+

WO1997010980A1 - Externally actuated hydraulic braking system - Google Patents

Externally actuated hydraulic braking system Download PDF

Info

Publication number
WO1997010980A1
WO1997010980A1 PCT/EP1995/003737 EP9503737W WO9710980A1 WO 1997010980 A1 WO1997010980 A1 WO 1997010980A1 EP 9503737 W EP9503737 W EP 9503737W WO 9710980 A1 WO9710980 A1 WO 9710980A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
brake
valve
pump
pressure accumulator
Prior art date
Application number
PCT/EP1995/003737
Other languages
German (de)
French (fr)
Inventor
Catalin Bungetzianu
Stefan Drumm
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
Priority to DE4431474A priority Critical patent/DE4431474A1/en
Application filed by Itt Automotive Europe Gmbh filed Critical Itt Automotive Europe Gmbh
Priority to PCT/EP1995/003737 priority patent/WO1997010980A1/en
Publication of WO1997010980A1 publication Critical patent/WO1997010980A1/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
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5087—Pressure release using restrictions
    • B60T8/5093—Pressure release using restrictions in hydraulic brake systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/26—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force characterised by producing differential braking between front and rear wheels
    • B60T8/266—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force characterised by producing differential braking between front and rear wheels using valves or actuators with external control means
    • 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
    • B60T8/26—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force characterised by producing differential braking between front and rear wheels
    • B60T8/266—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force characterised by producing differential braking between front and rear wheels using valves or actuators with external control means
    • B60T8/268—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force characterised by producing differential braking between front and rear wheels using valves or actuators with external control means using the valves of an ABS, ASR or ESP system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4072—Systems in which a driver input signal is used as a control signal for the additional fluid circuit which is normally used for braking
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/42—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having expanding chambers for controlling pressure, i.e. closed systems
    • B60T8/4275—Pump-back systems
    • B60T8/4291—Pump-back systems having means to reduce or eliminate pedal kick-back
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/48—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition connecting the brake actuator to an alternative or additional source of fluid pressure, e.g. traction control systems
    • B60T8/4809—Traction control, stability control, using both the wheel brakes and other automatic braking systems
    • B60T8/4827—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems
    • B60T8/4863—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems
    • B60T8/4872—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems pump-back systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • 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
    • 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
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • B60T8/5037—Pressure reapplication using restrictions in hydraulic brake systems closed systems

Definitions

  • the present invention is based on a brake system according to the top aspect of claim 1.
  • Such a brake system is known from US Pat. No. 4,977,238. It has the advantage that there is only a single solenoid valve in the brake line from the master cylinder to the wheel brake, in the pressure line from the external pressure source to the wheel brake and in the discharge line from the wheel brake to the volume sensor, so that no throttle effects due to series connection Solenoid valves occur.
  • hydraulic diaphragms can be inserted into the pressure and relief line without hindering pedal braking.
  • each individual wheel brake is independent of the second wheel brake arranged in the brake circuit can be acted upon by brake pressure as a function of the pedal travel or directly from the external pressure source.
  • the object of the present invention is to further improve a brake system of the type described in the introduction. This object is achieved in connection with the characterizing features of claim 1.
  • the principle of the invention therefore consists in converting the known open system of a generic brake system into a closed system.
  • a hydraulically operated pressure relief valve according to claim 4 also saves a solenoid valve and the associated electronic control.
  • FIG. 1 shows a first embodiment of a brake system according to the invention with a pressure-controlled intake valve
  • Fig. 3 shows an embodiment with a rinse ⁇ and pressure pump and Fig. 4 shows an embodiment with a special design of the high pressure accumulator.
  • a master cylinder 1 is connected to a pressure medium container 2 and can be actuated via a brake pedal 3.
  • Two brake circuits I and II emanate from it, only brake circuit II being shown and described.
  • Brake circuit I is identical to II.
  • the brake line 4 extends from the master cylinder 1 and is divided into the brake branches 5 and 6, each of which leads to one of the wheel brakes 8 and 24.
  • the wheel brakes 8 and 24 are completely equivalent in terms of their connections, so that only the connections of the wheel brake 8 are discussed in more detail here.
  • the brake branch 5 has the isolating valve 7, which is designed as an electromagnetically actuated, normally open 2/2-way valve.
  • the wheel brake 8 is connected to a high-pressure accumulator 13 via a pressure branch 10, which has a pressure valve 12, and via a pressure line 9.
  • a pressure branch 11 constructed analogously to the pressure branch 10 is assigned to the wheel brake 24.
  • the high-pressure accumulator 13 is connected to the pressure side of a pump 14, which can fill it via the check valve 15.
  • the suction side of the pump 14 is connected to a low pressure accumulator 16.
  • This can be connected to the wheel brakes 8 and 24 via a relief line 17, which is divided into two relief branches 18 and 19.
  • the relief branch 18 assigned to the wheel brake 8 carries an outlet valve 20 for this purpose.
  • the relief branch 19 is constructed identically to the relief branch 18.
  • the relief valve 20 and the pressure valve 12 are each formed by electromagnetically actuated, normally closed 2/2-way valves.
  • the task is to achieve an uninterrupted supply of pressure medium to the suction side of the pump which is unaffected by possible driver braking.
  • this object is achieved in that an intake line 21, which carries an intake valve 22 and 25, is placed between the low-pressure accumulator 16, that is to say the suction side of the pump 14 and the brake line 4.
  • the suction valve 22 according to FIG. 1 is a hydraulically actuated valve which interrupts the suction line 21 as long as there is pressure medium in the low-pressure accumulator 16 and releases this suction line as soon as the volume in the low-pressure accumulator 16 approaches zero, that is, so soon there is a negative pressure on the side of the intake valve 28 facing the low-pressure accumulator 16.
  • the pressure in the connection of the intake valve 22 connected to the brake line 4 has no influence on its switching position.
  • the pressure in the high-pressure accumulator 13 is limited to the opening pressure of the pressure relief valve 23. If this pressure is reached in the high-pressure accumulator, the pump 14 only delivers into the suction line 21.
  • unimpeded intake is achieved in that the intake valve 25 is not actuated by pressure, but rather is connected in a suitable manner to the position of the low-pressure accumulator piston with the brake system otherwise unchanged.
  • the intake valve 25 is opened. Pressure medium can be drawn in from the unpressurized master cylinder 1 or flows in from the pressurized master cylinder 1 until the suction valve 25 closes again by moving the low-pressure piston.
  • FIG. 3 An alternative solution to the use of an intake valve for the uninterrupted supply of pressure medium is shown in FIG. 3.
  • a further pressure pump 26 is used in order to ensure the uninterrupted reloading of the high-pressure accumulator.
  • the return pump 14 empties the low-pressure accumulator 16 as soon as there is pressure medium in it.
  • the outputs of the two pumps 14 and 26 are connected together. As soon as the low-pressure accumulator 16 is empty, the return pump 14 can no longer deliver pressure medium and the high-pressure accumulator 16 is recharged by the pressure pump 26 alone.
  • the intake valve may frequently switch over with simultaneous external and driver braking, which is reflected in undesired pedal movements. This would have to be taken into account in the design of the intake valve (use of a continuous directional valve, stability studies). This problem does not exist in the pump solution.
  • the pump solution In the design of the pumps 14 and 26, these can be optimized separately. For example, the return pump 14 must be able to deliver against any master cylinder pressure that occurs, while the pressure pump 26 must at most achieve the switching pressure of the pressure relief valve 23.
  • the accumulator pressure built up in the high-pressure accumulator 13 by the pumps 14 and 26 is again limited to the opening pressure of the pressure relief valve. If the desired pressure in the high-pressure accumulator 13 is reached, the pressure relief valve 13 is opened hydraulically by the pressure in the high-pressure accumulator 13, so that the return pump 14 conveys the pressure medium from the low-pressure accumulator 16 back to the master cylinder 1 and the pressure pump 26 only in the circuit without counterpressure promotes.
  • FIG. 4 A special design of the high-pressure accumulator is shown in FIG. 4, all the other components being the same as in FIG.
  • a high-pressure accumulator 27 is shown, which is designed so that it has a second hydraulic connection 28 connected to the master cylinder 1, from which as much pressure medium is displaced as flows into its pressure connection 29. This prevents the pedal movements which otherwise occur when the state of charge changes.
  • the volume design of the master cylinder 1 which is customary for anti-lock brake systems can be retained. Otherwise, for safety reasons, the fault of a high-pressure accumulator which has been emptied and only filled by the driver's braking would have to be taken into account by a larger master cylinder volume.
  • an orifice is arranged in each of the pressure valve 12 and the outlet valve 20, which limits the speed of the pressure build-up or pressure drop. Then a rapid pedal-operated braking can still be initiated via the isolating valve 7, which has no such aperture.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)

Abstract

For a braking system with an external pressure source, in which each wheel brake (8) is connected in parallel with an isolating valve (7), a pressure valve (12) and an outlet valve (20) leading to a master cylinder (1), an external pressure source consisting of a pump (14) and a high-pressure accumulator (13, 27) or to a reservoir (16), it is proposed that the braking system be designed as a closed system. To this end, the reservoir is a low-pressure accumulator and hydraulic means (22, 25, 26) are provided to ensure an uninterrupted supply of pressure medium to the intake side of the pump (14) even if the low-pressure accumulator (16) is empty.

Description

Hydraulische Bremsanlage mit FremdbetätigungHydraulic brake system with external actuation
Die vorliegende Erfindung geht aus von einer Bremsanlage gemäß dem Oberbergiff des Anspruches 1.The present invention is based on a brake system according to the top aspect of claim 1.
Eine derartige Bremsanlage ist aus der US-PS 4,977,238 be¬ kannt. Sie hat den Vorteil, daß in der Bremsleitung vom Hauptzylinder zur Radbremse, in der Druckleitung von der Fremddruckquelle zur Radbremse und in der Entlastungslei¬ tung von der Radbremse zum Volumenaufnehmer jeweils nur ein einziges Magnetventil liegt, so daß keine Drosselef¬ fekte durch in Reihe geschaltete Magnetventile auftreter. Außerdem können in die Druck- und Entlastungsleitung hy¬ draulische Blenden eingefugrt werden, ohne eine Pedalbrem¬ sung zu behindern.Such a brake system is known from US Pat. No. 4,977,238. It has the advantage that there is only a single solenoid valve in the brake line from the master cylinder to the wheel brake, in the pressure line from the external pressure source to the wheel brake and in the discharge line from the wheel brake to the volume sensor, so that no throttle effects due to series connection Solenoid valves occur. In addition, hydraulic diaphragms can be inserted into the pressure and relief line without hindering pedal braking.
Wenn innerhalb eines Bremskreises zwei Radbremsen symme¬ trisch angeordnet werden, wie es beispielsweise in der DE 41 12 137 AI, in welcher es um eine reine fremdkraftbe- tätigbare Bremsanlage geht der Fall ist, bietet sich zudem der Vorteil, daß jede einzelne Radbremse unabhängig von der zweiten im Bremskreis angeordneten Radbremse pedalwegabhängig oder unmittelbar von der Fremddruck¬ quelle mit Bremsdruck beaufschlagbar ist.If two wheel brakes are arranged symmetrically within a brake circuit, as is the case, for example, in DE 41 12 137 AI, which is a purely power-operated brake system, there is also the advantage that each individual wheel brake is independent of the second wheel brake arranged in the brake circuit can be acted upon by brake pressure as a function of the pedal travel or directly from the external pressure source.
Die Aufgabe der vorliegenden Erfindung besteht darin, eine Bremsanlage der eingangs beschriebenen Art weiter zu verbessern. Diese Aufgabe wird gelöst in Verbindung mit den kennzeichnenden Merkmalen des Anspruches 1. Das Prinzip der Erfindung besteht also darin, das bekannte offene System einer gattungsgemäßen Bremsanlage in ein geschlossenes System zu verwandeln.The object of the present invention is to further improve a brake system of the type described in the introduction. This object is achieved in connection with the characterizing features of claim 1. The principle of the invention therefore consists in converting the known open system of a generic brake system into a closed system.
Durch die Verwendung eines hydraulisch betätigten Ansaug¬ ventils in der Verbindung zwischen Niederdruckspeicher und Hauptzylinder wird die Anzahl der elektromagnetisch betä¬ tigten Ventile kleingehalten und keine zusätzliche elek¬ trische Ansteuerung benötigt.By using a hydraulically actuated intake valve in the connection between the low pressure accumulator and the master cylinder, the number of electromagnetically actuated valves is kept small and no additional electrical control is required.
Geräuschmindernd wirkt sich aus, daß das von der Pumpe geförderte Druckmittel zum Hauptzylinder abgeleitet wird, sobald der Hochdruckspeicher geladen ist.The fact that the pressure medium delivered by the pump is discharged to the master cylinder as soon as the high-pressure accumulator is charged has a noise-reducing effect.
Durch ein hydraulisch betätigtes Überdruckventil nach An¬ spruch 4 , wird auch hier ein Magnetventil sowie die zuge¬ hörige elektronische Ansteuerung eingespart.A hydraulically operated pressure relief valve according to claim 4 also saves a solenoid valve and the associated electronic control.
Eine nähere Erläuterung des Erfindungsgedankens erfolgt nun anhand der Bechreibung von vier Ausführungsbeispielen in vier Figuren. Es zeigen:A more detailed explanation of the concept of the invention will now be given with the description of four exemplary embodiments in four figures. Show it:
Fig. 1 eine erste Ausführungsform einer erfindungs¬ gemäßen Bremsanlage mit druckgesteuertem Ansaugventil,1 shows a first embodiment of a brake system according to the invention with a pressure-controlled intake valve,
Fig. 2 eine Ausführungsform mit weggesteuertem Ansaugventil,2 shows an embodiment with displacement-controlled suction valve,
Fig. 3 eine Ausführungsform mit je einer Rückförder¬ und Druckpumpe und Fig. 4 eine Ausführungsform mit spezieller Gestaltung des Hochdruckspeichers .Fig. 3 shows an embodiment with a Rückförder¬ and pressure pump and Fig. 4 shows an embodiment with a special design of the high pressure accumulator.
In Figur 1 ist ein Hauptzylinder 1 an einen Druckmittelbe¬ hälter 2 angeschlossen und über ein Bremspedal 3 betätig¬ bar. Von ihm gehen zwei Bremskreise I und II aus, wobei nur der Bremskreis II dargestellt ist und beschrieben wird. Der Bremskreis I ist mit II identisch. Vom Haupt¬ zylinder 1 geht die Bremsleitung 4 aus, die sich in die Bremszweige 5 und 6 aufteilt, die jeweils zu einer der Radbremsen 8 und 24 führen. Die Radbremsen 8 und 24 sind vollkommen gleichwertig bezüglich ihrer Anschlüsse, so daß hier nur näher auf die Verbindungen der Radbremse 8 eingegangen wird. Der Bremszweig 5 weist das Trennventil 7 auf, welches als elektromagnetisch betätigtes, stromlos offenes 2/2-Wegeventil gestaltet ist. Außerdem ist die Radbremse 8 über einen Druckzweig 10, der ein Druckventil 12 aufweist, und über eine Druckleitung 9 an einen Hochdruckspeicher 13 angeschlossen. Ein zum Druckzweig 10 analog aufgebauter Druckzweig 11 ist der Radbremse 24 zugeordnet. Der Hochdruckspeicher 13 ist an die Druckseite einer Pumpe 14 angeschlossen, welche ihn über das Rückschlag-ventil 15 befüllen kann. Die Saugseite der Pumpe 14 ist mit einem Niederdruckspeicher 16 verbunden. Dieser ist über eine Entlastungsleitung 17, die sich in zwei Entlastungszweige 18 und 19 aufteilt, mit den Radbremsen 8 bzw. 24 verbindbar. Der der Radbremse 8 zugeordnete Entlastungswezig 18 trägt hierzu ein Auslaßventil 20. Der Entlastungszweig 19 ist identisch zum Entlastungszweig 18 aufgebaut. Das Entlastungsventil 20 und das Druckventil 12 werden jeweils von elektro¬ magnetisch betätigten, stromlos geschlossenen 2/2- Wegeventilen gebildet. Damit der Pumpe 14 das zur Befullung des Hochdruckspei¬ chers 13 nötige Druckmittelvolumen jederzeit zur Verfügung steht, stellt sich die Aufgabe, eine von eventuellen Fahrerbremsungen unbeeinflußte, unterbrechungsfreie Ver¬ sorgung der Saugseite der Pumpe mit Druckmittel zu errei¬ chen. In den Figuren 1 und 2 ist diese Aufgabe dadurch gelöst, daß zwischen dem Niederdruckspeicher 16, also der Saugseite der Pumpe 14 und der Bremsleitung 4 eine Ansaug¬ leitung 21 angelegt ist, die ein Ansaugventil 22 bzw. 25 trägt.In FIG. 1, a master cylinder 1 is connected to a pressure medium container 2 and can be actuated via a brake pedal 3. Two brake circuits I and II emanate from it, only brake circuit II being shown and described. Brake circuit I is identical to II. The brake line 4 extends from the master cylinder 1 and is divided into the brake branches 5 and 6, each of which leads to one of the wheel brakes 8 and 24. The wheel brakes 8 and 24 are completely equivalent in terms of their connections, so that only the connections of the wheel brake 8 are discussed in more detail here. The brake branch 5 has the isolating valve 7, which is designed as an electromagnetically actuated, normally open 2/2-way valve. In addition, the wheel brake 8 is connected to a high-pressure accumulator 13 via a pressure branch 10, which has a pressure valve 12, and via a pressure line 9. A pressure branch 11 constructed analogously to the pressure branch 10 is assigned to the wheel brake 24. The high-pressure accumulator 13 is connected to the pressure side of a pump 14, which can fill it via the check valve 15. The suction side of the pump 14 is connected to a low pressure accumulator 16. This can be connected to the wheel brakes 8 and 24 via a relief line 17, which is divided into two relief branches 18 and 19. The relief branch 18 assigned to the wheel brake 8 carries an outlet valve 20 for this purpose. The relief branch 19 is constructed identically to the relief branch 18. The relief valve 20 and the pressure valve 12 are each formed by electromagnetically actuated, normally closed 2/2-way valves. In order for the pump 14 to have the pressure medium volume required to fill the high-pressure accumulator 13 at all times, the task is to achieve an uninterrupted supply of pressure medium to the suction side of the pump which is unaffected by possible driver braking. In FIGS. 1 and 2, this object is achieved in that an intake line 21, which carries an intake valve 22 and 25, is placed between the low-pressure accumulator 16, that is to say the suction side of the pump 14 and the brake line 4.
Das Ansaugventil 22 nach Figur 1 ist ein hydraulisch betä¬ tigtes Ventil, welches die Ansaugleitung 21 unterbricht, solange sich Druckmittel im Niederdruckspeicher 16 befin¬ det, und diese Ansaugleitung freigibt, sobald das Volumen im Niederdruckspeicher 16 gegen Null geht, das heißt, so¬ bald auf der dem Niederdruckspeicher 16 zugewandten Seite des Ansaugventils 28 ein Unterdruck herrscht. Der Druck in dem mit der Bremsleitung 4 verbundenen Anschluß des An¬ saugventils 22 hat keinen Einfluß auf seine Schaltstel¬ lung.The suction valve 22 according to FIG. 1 is a hydraulically actuated valve which interrupts the suction line 21 as long as there is pressure medium in the low-pressure accumulator 16 and releases this suction line as soon as the volume in the low-pressure accumulator 16 approaches zero, that is, so soon there is a negative pressure on the side of the intake valve 28 facing the low-pressure accumulator 16. The pressure in the connection of the intake valve 22 connected to the brake line 4 has no influence on its switching position.
Der Druck im Hochdruckspeicher 13 ist auf den Öffnungs¬ druck des Überdruckventils 23 begrenzt. Ist dieser Druck im Hochdruckspeicher erreicht, fördert die Pumpe 14 nur noch in die Ansaugleitung 21.The pressure in the high-pressure accumulator 13 is limited to the opening pressure of the pressure relief valve 23. If this pressure is reached in the high-pressure accumulator, the pump 14 only delivers into the suction line 21.
In Figur 2 wird ein ungehindertes Ansaugen dadurch er¬ reicht, daß das Ansaugventil 25 nicht druckbetätigt, son¬ dern in geeigneter Weise an die Lage des Niederdruckspei¬ cherkolbens angebunden ist bei ansonsten unveränderter Bremsanlage. Sobald die Pumpe 14 den Niederdruckspeicher 16 leergeför¬ dert hat, wird das Ansaugvetnil 25 geöffnet. Druckmittel kann aus dem drucklosen Hauptzylinder 1 angesaugt werden, bzw. strömt aus dem unter Druck stehenden HauptZylinder 1 so lange nach, bis durch Verschieben des Niederdruckspei¬ cherkolbens das Ansaugventil 25 wieder schließt.In FIG. 2, unimpeded intake is achieved in that the intake valve 25 is not actuated by pressure, but rather is connected in a suitable manner to the position of the low-pressure accumulator piston with the brake system otherwise unchanged. As soon as the pump 14 has emptied the low-pressure accumulator 16, the intake valve 25 is opened. Pressure medium can be drawn in from the unpressurized master cylinder 1 or flows in from the pressurized master cylinder 1 until the suction valve 25 closes again by moving the low-pressure piston.
Eine zur Verwendung eines Ansaugventils alternative Lösung zur unterbrechungsfreien Druckmittelbesorgung wird in Figur 3 gezeigt. Es wird neben der Rückförderpumpe 14 eine weitere Druckpumpe 26 eingesetzt, um das unterbrechungs- freie Nachladen des Hochdruckspeichers zu gewährleisten. Die Rückförderpumpe 14 entleert den Niederdruckspeicher 16, sobald sich Druckmittel darin befindet. Die Druckpumpe 26 saugt dagegen direkt aus der Ansaugleitung 21 an. Die Ausgänge der beiden Pumpen 14 und 26 sind zusammenge¬ schaltet. Sobald der Niederdruckspeicher 16 leer ist, kann die Rückförderpumpe 14 kein Druckmittel mehr fördern und der Hochdruckspeicher 16 wird alleine von der Druckpumpe 26 nachgeladen.An alternative solution to the use of an intake valve for the uninterrupted supply of pressure medium is shown in FIG. 3. In addition to the return pump 14, a further pressure pump 26 is used in order to ensure the uninterrupted reloading of the high-pressure accumulator. The return pump 14 empties the low-pressure accumulator 16 as soon as there is pressure medium in it. The pressure pump 26, however, sucks directly from the suction line 21. The outputs of the two pumps 14 and 26 are connected together. As soon as the low-pressure accumulator 16 is empty, the return pump 14 can no longer deliver pressure medium and the high-pressure accumulator 16 is recharged by the pressure pump 26 alone.
Bei den in den Figuren 1 und 2 dargestellten Lösungen mit Ansaugventil kann es bei gleichzeitiger Fremd- und Fahrer¬ bremsung zu einem häufigen Umschalten des Ansaugventils kommen, was sich in unerwünschten Pedalbewegungen nieder¬ schlägt. Dies müßte bei der konstruktiven Gestaltung des Ansaugventils (Einsatz eines Stetig-Wegeventils, Stabi¬ litätsuntersuchungen) berücksichtigt werden. In der Pumpenlösung gibt es dieses Problem nicht. Bei der konstruktiven Ausgestaltung der Pumpen 14 und 26 können diese getrennt optimiert werden. Beispielsweise muß die Rückförderpumpe 14 gegen jeden auftretenden Hauptzylinderdruck fördern können, während die Druckpumpe 26 maximal den Umschaltdurck des Überdruckventils 23 leisten muß.In the solutions shown in FIGS. 1 and 2 with an intake valve, the intake valve may frequently switch over with simultaneous external and driver braking, which is reflected in undesired pedal movements. This would have to be taken into account in the design of the intake valve (use of a continuous directional valve, stability studies). This problem does not exist in the pump solution. In the design of the pumps 14 and 26, these can be optimized separately. For example, the return pump 14 must be able to deliver against any master cylinder pressure that occurs, while the pressure pump 26 must at most achieve the switching pressure of the pressure relief valve 23.
Der im Hochdruckspeicher 13 von den Pumpen 14 und 26 aufgebaute Speicherdruck ist wieder auf den Öffnungsdruck des Überdruckventils begrenzt. Ist der gewünschte Druck im Hochdruckspeicher 13 erreicht, so wird das Überdruckventil 13 hydrau-lisch vom Druck im Hochdruckspeicher 13 geöffnet, so daß die Rückförderpumpe 14 das Druckmittel vom Niederdruckspeicher 16 zum Hauptzylinder 1 zurück¬ fördert und die Druckpumpe 26 nur noch ohne Gegendruck im Kreis fördert.The accumulator pressure built up in the high-pressure accumulator 13 by the pumps 14 and 26 is again limited to the opening pressure of the pressure relief valve. If the desired pressure in the high-pressure accumulator 13 is reached, the pressure relief valve 13 is opened hydraulically by the pressure in the high-pressure accumulator 13, so that the return pump 14 conveys the pressure medium from the low-pressure accumulator 16 back to the master cylinder 1 and the pressure pump 26 only in the circuit without counterpressure promotes.
Eine spezielle Gestaltung des Hochdruckspeichers zeigt Figur 4, wobei alle übrigen Komponenten mit Figur 3 übereinstimmen. Darstellt ist ein Hochdruckspeicher 27, der so gestaltet ist, daß er einen zweiten mit dem Hauptzylinder 1 verbundenen Hydraulikanschluß 28 aufweist, aus dem genausoviel Druckmittel verdrängt wird, wie in seinen Druckanschluß 29 hineinfließt. Dadurch werden die sonst auftretenden Pedalbewegungen bei Ladezustands¬ änderungen verhindert. Außerdem kann die für blockierge¬ schützte Bremsanlagen übliche Volumenauslegung des Hauptzylinders 1 beibehalten werden. Aus Sicherheits¬ gründen müßte ansonsten der Fehlerfall eines entleerten und erst durch die Fahrerbremsung gefüllten Hochdruck¬ speichers durch ein größeres Hauptzylindervolumen berücksichtigt werden.A special design of the high-pressure accumulator is shown in FIG. 4, all the other components being the same as in FIG. A high-pressure accumulator 27 is shown, which is designed so that it has a second hydraulic connection 28 connected to the master cylinder 1, from which as much pressure medium is displaced as flows into its pressure connection 29. This prevents the pedal movements which otherwise occur when the state of charge changes. In addition, the volume design of the master cylinder 1 which is customary for anti-lock brake systems can be retained. Otherwise, for safety reasons, the fault of a high-pressure accumulator which has been emptied and only filled by the driver's braking would have to be taken into account by a larger master cylinder volume.
Diese Maßnahme kann in allen in den Figuren 1, 2 und 3 dargestellten Varianten der vorgeschlagenen Bremsanlage zur Anwendung kommen. Die Funktionsweise dieser Bremsanlagen während einer Normal-bremsung ist die einer konventionellen Bremsanlage ohne Schlupfregelung. Sämtliche Ventile verbleiben in ihrer dar-gestellten Grundposition, so daß ein Bremsdruckaufbau in den Radbremsen 8 und 24 über die Bremsleitung 4 und die Bremszweige 5 und 6 erfolgt, wobei der Bremsdruckabbau denselben Weg nimmt.This measure can be used in all the variants of the proposed brake system shown in FIGS. 1, 2 and 3. The way these brake systems work during normal braking is that of a conventional brake system without slip control. All valves remain in their basic position shown, so that a brake pressure build-up in the wheel brakes 8 and 24 takes place via the brake line 4 and the brake branches 5 and 6, the brake pressure reduction taking the same path.
Im Falle einer elektronisch geregelten Bremsung - das kann eine Bremsschlupfregelung, eine Antriebsschlupfregelung, ein Fahrstabilitätsregeleingriff, eine Maßnahme zur elektronischen Bremskraftverteilung oder zur Fahrzeugver¬ zögerungsregelung sein - werden für jedes der betroffenen Räder die folgenden Ventilschaltungen durchgeführt, die am Beispiel der Radbremse 8 erläutert werden:In the case of electronically controlled braking - this can be brake slip control, traction control, driving stability control intervention, a measure for electronic braking force distribution or for vehicle deceleration control - the following valve circuits are carried out for each of the wheels concerned, which are explained using the example of wheel brake 8:
° Bremsdruck halten durch Schließen des Trennventils bei geschlossenem Druckventil 12 und geschlossenem Auslaßventil 20° Hold the brake pressure by closing the isolating valve with the pressure valve 12 closed and the outlet valve 20 closed
o Bremsdruck aufbauen durch Öffnen des Druckventils 12 bei geschlossenem Trennventil 7 und geschlossenem Auslaßventil 20o Build up brake pressure by opening the pressure valve 12 with the isolating valve 7 closed and the outlet valve 20 closed
° Bremsdruck aufbauen durch Öffnen des Auslaßventils 20 bei geschlossenem Trennventil 7 und geschlossenem Druckventil 12.° Build up brake pressure by opening exhaust valve 20 with isolation valve 7 and pressure valve 12 closed.
Da es keine Möglichkeit des Druckmittelaustauschs zwischen dem Druckmittelvorratsbehälter 2 und dem Bremskreis II gibt als die durch das Hauptzylinder 1, handelt es sich um eine geschlossene Bremsanlage. Das Pedalverhalten entspricht dem Grundcharakter einer geschlossenen Bremsanlage nach dem Rückförderungsprinzip. In den Niederdruckspeicher 16 abgelassenes Druckmittel wird zum Hauptzylinder 1 zurückgefördert und führt so zur Verringerung eines vom Fahrer getretenen Pedalwegs . Das beim Druckaufbau dem Hochdruckspeicher 13 bzw. 27 entnommene Druckmittel wird mit Hilfe der Pumpe 14 bzw. 26 aus dem Hauptzylinder 1 ersetzt. In den Figuren 1, 2 und 3 führt dies zur Vergrößerung des vom Fahrer getretenen Pedalwegs. Solange das Bremspedal 3 betätigt bleibt, entspricht daher die Bremspedalstellung der über die einzelnen Radbremsen mit den entsprechenden Volumenaufnahmen gewichtet gemittelten, tatsächlichen Bremsaktion.Since there is no possibility of pressure medium exchange between the pressure medium reservoir 2 and the brake circuit II than that through the master cylinder 1, it is a closed brake system. The pedal behavior corresponds to the basic character of a closed brake system based on the return principle. In the Low-pressure accumulator 16 discharged pressure medium is conveyed back to the master cylinder 1 and thus leads to a reduction in a pedal stroke which the driver has depressed. The pressure medium removed from the high-pressure accumulator 13 or 27 when the pressure builds up is replaced with the aid of the pump 14 or 26 from the master cylinder 1. In Figures 1, 2 and 3, this leads to an increase in the pedal travel taken by the driver. As long as the brake pedal 3 remains actuated, the brake pedal position therefore corresponds to the actual braking action weighted averaged over the individual wheel brakes with the corresponding volume receptacles.
Gegenüber einer herkömmlichen Bremsschlupfregelung nach dem Rückförderprinzip ergibt sich ein schnellerer und vor allem genauerer Druckaufbau, da dazu nicht der wechselnde Fahrerbremsdruck, sondern der durch das Überdruckventil 23 festgelegte Ladedruck des Hochdruckspeichers 13 zur Verfügung steht.Compared to a conventional brake slip control based on the return flow principle, there is a faster and, above all, more precise pressure build-up, since it is not the changing driver brake pressure that is available, but rather the boost pressure of the high-pressure accumulator 13 determined by the pressure relief valve 23.
Gegenüber einer herkömmlichen schlupfgeregelten Bremsanlage mit Antriebsschlupfregelung, die auch eingeschränkt fremdbremstatig ist, besteht der wichtigste Vorteil darin, daß auch die Fremdbremsungen radindividuell durchführbar sind. So ist es mit den vorgeschlagenen Anlagen nunmehr möglich, an verschiedenen Radbremsen eines Bremskreises gleichzeitig Bremsungen mit Drücken unter υüer über dem Fahrerbremsdruck frei zu kombinieren.Compared to a conventional slip-controlled brake system with traction control, which is also due to limited external braking, the most important advantage is that the external braking can also be carried out individually for the wheel. It is now possible with the proposed systems to freely combine braking on different wheel brakes of a brake circuit with pressures below the driver brake pressure.
Bei erhöhter Sicherheit durch das geschlossene System bleiben dem Fahrer also die Vorteile der aus dem Stand der Technik bekannten Bremsanlagen erhalten: Auch während einer pedalbetätigten Bremsung der Radbremsen 8 und 24 kann radindividuell ein Bremseneingriff durch die Fremdruckquelle vorgenommen werden. Das heißt, daß nur jeweils die Radbremse vom Hauptzylinder 1 abgetrennt zu werden braucht, in welcher eine Druckregelung über die Fremddruckquelle erfolgt.With increased safety thanks to the closed system, the driver therefore retains the advantages of the brake systems known from the prior art: even during pedal-operated braking of the wheel brakes 8 and 24 a brake intervention by the external pressure source can be carried out individually for the wheel. This means that only the wheel brake needs to be disconnected from the master cylinder 1, in which pressure control takes place via the external pressure source.
Es kann vorgesehen werden, daß im Druckventil 12 und im Auslaßventil 20 jeweils eine Blende angeordnet ist, die die Geschwindigkeit des Druckaufbaus bzw. des Druckabbaus begrenzt. Dann ist trotzdem über das Trennventil 7, welches keine solche Blende aufweist, eine schnelle pedalbetätigte Bremsung einleitbar. It can be provided that an orifice is arranged in each of the pressure valve 12 and the outlet valve 20, which limits the speed of the pressure build-up or pressure drop. Then a rapid pedal-operated braking can still be initiated via the isolating valve 7, which has no such aperture.

Claims

Patentansprüche claims
1. Hydraulische Bremsanlage mit mindestens einer Radbremse (8), in welcher über eine ein Trennventil aufweisende Bremsleitung (4,5), abhängig von der Stellung eineε Bremspedals (3) ein Bremsdruck auf- und abbaubar ist und welche über eine Druckleitung (9,10) mit einem Druckventil (12) an eine mit einer Pumpe (14) ausge¬ rüstete Fremddruckquelle (14,13) anschließbar ist und welche über eine Entlastungsleitung (18,17) mit einem Auslaßventil (20) an einem Volumenaufnehmer (16) anschließbar iεt, wobei der pedalabhängige Bremsdruck von einem Hauptzylinder 1 erzeugt wird, und das Trenn¬ ventil (7) das Druckventil (12) sowie das Auslaßventil (20) elektromagnetisch betätigbare 2-Wege-Ventile sind, dadurch gekennzeichnet, daß der Volumenaufnehmer ein Niederdruckspeicher (16) iεt, der an die Saugseite der einer Rückförderpumpe (14) angeschlossen iεt.1. Hydraulic brake system with at least one wheel brake (8), in which a brake pressure can be built up and released via a brake line (4, 5) having a isolating valve, depending on the position of a brake pedal (3), and which via a pressure line (9, 10) can be connected with a pressure valve (12) to an external pressure source (14, 13) equipped with a pump (14) and which can be connected via a relief line (18, 17) with an outlet valve (20) to a volume sensor (16) iεt, the pedal-dependent brake pressure being generated by a master cylinder 1, and the separating valve (7), the pressure valve (12) and the outlet valve (20) being electromagnetically operable 2-way valves, characterized in that the volume sensor is a low-pressure accumulator ( 16) is connected to the suction side of a return pump (14).
2. Bremsanlage nach Anspruch 1, dadurch gekennzeichnet, daß hydraulische Maßnahmen (22) getroffen sind, die eine unterbrechungsfreie Druckmittelversorgung der Saugseite mindestenε einer, einen Hochdruckspeicher (13) nachla-denden Pumpe (14, 26) auch für den Fall ermöglichen, daß der Niederdruckspeicher (16) leer ist.2. Brake system according to claim 1, characterized in that hydraulic measures (22) are taken which allow an uninterrupted supply of pressure medium to the suction side at least one, a high-pressure accumulator (13) recharging pump (14, 26) also in the event that the Low pressure accumulator (16) is empty.
3. Bremsanlage nach Anspruch 2, dadurch gekennzeichnet, daß die Saugseite der den Hochdruckspeicher (13) nachladenden Pumpe (14) über ein durch Unterdruck im Niederdruckspeicher (16) betätigtes Ansaugventil (22) an den Hauptzylinder (1) anschließbar ist. 3. Brake system according to claim 2, characterized in that the suction side of the pump (14) recharging the high pressure accumulator (13) can be connected to the master cylinder (1) via a suction valve (22) actuated by negative pressure in the low pressure accumulator (16).
PCT/EP1995/003737 1994-09-03 1995-09-22 Externally actuated hydraulic braking system WO1997010980A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE4431474A DE4431474A1 (en) 1994-09-03 1994-09-03 Hydraulic braking system for vehicle
PCT/EP1995/003737 WO1997010980A1 (en) 1994-09-03 1995-09-22 Externally actuated hydraulic braking system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4431474A DE4431474A1 (en) 1994-09-03 1994-09-03 Hydraulic braking system for vehicle
PCT/EP1995/003737 WO1997010980A1 (en) 1994-09-03 1995-09-22 Externally actuated hydraulic braking system

Publications (1)

Publication Number Publication Date
WO1997010980A1 true WO1997010980A1 (en) 1997-03-27

Family

ID=25939812

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1995/003737 WO1997010980A1 (en) 1994-09-03 1995-09-22 Externally actuated hydraulic braking system

Country Status (2)

Country Link
DE (1) DE4431474A1 (en)
WO (1) WO1997010980A1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0890492A3 (en) * 1997-07-08 1999-06-16 Toyota Jidosha Kabushiki Kaisha A brake force control apparatus for properly performing both an ABS function and a BA function
DE10063277A1 (en) * 2000-12-19 2002-06-20 Continental Teves Ag & Co Ohg Valve device for hydraulic system has casing containing stepped hydraulic piston
EP1106462A3 (en) * 1999-12-07 2003-08-27 Sumitomo (Sei) Brake Systems, Inc. Brake fluid pressure control device
WO2004012970A1 (en) * 2002-07-27 2004-02-12 Daimlerchrysler Ag Brake-pressure control device
KR100572496B1 (en) * 1997-01-15 2007-12-07 로베르트 보쉬 게엠베하 Hydraulic brake system

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19626289B4 (en) * 1996-07-01 2008-08-14 Continental Teves Ag & Co. Ohg Hydraulic brake system with a return pump
DE19644883B4 (en) * 1996-10-29 2009-09-24 Robert Bosch Gmbh Hydraulic vehicle brake system with a slip control device and / or a vehicle dynamics control device
WO1999008916A1 (en) * 1997-08-18 1999-02-25 Kelsey-Hayes Company Vehicular brake system arrangement for preventing pressure cross talk during vsc maneuver
DE19963760B4 (en) * 1999-12-30 2008-09-04 Robert Bosch Gmbh Hydraulic vehicle brake system
DE102012023319A1 (en) * 2012-11-29 2014-06-05 Lucas Automotive Gmbh Braking system for a land vehicle and method for controlling the braking system

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2538328A1 (en) * 1982-12-22 1984-06-29 Teves Gmbh Alfred HYDRAULIC BRAKE SYSTEM WITH TWO CIRCUITS, WITH BRAKE SLIDER CONTROL, IN PARTICULAR FOR MOTOR VEHICLE
JPS61108041A (en) * 1984-10-30 1986-05-26 Akebono Brake Chuo Gijutsu Kenkyusho:Kk Brake oil pressure controlling apparatus for car
JPS61202965A (en) * 1985-03-05 1986-09-08 Nippon Denso Co Ltd Anti-skid control device
EP0280740A1 (en) * 1986-08-30 1988-09-07 Sumitomo Electric Industries Limited Braking pressure control system
DE3737726A1 (en) * 1987-11-06 1989-05-18 Teves Gmbh Alfred Brake pressure control device
DE3844126A1 (en) * 1987-12-29 1989-07-13 Akebono Brake Ind Brake fluid pressure control device
JPH01182151A (en) * 1988-01-12 1989-07-20 Akebono Brake Ind Co Ltd Accumulator for vehicle antilock system
DE4028552A1 (en) * 1990-09-08 1992-03-12 Teves Gmbh Alfred Hydraulic brakes installation for motor vehicle - has servo pump fed via openbrakes circuit for non-driven wheels providing wheel-spincontrol
GB2248897A (en) * 1990-10-18 1992-04-22 Bosch Gmbh Robert Slip control braking system
DE4205041A1 (en) * 1991-02-20 1992-08-27 Tokico Ltd Vehicular hydraulic antilock braking and wheel-slip correction arrangement - incorporates two-channel two-position EM valves and fluid reservoirs disconnectable from pumped variable-vol. chambers
WO1992018363A1 (en) * 1991-04-19 1992-10-29 Alfred Teves Gmbh Braking system with a device for regulating both the braking and drive slip (asr)
DE4127040A1 (en) * 1991-08-16 1993-02-18 Teves Gmbh Alfred Four-wheel drive anti-skid brake system - has self priming hydraulic pump in closed system and with non-return valves to limit transfer of brake pulses
EP0566344A1 (en) * 1992-04-14 1993-10-20 Lucas Industries Public Limited Company Improvements in hydraulic braking systems for vehicles
DE4213740A1 (en) * 1992-04-25 1993-10-28 Bosch Gmbh Robert Accelerating braking engagement in drive slip regulating mode of motor vehicle - using hydraulic circuit, pressure medium reservoir, drive slip regulator and pump drawing pressure medium through suction line
DE4218402A1 (en) * 1992-06-04 1993-12-09 Kugelfischer G Schaefer & Co ABS system for motorbikes - has master cylinder connected to wheel cylinder via three valves, hydraulic pump and high/low pressure reservoir
DE4226646A1 (en) * 1992-08-12 1994-02-17 Bosch Gmbh Robert Hydraulic braking circuit for vehicle - incorporates wheel-spin controller and has hydraulic servo pump between master cylinder and wheels.

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3215739A1 (en) * 1982-04-28 1983-11-03 Robert Bosch Gmbh, 7000 Stuttgart DRIVE SLIP CONTROL
JPS63116966A (en) * 1986-10-31 1988-05-21 Sumitomo Electric Ind Ltd Vehicle brake pressure control device
DE3814045C2 (en) * 1988-04-26 1996-08-08 Teves Gmbh Alfred Slip-controlled hydraulic brake system
DE3940177C2 (en) * 1989-12-05 1999-03-18 Teves Gmbh Alfred Slip-controlled hydraulic vehicle brake system
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
DE4112137A1 (en) * 1991-04-13 1992-10-15 Bosch Gmbh Robert HYDRAULIC FOREIGN BRAKE SYSTEM WITH ANTI-BLOCKING PROTECTION AND DRIVE-SLIP CONTROL DEVICE, ESPECIALLY FOR MOTOR VEHICLES
JPH04353064A (en) * 1991-05-29 1992-12-08 Akebono Brake Ind Co Ltd Abs/tcs modulator
DE4201732A1 (en) * 1992-01-23 1993-07-29 Teves Gmbh Alfred BRAKE PRESSURE CONTROL DEVICE, IN PARTICULAR TO CONTROL THE DRIVE SLIP OF DRIVED WHEELS
DE4202388A1 (en) * 1992-01-29 1993-08-05 Bosch Gmbh Robert Vehicular hydraulic antilock braking system with wheel-slip controller - has blocking valve in pump induction line with steel ball and seating opened by impact piston

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2538328A1 (en) * 1982-12-22 1984-06-29 Teves Gmbh Alfred HYDRAULIC BRAKE SYSTEM WITH TWO CIRCUITS, WITH BRAKE SLIDER CONTROL, IN PARTICULAR FOR MOTOR VEHICLE
JPS61108041A (en) * 1984-10-30 1986-05-26 Akebono Brake Chuo Gijutsu Kenkyusho:Kk Brake oil pressure controlling apparatus for car
JPS61202965A (en) * 1985-03-05 1986-09-08 Nippon Denso Co Ltd Anti-skid control device
EP0280740A1 (en) * 1986-08-30 1988-09-07 Sumitomo Electric Industries Limited Braking pressure control system
DE3737726A1 (en) * 1987-11-06 1989-05-18 Teves Gmbh Alfred Brake pressure control device
DE3844126A1 (en) * 1987-12-29 1989-07-13 Akebono Brake Ind Brake fluid pressure control device
JPH01182151A (en) * 1988-01-12 1989-07-20 Akebono Brake Ind Co Ltd Accumulator for vehicle antilock system
DE4028552A1 (en) * 1990-09-08 1992-03-12 Teves Gmbh Alfred Hydraulic brakes installation for motor vehicle - has servo pump fed via openbrakes circuit for non-driven wheels providing wheel-spincontrol
GB2248897A (en) * 1990-10-18 1992-04-22 Bosch Gmbh Robert Slip control braking system
DE4205041A1 (en) * 1991-02-20 1992-08-27 Tokico Ltd Vehicular hydraulic antilock braking and wheel-slip correction arrangement - incorporates two-channel two-position EM valves and fluid reservoirs disconnectable from pumped variable-vol. chambers
WO1992018363A1 (en) * 1991-04-19 1992-10-29 Alfred Teves Gmbh Braking system with a device for regulating both the braking and drive slip (asr)
DE4127040A1 (en) * 1991-08-16 1993-02-18 Teves Gmbh Alfred Four-wheel drive anti-skid brake system - has self priming hydraulic pump in closed system and with non-return valves to limit transfer of brake pulses
EP0566344A1 (en) * 1992-04-14 1993-10-20 Lucas Industries Public Limited Company Improvements in hydraulic braking systems for vehicles
DE4213740A1 (en) * 1992-04-25 1993-10-28 Bosch Gmbh Robert Accelerating braking engagement in drive slip regulating mode of motor vehicle - using hydraulic circuit, pressure medium reservoir, drive slip regulator and pump drawing pressure medium through suction line
DE4218402A1 (en) * 1992-06-04 1993-12-09 Kugelfischer G Schaefer & Co ABS system for motorbikes - has master cylinder connected to wheel cylinder via three valves, hydraulic pump and high/low pressure reservoir
DE4226646A1 (en) * 1992-08-12 1994-02-17 Bosch Gmbh Robert Hydraulic braking circuit for vehicle - incorporates wheel-spin controller and has hydraulic servo pump between master cylinder and wheels.

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 10, no. 291 (M - 522) 3 October 1986 (1986-10-03) *
PATENT ABSTRACTS OF JAPAN vol. 11, no. 34 (M - 558)<2481> 31 January 1987 (1987-01-31) *
PATENT ABSTRACTS OF JAPAN vol. 13, no. 465 (M - 882) 20 October 1989 (1989-10-20) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100572496B1 (en) * 1997-01-15 2007-12-07 로베르트 보쉬 게엠베하 Hydraulic brake system
EP0890492A3 (en) * 1997-07-08 1999-06-16 Toyota Jidosha Kabushiki Kaisha A brake force control apparatus for properly performing both an ABS function and a BA function
US6027182A (en) * 1997-07-08 2000-02-22 Toyota Jidosha Kabushiki Kaisha Brake force control apparatus for properly performing both an ABS function and a BA function
EP1106462A3 (en) * 1999-12-07 2003-08-27 Sumitomo (Sei) Brake Systems, Inc. Brake fluid pressure control device
DE10063277A1 (en) * 2000-12-19 2002-06-20 Continental Teves Ag & Co Ohg Valve device for hydraulic system has casing containing stepped hydraulic piston
WO2004012970A1 (en) * 2002-07-27 2004-02-12 Daimlerchrysler Ag Brake-pressure control device
US7264318B2 (en) 2002-07-27 2007-09-04 Daimlerchrysler Ag Brake pressure control arrangement

Also Published As

Publication number Publication date
DE4431474A1 (en) 1996-03-07

Similar Documents

Publication Publication Date Title
DE3832023C2 (en) Starting slip control device (ASR)
DE3827366A1 (en) BLOCK-PROTECTED HYDRAULIC BRAKE SYSTEM
DE4108756A1 (en) MOTOR VEHICLE BRAKE SYSTEM WITH SLIP-RELATED REGULATION OF THE BRAKE PRESSURE
DE3927886A1 (en) HYDRAULIC BRAKE SYSTEM
DE3929464A1 (en) BRAKE CONTROL DEVICE FOR VEHICLES
DE4110851A1 (en) MOTOR VEHICLE BRAKE SYSTEM WITH BRAKE-SLIP AND DRIVE-SLIP-RELATED REGULATION OF THE BRAKE PRESSURE
EP0857131A1 (en) Brake system
DE19835250A1 (en) Hydraulic brake circuit for motor vehicles
DE69615894T2 (en) Antilock brake fluid pressure control device
WO1997010980A1 (en) Externally actuated hydraulic braking system
DE19905660A1 (en) Electronically regulated brake actuating system for motor vehicles has pressure source with proportional regulating valve that enables pressure produced by pump to be adjusted
DE19519234A1 (en) Vehicle anti-blocking brake control
WO1996019369A1 (en) Antiskid hydraulic braking system
WO1989001890A1 (en) Brake pressure regulating device
DE4021454A1 (en) HYDRAULIC BRAKE SYSTEM
DE4016308A1 (en) HYDRAULIC TWO-CIRCUIT BRAKE SYSTEM
DE19601268A1 (en) Hydraulic brake system with traction control
DE4335076C2 (en) Pressure control device for an anti-lock and traction-controlled vehicle brake system
DE3426456C2 (en) Brake system with slip control
DE19649010B4 (en) Hydraulic brake system with an external pressure source
EP0365769A1 (en) Hydraulic dual circuit braking system
DE2942552A1 (en) HYDRAULIC BRAKE AMPLIFIER
WO2023066587A1 (en) Electrohydraulic power braking system
WO2018054937A1 (en) Method for operating a brake system
DE4024627A1 (en) HYDRAULIC VEHICLE BRAKE SYSTEM WITH ANTI-BLOCKING PROTECTION AND DRIVE SLIP LIMITATION DEVICE

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): JP US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
122 Ep: pct application non-entry in european phase
点击 这是indexloc提供的php浏览器服务，不要输入任何密码和下载