WO1997022504A1 - Hydraulic vehicle brake system - Google Patents

Hydraulic vehicle brake system Download PDF

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Publication number
WO1997022504A1
WO1997022504A1 PCT/EP1996/005124 EP9605124W WO9722504A1 WO 1997022504 A1 WO1997022504 A1 WO 1997022504A1 EP 9605124 W EP9605124 W EP 9605124W WO 9722504 A1 WO9722504 A1 WO 9722504A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
return
booster
brake system
vehicle brake
Prior art date
Application number
PCT/EP1996/005124
Other languages
German (de)
French (fr)
Inventor
Helmut Steffes
Hans-Dieter Reinartz
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
Publication of WO1997022504A1 publication Critical patent/WO1997022504A1/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
    • 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
    • B60T8/4845—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems using a booster or a master cylinder for traction control
    • 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
    • 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
    • B60T8/44—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 co-operating with a power-assist booster means associated with a master cylinder for controlling the release and reapplication of brake pressure through an interaction with the power assist device, i.e. open systems

Definitions

  • the hydraulic circuit diagram contains a hydraulic booster 2 for actuating a master brake cylinder 15, to which a plurality of wheel brakes VR, HL, HR, VL are connected via brake lines 16 and pressure modulation valves 17, 18.
  • a connection to the master cylinder 15 via the wheel brakes VR, HL, HR, VL which is closed in the basic position and is connected to the master cylinder 15, a return cylinder 9 being inserted into the pressure medium return lines 19 and having a stepped piston 12 and floating piston 13 is provided.
  • the return cylinder 9 is protected against the inflow of pressure medium from the master cylinder 15 by means of check valves inserted in the pressure medium return lines 19.
  • the large end face of the stepped piston 12 is connected via a valve 10, which is electromagnetically open in the basic position, to the suction connection of a pump 11, which is connected to a storage container 3.
  • a pressure switch 20 connected to the pressure side of the pump 11 is used to control a pump motor. Furthermore, the pressure medium connection from the pump 11 closes to the accumulator 4, a pressure relief valve 21 which discharges excess pressure medium to the reservoir 3 in the open state.
  • a pressure reducing valve 22 which can be controlled by the regulated pressure of the booster 2 and which, when the brake system is in active operation, has a constant, reduced pressure level at all times for the booster 2 provides via the feed line 13.
  • a further dashed-line pressure medium path 23 to the booster chamber of the booster 2 via the symbolically illustrated control lines in front of and behind the pressure reducing valve 22 in order to use the pressure regulated in the booster 2 as a control variable for the pressure reducing valve 22.
  • the power amplifier 2 also has a return 1 to the storage container 3, in which an electromagnetically actuated shut-off valve 5 is inserted in the basic position.
  • Another connection to the return line 1 is in the form of a pressure medium path 6, which is connected to the outlet of the pressure reducing valve 22.
  • the pressure medium path 6 has an inlet valve 7 which is electromagnetically closed in the basic position, so that in the selected illustration there is normally no connection from the pressure reducing valve 22 to the return line 1 of the booster 2.
  • a pressure medium connection, provided with an electromagnetically non-energized, closed valve 14, leads from the feed line 24 to the large piston stage in the return cylinder 9.
  • a floating piston 13 is located in the return cylinder 9, facing away from the large end face of the step piston 12. which is acted upon by the pressure in the pressure medium return lines 19 to its two end faces.
  • the shut-off valve 5 closes electromagnetically, so that the reservoir 3 is separated from the return 1 of the booster 2.
  • the inlet valve 7 opens the pressure medium path 6 in an electromagnetically excited manner, so that the pressure medium volume coming from the direction of the accumulator 4 via the pressure reducing valve 22 reaches the return line 1 of the booster 2 via the open inlet valve 7. Since the return 1 in the operating release position of the booster 2 is connected to the booster chamber, the reduced accumulator pressure acts in the sense of actuation on the booster piston of the booster 2.
  • pressure medium volume 19 passes through the pressure medium return line assigned to it into the return cylinder 9, which has the function of a low pressure accumulator. If pressure medium volume of the wheel cylinder is released into the return cylinder 9, then all or a partial volume is available to each brake circuit as required. This functional principle results from the floating piston 13, but the storage volume of the return cylinder 9 should be kept as small as possible in order to avoid effects on the pedal.
  • valves 10, 14 are switched back to the basic position shown in the illustration, so that, depending on a check valve integrated between the valve 10 and the suction connection to the pump 11, a low admission pressure of approximately 1 bar remains on the stepped piston 12.
  • the check valve also prevents the generation of a vacuum on the stepped piston 12.
  • the circuitry-related design of the external pressure source allows the booster pressure to be regulated sensitively, the pressure which is present at the wheel brakes being the only one required.
  • the pressure medium volume can be regulated particularly quickly, comfortably and quietly by using a hydraulic power amplifier.
  • the energy supply for the entire brake system is limited to only one external pressure source. No further pressure medium or vacuum pumps are required.

Abstract

The invention relates to a hydraulic vehicle brake system with a hydraulic power booster (2) for actuating a master cylinder (15), an external pressure source comprising a pump (11) and an accumulator (4). A pressure reducing valve (22) controllable by the regulated pressure of the power booster (2) is arranged preferably in the hydraulic connection between the accumulator (4) and the feed connection (8) of the power booster (2). Said hydraulic vehicle brake system also has a pressure medium line connected to the return (1) of the power booster (2) and leading to a reservoir (3), and wheel brakes VR, HL, HR, VL connected to the master cylinder (15) which are provided, for control of wheel slip, with pressure modulation valves (17, 18). For automatic brake engagement, the return (1) of the power booster (2) to the reservoir (3) is separated, and the accumulator (4) is connected to the return (1) of the power booster (2).

Description

Hydraulische KraftfahrzeugbremsanlägeHydraulic motor vehicle brake systems
Die Erfindung betrifft eine hydraulische Kraftfahrzeugbrems¬ anlage nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic motor vehicle brake system according to the preamble of patent claim 1.
Aus der DE 40 15 883 AI ist bereits eine hydraulische Kraft¬ fahrzeugbremsanlage bekannt geworden, die über einen hy¬ draulischen Kraftverstärker verfügt, dem ein Bremsdruckgeber zugeordnet ist. Eine Fremddruckquelle, bestehend aus einer Pumpe und einem Speicher, schließt sich über ein Druckmin¬ derventil am Kraftverstärker an. Dem Druckminderventil ist ferner ein Druckbegrenzerventil zugeordnet, daß von dem im Verstärkerraum anstehenden Druck ansteuerbar ist. Zur Be¬ tätigung der beschriebenen Bremsanlage bedarf es der manuel¬ len Ansteuerung einer Betätigungskraft, die ein im Verstär¬ kerkolben des Kraftverstärkers geführtes Schieberventil der¬ art betätigt, daß Druck der Fremddruckquelle die Stirnfläche des Verstärkerkolbens beaufschlagen kann, wodurch diese im Sinne einer Verdrängung von Druckmittel aus den Arbeitskam¬ mern des Bremsdruckgebers zu den Radbremsen betätigt wird.A hydraulic motor vehicle brake system is already known from DE 40 15 883 A1, which has a hydraulic power amplifier to which a brake pressure sensor is assigned. An external pressure source, consisting of a pump and a memory, connects to the power amplifier via a pressure reducing valve. The pressure reducing valve is also assigned a pressure limiting valve that can be controlled by the pressure in the booster chamber. In order to actuate the brake system described, manual actuation of an actuating force is required which actuates a slide valve guided in the booster piston of the power booster in such a way that pressure from the external pressure source can act on the end face of the booster piston, thereby displacing it Pressure medium is actuated from the working chambers of the brake pressure transmitter to the wheel brakes.
Nunmehr ist es die Aufgabe der Erfindung, eine hydraulische Kraftfahrzeugbremsanlage der vorgenannten Art dahingehend zu erweitern, daß unabhängig von einer manuellen Betätigung des Kraftverstärkers ein Bremseneingriff zustande kommen kann.It is now the object of the invention to expand a hydraulic motor vehicle brake system of the aforementioned type in such a way that brake intervention can take place independently of a manual actuation of the power amplifier.
Erfindungsgemäß ist diese vorbezeichnete Aufgabe für die gattungsbildende Bremsanlage durch die kennzeichnenden Merk¬ male des Patentanspruchs 1 erfüllt. Weitere Merkmale, Vorteile und Ausgestaltungsvarianten der vorliegenden Erfindung gehen im nachfolgenden aus den Unter¬ ansprüchen und der Beschreibung eines Ausführungsbeispiels anhand einer Zeichnung hervor.According to the invention, this aforementioned task for the generic brake system is achieved by the characterizing features of claim 1. Further features, advantages and design variants of the present invention will become apparent in the following from the subclaims and the description of an exemplary embodiment with reference to a drawing.
Es zeigt die einzige Figur 1 die hydraulische Kraftfahrzeug¬ bremsanlage gemäß der beanspruchten Erfindung in einer Prin¬ zipdarstellung des Hydraulikschaltplanes. Der Hydraulik¬ schaltplan beinhaltet einen hydraulischen Kraftverstärker 2 zur Betätigung eines Hauptbremszylinders 15, an dem über Bremsleitungen 16 und Druckmodulationsventile 17,18 mehrere Radbremsen VR, HL, HR, VL, angeschlossen sind. Über den Rad¬ bremsen VR, HL, HR, VL zugeordnete, in der Grundstellung geschlossene Druckmodulationsventile 18 besteht ein Anschluß zum Hauptzylinder 15, wobei in die Druckmit-telrücklauflei¬ tungen 19 ein Rückförderzylinder 9 eingesetzt ist, der mit einem Stufenkolben 12 und Schwimmkolben 13 versehen ist. Der Rückförderzylinder 9 ist mittels in den Druckmittelrücklauf¬ leitungen 19 eingesetzte Rückschlagventile gegen das Ein¬ strömen von Druckmittel aus dem Hauptzylinder 15 geschützt. Die große Stirnfläche des Stufenkolbens 12 ist über ein in der Grundstellung elektromagnetisch geöffnetes Ventil 10 mit dem Sauganschluß einer Pumpe 11 verbunden, der an einem Vor¬ ratsbehalter 3 angeschlossen ist. Die Pumpe 11 bildet mit einem ihr nachgeschalteten Speicher 4 die Fremddruckquelle zur Hochdruckversorgung des hydraulischen Kraftverstärkers 2. Ein an der Druckseite der Pumpe 11 angeschlossener Druck¬ schalter 20 dient zur Steuerung eines Pumpenmotors. Ferner schließt sich an der Druckmittelverbindung von der Pumpe 11 zum Speicher 4 ein Überdruckventil 21 an, das im geöffneten Zustand überschüssiges Druckmittel zum Vorratsbehalter 3 ableitet. Zwischen dem Speicher 4 und dem Einspeiseanschluß 8 am Kraftverstärker 2 befindet sich in der sogenannten Ein¬ speiseleitung 24 ein vom geregelten Druck des Kraftverstär¬ kers 2 steuerbares Druckminderventil 22, daß im aktiven Be¬ trieb der Bremsanlage jederzeit ein konstantes, reduziertes Druckniveau dem Kraftverstärker 2 über die Einspeiseleitung 13 zur Verfügung stellt. Zwangsläufig bestehen hierzu über die symbolisch dargestellten Steuerleitungen vor und hinter dem Druckminderventil 22 einer weitere strichlinierter Druckmittelpfad 23 zum Verstärkerraum des Kraftverstärkers 2, um den im Kraftverstärker 2 geregelten Druck als Steuer¬ größe für das Druckminderventil 22 zu verwenden. Der Kraft¬ verstärker 2 weist überdies einen Rücklauf 1 zum Vorrats¬ behalter 3 auf, in den ein in der Grundstellung geöffnetes und elektromagnetisch betätigbares Sperrventil 5 eingesetzt ist. Ein weiterer Anschluß an den Rücklauf 1 besteht in Form eines Druckmittelpfades 6, der mit dem Ausgang des Druck¬ minderventils 22 in Verbindung steht. Der Druckmittelpfad 6 weist ein in der Grundstellung elektromagnetisch geschlosse¬ nes Zulaufventil 7 auf, so daß in der gewählten Darstellung normalerweise keine Verbindung vom Druckminderventil 22 zum Rücklauf 1 des Kraftverstärkers 2 besteht. Von der Einspei¬ seleitung 24 führt eine mit einem elektromagnetisch nicht erregten, geschlossenen Ventil 14 versehene Druckmittelver¬ bindung zur großen Kolbenstufe im Rückförderzylinder 9. Ab¬ gewandt von der großen Stirnfläche des Stufenkolbens 12 be¬ findet sich im Rückförderzylinder 9 ein Schwimmkolben 13, der zu seinen beiden Stirnflächen vom Druck in den Druck¬ mittelrücklaufleitungen 19 beaufschlagt wird.1 shows the hydraulic motor vehicle brake system according to the claimed invention in a basic representation of the hydraulic circuit diagram. The hydraulic circuit diagram contains a hydraulic booster 2 for actuating a master brake cylinder 15, to which a plurality of wheel brakes VR, HL, HR, VL are connected via brake lines 16 and pressure modulation valves 17, 18. There is a connection to the master cylinder 15 via the wheel brakes VR, HL, HR, VL, which is closed in the basic position and is connected to the master cylinder 15, a return cylinder 9 being inserted into the pressure medium return lines 19 and having a stepped piston 12 and floating piston 13 is provided. The return cylinder 9 is protected against the inflow of pressure medium from the master cylinder 15 by means of check valves inserted in the pressure medium return lines 19. The large end face of the stepped piston 12 is connected via a valve 10, which is electromagnetically open in the basic position, to the suction connection of a pump 11, which is connected to a storage container 3. The pump 11, together with an accumulator 4 connected downstream, forms the external pressure source for the high pressure supply of the hydraulic power amplifier 2. A pressure switch 20 connected to the pressure side of the pump 11 is used to control a pump motor. Furthermore, the pressure medium connection from the pump 11 closes to the accumulator 4, a pressure relief valve 21 which discharges excess pressure medium to the reservoir 3 in the open state. Located in the so-called feed line 24 between the store 4 and the feed connection 8 on the booster 2 is a pressure reducing valve 22 which can be controlled by the regulated pressure of the booster 2 and which, when the brake system is in active operation, has a constant, reduced pressure level at all times for the booster 2 provides via the feed line 13. Inevitably, there are a further dashed-line pressure medium path 23 to the booster chamber of the booster 2 via the symbolically illustrated control lines in front of and behind the pressure reducing valve 22 in order to use the pressure regulated in the booster 2 as a control variable for the pressure reducing valve 22. The power amplifier 2 also has a return 1 to the storage container 3, in which an electromagnetically actuated shut-off valve 5 is inserted in the basic position. Another connection to the return line 1 is in the form of a pressure medium path 6, which is connected to the outlet of the pressure reducing valve 22. The pressure medium path 6 has an inlet valve 7 which is electromagnetically closed in the basic position, so that in the selected illustration there is normally no connection from the pressure reducing valve 22 to the return line 1 of the booster 2. A pressure medium connection, provided with an electromagnetically non-energized, closed valve 14, leads from the feed line 24 to the large piston stage in the return cylinder 9. A floating piston 13 is located in the return cylinder 9, facing away from the large end face of the step piston 12. which is acted upon by the pressure in the pressure medium return lines 19 to its two end faces.
Im nachfolgenden wird auf die Funktionsweise der abgebilde¬ ten Bremsanlage eingegangen. Alle in der Fig. 1 gezeigten Funktionselemente befinden sich in ihrer Grundstellung, die sowohl der Bremslöse- als auch der Betriebsbremsstellung entspricht. Hinsichtlich der Funktionsweise des Kraftver¬ stärkers 2 in Verbindung mit der dargestellten Fremddruck¬ quelle wird auf die DE 40 15 883 AI verwiesen. Im nachfol¬ genden wird ausschließlich auf das Wesen der Erfindung im Hinblick auf einen automatischen Bremseneingriff Bezug ge¬ nommen, der sowohl zur Antriebsschlupfregelung als auch zur Fahrdynamikregelung genutzt werden kann.The mode of operation of the brake system shown is discussed below. All of the functional elements shown in FIG. 1 are in their basic position, which corresponds to both the brake release position and the service brake position. With regard to the functioning of the booster 2 in connection with the external pressure source shown, reference is made to DE 40 15 883 A1. In the following, reference is made exclusively to the essence of the invention with regard to an automatic brake intervention, which can be used both for traction control and for driving dynamics control.
Zwecks eines automatischen Bremseneingriffs schließt das Sperrventil 5 elektromagnetisch erregt, so daß der Vorrats¬ behalter 3 vom Rücklauf 1 des Kraftverstärkers 2 abgetrennt ist. Das Zulaufventil 7 öffnet elektromagnetisch erregt den Druckmittelpfad 6, so daß das aus Richtung des Speichers 4 über das Druckminderventil 22 kommende Druckmittelvolumen über das offen geschaltete Zulaufventil 7 zum Rücklauf 1 des Kraftverstärkers 2 gelangt. Da der Rücklauf 1 in der Be- triebslösestellung des Kraftverstärkers 2 mit dem Verstär¬ kerraum in Verbindung steht, wirkt der reduzierte Speicher¬ druck im Betätigungssinne auf den Verstärkerkolben des Kraftverstärkers 2. Die in der Abbildung nicht gezeigten Arbeitskolben im Hauptzylinder 15 werden zwangsläufig durch den Hub des Verstärkerkolbens betätigt, womit Druckmittelvo- lumen des Hauptzylinders 15 über die Bremsleitungen 16 und über die in der Grundstellung geöffneten Druckmodulations¬ ventile 17 zu den Radbremsen VR, HL, HR, VL verdrängt wird. Analog zu den bisher bekannten Bremsdruckregelzyklen zum Zwecke einer Begrenzung des Radschlupfes, werden durch Druckhalte-, Druckabbau- und Druckaufbauphasen an der oder den zu regelnden Radbremsen die Bremsdrücke durch Schalten der Druckmodulationsventile 17,18 geändert. Befindet sich eines der abgebildeten, in der Grundstellung geschlossenen Druckmodulationsventile 18 in Offenstellung, so gelangt durch die ihm zugeordnete Druckmittelrücklaufleitung 19 Druckmittelvolumen in den Rückförderzylinder 9, der die Funktion eines Niederdruckspeichers inne hat. Wenn Druck¬ mittelvolumen der Radzylinder in den Rückförderzylinder 9 abgelassen wird, so steht jedem Bremskreis nach Bedarf das gesamte oder ein Teilvolumen zur Verfügung. Dieses Funk¬ tionsprinzip ergibt sich durch den Schwimmkolben 13, wobei jedoch zur Vermeidung von Rückwirkungen auf das Pedal das Speichervolumen des Rückförderzylinders 9 möglichst klein gehalten werden soll. Dies wird dadurch gewährleistet, daß durch das Schließen des Ventils 10 die sich an der Saugseite der Pumpe 11 und sich damit gleichfalls an den Vorratsbehal¬ ter 3 anschließende Druckmittelverbindung zum Stufenkolben 12 unterbrochen wird und durch Öffnen des Ventils 14 eine hydraulische Verbindung zum reduzierten Speicherdruck ge¬ schaffen wird. Damit steht der Speicherdruck als Antrieb auf der großen Stirnfläche des Stufenkolbens 12 an, womit durch die Relativbewegung des Stufenkolbens 12 in Richtung des Schwimmkolbens 13 ein kleines Speichervolumen im Rückförder- zylinder 9 eingehalten werden kann. Zum Zwecke der Beendi¬ gung des automatischen Bremseneingriffs erfolgt in umgekehr¬ ter Reihenfolge ein Umschalten des Zulaufventils 7 und des Sperrventils 5 in die abbildungsgemäße Grundstellung. Gleichfalls werden die Ventile 10,14 in die abbildungsgemäße Grundstellung zurückgeschaltet, so daß in Abhängigkeit von einem zwischen dem Ventil 10 und dem Sauganschluß an die Pumpe 11 integrierten Rückschlagventil ein geringer Vordruck von ca. 1 bar auf dem Stufenkolben 12 verharrt. Das Rück¬ schlagventil verhindert auch die Entstehung von Vakuum am Stufenkolben 12. Durch den vorgestellten schaltungstechni¬ schen Aufbau der Fremddruckquelle kann der Verstärkerdruck feinfühlig geregelt werden, wobei an den Radbremsen aus¬ schließlich der Druck ansteht, der jeweils benötigt wird. Im Gegensatz zur Verwendung von Vakuum-Bremskraltverstärkern läßt sich durch Verwendung eines hydraulischen Kraftverstar¬ kers besonders schnell, komfortabel und geräuscharm das Druckmittelvolumen regeln. Überdies beschränkt sich die Energieversorgung der gesamten Bremsanlage auf ausschlie߬ lich eine Fremddruckquelle. Weitere Druckmittel bzw. Vakuum¬ pumpen sind nicht erforderlich. For the purpose of automatic brake intervention, the shut-off valve 5 closes electromagnetically, so that the reservoir 3 is separated from the return 1 of the booster 2. The inlet valve 7 opens the pressure medium path 6 in an electromagnetically excited manner, so that the pressure medium volume coming from the direction of the accumulator 4 via the pressure reducing valve 22 reaches the return line 1 of the booster 2 via the open inlet valve 7. Since the return 1 in the operating release position of the booster 2 is connected to the booster chamber, the reduced accumulator pressure acts in the sense of actuation on the booster piston of the booster 2. The working pistons in the master cylinder 15, not shown in the figure, are inevitably caused by the Actuator piston stroke actuated, with which pressure medium lumen of the master cylinder 15 is displaced to the wheel brakes VR, HL, HR, VL via the brake lines 16 and the pressure modulation valves 17 which are open in the basic position. Analogous to the previously known brake pressure control cycles for the purpose of limiting the wheel slip, the brake pressures are changed by switching the pressure modulation valves 17, 18 through pressure maintenance, pressure reduction and pressure build-up phases on the wheel brakes to be controlled. If one of the depicted pressure modulation valves 18, which is closed in the basic position, is in the open position, pressure medium volume 19 passes through the pressure medium return line assigned to it into the return cylinder 9, which has the function of a low pressure accumulator. If pressure medium volume of the wheel cylinder is released into the return cylinder 9, then all or a partial volume is available to each brake circuit as required. This functional principle results from the floating piston 13, but the storage volume of the return cylinder 9 should be kept as small as possible in order to avoid effects on the pedal. This is ensured in that the pressure medium connection to the stepped piston 12, which is connected to the suction side of the pump 11 and thus also to the storage container 3, is interrupted by the closing of the valve 10, and a hydraulic connection to the reduced accumulator pressure is opened by opening the valve 14 ¬ will create. The accumulator pressure is thus present as a drive on the large end face of the stepped piston 12, which means that the relative movement of the stepped piston 12 in the direction of the floating piston 13 results in a small accumulator volume in the return flow. cylinder 9 can be maintained. For the purpose of terminating the automatic brake intervention, the inlet valve 7 and the shut-off valve 5 are switched over to the basic position shown in the reverse order. Likewise, the valves 10, 14 are switched back to the basic position shown in the illustration, so that, depending on a check valve integrated between the valve 10 and the suction connection to the pump 11, a low admission pressure of approximately 1 bar remains on the stepped piston 12. The check valve also prevents the generation of a vacuum on the stepped piston 12. The circuitry-related design of the external pressure source allows the booster pressure to be regulated sensitively, the pressure which is present at the wheel brakes being the only one required. In contrast to the use of vacuum brake boosters, the pressure medium volume can be regulated particularly quickly, comfortably and quietly by using a hydraulic power amplifier. In addition, the energy supply for the entire brake system is limited to only one external pressure source. No further pressure medium or vacuum pumps are required.
BezugszeicheniisteReference number list
1 Rücklauf1 return
2 Kraftverstärker2 power boosters
3 Vorratsbehalter3 storage containers
4 Speicher4 memory
5 Sperrventil5 shut-off valve
6 Druckmittelpfad6 pressure medium path
7 Zulaufventil7 inlet valve
8 Einspeiseanschluß8 feed connection
9 Rückförderzylinder9 return cylinder
10 Ventil10 valve
11 Pumpe11 pump
12 Stufenkolben12 step pistons
13 Schwimmkolben13 floating pistons
14 Ventil14 valve
15 Hauptzylinder15 master cylinders
16 Bremsleitung16 brake line
17 Druckmodulationsventil17 pressure modulation valve
18 Druckmodulationsventil18 pressure modulation valve
19 Druckmittelrücklaufleitung19 pressure medium return line
20 Druckschalter20 pressure switches
21 Überdruckventil21 pressure relief valve
22 Druckminderventil 23 Druckmittelpfad 24 Einspeiseleitung 22 Pressure reducing valve 23 Pressure medium path 24 Feed line

Claims

Patentansprüche claims
1. Hydraulische Kraftfahrzeugbremsanlage, mit einem hydraulischen Kraftverstärker zur Betätigung eines Hauptbremszylinders, mit einer Fremddruckquelle, beste¬ hend aus einer Pumpe und einem Speicher, wobei vorzugs¬ weise in der Hydraulikverbindung zwischen dem Speicher und dem Einspeiseanschluß des Kraftverstärkers ein vom geregelten Druck des Kraftverstärkers steuerbares Druck¬ minderventil angeordnet ist, mit einer am Rücklauf des Kraftverstärkers angeschlossenen und zu einem Vorrats- behälter führenden Druckmittelleitung, sowie mit am Hauptbremszylinder angeschlossenen Radbremsen, die zur Regelung des Radschlupfes mit Druckmodulationsventilen versehen sind, dadurch gekennzeichnet, daß zum automati¬ schen Bremseneingriff der Rücklauf (1) des Kraftverstär¬ kers (2) zum Vorratsbehalter (3) abgetrennt und der Speicher (4) am Rücklauf (1) des Kraftverstärkers (2) angeschlossen ist.1. Hydraulic motor vehicle brake system, with a hydraulic booster for actuating a master brake cylinder, with an external pressure source, consisting of a pump and a store, preferably in the hydraulic connection between the store and the feed port of the booster, a controllable by the regulated pressure of the booster Pressure reducing valve is arranged, with a pressure medium line connected to the return of the booster and leading to a reservoir, and with wheel brakes connected to the master brake cylinder, which are provided with pressure modulation valves for regulating the wheel slip, characterized in that the return for automatic brake intervention (1) of the power amplifier (2) to the storage container (3) is separated and the memory (4) is connected to the return (1) of the power amplifier (2).
2. Hydraulische Kraftfahrzeugbremsanlage nach Anspruch 1, dadurch gekennzeichnet, daß zwischen dem Rücklauf (1) des Kraftverstärkers (2) und dem Vorratsbehalter (3) ein in der Grundstellung offenes Sperrventil (5) angeordnet ist.2. Hydraulic motor vehicle brake system according to claim 1, characterized in that between the return (1) of the booster (2) and the reservoir (3) is arranged in the basic position open check valve (5).
3. Hydraulische Kraftfahrzeugbremsanlage nach Anspruch 1, dadurch gekennzeichnet, daß zwischen dem Rücklauf (1) des Kraftverstärkers (2) und dem Speicher (4) ein Druck- mittelpfad (6) besteht, der ein in der Grundstellung geschlossenes Zulaufventil (7) aufweist.3. Hydraulic motor vehicle brake system according to claim 1, characterized in that between the return (1) of the booster (2) and the memory (4) a pressure there is a medium path (6) which has a supply valve (7) which is closed in the basic position.
4. Hydraulische Kraftfahrzeugbremsanlage nach Anspruch 1, dadurch gekennzeichnet, daß eine zum Kraftverstärker (2) führende Einspeiseleitung (24) über ein Ventil (14) mit einem Rückförderzylinder (9) verbindbar ist, der normalerweise über ein in der Grundstellung geöffnetes Ventil (10) mit den Vorratsbehalter (3) verbunden ist.4. Hydraulic motor vehicle brake system according to claim 1, characterized in that a feed line (24) leading to the booster (2) can be connected via a valve (14) to a return cylinder (9) which is normally open via a valve (10) which is open in the basic position. is connected to the storage container (3).
5. Hydraulische Kraftfahrzeugbremsanlage nach Anspruch 4, dadurch gekennzeichnet, daß in dem Rückförderzylinder (9) ein Stufenkolben (12) angeordnet ist, dessen große Stirnfläche vom geminderten Druck des Speichers (4) be¬ aufschlagbar ist und an dessen kleine Stirnfläche der Ablaufdruck der Radbremsen (VR, HL, HR, VL) anlegbar ist.5. Hydraulic motor vehicle brake system according to claim 4, characterized in that a step piston (12) is arranged in the return cylinder (9), the large end face of the reduced pressure of the accumulator (4) can be hit and the small end face of the outlet pressure of the wheel brakes (VR, HL, HR, VL) can be created.
6. Hydraulische Kraftfahrzeugbremsanlage nach Anspruch 5, dadurch gekennzeichnet, daß der kleinen Stirnfläche des Stufenkolbens (12) zugewandt, ein Schwimmkolben (13) mit konstantem Querschnitt vorgeordnet ist. 6. Hydraulic motor vehicle brake system according to claim 5, characterized in that the small end face of the stepped piston (12) facing, a floating piston (13) is arranged upstream with a constant cross section.
PCT/EP1996/005124 1995-12-20 1996-11-20 Hydraulic vehicle brake system WO1997022504A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19547542.9 1995-12-20
DE1995147542 DE19547542A1 (en) 1995-12-20 1995-12-20 Hydraulic motor vehicle brake system

Publications (1)

Publication Number Publication Date
WO1997022504A1 true WO1997022504A1 (en) 1997-06-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1996/005124 WO1997022504A1 (en) 1995-12-20 1996-11-20 Hydraulic vehicle brake system

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DE (1) DE19547542A1 (en)
WO (1) WO1997022504A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1078833A2 (en) * 1999-08-25 2001-02-28 Continental Teves & Co. oHG Braking system for motor vehicles and method for operating a braking system

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10030031B4 (en) * 2000-03-10 2012-05-31 Continental Teves Ag & Co. Ohg Electrohydraulic brake system

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DE3833542A1 (en) * 1987-10-12 1989-04-20 Volkswagen Ag Motor vehicle hydraulic brake system with antilock control device
GB2217411A (en) * 1988-04-12 1989-10-25 Lucas Ind Plc Improvements in hydraulic systems for vehicles
EP0420175A2 (en) * 1989-09-27 1991-04-03 Robert Bosch Gmbh Brake booster
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1078833A2 (en) * 1999-08-25 2001-02-28 Continental Teves & Co. oHG Braking system for motor vehicles and method for operating a braking system
EP1078833A3 (en) * 1999-08-25 2003-07-30 Continental Teves & Co. oHG Braking system for motor vehicles and method for operating a braking system

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