JP2005053310A - Brake fluid pressure generating device - Google Patents

Brake fluid pressure generating device Download PDF

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JP2005053310A
JP2005053310A JP2003285178A JP2003285178A JP2005053310A JP 2005053310 A JP2005053310 A JP 2005053310A JP 2003285178 A JP2003285178 A JP 2003285178A JP 2003285178 A JP2003285178 A JP 2003285178A JP 2005053310 A JP2005053310 A JP 2005053310A
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brake
pressure
valve
fluid pressure
reaction force
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Tei Terasawa
禎 寺澤
Yoji Inoue
陽治 井上
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Advics Co Ltd
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Advics Co Ltd
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Priority to JP2003285178A priority Critical patent/JP2005053310A/en
Priority to DE102004036984A priority patent/DE102004036984A1/en
Priority to US10/902,581 priority patent/US7104612B2/en
Publication of JP2005053310A publication Critical patent/JP2005053310A/en
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  • Braking Systems And Boosters (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To suppress fluctuation of brake manipulated variable due to consumed fluid amount fluctuation and fluid pressure fluctuation of a brake circuit by simple structure to advantageously realize a desired stroke characteristic of a brake operation means, in a brake fluid pressure generating device having a boosting device. <P>SOLUTION: This device is provided with a negative type boosting device 21 having an input shaft 28 operated by a brake operation, a stroke simulator 29 for imparting stroke and reaction according to the brake manipulated variable to the input shaft 28 and a control valve 37, a master cylinder 22 for generating brake fluid pressure, and a pressure detecting member 23 for detecting fluid pressure of a pressure chamber 22b to apply the reaction according to the detected fluid pressure to a valve member 40 of the control valve 37. An input transmitted via a stroke simulator 29 and the reaction from the pressure detecting member 23 are opposed and received by the control valve 37 to balance the reaction in relation to the input. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

この発明は、倍力手段の出力を制御弁で調整し、その調整された出力でマスタシリンダを作動させてブレーキ操作量に応じたブレーキ液圧を発生させる車両用のブレーキ液圧発生装置、特に、ブレーキ回路の消費液量変動・液圧変動によるブレーキ操作量(操作ストローク)の変動や操作フィーリングの悪化を防止し、併せて、ブレーキ操作初期の出力液圧を適正化する機能(所謂ジャンピング機能)を付加したブレーキ液圧発生装置に関する。   The present invention relates to a brake fluid pressure generator for a vehicle that adjusts an output of a booster with a control valve, and operates a master cylinder with the adjusted output to generate a brake fluid pressure according to a brake operation amount. , Function to prevent fluctuations in brake operation amount (operation stroke) and deterioration in operation feeling due to fluctuations in fluid consumption and fluid pressure in the brake circuit, and to optimize output hydraulic pressure at the initial stage of brake operation (so-called jumping) The present invention relates to a brake fluid pressure generator with a function).

倍力装置を備えるブレーキ液圧発生装置は、ブレーキ操作力を倍力装置で増幅してその増幅した力をマスタシリンダに加える構成になっている。倍力装置としては負圧式倍力装置や液圧式倍力装置などが用いられている。その倍力装置を備えるブレーキ液圧発生装置の中に、ブレーキペダルの操作量とマスタシリンダからの吐出液量が直接対応する構造のものがあるが、これは、車両のアンチロック制御、回生協調ブレーキ制御、車両安定制御(VSC)などが実行されときにブレーキ回路の消費液量増加の影響がブレーキ操作手段、例えばブレーキペダルの操作量に反映されて運転者の操作フィーリングが悪くなることを避けられない。   A brake fluid pressure generating device including a booster is configured to amplify a brake operation force with a booster and apply the amplified force to a master cylinder. As the booster, a negative pressure booster or a hydraulic booster is used. Some brake fluid pressure generators equipped with the booster have a structure in which the amount of brake pedal operation and the amount of fluid discharged from the master cylinder directly correspond to each other. When brake control, vehicle stability control (VSC), etc. are executed, the influence of the increase in the amount of liquid consumption of the brake circuit is reflected in the operation amount of the brake operation means, for example, the brake pedal, and the driver's operation feeling deteriorates. Unavoidable.

その問題の対応策として、下記特許文献1は、運転者の意思によらない液圧制御が実行されてブレーキ回路の消費液量が変動してもブレーキ操作量の変動が抑制されるブレーキ液圧発生装置の様々な形態を詳しく紹介している。
特開2002−173016号公報
As a countermeasure against this problem, Patent Document 1 below discloses a brake fluid pressure in which a variation in brake operation amount is suppressed even when a fluid pressure control not performed by the driver's intention is executed and a consumed fluid amount in the brake circuit varies. Various forms of generators are introduced in detail.
JP 2002-173016 A

この特許文献1の図4とほぼ同じ構造を図6に示す。特許文献1には、この構成について詳しい説明がなされているが、ここでも簡単に述べる。   FIG. 6 shows almost the same structure as that of FIG. Japanese Patent Application Laid-Open No. 2003-228561 provides a detailed description of this configuration, but it will be briefly described here.

パワープレート15aの内側にパワープレート15aに対して軸方向に相対移動できるバルブピストン5b(第2弁要素)を配置し、入力軸4と一体の第1弁要素に設けた大気圧弁座5b3 と、バルブピストン5bに設けた負圧弁座5b4 と、バルブピストン5bの内部に配置した弁体5とで変圧室(動力室)15bの圧力を制御してパワープレート15aの出力を調整する制御弁を構成している。 A valve piston 5b (second valve element) that can move in the axial direction relative to the power plate 15a is disposed inside the power plate 15a, and an atmospheric pressure valve seat 5b 3 provided in the first valve element integral with the input shaft 4; A control valve that adjusts the output of the power plate 15a by controlling the pressure in the variable pressure chamber (power chamber) 15b by the negative pressure valve seat 5b 4 provided in the valve piston 5b and the valve body 5 disposed inside the valve piston 5b. Is configured.

また、バルブピストン5bと固定シェル(ハウジング)2との間及びバルブピストン5bとパワープレート15aとの間にそれぞれスプリング(ストローク−力変換装置)7、18を設けている。   Further, springs (stroke-force conversion devices) 7 and 18 are provided between the valve piston 5b and the fixed shell (housing) 2 and between the valve piston 5b and the power plate 15a, respectively.

図示のブレーキ液圧発生装置は、パワープレート15aが変圧室15bの圧力と定圧室(負圧室)15cの圧力の差を受けて入力を増幅した力を出力し、その出力でマスタシリンダピストン16aが作動してマスタシリンダ16がブレーキ操作量に応じたブレーキ液圧を発生させ、その液圧がブレーキ回路(ホイールシリンダ9側)に供給される。さらに、入力軸4がその液圧を反力として受ける。   In the illustrated brake fluid pressure generator, the power plate 15a receives the difference between the pressure in the variable pressure chamber 15b and the pressure in the constant pressure chamber (negative pressure chamber) 15c, and outputs a force obtained by amplifying the input. The master cylinder 16 generates a brake fluid pressure corresponding to the amount of brake operation, and the fluid pressure is supplied to the brake circuit (wheel cylinder 9 side). Further, the input shaft 4 receives the hydraulic pressure as a reaction force.

入力軸4のストロークはバルブピストン5bのストロークとほぼ等しい。この入力軸4のストロークは、変圧室15bの圧力によってバルブピストン5bに生じる推力がスプリング7の反発力と釣り合う位置までスプリング7が圧縮されることによって決まる。一方、ブレーキペダル操作時の反力は、入力軸4が先端部にマスタシリンダ16が発生させた液圧(マスタシリンダの出力液圧)を受けて発生するが、マスタシリンダの出力液圧は変圧室15bの圧力に応じて発生するので、結局、ブレーキペダルのストロークとブレーキペダルに加わる反力との関係をブレーキ回路の消費液量と無関係に設定できることになる。   The stroke of the input shaft 4 is substantially equal to the stroke of the valve piston 5b. The stroke of the input shaft 4 is determined by compressing the spring 7 to a position where the thrust generated in the valve piston 5 b by the pressure in the variable pressure chamber 15 b is balanced with the repulsive force of the spring 7. On the other hand, the reaction force when the brake pedal is operated is generated when the input shaft 4 receives the hydraulic pressure generated by the master cylinder 16 at the tip (the output hydraulic pressure of the master cylinder). Since it occurs according to the pressure in the chamber 15b, the relationship between the stroke of the brake pedal and the reaction force applied to the brake pedal can be set regardless of the amount of liquid consumed in the brake circuit.

上記特許文献1が開示しているブレーキ液圧発生装置は、入力軸4と一体の第1弁要素と第1弁要素に対して軸方向の相対移動を可能にした第2弁要素(バルブピストン5b)が入力操作に応じて共に移動する構造になっているため、ブレーキ回路の消費液量の変動によるブレーキ操作量の変動を無くす必要上、バルブピストン5bの位置制御のための複雑なストローク−力変換装置を設ける必要があり、コストや小型化等の面で不利なものになっている。   The brake hydraulic pressure generator disclosed in Patent Document 1 is a first valve element integrated with an input shaft 4 and a second valve element (valve piston) that enables relative movement in the axial direction with respect to the first valve element. 5b) is structured to move together in response to an input operation, so that it is necessary to eliminate fluctuations in the brake operation amount due to fluctuations in the amount of liquid consumed in the brake circuit, and a complicated stroke for controlling the position of the valve piston 5b- It is necessary to provide a force conversion device, which is disadvantageous in terms of cost and miniaturization.

また、ブレーキ操作初期の出力液圧を高めるジャンピング機能が無く、ブレーキ操作初期の出力液圧の適正化が図れないと言う不具合もあった。   There is also a problem that there is no jumping function for increasing the output hydraulic pressure at the initial stage of the brake operation, and the output hydraulic pressure at the initial stage of the brake operation cannot be optimized.

この発明は、ブレーキ操作手段の望ましいストローク特性を有利に実現するために、ブレーキ回路の消費液量変動・液圧変動によるブレーキ操作量の変動を簡素な構造で抑制できるようにし、併せてブレーキ操作初期の出力液圧を高めるジャンピング機能を付加してブレーキ液圧発生装置の性能をさらに高めることを課題としている。   In order to advantageously realize the desired stroke characteristics of the brake operation means, the present invention makes it possible to suppress the fluctuation of the brake operation amount due to the consumption fluid amount fluctuation / hydraulic pressure fluctuation of the brake circuit with a simple structure. It is an object to further improve the performance of the brake fluid pressure generator by adding a jumping function to increase the initial output fluid pressure.

上記の課題を解決するため、この発明においては、ブレーキ操作によって作動する入力軸と、この入力軸にブレーキ操作量に応じたストロークと反力を与えるストロークシミュレータと、倍力手段の出力を前記ブレーキ操作手段の操作量に応じて調整する制御弁とを内蔵した入力部と、前記倍力手段の出力を受ける出力部が前記入力部と相対移動可能であり、前記出力部の出力を受けてブレーキ液圧を発生させるマスタシリンダと、このマスタシリンダの出力液圧を検出して検出液圧に応じた反力を前記制御弁に加える圧力検出部材とを備えさせ、前記制御弁が、前記ストロークシミュレータを介して前記入力軸から伝達される入力と前記圧力検出部材からの反力を対抗して受けて前記入力に対して前記反力をバランスさせるようにした。また、これに加えてさらに、前記マスタシリンダの出力液圧が所定の圧力になるまで前記圧力検出部材に移動抵抗を加えて前記制御弁に対する反力の伝達を止める移動抵抗付与手段を備えさせた。   In order to solve the above-described problems, in the present invention, an input shaft that is operated by a brake operation, a stroke simulator that applies a stroke and a reaction force according to the amount of brake operation to the input shaft, and an output of a booster are used for the brake. An input unit including a control valve that adjusts according to an operation amount of the operation unit, and an output unit that receives the output of the boosting unit are movable relative to the input unit, and receives an output of the output unit to receive a brake. A master cylinder that generates hydraulic pressure, and a pressure detection member that detects an output hydraulic pressure of the master cylinder and applies a reaction force corresponding to the detected hydraulic pressure to the control valve, and the control valve includes the stroke simulator The reaction force from the input shaft and the reaction force from the pressure detection member are received against each other to balance the reaction force against the input. In addition to this, there is further provided a movement resistance applying means for applying a movement resistance to the pressure detection member until the output hydraulic pressure of the master cylinder reaches a predetermined pressure to stop transmission of reaction force to the control valve. .

前記倍力手段は、負圧式倍力装置、液圧式倍力装置を問わない。   The booster may be a negative pressure booster or a hydraulic booster.

また、前記移動抵抗付与手段は、反力と対向する方向の反発力を圧力検出部材に付与するスプリングでよいが、スプリングを用いる場合には、前記圧力検出部材と前記制御弁との間に隙間を設け、その隙間がマスタシリンダの出力液圧が所定の液圧になるまで無くならないようにしておく。   The movement resistance applying means may be a spring that applies a repulsive force in a direction opposite to the reaction force to the pressure detection member. However, when a spring is used, a gap is provided between the pressure detection member and the control valve. The gap is set so as not to disappear until the output hydraulic pressure of the master cylinder reaches a predetermined hydraulic pressure.

マスタシリンダの出力液圧が所定の液圧になるまで圧力検出部材の動きを確実に停止させうる移動抵抗付与手段を用いる場合には、上記の隙間は不要である。   In the case of using a movement resistance applying means that can surely stop the movement of the pressure detection member until the output hydraulic pressure of the master cylinder reaches a predetermined hydraulic pressure, the above gap is unnecessary.

ブレーキ回路の消費液量が増加すると制御弁に加わる反力も増大するが、この発明のブレーキ液圧発生装置は、制御弁が入力に対して反力をバランスさせるので反力の変動とその反力の変動による圧力検出部材の変位が小さく抑えられ、ブレーキ回路の消費液量増加によるブレーキ操作力の変化、入力軸のストローク変化(すなわちブレーキ操作量の変化)が殆ど起こらない。ブレーキ回路の液圧が上昇したときにも同様の作用によってブレーキ操作力とブレーキ操作量の変動が抑制される。   Although the reaction force applied to the control valve increases as the amount of fluid consumed by the brake circuit increases, the brake fluid pressure generator of this invention balances the reaction force against the input, so the fluctuation of the reaction force and the reaction force The displacement of the pressure detecting member due to the fluctuation of the pressure is kept small, and the change in the brake operation force and the change in the stroke of the input shaft (that is, the change in the brake operation amount) hardly occur due to the increase in the amount of liquid consumption of the brake circuit. Even when the hydraulic pressure in the brake circuit rises, fluctuations in the brake operation force and the brake operation amount are suppressed by the same action.

また、車輪ブレーキとして、車両の燃費改善やブレーキ振動の低減を狙った低引きずり特性の、マスタシリンダからの供給液量が多くなるブレーキキャリパ等を使用する場合にも、ブレーキ操作手段の操作量に影響がでない。   In addition, when using a brake caliper that increases the amount of fluid supplied from the master cylinder and has low drag characteristics that aim to improve vehicle fuel efficiency and reduce brake vibration, the brake operation means can be operated with the same amount of braking. There is no impact.

さらに、運転者のブレーキフィーリング特性は入力軸と制御弁との間に介在したストロークシミュレータによって一義的に決定されるため、ブレーキ回路の消費液量が変動してもブレーキフィーリングには影響が出ず、良好なブレーキフィーリングが得られる。   Furthermore, since the driver's brake feeling characteristics are uniquely determined by a stroke simulator interposed between the input shaft and the control valve, the brake feeling is affected even if the amount of liquid consumed in the brake circuit varies. Good brake feeling can be obtained.

また、移動抵抗付与手段の働きにより、マスタシリンダの出力液圧が所定の液圧になるまでは制御弁に反力が伝わらないため、ブレーキ操作の初期に入力を増加させずに出力液圧を高めるジャンピング特性の付与が可能になる。   In addition, because of the action of the movement resistance applying means, the reaction force is not transmitted to the control valve until the output hydraulic pressure of the master cylinder reaches the predetermined hydraulic pressure, so the output hydraulic pressure can be increased without increasing the input at the initial stage of the brake operation. It is possible to impart jumping characteristics that enhance.

この発明のブレーキ液圧発生装置の実施形態を図1に示す。図示のブレーキ液圧発生装置は、負圧式倍力装置の出力でマスタシリンダを作動させてブレーキ液圧を発生させるものである。   FIG. 1 shows an embodiment of the brake fluid pressure generating device of the present invention. The illustrated brake fluid pressure generator operates a master cylinder with the output of a negative pressure booster to generate brake fluid pressure.

図中20はブレーキペダル、21は負圧式倍力装置、22はマスタシリンダ、23は圧力検出部材、24はリザーバ、25は、ブレーキ液圧制御装置26と車輪ブレーキ27とを有するブレーキ回路である。   In the figure, 20 is a brake pedal, 21 is a negative pressure booster, 22 is a master cylinder, 23 is a pressure detection member, 24 is a reservoir, and 25 is a brake circuit having a brake hydraulic pressure control device 26 and a wheel brake 27. .

負圧式倍力装置21は、ブレーキペダル20から操作力を受けて作動する入力軸28と、この入力軸28にブレーキ操作量に応じたストロークと反力を与えるストロークシミュレータ29と、エンジンの吸気マニフォルドなどの負圧源に接続される定圧室30と、ブレーキ操作時にブレーキ操作量に応じた大気が導入される変圧室31と、定圧室30と変圧室31を外部から画する固定シェル32(32aは負圧導入口)と、定圧室30の圧力と変圧室31の圧力を対抗して受けるパワープレート33と、パワープレート33の復帰スプリング34と、ストロークシミュレータ29と後述する制御弁37とを内蔵したバルブピストン35と、このバルブピストン35を後ろ向きに付勢するスプリング36と、定圧室30と変圧室31との間の差圧を調整する制御弁37とを備えている。   The negative pressure booster 21 includes an input shaft 28 that operates by receiving an operation force from the brake pedal 20, a stroke simulator 29 that applies a stroke and a reaction force according to the amount of brake operation to the input shaft 28, and an intake manifold of the engine. A constant pressure chamber 30 connected to a negative pressure source such as, a variable pressure chamber 31 into which air corresponding to the amount of brake operation is introduced during brake operation, and a fixed shell 32 (32a) that defines the constant pressure chamber 30 and the variable pressure chamber 31 from the outside. Is a negative pressure inlet), a power plate 33 that receives the pressure of the constant pressure chamber 30 and the pressure of the variable pressure chamber 31, a return spring 34 of the power plate 33, a stroke simulator 29, and a control valve 37 described later. Between the constant pressure chamber 30 and the variable pressure chamber 31, the spring 36 for urging the valve piston 35 backward, And a control valve 37 for adjusting the pressure.

ブレーキペダル20には、回動支点の部分においてスプリング(図示せず)による復帰力を加えている。ストロークシミュレータ29は、対向配置のリテーナ29a、29bと、両リテーナ29a、29b間に配置した弾性体29cとで構成されている。弾性体29cは、図示のもの、即ち、スプリング29c-1とゴム部材29c-2とを併用してブレーキ操作量に対する反発力が途中から増加するようにしたものが好ましい。 A return force by a spring (not shown) is applied to the brake pedal 20 at the rotation fulcrum. The stroke simulator 29 is configured by retainers 29a and 29b arranged opposite to each other, and an elastic body 29c disposed between the retainers 29a and 29b. The elastic body 29c is preferably the one shown in the drawing, that is, the one in which the spring 29c- 1 and the rubber member 29c- 2 are used in combination so that the repulsive force against the brake operation amount increases from the middle.

入力軸28、ストロークシミュレータ29及び制御弁37を内蔵して入力部を構成するバルブピストン35は、出力部であるパワープレート33の円筒部33aの内側に、パワープレート33との軸方向相対移動が許容されるように挿入され、パワープレート33との間に縮設したスプリング36の力で図示の位置に保持されている。   The valve piston 35 constituting the input unit including the input shaft 28, the stroke simulator 29, and the control valve 37 has an axial relative movement with the power plate 33 inside the cylindrical portion 33 a of the power plate 33 that is the output unit. It is inserted so as to be allowed, and is held at the position shown in the figure by the force of a spring 36 that is contracted between the power plate 33.

制御弁37は、定圧室30と変圧室31との間の通路を開閉する負圧弁38と、変圧室31と固定シェル32の外部との間の通路を開閉する大気弁39とから成る。負圧弁38は、バルブピストン35の内部に配置した伸縮可能な弁体39aとバルブピストン35に形成した弁座38aとで構成され、また、大気弁39は、前記弁体39aと、弁部材40に形成した弁座39bと、弁体39aとリテーナ29bとの間に縮設されて弁体39aを閉弁方向に付勢するスプリング39c及び弁部材40及び弁体39aを後ろ向きに付勢するスプリング39dとで構成されている。   The control valve 37 includes a negative pressure valve 38 that opens and closes a passage between the constant pressure chamber 30 and the variable pressure chamber 31, and an atmospheric valve 39 that opens and closes a passage between the variable pressure chamber 31 and the outside of the fixed shell 32. The negative pressure valve 38 is configured by an expandable / contractible valve body 39a disposed inside the valve piston 35 and a valve seat 38a formed in the valve piston 35. The atmospheric valve 39 includes the valve body 39a and the valve member 40. And a spring 39c that is contracted between the valve body 39a and the retainer 29b and biases the valve body 39a in the valve closing direction, and a spring that biases the valve member 40 and the valve body 39a backward. 39d.

弁部材40は、バルブピストン35に対して軸方向に相対移動できるようにしてあり、この弁部材40の変位によって負圧弁38と大気弁39が開閉される。   The valve member 40 can move relative to the valve piston 35 in the axial direction, and the negative pressure valve 38 and the atmospheric valve 39 are opened and closed by the displacement of the valve member 40.

パワープレート33は、変圧室31と定圧室30との間に生じた差圧を受けて前進し、入力を増幅した力を出力する。その出力でマスタシリンダピストン22aが復帰スプリング22cを圧縮して押し動かされて圧力室22bにブレーキ操作量に応じたブレーキ液圧が発生する。   The power plate 33 advances by receiving the differential pressure generated between the variable pressure chamber 31 and the constant pressure chamber 30, and outputs a force obtained by amplifying the input. As a result, the master cylinder piston 22a compresses and pushes the return spring 22c, and a brake fluid pressure corresponding to the brake operation amount is generated in the pressure chamber 22b.

圧力検出部材23は、マスタシリンダ22で発生させた液圧(マスタシリンダの出力液圧)を検出して検出液圧に応じた反力を弁部材40に加える。この圧力検出部材23とバルブピストン35との間に移動対抗付与手段である弾性体(図のそれはスプリング)41を配置してその弾性体41により圧力検出部材23の反力伝達方向への移動に抵抗を加えている。また、ブレーキ操作が成されていない初期状態で圧力検出部材23と弁部材40との間に隙間42を設け、マスタシリンダ22の出力液圧が所定の圧力になるまでは弾性体41の反発力でその隙間42が維持されて弁部材40に反力が伝わらないようにしている。   The pressure detection member 23 detects the hydraulic pressure generated in the master cylinder 22 (output hydraulic pressure of the master cylinder) and applies a reaction force corresponding to the detected hydraulic pressure to the valve member 40. An elastic body (a spring in the figure is a spring) 41 as a movement counter-giving means is arranged between the pressure detection member 23 and the valve piston 35, and the elastic body 41 moves the pressure detection member 23 in the reaction force transmission direction. Adding resistance. In addition, a clearance 42 is provided between the pressure detection member 23 and the valve member 40 in an initial state where no brake operation is performed, and the repulsive force of the elastic body 41 is maintained until the output hydraulic pressure of the master cylinder 22 reaches a predetermined pressure. Thus, the gap 42 is maintained so that no reaction force is transmitted to the valve member 40.

以下に、例示のブレーキ液圧発生装置の通常作動時、ブレーキ回路の消費液量変動時、負圧式倍力装置の失陥時の動作を項分けして説明する。   In the following, the operations when the illustrated brake fluid pressure generating device is in normal operation, when the amount of consumed fluid in the brake circuit varies, and when the negative pressure booster fails are described.

−通常作動時−
例示のブレーキ液圧発生装置は、非作動時には図1に示すように大気弁39が閉じ、負圧弁38が開いている。従って、定圧室30と変圧室31は互いに連通して同じ圧力になっており、パワープレート33は図示の初期位置に保持されている。
-During normal operation-
In the illustrated brake fluid pressure generating device, the atmospheric valve 39 is closed and the negative pressure valve 38 is opened as shown in FIG. Therefore, the constant pressure chamber 30 and the variable pressure chamber 31 communicate with each other and have the same pressure, and the power plate 33 is held in the illustrated initial position.

この状態からブレーキペダル20が踏み込まれると、ストロークシミュレータ29経由で伝達される入力によって弁部材40が図中左方に押し動かされ、その弁部材40に弁体39aが追従して図2に示すように負圧弁38が閉じ、定圧室30と変圧室31の連通を遮断する。その後、弁部材40が弁体39aから離れて大気弁39が開き、変圧室31に大気が流入する。このために、定圧室30と変圧室31との間に差圧(圧力差)が生じ、その差圧を受けたパワープレート33が前進してマスタシリンダピストン22aを図中左方に押す。これによりマスタシリンダ22が作動して圧力室22bに液圧を発生させる。   When the brake pedal 20 is depressed from this state, the valve member 40 is pushed to the left in the drawing by the input transmitted via the stroke simulator 29, and the valve body 39a follows the valve member 40 and is shown in FIG. Thus, the negative pressure valve 38 is closed, and the communication between the constant pressure chamber 30 and the variable pressure chamber 31 is cut off. Thereafter, the valve member 40 is separated from the valve body 39 a, the atmospheric valve 39 is opened, and the atmosphere flows into the variable pressure chamber 31. For this reason, a differential pressure (pressure difference) is generated between the constant pressure chamber 30 and the variable pressure chamber 31, and the power plate 33 receiving the differential pressure advances to push the master cylinder piston 22a to the left in the figure. As a result, the master cylinder 22 operates to generate a hydraulic pressure in the pressure chamber 22b.

圧力検出部材23は、圧力室22bに発生した液圧を先端に受けて図中右方に動くが、弾性体41が隙間42の大きさ相当分圧縮されるまでは図2のように弁部材40から離れており、従って、反力は制御弁37の弁部材40に伝わらず、その間は大気弁39が閉じないため、ジャンピング機能が発揮されてブレーキペダル20からの入力を増加させなくても変圧室31に大気が導入され、負圧式倍力装置21の出力が増加し、マスタシリンダ22の出力液圧が高まる。   The pressure detection member 23 receives the hydraulic pressure generated in the pressure chamber 22b at the tip and moves to the right in the figure. However, until the elastic body 41 is compressed by an amount corresponding to the size of the gap 42, the valve member as shown in FIG. Therefore, the reaction force is not transmitted to the valve member 40 of the control valve 37, and the atmospheric valve 39 is not closed during that time. Therefore, even if the jumping function is exhibited and the input from the brake pedal 20 is not increased. Air is introduced into the variable pressure chamber 31, the output of the negative pressure booster 21 is increased, and the output hydraulic pressure of the master cylinder 22 is increased.

この発明のブレーキ液圧発生装置とジャンピング機能を持たない従来装置(比較例)のブレーキの効きとペダル踏力(ブレーキペダル20に加えられる踏力)の関係を図4に示す。このように、ジャンピング機能があるとブレーキ操作初期のブレーキの効きが良くなる。   FIG. 4 shows the relationship between the braking effectiveness and the pedal effort (the pedal effort applied to the brake pedal 20) of the brake fluid pressure generating device of the present invention and the conventional device (comparative example) having no jumping function. Thus, if there is a jumping function, the effectiveness of the brake at the initial stage of the brake operation is improved.

図5は、圧力検出部材23に対する移動抵抗の付与を弾性体41で行ったときのブレーキの効きとペダル踏力の関係を示している。この図5から分かるように、移動抵抗付与手段として弾性体41を採用するとブレーキの効きが滑らかになる。   FIG. 5 shows the relationship between the braking effectiveness and the pedal effort when the elastic body 41 gives the movement resistance to the pressure detection member 23. As can be seen from FIG. 5, when the elastic body 41 is used as the movement resistance applying means, the braking effect becomes smooth.

次に、ブレーキ操作力が増加して隙間42が吸収され、圧力検出部材23が弁部材40に当接して図3の状態になると、マスタシリンダ22からの反力が弁部材40に伝わる。以後、制御弁37はその反力とブレーキペダル20からの入力が釣り合うまで大気弁39を開弁させ、弁部材40に加わる入力と反力がバランスしたら負圧弁38と大気弁39が閉じる。   Next, when the brake operation force is increased and the gap 42 is absorbed and the pressure detection member 23 comes into contact with the valve member 40 to reach the state shown in FIG. 3, the reaction force from the master cylinder 22 is transmitted to the valve member 40. Thereafter, the control valve 37 opens the atmospheric valve 39 until the reaction force and the input from the brake pedal 20 are balanced, and when the input applied to the valve member 40 and the reaction force are balanced, the negative pressure valve 38 and the atmospheric valve 39 are closed.

なお、バルブピストン35は、パワープレート33の前進量にかかわらず、スプリング36の力で初期位置に保たれる。また、ブレーキペダル20に加わる反力は、弾性体29cの選定によって任意に設定することができる。   The valve piston 35 is maintained at the initial position by the force of the spring 36 regardless of the amount of advance of the power plate 33. The reaction force applied to the brake pedal 20 can be arbitrarily set by selecting the elastic body 29c.

この通常作動時は、ペダル踏力(ブレーキペダル20に加えられる力)をF1、弾性体29cの弾性係数をk1、入力軸28のストロークをL1とすると、それらの関係は式(1)で示されるものになる。
L1=F1/k1 ・・・・(1)
また、パワープレート33に加わる力のバランス式は、パワープレート33のストロークをL2、パワープレート33の出力をF2、ブレーキ回路の消費液量をM1、圧力室22bに発生する液圧をP1とすると、それらの関係が式(2)で示されるものになる。
M1=(F2/P1)×L2 ・・・・(2)
ここで、マスタシリンダピストン22aの断面積(受圧面積)をS22、圧力検出部材23の断面積(受圧面積)をS23とすると、それらの面積比k2は、
k2=S23/S22 ・・・・(3)
となる。ブレーキ回路の消費液量にかかわらず、圧力検出部材23とパワープレート33に加わる圧力が面積比k2に比例して等しくなるように制御弁37が変圧室31への大気導入量を調整する。そのため、上式(2)に於ける消費液量M1が大きい場合には、変圧室31への大気導入量が増え、パワープレート33のストロークL2が大きくなって入力と反力がバランスすることになり、ペダル踏力F1と入力軸28のストロークL1(即ちブレーキ操作量)は変化しない。
In this normal operation, when the pedal depression force (the force applied to the brake pedal 20) is F1, the elastic coefficient of the elastic body 29c is k1, and the stroke of the input shaft 28 is L1, the relationship is expressed by Expression (1). Become a thing.
L1 = F1 / k1 (1)
Further, the balance formula of the force applied to the power plate 33 is as follows: L2 is the stroke of the power plate 33, F2 is the output of the power plate 33, M1 is the amount of liquid consumed by the brake circuit, and P1 is the hydraulic pressure generated in the pressure chamber 22b. The relationship between them is expressed by the equation (2).
M1 = (F2 / P1) × L2 (2)
Here, when the cross-sectional area (pressure receiving area) of the master cylinder piston 22a is S22 and the cross-sectional area (pressure receiving area) of the pressure detecting member 23 is S23, the area ratio k2 is
k2 = S23 / S22 (3)
It becomes. Regardless of the amount of liquid consumed by the brake circuit, the control valve 37 adjusts the amount of air introduced into the variable pressure chamber 31 so that the pressure applied to the pressure detection member 23 and the power plate 33 becomes equal in proportion to the area ratio k2. Therefore, when the consumed liquid amount M1 in the above equation (2) is large, the amount of air introduced into the variable pressure chamber 31 is increased, and the stroke L2 of the power plate 33 is increased to balance the input and the reaction force. Thus, the pedal depression force F1 and the stroke L1 (that is, the brake operation amount) of the input shaft 28 do not change.

−ブレーキ回路の消費液量変動・液圧変動時−
例えば、回生協調ブレーキ制御、車両安定制御(VSC)等の実行に伴い、車輪ブレーキ27側のブレーキ液圧Pwの制御がブレーキ液圧制御装置26によって行われた場合、そのときの消費液量をM2とすると、前記式(2)の消費液量M1がM2に変化するが、その変化量に応じて制御弁37が定圧室30と変圧室31との間の差圧を調整し、パワープレート33の出力F2を変化させる。
-When the fluid consumption and fluid pressure of the brake circuit vary-
For example, when the brake fluid pressure control device 26 controls the brake fluid pressure Pw on the wheel brake 27 side with the execution of regenerative cooperative brake control, vehicle stability control (VSC), etc., the amount of fluid consumed at that time is When M2, the consumed liquid amount M1 of the above formula (2) changes to M2, and the control valve 37 adjusts the differential pressure between the constant pressure chamber 30 and the variable pressure chamber 31 according to the change amount, and the power plate The output F2 of 33 is changed.

例えば、ブレーキ回路の消費液量がM1からM2に増加したとすると、圧力室22b内の液量が増加して圧力室22bの液圧P1が高まり、圧力検出部材23から弁部材40に伝達される反力も大きくなるが、この状況になると、弁部材40が大気弁39を閉じた状態で負圧弁38を僅かに開弁させる。そのために変圧室31の圧力が低下してパワープレート33が後退し、パワープレート33の出力F2が小さくなって液圧P1および液圧P1による反力が低下する。   For example, if the amount of fluid consumed by the brake circuit increases from M1 to M2, the amount of fluid in the pressure chamber 22b increases and the fluid pressure P1 in the pressure chamber 22b increases and is transmitted from the pressure detection member 23 to the valve member 40. The reaction force also increases, but in this situation, the valve member 40 slightly opens the negative pressure valve 38 with the atmospheric valve 39 closed. For this reason, the pressure in the variable pressure chamber 31 is reduced, the power plate 33 is retracted, the output F2 of the power plate 33 is reduced, and the hydraulic pressure P1 and the reaction force due to the hydraulic pressure P1 are reduced.

これにより、ペダル踏力F1と入力軸28のストロークL1の変動がほぼ無い状態で弁部材40に加わる入力と反力がバランスする。入力変動の無いときにブレーキ回路の液圧が変動した場合も同様である。   Thereby, the input applied to the valve member 40 and the reaction force are balanced in a state where there is almost no variation in the pedal depression force F1 and the stroke L1 of the input shaft 28. The same applies when the hydraulic pressure of the brake circuit fluctuates when there is no input fluctuation.

この発明のブレーキ液圧発生装置は、図4のストロークとペダル踏力、ストロークとブレーキの効きの関係から分かるように、同じブレーキの効きを小さな操作量で確保することができ、従って、車両の燃費改善やブレーキ振動の低減を狙った低引きずり特性のブレーキキャリパ等を使用する場合にも、その有効性が発揮される。   As can be seen from the relationship between the stroke and pedal depression force and the stroke and brake effectiveness in FIG. 4, the brake hydraulic pressure generating device of the present invention can ensure the same brake effectiveness with a small operation amount. The effectiveness is also demonstrated when using a brake caliper with low drag characteristics that aims to improve or reduce brake vibration.

−倍力機能失陥時−
ブレーキペダル20が踏み込まれると、ストロークシミュレータ29が図中左方に動いて弁部材40を押し、弁部材40がバルブピストン35に当たって入力がバルブピストン35に伝わる。スプリング36の力は復帰スプリング34の力よりも弱いため、バルブピストン35がストロークシミュレータ29と制御弁37を伴って図中左方に移動し、パワープレート33を押し動かす。このときには、定圧室30には負圧が導入されておらず、倍力装置21による助勢力は得られないが、運転者の操作力でブレーキ液圧を発生させることができる。
−In case of failure of boost function−
When the brake pedal 20 is depressed, the stroke simulator 29 moves to the left in the figure to push the valve member 40, the valve member 40 hits the valve piston 35, and the input is transmitted to the valve piston 35. Since the force of the spring 36 is weaker than the force of the return spring 34, the valve piston 35 moves to the left in the drawing together with the stroke simulator 29 and the control valve 37, and pushes the power plate 33. At this time, no negative pressure is introduced into the constant pressure chamber 30 and the assisting force by the booster 21 cannot be obtained, but the brake fluid pressure can be generated by the operating force of the driver.

なお、圧力検出部材23に膨出部23aを設け、バルブピストン35がパワープレート33を初期位置に残したまま図中左方に前進できる構造にして、倍力機能失陥時にブレーキ操作力を圧力検出部材23経由でマスタシリンダピストン22aに直接伝達することもできる。   The pressure detection member 23 is provided with a bulging portion 23a so that the valve piston 35 can move forward in the figure while leaving the power plate 33 in the initial position, and the brake operation force is reduced when the boosting function is lost. It can also be transmitted directly to the master cylinder piston 22a via the detection member 23.

この発明のブレーキ液圧発生装置の実施形態を示す非作動状態の断面図Sectional drawing of the non-operation state which shows embodiment of the brake fluid pressure generator of this invention 図1のブレーキ液圧発生装置のブレーキ操作初期の作動状態を示す図The figure which shows the operating state of the brake operation initial stage of the brake fluid pressure generator of FIG. 図1のブレーキ液圧発生装置の入力と反力のバランス制御がなされるときの図The figure when the balance control of the input and reaction force of the brake hydraulic pressure generator of FIG. 1 is made 入力軸のストロークとペダル踏力とブレーキの効き関係を示す図Diagram showing input shaft stroke, pedal effort and braking effectiveness 移動抵抗付与手段として弾性体を使用したときのペダル踏力とブレーキの効き関係を示す図The figure which shows the pedal depression force and the effect of the brake when the elastic body is used as the movement resistance giving means 従来のブレーキ液圧発生装置の一例を示す断面図Sectional drawing which shows an example of the conventional brake fluid pressure generator

符号の説明Explanation of symbols

20 ブレーキペダル
21 負圧式倍力装置
22 マスタシリンダ
22a マスタシリンダピストン
22b 圧力室
22c 復帰スプリング
23 圧力検出部材
23a 膨出部
24 リザーバ
25 ブレーキ回路
26 ブレーキ液圧制御装置
27 車輪ブレーキ
28 入力軸
29 ストロークシミュレータ
29a、29b リテーナ
29c 弾性体
29c-1 スプリング
29c-2 ゴム部材
30 定圧室
31 変圧室
32 固定シェル
32a 負圧導入口
33 パワープレート
33a 円筒部
34 復帰スプリング
35 バルブピストン
36 スプリング
37 制御弁
38 負圧弁
38a 弁座
39 大気弁
39a 弁体
39b 弁座
39c、39d スプリング
40 弁部材
41 弾性体
42 隙間
20 brake pedal 21 negative pressure booster 22 master cylinder 22a master cylinder piston 22b pressure chamber 22c return spring 23 pressure detection member 23a bulging portion 24 reservoir 25 brake circuit 26 brake hydraulic pressure control device 27 wheel brake 28 input shaft 29 stroke simulator 29a, 29b Retainer 29c Elastic body 29c -1 Spring 29c- 2 Rubber member 30 Constant pressure chamber 31 Variable pressure chamber 32 Fixed shell 32a Negative pressure inlet 33 Power plate 33a Cylindrical portion 34 Return spring 35 Valve piston 36 Spring 37 Control valve 38 Negative pressure valve 38a Valve seat 39 Atmospheric valve 39a Valve body 39b Valve seat 39c, 39d Spring 40 Valve member 41 Elastic body 42 Gap

Claims (1)

ブレーキ操作によって作動する入力軸と、この入力軸にブレーキ操作量に応じたストロークと反力を与えるストロークシミュレータと、倍力手段の出力を前記ブレーキ操作手段の操作量に応じて調整する制御弁とを内蔵した入力部と、前記倍力手段の出力を受ける出力部が前記入力部と相対移動可能であり、前記出力部の出力を受けてブレーキ液圧を発生させるマスタシリンダと、このマスタシリンダの出力液圧を検出して検出液圧に応じた反力を前記制御弁に加える圧力検出部材とを有し、前記制御弁が、前記ストロークシミュレータを介して前記入力軸から伝達される入力と前記圧力検出部材からの反力を対抗して受けて前記入力に対して前記反力をバランスさせるように構成されており、なおかつ、前記マスタシリンダの出力液圧が所定の圧力になるまで前記圧力検出部材に移動抵抗を加えて前記制御弁に対する反力の伝達を止める移動抵抗付与手段を備えているブレーキ液圧発生装置。   An input shaft that is operated by a brake operation, a stroke simulator that applies a stroke and a reaction force according to a brake operation amount to the input shaft, a control valve that adjusts an output of a booster unit according to an operation amount of the brake operation unit, And a master cylinder that generates a brake fluid pressure by receiving the output of the output unit, and an output unit that receives the output of the booster is movable relative to the input unit. A pressure detection member that detects an output hydraulic pressure and applies a reaction force corresponding to the detected hydraulic pressure to the control valve, and the control valve transmits the input transmitted from the input shaft via the stroke simulator, and It is configured to counteract the reaction force from the pressure detection member and balance the reaction force against the input, and the output hydraulic pressure of the master cylinder is The pressure sensing member to transfer resistance to addition reaction force of the movement resistance applying means has a brake fluid pressure generating device comprises a stop transfer to the control valve to a pressure of.
JP2003285178A 2003-08-01 2003-08-01 Brake fluid pressure generating device Pending JP2005053310A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2003285178A JP2005053310A (en) 2003-08-01 2003-08-01 Brake fluid pressure generating device
DE102004036984A DE102004036984A1 (en) 2003-08-01 2004-07-30 VEHICLE BRAKE HYDRAULIC PRESSURE GENERATOR
US10/902,581 US7104612B2 (en) 2003-08-01 2004-07-30 Vehicle brake hydraulic pressure generator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2003285178A JP2005053310A (en) 2003-08-01 2003-08-01 Brake fluid pressure generating device

Publications (1)

Publication Number Publication Date
JP2005053310A true JP2005053310A (en) 2005-03-03

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JP2003285178A Pending JP2005053310A (en) 2003-08-01 2003-08-01 Brake fluid pressure generating device

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Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010163161A (en) * 2009-01-15 2010-07-29 Robert Bosch Gmbh Three-way valve simulator for vehicle brake booster having play compensation

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010163161A (en) * 2009-01-15 2010-07-29 Robert Bosch Gmbh Three-way valve simulator for vehicle brake booster having play compensation

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