) * | 1987-05-22 | 1995-07-20 | Teves Gmbh Alfred | Brake system with anti-lock and / or traction control |
JPS6412964A (en) * | 1987-07-04 | 1989-01-17 | Nippon Abs Ltd | Vehicle driving force control apparatus having anti-skid device |
JPS6474153A (en) * | 1987-09-17 | 1989-03-20 | Aisin Seiki | Wheel brake control device |
DE3731636C1 (en) * | 1987-09-19 | 1989-04-06 | Bosch Gmbh Robert | Vehicle brake system with device for limiting wheel slip |
DE3839178A1 (en) * | 1988-01-26 | 1989-08-03 | Daimler Benz Ag | ANTI-BLOCKING SYSTEM |
DE3803363A1 (en) * | 1988-02-05 | 1989-08-17 | Teves Gmbh Alfred | PRESSURE-OPERATED BRAKE SYSTEM WITH BLOCK-PROTECTED DRIVE-SLIP CONTROL |
DE3903532A1 (en) * | 1988-02-18 | 1989-08-31 | Volkswagen Ag | Hydraulic motor-vehicle brake system with an anti-lock control device |
DE3906141C2 (en) * | 1988-03-10 | 1996-02-22 | Volkswagen Ag | Hydraulic motor vehicle brake system with anti-lock control device |
JP2642947B2 (en) * | 1988-05-27 | 1997-08-20 | 曙ブレーキ工業株式会社 | Acceleration slip control device |
DE3832023C3 (en) * | 1988-09-21 | 1999-09-23 | Bosch Gmbh Robert | Starting slip control device (ASR) |
DE3900851C1 (en) * | 1989-01-13 | 1990-01-25 | Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De | |
DE3940177C2 (en) * | 1989-12-05 | 1999-03-18 | Teves Gmbh Alfred | Slip-controlled hydraulic vehicle brake system |
DE59106626D1 (en) * | 1990-08-31 | 1995-11-09 | Teves Gmbh Alfred | HYDRAULIC BRAKE SYSTEM WITH A DEVICE FOR REGULATING THE BRAKE AND / OR DRIVE SLIP. |
-
1990
- 1990-01-13 DE DE19904000837 patent/DE4000837B4/en not_active Expired - Lifetime
- 1990-10-11 GB GB9022076A patent/GB2239913B/en not_active Expired - Fee Related
-
1991
- 1991-01-02 FR FR9100016A patent/FR2657059B1/en not_active Expired - Fee Related
- 1991-01-14 JP JP271291A patent/JPH04212664A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
FR2657059A1 (en) | 1991-07-19 |
GB2239913B (en) | 1994-01-12 |
FR2657059B1 (en) | 1995-09-01 |
DE4000837A1 (en) | 1991-07-18 |
GB9022076D0 (en) | 1990-11-21 |
DE4000837B4 (en) | 2005-03-03 |
GB2239913A (en) | 1991-07-17 |
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