WO1997019842A1 - Braking system with active braking device - Google Patents

Braking system with active braking device Download PDF

Info

Publication number
WO1997019842A1
WO1997019842A1 PCT/EP1996/004944 EP9604944W WO9719842A1 WO 1997019842 A1 WO1997019842 A1 WO 1997019842A1 EP 9604944 W EP9604944 W EP 9604944W WO 9719842 A1 WO9719842 A1 WO 9719842A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve body
valve
pressure
pump
master cylinder
Prior art date
Application number
PCT/EP1996/004944
Other languages
German (de)
French (fr)
Inventor
Erhard Beck
Original Assignee
Itt Automotive Europe Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Itt Automotive Europe Gmbh filed Critical Itt Automotive Europe Gmbh
Priority to EP96938182A priority Critical patent/EP0861176A1/en
Priority to JP9520106A priority patent/JP2000500718A/en
Publication of WO1997019842A1 publication Critical patent/WO1997019842A1/en

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • B60T11/22—Master control, e.g. master cylinders characterised by being integral with reservoir
    • 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
    • B60T8/341—Systems characterised by their valves
    • 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
    • B60T8/4881—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems pump-back systems having priming means

Definitions

  • the present invention relates to a brake system according to the preamble of claim 1.
  • Such a brake system is known for example from DE 41 28 091 AI.
  • the publication relates to a brake system with anti-lock and traction control, with a master cylinder which can be acted upon by a brake pedal with brake pressure, which is fed with pressure medium from a reservoir and is connected to at least one wheel brake of at least one wheel brake of a driven wheel, with a low pressure accumulator and a return pump for anti-lock operation as well as with a pre-pressure generator, however with a limited delivery volume, for the traction control.
  • the pre-pressure generator is arranged in the storage container and is also provided for quickly filling the wheel brake of the driven wheel as well as for generating a pre-pressure on the suction side of the return pump.
  • the known brake system is the only form of active braking that controls traction control.
  • active braking means that a brake intervention can take place independently of the brake pedal.
  • Another goal of active braking can be yaw moment control when driving through a curve, for example, if the vehicle tends to oversteer or understeer.
  • yaw moment control in particular, the fastest possible brake intervention is required in order to maintain the driving stability of the vehicle.
  • a starting slip control it does not matter, for example, whether the driven wheel continues to spin for a few milliseconds or not. A subpoena is then not necessary for such purposes.
  • the self-priming return pump is able to draw its own pressure medium from the reservoir - in contrast to a pure return pump, which requires a pre-pressure.
  • a pure return pump which requires a pre-pressure.
  • it must be ensured that the return pump does not have to overcome excessively high throttle resistances during suction.
  • a corresponding amount of pressure medium must be available in order to build up the necessary brake pressure. If, however, a pre-charging takes place, it would be desirable if the pre-pressure source were not exhausted after a single actuation.
  • the object of the present invention is to provide a slip-controlled hydraulic brake system of the type mentioned at the outset, in which the pre-pressure source, which builds up a pre-pressure via the master cylinder in the brake system, spends a basically unlimited delivery volume in the brake circuits can and in which the return pump has the possibility of automatically sucking in pressure medium from the reservoir via the brake line and the master cylinder even without precharging with the lowest possible throttle losses.
  • a hydraulically actuated one Valve which connects the pressure side of the precharge pump to the master cylinder in the case of precharge and, in the case of suction by the return pump without precharging the suction side to the reservoir volume of the pressure medium container, ensures on the one hand that the precharge pump in principle unlimited volume can be brought into the brake circuits, and on the other hand that the suction side of the return pump when the return pump is operating without charging not only in connection with the limited volume of a pre-charging chamber but with the total supply volume of the pressure medium container stands.
  • Such a valve is preferably actuated hydraulically, since electrical lines and an electrical control logic are thus saved.
  • the delivery pressure and / or pulse of the pre-charge pump allows the valve to move a valve body and thus open the way into the brake circuit;
  • valve body Despite a bypass, it is recommended to also allow a pressure medium flow along the valve body, but this is only throttled. In this way, a pressure reduction from the brake circuits or from the pressure side of the precharge pump is possible, even if the bypass is still blocked by the valve body.
  • the design of the valve body There are two possibilities for the design of the valve body: If the density of the valve body is greater than that of the pressure medium, that is after the design in the basic position of the valve, that is to say with the precharging pump at rest, the bypass from the master cylinder to the supply volume of the pressure medium container opened.
  • the other version in which the valve body has a lower density than the pressure medium, has the advantage that the brake circuits can be precharged immediately without first having to swallow a certain quantity of pressure medium inside the container by moving the valve body the pressure reaches the brake circuits.
  • a precharging pump also has to draw in its pumped pressure medium from a container, it is recommended that its suction side be connected to the pressure medium container itself. It is of course also conceivable to provide a separate container for the precharging pump. Then, however, it must be ensured that this separate container is refilled when its volume is exhausted.
  • FIG. 1 shows a section of a brake system according to the invention, in which a part of a pressure medium container and a master cylinder is shown, with a hydraulically operated valve being arranged in the connection between the pressure medium container and the master cylinder, which valve is actuated by the delivery pressure of a precharging pump.
  • a pressure medium container 2 which is only shown in sections, is attached to a master cylinder 1 in a manner known per se. increases. Also only a section of the master cylinder 1 is shown, which shows a trailing bore 3 and part of the cylinder bore 4, the actuating pistons which are displaceable within the cylinder bore 4 not being shown.
  • the trailing bore 3 connects the cylinder bore 4 to the container connection 5.
  • the pressure medium container 2 is filled with pressure medium to a height that lies above the cutout shown.
  • the pressure medium container 2 is divided into a storage chamber 6 and a valve chamber 7.
  • the valve chamber 7 has a bypass 8, which connects its upper end 9 to its lower end 10, which is connected to the container connection 5.
  • the wall 11 of the valve chamber 7 is cylindrical and receives a valve body 12 which is guided axially displaceably within the valve chamber 7 with a loose fit.
  • the valve chamber 7 has an opening 13 which, like the upper connection 14 of the valve chamber 7 to the bypass 8, is covered by an upward movement of the valve body 12.
  • the valve body 12 On its underside, the valve body 12 has a cylindrical recess 15, into which a tube 16 projects vertically, the other end of which extends out of the pressure medium container 2 and is connected to the pressure side of a precharge pump 17.
  • valve body 12 In order to lend the valve body 12 a defined basic position, there are two possibilities.
  • valve body If the valve body is designed so that its density is greater than that of the pressure medium used, for example brake fluid, then it is in its basic position on the end of the tube 16, so that the pressure medium connection from the opening 13 via the bypass 8 to the container connection 5 ge ⁇ opens.
  • the precharge pump 17 starts up, the The valve body 12 is raised as a result of the pressure medium pulse and the pressure drop between its lower and upper sides, which is reduced by the gap between the valve body 12 and the wall 11, and closes the opening 13 and the upper connection 14 of the bypass 8 to the valve chamber 7. Absolute tightness is not necessary, since the precharge pump 17 can continuously deliver pressure medium, even if a partial flow flows into the reservoir volume 6 of the pressure medium container 2.
  • the volume in the valve chamber 7 initially decreases with the bypass 8 still closed over the gap between the valve body 12 and the wall 11 until the upper connection 14 of the bypass 8 by lowering the valve body 12 is open again.
  • valve body 12 can also have a lower density than the pressure medium used. However, it must then be designed such that the valve body 12 lowers at a low negative pressure of the order of 10 mbar from the container connection 5 and releases the connection from the upper opening 13 via the bypass 8 to the container connection 5, so that the Pressure medium can reach the suction side of a self-priming return pump via the follow-up bore 3.
  • the precharging pump 17 does not have to move the valve body 12 in order to build up a pre-pressure. Pressure and volume are therefore immediately available for the purpose of pre-charging as part of active braking.
  • Refilling by the return pump is also possible at any time, since the valve body 12 lowers at the lower end of the valve chamber 7 in accordance with the decrease in the pressure medium volume and releases the bypass 8.
  • a discharge of pressure medium from the master cylinder into the pressure medium container 2 can take place along the valve body 12 or also via the precharge pump 17, which in turn is connected with its suction side to the reservoir tank 2 (pump leakage).
  • Both variants offer the possibility, even without operation of the precharging pump 17, of having the self-priming return pump draw in pressure medium from the supply volume 6 even without large throttle loss.
  • container connection 5 pressure medium container 2
  • valve arrangement and pump connection shown is used for the pressure rod circuit of the master cylinder 1 which is actuated directly by the brake pedal, a pre-charge of both brake circuits can be achieved by means of a single upstream pressure generator, since the floating piston , which separates the two brake circuits from one another within the master cylinder 1, distributes the built-up pressure evenly between the two brake circuits.

Abstract

The invention concerns a drive slip-controlled hydraulic braking system comprising an active braking device and provided with an inlet pressure generator (17) which builds up inlet pressure in a brake circuit via a connection (5) to the reservoir of the master cylinder (1). To this end, disposed at a reservoir connection (5) is a valve which comprises a valve chamber (7) with a vertically rectilinear wall (11), inside which a valve body (12) is disposed so as to be axially displaceable. Above the valve body (12), the valve chamber (7) has an opening (13) to a reservoir space (6) in the pressurized medium reservoir (2). Below the valve body (12) a tube (16), which is connected to the delivery side of a pre-charging pump (17), leads into the valve chamber (7). The upper end (9) and the lower end (10) of the valve chamber (7) are connected by a bypass (8) in front of which the valve body (12) is displaced when the pre-charging pump (17) is operating, the valve body (12) simultaneously closing the opening (13) to the reservoir space (6). Thus, the pre-charging pump (17) can build up inlet pressure below the valve body (12) in the valve chamber (7), the inlet pressure spreading into the associated braking circuit via the reservoir port (3) and the master cylinder (1), whilst a pump in the braking circuit can automatically draw pressurized medium out of the reservoir space (6) via the bypass (8).

Description

Bremsanlage mit einer Einrichtung zur AktivbremsungBrake system with a device for active braking
Die vorliegende Erfindung betrifft eine Bremsanlage gemäß dem Oberbegriff des Anspruchs 1.The present invention relates to a brake system according to the preamble of claim 1.
Eine derartige Bremsanlage iεt beispielsweise aus der DE 41 28 091 AI bekannt. Die Druckschrift betrifft eine Bremsanlage mit Blockierschutz- und Antriebsschlupfregelung, mit einem von einem Bremspedal mit Bremsdruck beaufschlagba¬ ren Hauptzylinder, der von einem Vorratsbehälter mit Druck¬ mittel gespeist wird und über mindestens eine Bremsleitung an mindestens einer Radbremse eines angetriebenen Rades ange¬ schlossen ist, mit einem Niederdruckspeicher und einer Rück¬ förderpumpe für den Blockierεchutzbetrieb sowie mit einem Vordruckerzeuger, allerdings mit begrenztem Fördervolumen, für die Antriebsschlupfregelung. Der Vordruckerzeuger ist im Vorratsbehälter angeordnet und ist ebenso zum schnellen Vor¬ füllen der Radbremse des angetriebenen Rades vorgesehen wie auch zur Erzeugung eines Vordrucks an der Saugseite der Rück¬ förderpumpe. Die bekannte Bremsanlage beherrscht als einzige Form der Aktivbremεung die Antriebsschlupfregelung. Aktiv¬ bremsung bedeutet in diesem Zusammenhang, daß ein Bremsenein¬ griff unabhängig vom Bremspedal erfolgen kann. Ein andereε- Ziel einer Aktivbremsung kann beispielsweiεe die Giermomen- tenregelung beim Durchfahren einer Kurve sein, wenn das Fahr¬ zeug zu übersteuerndem oder untersteuerndem Verhalten neigt. Gerade bei einer Giermomentenregelung ist ein möglichst schneller Bremseneingriff erforderlich, um die Fahrεtabilität des Fahrzeugs zu erhalten. Bei einer Anfahrschlupfregelung jedoch spielt es beispielsweise keine Rolle, ob das angetrie¬ bene Rad noch einige Millisekunden länger durchdreht oder nicht. Für solche Zwecke dann ist eine Vorladung nicht er¬ forderlich. Die selbstansaugende Rückförderpumpe iεt in der Lage, ihr Druckmittel selbst aus dem Vorratsbehälter anzusau¬ gen - im Gegensatz zu einer reinen Rückförderpumpe, die einen Vordruck benötigt. Jedoch auch in Fällen ohne Vorladung muß sichergestellt werden, daß die Rückförderpumpe bei der An¬ saugung keine allzu hohen Drosselwiderstände überwinden muß. Außerdem muß eine entsprechende Druckmittelmenge zur Verfü¬ gung stehen, um den notwendigen Bremsdruck aufbauen zu kön¬ nen. Wenn aber eine Vorladung erfolgt, εo wäre es wünschens¬ wert, wenn die Vordruckquelle nicht nach einmaliger Betäti¬ gung erschöpft wäre.Such a brake system is known for example from DE 41 28 091 AI. The publication relates to a brake system with anti-lock and traction control, with a master cylinder which can be acted upon by a brake pedal with brake pressure, which is fed with pressure medium from a reservoir and is connected to at least one wheel brake of at least one wheel brake of a driven wheel, with a low pressure accumulator and a return pump for anti-lock operation as well as with a pre-pressure generator, however with a limited delivery volume, for the traction control. The pre-pressure generator is arranged in the storage container and is also provided for quickly filling the wheel brake of the driven wheel as well as for generating a pre-pressure on the suction side of the return pump. The known brake system is the only form of active braking that controls traction control. In this context, active braking means that a brake intervention can take place independently of the brake pedal. Another goal of active braking can be yaw moment control when driving through a curve, for example, if the vehicle tends to oversteer or understeer. In the case of yaw moment control in particular, the fastest possible brake intervention is required in order to maintain the driving stability of the vehicle. In the case of a starting slip control, however, it does not matter, for example, whether the driven wheel continues to spin for a few milliseconds or not. A subpoena is then not necessary for such purposes. The self-priming return pump is able to draw its own pressure medium from the reservoir - in contrast to a pure return pump, which requires a pre-pressure. However, even in cases without pre-charging, it must be ensured that the return pump does not have to overcome excessively high throttle resistances during suction. In addition, a corresponding amount of pressure medium must be available in order to build up the necessary brake pressure. If, however, a pre-charging takes place, it would be desirable if the pre-pressure source were not exhausted after a single actuation.
Die Aufgabe der vorliegenden Erfindung besteht darin, eine schlupfgeregelte hydraulische Bremsanlage der eingangs ge¬ nannten Art zu schaffen, bei welcher die Vordruckquelle, die über den Hauptzylinder in der Bremsanlage einen Vordruck auf¬ baut, ein im Prinzip unbegrenztes Fördervolumen in die Brems- kreise verbringen kann und bei welcher die Rückförderpumpe die Möglichkeit hat, auch ohne Vorladung mit möglichst gerin¬ gen Drosselverlusten selbsttätig Druckmittel aus dem Vor- ratεbehälter über die Bremsleitung und den Hauptzylinder an¬ zusaugen.The object of the present invention is to provide a slip-controlled hydraulic brake system of the type mentioned at the outset, in which the pre-pressure source, which builds up a pre-pressure via the master cylinder in the brake system, spends a basically unlimited delivery volume in the brake circuits can and in which the return pump has the possibility of automatically sucking in pressure medium from the reservoir via the brake line and the master cylinder even without precharging with the lowest possible throttle losses.
Diese Aufgabe wird gelöst in Verbindung mit den kennzeichnen¬ den Merkmalen deε Anεpruchε 1. Ein hydrauliεch betätigtes Ventil, welches im Falle einer Vorladung die Druckseite der Vorladepumpe mit dem Hauptzylinder verbindet und im Falle einer Ansaugung durch die Rückförderpumpe ohne Vorladung de¬ ren Saugseite mit dem Vorratsvolumen des Druckmittelbehälters verbindet, stellt zum einen sicher, daß durch die Vorladepum¬ pe ein im Prinzip unbegrenztes Volumen in den Bremskreiε ver¬ bracht werden kann, und zum anderen, daß die Saugseite der Rückförderpumpe bei Betrieb der Rückförderpumpe ohne Vorla¬ dung nicht nur mit dem begrenzten Volumen einer Vorladekam¬ mer, sondern mit dem gesamten Vorratsvolumen des Druckmit¬ telbehälters in Verbindung steht.This object is achieved in connection with the characterizing features of claim 1. A hydraulically actuated one Valve, which connects the pressure side of the precharge pump to the master cylinder in the case of precharge and, in the case of suction by the return pump without precharging the suction side to the reservoir volume of the pressure medium container, ensures on the one hand that the precharge pump in principle unlimited volume can be brought into the brake circuits, and on the other hand that the suction side of the return pump when the return pump is operating without charging not only in connection with the limited volume of a pre-charging chamber but with the total supply volume of the pressure medium container stands.
Eine Betätigung eines derartigen Ventils erfolgt vorzugsweise hydraulisch, weil somit elektrische Leitungen und eine elek¬ trische Ansteuerlogik eingespart werden. Beispielsweise kann das Ventil durch den Förderdruck und/oder -impuls der Vorla¬ depumpe einen Ventilkörper verschieben und somit sich den Weg in den Bremskreis öffnen;Such a valve is preferably actuated hydraulically, since electrical lines and an electrical control logic are thus saved. For example, the delivery pressure and / or pulse of the pre-charge pump allows the valve to move a valve body and thus open the way into the brake circuit;
Eine selbsttätige Ansaugung durch die Rückförderpumpe ohne Vorladung unter Vermeidung von großen Drosselverlusten wird unterstützt, wenn zusätzlich das hydraulisch betätigte Ventil mit einem Bypass versehen ist, welcher vom Ventilkörper er¬ zeugte Drosseleffekte umgeht, welcher jedoch bei Betätigung der Vorladepumpe verschloεεen wird.An automatic suction by the return pump without precharging while avoiding large throttle losses is supported if the hydraulically operated valve is additionally provided with a bypass which bypasses throttling effects generated by the valve body, but which is closed when the precharging pump is actuated.
Trotz einem Bypass ist es empfehlenswert, auch einen Druck¬ mittelfluß am Ventilkörper entlang zu erlauben, dies jedoch nur gedrosselt. Auf diese Weise ist ein Druckabbau aus den Bremskreisen bzw. von der Druckseite der Vorladepumpe mög¬ lich, auch wenn der Bypass noch vom Ventilkörper versperrt ist. Zur Gestaltung des Ventilkörpers ergeben sich zwei Möglich¬ keiten: Wenn die Dichte des Ventilkörpers größer iεt als die des Druckmittels, εo iεt nach der Konεtruktion in der Grund- εtellung deε Ventils, also bei ruhender Vorladepumpe, der Bypass vom Hauptzylinder zum Vorratsvolumen des Druckmittel¬ behälters geöffnet. Die andere Version, bei welcher der Ven¬ tilkörper eine geringere Dichte aufweist als das Druckmittel, hat den Vorteil, daß eine sofortige Vorladung der Bremskreise möglich ist, ohne daß durch Verschieben des Ventilkörperε zunächst eine bestimmte Druckmittelmenge innerhalb des Behäl¬ ters geschluckt wird, bevor der Druck in die Bremskreiεe ge¬ langt.Despite a bypass, it is recommended to also allow a pressure medium flow along the valve body, but this is only throttled. In this way, a pressure reduction from the brake circuits or from the pressure side of the precharge pump is possible, even if the bypass is still blocked by the valve body. There are two possibilities for the design of the valve body: If the density of the valve body is greater than that of the pressure medium, that is after the design in the basic position of the valve, that is to say with the precharging pump at rest, the bypass from the master cylinder to the supply volume of the pressure medium container opened. The other version, in which the valve body has a lower density than the pressure medium, has the advantage that the brake circuits can be precharged immediately without first having to swallow a certain quantity of pressure medium inside the container by moving the valve body the pressure reaches the brake circuits.
Da auch eine Vorladepumpe ihr gefördertes Druckmittel auε einem Behälter anεaugen muß, empfiehlt es εich, daß ihre Saugseite an den Druckmittelbehälter selbst angeschloεsen ist. Es iεt natürlich auch denkbar, für die Vorladepumpe ei¬ nen εeparaten Behälter vorzuεehen. Dann muß aber dafür ge- εorgt werden, daß dieεer separate Behälter nachbefüllt wird, wenn εein Volumen erεchöpft iεt.Since a precharging pump also has to draw in its pumped pressure medium from a container, it is recommended that its suction side be connected to the pressure medium container itself. It is of course also conceivable to provide a separate container for the precharging pump. Then, however, it must be ensured that this separate container is refilled when its volume is exhausted.
Eine nähere Erläuterung deε Erfindungεgedankens erfolgt nun anhand der Beschreibung eines Ausführungsbeispiels in einer Zeichnung. Die einzige Figur zeigt einen Ausschnitt aus einer erfindungsgemäßen Bremsanlage, in welchem ein Teil eines Druckmittelbehälters und eines Hauptzylinders dargestellt ist, wobei in der Verbindung zwischen Druckmittelbehälter und Hauptzylinder ein hydraulisch betätigtes Ventil angeordnet ist, welches vom Förderdruck einer Vorladepumpe betätigt wird.A more detailed explanation of the concept of the invention is now given on the basis of the description of an exemplary embodiment in a drawing. The single figure shows a section of a brake system according to the invention, in which a part of a pressure medium container and a master cylinder is shown, with a hydraulically operated valve being arranged in the connection between the pressure medium container and the master cylinder, which valve is actuated by the delivery pressure of a precharging pump.
Ein nur ausschnittsweise dargestellter Druckmittelbehälter 2 ist auf an sich bekannte Weise an einem Hauptzylinder 1 befe- stigt. Auch vom Hauptzylinder 1 ist nur ein Ausschnitt darge¬ stellt, welcher eine Nachlaufbohrung 3 und einen Teil der Zylinderbohrung 4 zeigt, wobei die innerhalb der Zylinderboh¬ rung 4 verschiebbaren Betätigungskolben nicht dargestellt sind. Die Nachlaufbohrung 3 verbindet die Zylinderbohrung 4 mit dem Behälteranεchluß 5. Der Druckmittelbehälter 2 iεt mit Druckmittel gefüllt biε zu einer Höhe, die oberhalb des dar¬ gestellten Auεεchnitteε liegt. Der Druckmittelbehälter 2 ist unterteilt in eine Vorratskammer 6 und eine Ventilkammer 7. Die Ventilkammer 7 besitzt einen Bypass 8, welcher ihr oberes Ende 9 mit ihrem unteren, mit dem Behälteranschluß 5 verbun¬ denen Ende 10 verbindet. Die Wandung 11 der Ventilkammer 7 ist zylindrisch und nimmt einen Ventilkörper 12 auf, welcher innerhalb der Ventilkammer 7 mit loεer Passung axial ver¬ schiebbar geführt ist. An ihrem oberen Ende 9 besitzt die Ventilkammer 7 eine Öffnung 13, welche wie die obere Verbin¬ dung 14 der Ventilkammer 7 zum Bypass 8 bei einer Aufwärts¬ bewegung des Ventilkörper 12 verdeckt wird. An seiner Unter¬ seite besitzt der Ventilkörper 12 eine zylindrische Ausneh¬ mung 15, in welche vertikal ein Rohr 16 hineinragt, welches mit seinem anderen Ende aus dem Druckmittelbehälter 2 her¬ ausgeführt und an die Druckseite einer Vorladepumpe 17 an¬ geschlossen ist.A pressure medium container 2, which is only shown in sections, is attached to a master cylinder 1 in a manner known per se. increases. Also only a section of the master cylinder 1 is shown, which shows a trailing bore 3 and part of the cylinder bore 4, the actuating pistons which are displaceable within the cylinder bore 4 not being shown. The trailing bore 3 connects the cylinder bore 4 to the container connection 5. The pressure medium container 2 is filled with pressure medium to a height that lies above the cutout shown. The pressure medium container 2 is divided into a storage chamber 6 and a valve chamber 7. The valve chamber 7 has a bypass 8, which connects its upper end 9 to its lower end 10, which is connected to the container connection 5. The wall 11 of the valve chamber 7 is cylindrical and receives a valve body 12 which is guided axially displaceably within the valve chamber 7 with a loose fit. At its upper end 9, the valve chamber 7 has an opening 13 which, like the upper connection 14 of the valve chamber 7 to the bypass 8, is covered by an upward movement of the valve body 12. On its underside, the valve body 12 has a cylindrical recess 15, into which a tube 16 projects vertically, the other end of which extends out of the pressure medium container 2 and is connected to the pressure side of a precharge pump 17.
Um dem Ventilkörper 12 eine definierte Grundstellung zu ver¬ leihen, bieten sich zwei Möglichkeiten an.In order to lend the valve body 12 a defined basic position, there are two possibilities.
Ist der Ventilkörper so ausgeführt, daß seine Dichte größer ist als die des verwendeten Druckmittels, also beispielsweise Bremsflüssigkeit, dann liegt er in seiner Grundstellung auf dem Ende des Rohres 16, so daß die Druckmittelverbindung von der Öffnung 13 über den Bypass 8 zum Behälteranschluß 5 ge¬ öffnet ist. Beim Anlaufen der Vorladepumpe 17 wird dann der Ventilkörper 12 infolge des Druckmittelimpulses und des Druckabfalls zwischen seiner Unter- und seiner Oberseite, welche sich durch den zwiεchen dem Ventilkörper 12 und der Wandung 11 befindlichen Spalt abbaut, angehoben und schließt die Öffnung 13 sowie die obere Verbindung 14 des Bypasεes 8 zur Ventilkammer 7. Es ist keine absolute Dichtheit erforder¬ lich, da die Vorladepumpe 17 permanent Druckmittel nachför¬ dern kann, auch wenn ein Teilstrom in das Vorratεvolumen 6 deε Druckmittelbehälters 2 abströmt. Wenn bei Beendigung der Vorladung die Vorladepumpe 17 stillsteht, baut sich das in der Ventilkammer 7 befindliche Volumen zunächst bei noch ver¬ schlossenem Bypass 8 über den Spalt zwischen Ventilkörper 12 und Wandung 11 ab, bis die obere Verbindung 14 des Bypasseε 8 durch Abεenken deε Ventilkörpers 12 wieder geöffnet ist.If the valve body is designed so that its density is greater than that of the pressure medium used, for example brake fluid, then it is in its basic position on the end of the tube 16, so that the pressure medium connection from the opening 13 via the bypass 8 to the container connection 5 ge ¬ opens. When the precharge pump 17 starts up, the The valve body 12 is raised as a result of the pressure medium pulse and the pressure drop between its lower and upper sides, which is reduced by the gap between the valve body 12 and the wall 11, and closes the opening 13 and the upper connection 14 of the bypass 8 to the valve chamber 7. Absolute tightness is not necessary, since the precharge pump 17 can continuously deliver pressure medium, even if a partial flow flows into the reservoir volume 6 of the pressure medium container 2. When the precharging pump 17 stops at the end of the precharging, the volume in the valve chamber 7 initially decreases with the bypass 8 still closed over the gap between the valve body 12 and the wall 11 until the upper connection 14 of the bypass 8 by lowering the valve body 12 is open again.
Alternativ hierzu kann der Ventilkörper 12 auch eine geringe¬ re Dichte als das verwendete Druckmittel aufweisen. Er muß dann aber so ausgelegt sein, daß εchon bei einem geringen Unterdruck in der Größenordnung von 10 mbar von seiten des Behälteranschlusses 5 her sich der Ventilkörper 12 absenkt und die Verbindung von der oberen Öffnung 13 über den Bypass 8 zum Behälteranschluß 5 freigibt, damit das Druckmittel über die Nachlaufbohrung 3 zur Saugseite einer selbstanεaugenden Rückförderpumpe gelangen kann. Bei dieser Version muß die Vorladepumpe 17 nicht erεt den Ventilkörper 12 verschieben, um einen Vordruck aufbauen zu können. Es stehen also sofort Druck und Volumen zum Zwecke einer Vorladung im Rahmen einer Aktivbremsung zur Verfügung. Nachsaugen durch die Rückförder¬ pumpe ist auch jederzeit möglich, da sich der Ventilkörper 12 entsprechend der Abnahme deε Druckmittelvolumens am unteren Ende der Ventilkammer 7 absenkt und den Bypass 8 freigibt. Ein Ablauf von Druckmittel aus dem Hauptzylinder in den Druckmittelbehälter 2 kann am Ventilkörper 12 entlang oder auch über die Vorladepumpe 17 erfolgen, welche mit ihrer Saugseite wiederum an den Vorratsbehälter 2 angeschlossen ist (Pumpenleckage) .As an alternative to this, the valve body 12 can also have a lower density than the pressure medium used. However, it must then be designed such that the valve body 12 lowers at a low negative pressure of the order of 10 mbar from the container connection 5 and releases the connection from the upper opening 13 via the bypass 8 to the container connection 5, so that the Pressure medium can reach the suction side of a self-priming return pump via the follow-up bore 3. In this version, the precharging pump 17 does not have to move the valve body 12 in order to build up a pre-pressure. Pressure and volume are therefore immediately available for the purpose of pre-charging as part of active braking. Refilling by the return pump is also possible at any time, since the valve body 12 lowers at the lower end of the valve chamber 7 in accordance with the decrease in the pressure medium volume and releases the bypass 8. A discharge of pressure medium from the master cylinder into the pressure medium container 2 can take place along the valve body 12 or also via the precharge pump 17, which in turn is connected with its suction side to the reservoir tank 2 (pump leakage).
Beide Varianten bieten die Möglichkeit, auch ohne Betrieb der Vorladepumpe 17 durch die selbstanεaugende Rückförderpumpe selbst ohne große Drosεelverluεte Druckmittel aus dem Vor¬ ratsvolumen 6 ansaugen zu laεsen. Wenn die dargestellte Kom¬ bination aus Behälteranschluß 5, Druckmittelbehälter 2, Ven- tilanordnung und Pumpenanschluß für den direkt vom Bremspedal betätigten Druckstangenkreis des Hauptzylinderε 1 verwendet wird, kann durch einen einzigen Vordruckerzeuger wie darge¬ stellt eine Vorladung beider Bremskreise erzielt werden, da der Schwimmkolben, welcher innerhalb des HauptZylinders 1 die beiden Bremskreise voneinander trennt, den aufgebauten Vor¬ druck gleichmäßig auf die beiden Bremskreise verteilt. Both variants offer the possibility, even without operation of the precharging pump 17, of having the self-priming return pump draw in pressure medium from the supply volume 6 even without large throttle loss. If the combination of container connection 5, pressure medium container 2, valve arrangement and pump connection shown is used for the pressure rod circuit of the master cylinder 1 which is actuated directly by the brake pedal, a pre-charge of both brake circuits can be achieved by means of a single upstream pressure generator, since the floating piston , which separates the two brake circuits from one another within the master cylinder 1, distributes the built-up pressure evenly between the two brake circuits.

Claims

Patentansprüche claims
1. Schlupfgeregelte hydraulische Bremsanlage mit einer Ein¬ richtung zur Aktivbremsung, mit einem pedalbetätigten Hauptzylinder (1), der an einen Druckmittelbehälter (2) mit einem Vorratsvolumen (6) angeschlossen ist und über mindestens eine Bremsleitung mit mindestens einer Rad¬ bremse verbunden ist, mit einem Trennventil in der Brems¬ leitung, mit einer selbεtansaugenden Rückförderpumpe, die aus den Radbremsen zur Druckreduzierung abgelassenes Druckmittel in die Trennleitung zwischen Trennventil und Radbremse zurückfördert und zum Zwecke einer Aktivbrem¬ sung eine Ansaugleitung besitzt, die an die Bremsleitung zwischen Hauptzylinder (1) und Trennventil anknüpft, und mit einem Vordruckerzeuger (17), der über einen Behäl¬ teranschluß (5) des Hauptzylinders (1) durch den Haupt¬ zylinder (1) hindurch in der Bremsleitung einen Vordruck aufbaut, dadurch gekennzeichnet, daß der Vordruckerzeuger eine Vorladepumpe (17) ist und im Druckmittelbehälter (2) am Behälteranschluß (5) ein hydraulisch betätigtes Ventil (11,12,13) angeordnet ist, das bei fördernder Vorladepum¬ pe 17 die Verbindung des Hauptzylinders (1) zum Vorrats¬ volumen (6) weitgehend absperrt und die Druckseite der Vorladepumpe (17) mit dem Hauptzylinder (1) verbindet. 1. Slip-controlled hydraulic brake system with a device for active braking, with a pedal-operated master cylinder (1) which is connected to a pressure medium container (2) with a storage volume (6) and is connected to at least one wheel brake via at least one brake line. with a separating valve in the brake line, with a self-priming return pump that delivers pressure medium discharged from the wheel brakes to reduce the pressure back into the separating line between the separating valve and wheel brake and has an intake line for the purpose of active braking that connects to the brake line between the master cylinder (1) and separating valve, and with a pre-pressure generator (17), which builds up a pre-pressure in the brake line via a container connection (5) of the master cylinder (1) through the master cylinder (1), characterized in that the pre-pressure generator is a precharge pump (17) and in the pressure medium container (2) at the container connection ß (5) a hydraulically actuated valve (11, 12, 13) is arranged, which largely shuts off the connection of the master cylinder (1) to the supply volume (6) when the precharging pump 17 is conveying, and also the pressure side of the precharging pump (17) connects the master cylinder (1).
2. Bremsanlage nach Anspruch 1, dadurch gekennzeichnet, daß die Druckseite der Vorladepumpe (17) zwischen dem Haupt¬ zylinder (1) und einem Ventilkörper (12) an eine Ventil¬ kammer (7) angeschlossen ist und durch den Förderdruck und/oder -impuls den Ventilkörper (12) vor eine Öffnung (13) zwischen der Ventilkammer (7) und dem Vorratsvolumen (6) schiebt.2. Brake system according to claim 1, characterized in that the pressure side of the precharge pump (17) between the main cylinder (1) and a valve body (12) is connected to a valve ¬ chamber (7) and by the delivery pressure and / or - impulse pushes the valve body (12) in front of an opening (13) between the valve chamber (7) and the storage volume (6).
3. Bremsanlage nach Anspruch 1 oder 2, dadurch gekennzeich¬ net, daß die Ventilkammer (7) oben mit der Öffnung (13) zum Vorratsvolumen (6) versehen ist und eine vertikal geradlinige Wandung (11) aufweist, innerhalb derer der Ventilkörper (12) vertikal verschiebbar angeordnet ist, daß die Ventilkammer (7) mit einem Bypass (8) versehen ist, der ihr oberes Ende (9) mit ihrem unteren Ende (10) verbindet, wobei der Ventilkörper (12) vom Förderdruck der Vorladepumpe (17) den Ventilkörper (12) gegen die obere Öffnung (13) der Ventilkammer (7) und vor die obere Bypassverbindung (14) verschiebt.3. Brake system according to claim 1 or 2, characterized gekennzeich¬ net that the valve chamber (7) is provided at the top with the opening (13) to the storage volume (6) and has a vertical straight wall (11) within which the valve body (12th ) is vertically displaceable so that the valve chamber (7) is provided with a bypass (8) which connects its upper end (9) with its lower end (10), the valve body (12) being dependent on the delivery pressure of the precharge pump (17) the valve body (12) against the upper opening (13) of the valve chamber (7) and in front of the upper bypass connection (14).
4. Bremsanlage nach einem der vorhergehenden Ansprüche, da¬ durch gekennzeichnet, daß der Ventilkörper (12) mit loser Passung in der Ventilkammer (7) liegt und mit der Wandung (12) einen Spalt bildet.4. Brake system according to one of the preceding claims, characterized in that the valve body (12) lies with a loose fit in the valve chamber (7) and forms a gap with the wall (12).
5. Bremsanlage nach einem der vorhergehenden Ansprüche, da¬ durch gekennzeichnet, daß die Dichte des Ventilkörpers (12) größer ist als die des verwendeten Druckmittels.5. Brake system according to one of the preceding claims, da¬ characterized in that the density of the valve body (12) is greater than that of the pressure medium used.
6. Bremsanlage nach einem der vorhergehenden Ansprüche, da¬ durch gekennzeichnet, daß die Dichte des Ventilkörpers (12) kleiner ist als die des verwendeten Druckmittels. Bremsanlage nach einem der vorhergehenden Ansprüche, da¬ durch gekennzeichnet, daß die Saugseite der Vorladepumpe (17) an den Druckmittelbehälter (2) angeschlossen ist. 6. Brake system according to one of the preceding claims, da¬ characterized in that the density of the valve body (12) is less than that of the pressure medium used. Brake system according to one of the preceding claims, characterized in that the suction side of the precharge pump (17) is connected to the pressure medium container (2).
PCT/EP1996/004944 1995-11-29 1996-11-12 Braking system with active braking device WO1997019842A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP96938182A EP0861176A1 (en) 1995-11-29 1996-11-12 Braking system with active braking device
JP9520106A JP2000500718A (en) 1995-11-29 1996-11-12 Braking device with active braking device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19544442.6 1995-11-29
DE1995144442 DE19544442A1 (en) 1995-11-29 1995-11-29 Brake system with a device for active braking

Publications (1)

Publication Number Publication Date
WO1997019842A1 true WO1997019842A1 (en) 1997-06-05

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ID=7778671

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Application Number Title Priority Date Filing Date
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EP (1) EP0861176A1 (en)
JP (1) JP2000500718A (en)
DE (1) DE19544442A1 (en)
WO (1) WO1997019842A1 (en)

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WO1997042067A1 (en) * 1996-05-08 1997-11-13 Robert Bosch Gmbh Hydraulic vehicle brake system

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DE102009047738A1 (en) * 2009-12-09 2011-06-16 Robert Bosch Gmbh Vehicle braking system

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DE3337545A1 (en) * 1983-10-15 1985-04-25 Robert Bosch Gmbh, 7000 Stuttgart HYDRAULIC BRAKE SYSTEM
DE4020448A1 (en) * 1990-06-27 1992-01-02 Teves Gmbh Alfred Brake pressure pick=up for antiskid braking system - is integral construction for fluid reservoirs and master cylinder with mountings for solenoid valves
WO1992017357A1 (en) * 1991-04-04 1992-10-15 Alfred Teves Gmbh Motor vehicle braking system with brake slip and drive slip-dependent control of the braking pressure
DE4128091A1 (en) * 1991-08-24 1993-02-25 Teves Gmbh Alfred BRAKE SYSTEM WITH ANTI-BLOCK PROTECTION AND SLIP CONTROL
DE4445401A1 (en) * 1993-12-21 1995-06-22 Aisin Seiki Vehicle hydraulic braking system

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DE4017874A1 (en) * 1990-06-02 1991-12-05 Bosch Gmbh Robert Hydraulic twin-circuit braking system with wheel-slip control - includes valve unit preventing filling of low-pressure reservoirs at onset of braking on driven wheels
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DE3337545A1 (en) * 1983-10-15 1985-04-25 Robert Bosch Gmbh, 7000 Stuttgart HYDRAULIC BRAKE SYSTEM
DE4020448A1 (en) * 1990-06-27 1992-01-02 Teves Gmbh Alfred Brake pressure pick=up for antiskid braking system - is integral construction for fluid reservoirs and master cylinder with mountings for solenoid valves
WO1992017357A1 (en) * 1991-04-04 1992-10-15 Alfred Teves Gmbh Motor vehicle braking system with brake slip and drive slip-dependent control of the braking pressure
DE4128091A1 (en) * 1991-08-24 1993-02-25 Teves Gmbh Alfred BRAKE SYSTEM WITH ANTI-BLOCK PROTECTION AND SLIP CONTROL
DE4445401A1 (en) * 1993-12-21 1995-06-22 Aisin Seiki Vehicle hydraulic braking system

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Publication number Priority date Publication date Assignee Title
WO1997042067A1 (en) * 1996-05-08 1997-11-13 Robert Bosch Gmbh Hydraulic vehicle brake system

Also Published As

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DE19544442A1 (en) 1997-06-05
JP2000500718A (en) 2000-01-25
EP0861176A1 (en) 1998-09-02

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