WO1995020511A1 - Brake system with skid and traction control - Google Patents

Brake system with skid and traction control Download PDF

Info

Publication number
WO1995020511A1
WO1995020511A1 PCT/EP1995/000265 EP9500265W WO9520511A1 WO 1995020511 A1 WO1995020511 A1 WO 1995020511A1 EP 9500265 W EP9500265 W EP 9500265W WO 9520511 A1 WO9520511 A1 WO 9520511A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
line
pump
suction
valve
Prior art date
Application number
PCT/EP1995/000265
Other languages
German (de)
French (fr)
Inventor
Erhard Beck
Hans-Jörg INGENDAHL
Gottfried Dehio
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 WO1995020511A1 publication Critical patent/WO1995020511A1/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
    • B60T8/4863—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

Definitions

  • the present invention relates to a brake system according to the preamble of claim 1.
  • Such a brake system is known from DE-41 28 386 AI.
  • the suction accumulator is arranged in the brake line between the master cylinder and the isolation valve. It is an essentially cylindrical accumulator with two axially opposite pressure medium connections, one of which leads to the master cylinder and the other to the isolating valve.
  • the storage volume is surrounded by a substantially hollow cylindrical membrane, the outside of which is supported on the storage housing and is exposed to atmospheric pressure.
  • This suction reservoir is intended to provide a sufficient pressure medium volume for traction control even at low temperatures and a correspondingly high viscosity of the pump pressure medium.
  • Dip object of the present invention is therefore c " .i, to further improve the suction performance of the pump with traction control in a brake system of the type described in the introduction. This object is achieved by the features in the characterizing part of claim 1.
  • a plate membrane has the advantage over a hollow cylindrical membrane that it is much easier to assemble in the storage housing. Compared to a piston, it has the advantage that no additional sealing is required.
  • the suction accumulator can be precisely matched to the conditions of the brake system.
  • an adapted compression spring can overcome the throttling losses between the master cylinder and the suction accumulator due to its pretensioning, but the spring hardness is selected so that the compression spring yields when the pump is drawn in.
  • a throttle point on the side of the plate membrane facing the atmosphere prevents jerky emptying of the suction reservoir and fluttering of the plate membrane, which could lead to damage to the plate membrane surface.
  • Fig. 2 shows a suction accumulator for a brake system according to the invention.
  • a brake line 3 extends from the master cylinder 1 and leads via a separating valve 8 and an inlet valve 6 to a wheel brake 4.
  • the return line 5 leads via the outlet valve 7 and the low-pressure accumulator 9 to the suction side of the pump 11, a suction accumulator 10 being arranged directly in front of the suction side 11 and being biased by spring force in the accumulator filling direction.
  • the pressure side of the pump 11 connects to the brake line between the isolating valve 8 and the inlet valve 6 via a pressure line 12.
  • the suction side of the pump 11 is also connected via the suction line 13 and the switching valve 14 to the brake line 3 between the master cylinder 1 and the isolation valve 8. While the isolation valve 8 and the inlet valve 6 are normally open solenoid valves, the outlet valve 7 is a normally closed solenoid valve.
  • the changeover valve 14 is actuated hydraulically in that the master cylinder pressure closes the valve when the brake is operated by the pedal. If, in the case of a traction control system, the pump 11 is switched on, the volume of the suction accumulator 10 is available for delivery directly on its suction side.
  • the suction accumulator 10 automatically sucks in pressure medium through the changeover valve 14 and the master cylinder 1 from the pressure medium container 2 due to its preload. During the subsequent suction stroke of the pump 11, a sufficient amount of pressure medium is again available.
  • the other functioning of the brake system shown corresponds to the prior art.
  • the changeover valve 14 is therefore closed during a pedal-operated braking, while the isolating valve 8 is closed only for traction control, in which the changeover valve 14 is open, since no master cylinder pressure is built up.
  • FIG. 2 shows a preferred embodiment of a suction accumulator which can be used in a brake system according to FIG. 1. While Fig. 1 indicates the suction accumulator 10 only chemically, it can be seen in Fig. 2 that the storage chamber 15, which is connected to the return line 5 as shown in Fig. 1, is axially delimited by a plate membrane 16.
  • the housing of the suction accumulator 10 essentially consists of four parts, namely the housing body 17, the housing insert 18, the housing attachment 19 and the housing cover 20.
  • the essentially rotationally symmetrical housing body 17 has a cylindrical recess 21 and 22 from both axial sides . These two recesses 21 and 22 are connected to each other by a central, axially extending channel 23.
  • the recess 22 has radial atmosphere connections 24. It receives the housing cover 20, which is caulked to the housing body 17 at the edge for attachment to the housing.
  • the housing cover 20 is shaped like a pot, with the bottom of the pot facing outwards.
  • the housing cover 20 also has radial openings 25 which are axially offset from the atmosphere connections 24, so that it is not possible to insert a pointed object into the interior of the housing cover 20.
  • the housing cover 20 holds a flexible protective cap 26 on the housing body 17 so that no moisture can penetrate into the other recess 21.
  • the housing insert 18 is inserted, which essentially has the shape of a cylindrical sleeve, and serves to guide the piston 27. Both the housing insert 18 and the piston 27 are supported on the bottom surface of the recess 21 on the housing body 17. Housing insert 18 and piston 27 together in their rest position shown form a bowl-shaped support surface for the plate membrane 16, which is fixed in place on the housing by the housing attachment 19 which is sheared with the housing body 17.
  • the housing attachment 19 with the plate membrane 16 has an annular, radial contact surface, the inner radius of which is smaller than the outer radius of the housing insert 18, so that the housing insert 18 is also held fixed to the housing.
  • the piston 27, however, is axially displaceable. It has a plurality of radial annular grooves 28 on its circumference and is narrower with it Fit in the housing insert 18 that only a strongly throttled air flow can move towards or away from the plate membrane 16 along its circumference in the axial direction.
  • the plate membrane 16 is acted upon by the force of a compression spring 29, which is supported on the housing attachment 19, in the direction of the piston 27, so that the storage chamber 15 takes up its greatest volume even under atmospheric pressure. While the storage chamber 15 is filled with pressure medium, that is to say with brake fluid, the area located beyond the membrane is free of pressure medium. The throttling of the air flowing aixally along the circumference of the piston 27 prevents excessive stress on the plate membrane due to deformations that are too backward.

Abstract

The invention concerns a hydraulic brake system which, during skid control, operates in accordance with the recirculation principle, while a self-priming pump (11) draws in hydraulic fluid for traction control and delivers fluid to the brake (4) of a driven wheel. To ensure that a sufficiently large volume for traction control is available on the intake side of the pump, without high flow resistances occurring caused by the central valves in the master cylinder and by the change-over valve (14) in the intake line (13), the invention proposes that a suction reservoir (10) is fitted on the intake side of the pump (11), the reservoir automatically drawing in hydraulic fluid along the intake line (13) and through the change-over valve (14) and the central valves in the master cylinder (1) when the pump is carrying out its delivery stroke, i.e. displaces hydraulic fluid into the brake line.

Description

Bremsschlupf- und antriebsschlupfgergelte BremsanlageBrake slip and traction slip controlled brake system
Die vorliegende Erfindung betrifft eine Bremsanlage gemäß dem Oberbegriff des Anspruches 1.The present invention relates to a brake system according to the preamble of claim 1.
Eine derartige Bremsanlage ist aus der DE-41 28 386 AI bekannt. In der bekannten Bremsanlage ist der Saugspeicher in der Bremsleitung zwischen Hauptzylinder und Trennventil angeordnet. Es handelt sich um einen im wesentlichen zylindrischen Speicher mit zwei axial gegenüberliegenden Druckmittelanschlüssen, von denen einer zum Hauptzylinder und der andere zum Trennventil führt. Das Speichervolumen ist von einer im wesentlichen hohlzylinderförmigen Membran umgeben deren Außenseite sich am Speichergehäuse abstützt und Atmosphärendruck ausgesetzt ist. Dieser Saugspeicher soll dazu dienen, auch bei tiefen Temperaturen und entsprechend hoher Viskosität des Druckmittels der Pumpe ein zur Antriebsschlupfregelung ausreichendes Druckmittelvolumen zur Verfügung zu stellen. Zwar hat die Pumpe bei der Ansaugung dieses Druckmittelvolumens nicht mehr die engen Querschnitte des Hauptzylinders zu überwinden, jedoch bleiben lange Leitungswege und ein Drosseleffekt am Umschaltventil bestehen, wenn das Saugspeichervolumen zur Saugseite der Pumpe gelangen soll. Dip Aufgabe der vorliegenden Erfindung besteht daher c" .i, bei einer Bremsanlage der eingangs beschriebenen Art die Ansaugleistung der Pumpe bei Antriebsschlupfregelung weiter zu verbessern. Diese Aufgabe wird gelöst durch die Merkmale im kennzeichnenden Teil des Anspruches 1. Durch Anordnung des Saugspeichers unmittelbar an der Saugseite der Pumpe entfallen lange Leitungswege, so daß das Druckmittelvolumen sofort zur Verfügung steht.Such a brake system is known from DE-41 28 386 AI. In the known brake system, the suction accumulator is arranged in the brake line between the master cylinder and the isolation valve. It is an essentially cylindrical accumulator with two axially opposite pressure medium connections, one of which leads to the master cylinder and the other to the isolating valve. The storage volume is surrounded by a substantially hollow cylindrical membrane, the outside of which is supported on the storage housing and is exposed to atmospheric pressure. This suction reservoir is intended to provide a sufficient pressure medium volume for traction control even at low temperatures and a correspondingly high viscosity of the pump pressure medium. Although the pump no longer has to overcome the narrow cross-sections of the master cylinder when this pressure medium volume is sucked in, long piping paths and a throttling effect remain at the changeover valve if the suction storage volume is to reach the suction side of the pump. Dip object of the present invention is therefore c " .i, to further improve the suction performance of the pump with traction control in a brake system of the type described in the introduction. This object is achieved by the features in the characterizing part of claim 1. By arranging the suction accumulator directly on the suction side of the pump, long line paths are eliminated, so that the pressure medium volume is immediately available.
Die Verwendung einer Tellermembran hat gegenüber einer hohlzylinderförmigen Membran den Vorteil, daß ihre Montage im Speichergehäuse wesentlich einfacher ist. Gegenüber einem Kolben hat sie den Vorteil, daß keine zusätzliche Abdichtung erforderlich ist.The use of a plate membrane has the advantage over a hollow cylindrical membrane that it is much easier to assemble in the storage housing. Compared to a piston, it has the advantage that no additional sealing is required.
Durch die Vorspannung der Tellermembran mittels einer Druckfeder läßt sich der Saugspeicher genau auf die Gegebenheiten der Bremsanlage abstimmen. So kann eine angepaßte Druckfeder durch ihre Vorspannung die Drosselverluste zwischen Hauptzylinder und Saugspeicher überwinden, wobei die Federhärte aber so gewählt ist, daß die Druckfeder beim Ansaugen der Pumpe nachgibt.By prestressing the plate membrane using a compression spring, the suction accumulator can be precisely matched to the conditions of the brake system. For example, an adapted compression spring can overcome the throttling losses between the master cylinder and the suction accumulator due to its pretensioning, but the spring hardness is selected so that the compression spring yields when the pump is drawn in.
Eine Drosselstelle auf der der Atmosphäre zugewandten Seite der Tellermembran verhindert ruckartige Entleerungen des Saugspeichers und ein Flattern der Tellermembran, was zu einer Beschädigung der Tellermembranfläche führen könnte.A throttle point on the side of the plate membrane facing the atmosphere prevents jerky emptying of the suction reservoir and fluttering of the plate membrane, which could lead to damage to the plate membrane surface.
Einer Beschädigung der Membran wird weiterhin dadurch vorgebeugt, daß sie atmosphärenseitig großflächig abgestützt ist. Eine nähere Erläuterung des Erfindungsgedankens findet sich in der folgenden Beschreibung einer bevorzugten Ausführungsform der Erfindung anhand von zwei Figuren. Es zeigt:Damage to the membrane is further prevented by supporting it over a large area on the atmosphere side. A more detailed explanation of the inventive concept can be found in the following description of a preferred embodiment of the invention using two figures. It shows:
Fig. 1 eine erfindungsgemäße Bremsanlage,1 shows a brake system according to the invention,
Fig. 2 einen Saugspeicher für eine erfindungsgemäße Bremsanlage.Fig. 2 shows a suction accumulator for a brake system according to the invention.
Die Bremsanlage nach Fig. 1 besitzt einen Hauptzylinder 1 welcher mit einem Druckmittelbehälter 2 in Verbindung steht. Vom Hauptzylinder 1 geht eine Bremsleitung 3 aus, welche über, ein Trennventil 8 und ein Einlaßventil 6 zu einer Radbremse 4 führt. Von der Radbremse 4, welche einem angetriebenen Rad zugeordnet ist, führt die Rücklaufleitung 5 über das Auslaßventil 7 und den Niederdruckspeicher 9 zur Saugseite der Pumpe 11, wobei unmittelbar vor der Saugseite 11 ein Saugspeicher 10 angeordnet ist, welcher durch Federkraft in Speicherfüllrichtung vorgespannt ist. Die Druckseite der Pumpe 11 schließt über eine Druckleitung 12 an die Bremsleitung zwischen dem Trennventil 8 und dem Einlaßventil 6 an. Die Saugseite der Pumpe 11 ist außerdem über die Saugleitung 13 und das Umschaltventil 14 an die Bremsleitung 3 zwischen dem Hauptzylinder 1 und dem Trennventil 8 angeschlossen. Während das Trennventil 8 und das Einlaßventil 6 stromlos offene Elektromagnetventile sind, ist das Auslaßventil 7 ein stromlos geschlossenes Elektromagnetventil. Das Umschaltventil 14 wird hydraulisch betätigt, indem der Hauptzylinderdruck bei pedalbetätigter Bremsung das Ventil schließt. Wenn im Falle einer Antriebsschlupfregelung die Pumpe 11 eingeschaltet wird, steht unmittelbar an ihrer Saugseite das Volumen des Saugspeichers 10 zur Förderung zur Verfügung. Während die Pumpe 11 ihre Förderung vollzieht, also in Phasen, in welchen die Pumpe 11 Druckmittel in die Bremsleitung 3 verdrängt, saugt der Saugspeicher 10 durch seine Vorspannung selbstätig Druckmittel über das Umschaltventil 14 und den Hauptzylinder 1 aus dem Druckmittelbehälter 2 nach. Beim darauffolgenden Saughub der Pumpe 11 steht also wieder eine ausreichende Menge Druckmittel zur Verfügung. Die sonstige Funktionsweise der dargestellten Bremsanlage entspricht dem Stand der Technik. Das Umschaltventil 14 ist bei einer pedalbetätigten Bremsung also geschlossen, während das Trennventil 8 nur zu einer Antriebsschlupfregelung geschlossen wird, bei welcher das Umschaltventil 14 geöffnet ist, da kein Hauptzylinderdruck aufgebaut wird.1 has a master cylinder 1 which is connected to a pressure medium container 2. A brake line 3 extends from the master cylinder 1 and leads via a separating valve 8 and an inlet valve 6 to a wheel brake 4. From the wheel brake 4, which is assigned to a driven wheel, the return line 5 leads via the outlet valve 7 and the low-pressure accumulator 9 to the suction side of the pump 11, a suction accumulator 10 being arranged directly in front of the suction side 11 and being biased by spring force in the accumulator filling direction. The pressure side of the pump 11 connects to the brake line between the isolating valve 8 and the inlet valve 6 via a pressure line 12. The suction side of the pump 11 is also connected via the suction line 13 and the switching valve 14 to the brake line 3 between the master cylinder 1 and the isolation valve 8. While the isolation valve 8 and the inlet valve 6 are normally open solenoid valves, the outlet valve 7 is a normally closed solenoid valve. The changeover valve 14 is actuated hydraulically in that the master cylinder pressure closes the valve when the brake is operated by the pedal. If, in the case of a traction control system, the pump 11 is switched on, the volume of the suction accumulator 10 is available for delivery directly on its suction side. While the pump 11 carries out its delivery, that is, in phases in which the pump 11 displaces pressure medium into the brake line 3, the suction accumulator 10 automatically sucks in pressure medium through the changeover valve 14 and the master cylinder 1 from the pressure medium container 2 due to its preload. During the subsequent suction stroke of the pump 11, a sufficient amount of pressure medium is again available. The other functioning of the brake system shown corresponds to the prior art. The changeover valve 14 is therefore closed during a pedal-operated braking, while the isolating valve 8 is closed only for traction control, in which the changeover valve 14 is open, since no master cylinder pressure is built up.
Fig. 2 zeigt eine bevorzugte Ausführungsform eines Saugspeichers, der in einer Bremsanlage nach Fig. 1 Verwendung finden kann. Während Fig. 1 den Saugspeicher 10 nur s^chematisch andeutet, ist in Fig. 2 zu erkennen, daß die Speicherkammer 15, welcher wie in Fig. 1 dargestellt an die Rücklaufleitung 5 angeschlossen ist, axial von einer Tellermembran 16 begrenzt wird. Das Gehäuse des Saugspeichers 10 besteht im wesentlichen aus vier Teilen, nämlich dem Gehäusekörper 17, dem Gehäuseeinsatz 18, dem Gehäuseaufsatz 19 und dem Gehäusedeckel 20. Der im wesentlichen rotationssymmetrische Gehäusekörper 17 weist von beiden axialen Seiten her jeweils eine zylindrische Ausnehmung 21 bzw. 22 auf. Diese zwei Ausnehmungen 21 und 22 sind durch einen zentralen, axial verlaufenden Kanal 23 miteinander verbunden. Die Ausnehmung 22 besitzt radiale Atmosphärenanschlüsse 24. Sie nimmt den Gehäusedeckel 20 auf, welcher zur gehäusefesten Anbringung mit dem Gehäusekörper 17 am Rand verstemmt ist. Der Gehäusedeckel 20 ist topfartig geformt, wobei der Topfboden nach außen weist. Auch der Gehäusedeckel 20 weist radiale Öffnungen 25 auf, welche gegenüber den Atmosphärenanschlüssen 24 axial versetzt sind, so daß ein Einführen eines spitzen Gegenstandes in den Innenraum des Gehäusedeckels 20 nicht möglich ist. Zum weiteren Schutz des Innenraums hält der Gehäusedeckel 20 eine flexible Schutzkappe 26 am Gehäusekörper 17 fest, so daß keine Feuchtigkeit in die andere Ausnehmung 21 eindringen kann.FIG. 2 shows a preferred embodiment of a suction accumulator which can be used in a brake system according to FIG. 1. While Fig. 1 indicates the suction accumulator 10 only chemically, it can be seen in Fig. 2 that the storage chamber 15, which is connected to the return line 5 as shown in Fig. 1, is axially delimited by a plate membrane 16. The housing of the suction accumulator 10 essentially consists of four parts, namely the housing body 17, the housing insert 18, the housing attachment 19 and the housing cover 20. The essentially rotationally symmetrical housing body 17 has a cylindrical recess 21 and 22 from both axial sides . These two recesses 21 and 22 are connected to each other by a central, axially extending channel 23. The recess 22 has radial atmosphere connections 24. It receives the housing cover 20, which is caulked to the housing body 17 at the edge for attachment to the housing. The housing cover 20 is shaped like a pot, with the bottom of the pot facing outwards. The housing cover 20 also has radial openings 25 which are axially offset from the atmosphere connections 24, so that it is not possible to insert a pointed object into the interior of the housing cover 20. To further protect the interior, the housing cover 20 holds a flexible protective cap 26 on the housing body 17 so that no moisture can penetrate into the other recess 21.
In die Ausnehmung 21 ist der Gehäuseeinsatz 18 eingesetzt, welcher im wesentlichen die Form einer zylindrischen Hülse hat, und zur Führung des Kolbens 27 dient. Sowohl der Gehäuseeinsatz 18 als auch der Kolben 27 stützen sich an der Bodenfläche der Ausnehmung 21 am Gehäusekörper 17 ab. Gehäuseeinsatz 18 und Kolben 27 bilden zusammen in ihrer dargestellten Ruhelage eine schüsseiförmige Stützfläche für die Tellermembran 16, welche durch den mit dem Gehäusekörper 17 verscherten Gehäuseaufsatz 19 gehäusefest fixiert ist. Dabei weist der Gehäuseaufsatz 19 mit der Tellermembran 16 eine ringförmige, radiale Berührungsfläche auf, deren Innenradius kleiner ist als der Außenradius des Gehäuseeinsatzes 18, so daß auch der Gehäuseeinsatz 18 gehäusefest gehalten wird. Der Kolben 27 hingegen ist axial verschiebbar. Er weist an seinem Umfang mehrere radiale Ringnuten 28 auf und ist mit so enger Passung im Gehäuseeinsatz 18 geführt, daß sich an seinem Umfang entlang in axialer Richtung nur ein stark gedrosselter Luftstrom zur Tellermembran 16 hin oder von dieser wegbewegen kann.In the recess 21, the housing insert 18 is inserted, which essentially has the shape of a cylindrical sleeve, and serves to guide the piston 27. Both the housing insert 18 and the piston 27 are supported on the bottom surface of the recess 21 on the housing body 17. Housing insert 18 and piston 27 together in their rest position shown form a bowl-shaped support surface for the plate membrane 16, which is fixed in place on the housing by the housing attachment 19 which is sheared with the housing body 17. The housing attachment 19 with the plate membrane 16 has an annular, radial contact surface, the inner radius of which is smaller than the outer radius of the housing insert 18, so that the housing insert 18 is also held fixed to the housing. The piston 27, however, is axially displaceable. It has a plurality of radial annular grooves 28 on its circumference and is narrower with it Fit in the housing insert 18 that only a strongly throttled air flow can move towards or away from the plate membrane 16 along its circumference in the axial direction.
Die Tellermembran 16 ist von der Kraft einer Druckfeder 29, welche sich am Gehäuseaufsatz 19 abstützt, in Richtung auf den Kolben 27 hin beaufschlagt, so daß auch unter Atmosphärendruck die Speicherkammer 15 ihr größtes Volumen einnimmt. Während die Speicherkammer 15 mit Druckmittel gefüllt ist, also mit Bremsflüssigkeit, ist der jenseits der Membran befindliche Bereich druckmittelfrei. Die Drosselung der aixal am Umfang des Kolbens 27 entlang strömenden Luft verhindert eine zu starke Beanspruchung der Tellermembran aufgrund von zu rückartigen Verformungen. The plate membrane 16 is acted upon by the force of a compression spring 29, which is supported on the housing attachment 19, in the direction of the piston 27, so that the storage chamber 15 takes up its greatest volume even under atmospheric pressure. While the storage chamber 15 is filled with pressure medium, that is to say with brake fluid, the area located beyond the membrane is free of pressure medium. The throttling of the air flowing aixally along the circumference of the piston 27 prevents excessive stress on the plate membrane due to deformations that are too backward.
BezugszeichenlisteReference list
1 Hauptzylinder1 master cylinder
2 Druckmittelbehälter2 pressure medium tanks
3 Bremsleitung3 brake line
4 Radbremse4 wheel brake
5 Rücklaufleitung5 return line
6 Einlaßventil6 inlet valve
7 Auslaßventil7 exhaust valve
8 Trennventil8 isolation valve
9 Niederdruckspeicher9 low pressure accumulators
10 Saugspeicher10 suction tanks
11 Pumpe11 pump
12 Druckleitung12 pressure line
13 Saugleitung13 suction line
14 Umschaltventil14 changeover valve
15 Speicherkammer15 storage chamber
16 Tellermembran16 plate membrane
17 Gehäusekörper17 housing body
18 Gehäuseeinsatz18 housing insert
19 Gehäuseaufsatz19 housing attachment
20 Gehäusedeckel20 housing cover
21 Ausnehmung21 recess
22 Ausnehmung22 recess
23 Kanal23 channel
24 Atmosphärenanschlüsse24 atmosphere connections
25 Öffnungen25 openings
26 Schutzkappe26 protective cap
27 Kolben27 pistons
28 Ringnuten28 ring grooves
29 Druckfeder 29 compression spring

Claims

PatentanprüchePatent claims
Bremsanlage mit einer Einrichtung zur Regelung des BremsSchlupfes und des Antriebsschlupfes, mit einem Hauptzylinder (1) der an einen DruckmittelbehälterBrake system with a device for regulating brake slip and drive slip, with a master cylinder (1) which is connected to a pressure medium container
(2) angeschlossen ist, mit mindestens einer Radbremse (4) eines angetriebenen Rades, mit einer Bremsleitung (3) vom Hauptzylinder (1) zur Radbremse (4), mit einer Rücklaufleitung (5) von der Radbremse (4) zur Saugseite einer selbstansaugenden Pumpe (11), mit einem Einlaßventil (6) in der Bremsleitung (3) unter einem Auslaßventil (7) in der Rücklaufleitung (5), mit einem Trennventil (8) in der Bremsleitung (3) zwischen Hauptzylinder (1) und Einlaßventil (6), mit einer Saugleitung (13) welche zwischen Hauptzylinder (1) und Trennventil (8) von der Bremsleitung (3) abzweigt und an die(2) is connected, with at least one wheel brake (4) of a driven wheel, with a brake line (3) from the master cylinder (1) to the wheel brake (4), with a return line (5) from the wheel brake (4) to the suction side of a self-priming Pump (11), with an inlet valve (6) in the brake line (3) under an outlet valve (7) in the return line (5), with a separating valve (8) in the brake line (3) between the master cylinder (1) and the inlet valve ( 6), with a suction line (13) which branches off from the brake line (3) between the master cylinder (1) and the isolating valve (8) and to the
Rücklaufleitung (5) zwischen Auslaßventil (7) und Pumpe (11) anschließt mit einem Umschaltventil (14) in der Saugleitung (13) mit einer Druckleitung (12) von der Druckseite der Pumpe (11) zur BremsleitungReturn line (5) between outlet valve (7) and pump (11) connects to a changeover valve (14) in the suction line (13) with a pressure line (12) from the pressure side of the pump (11) to the brake line
(3) zwischen Trennventil ((8) und Einlaßventil (6) sowie mit einem bei Atmosphärendruck gefüllten Saugspeicher (10) in der Leitungsverbindung zwischen Hauptzylinder (1) und Saugseite der Pumpe (11) dadurch g e k e n n z e i c h n e t, daß der Saugspeicher (10) zwischen dem Umschaltventil (14) und der Saugseite der Pumpe (11) angeordnet ist. Bremsanlage nach Anspruch 1, dadurch g e k e n n z e i c h n e t, daß der Saugspeicher (10) in einem Gehäuse (17,18,19,20) eine von einer Tellermembran (16) begrenzte Speicherkammer (15) aufweist.(3) between the separating valve ((8) and inlet valve (6) and with a suction accumulator (10) filled at atmospheric pressure in the line connection between the master cylinder (1) and the suction side of the pump (11), characterized in that the suction accumulator (10) between the Switching valve (14) and the suction side of the pump (11) is arranged. Brake system according to claim 1, characterized in that the suction accumulator (10) has a storage chamber (15) delimited by a plate membrane (16) in a housing (17,18,19,20).
Bremsanlage nach Anspruch 2, dadurch g e k e n n z e i c h n e t, daß in der Speicherkammer (15) eine Druckfeder (29) angeordnet ist, die die Tellermembran (16) in Richtung auf eine Vergrößerung des Volumens der Speicherkammer (15) hin beaufschlagt.Brake system according to claim 2, characterized in that a compression spring (29) is arranged in the storage chamber (15), which acts on the plate membrane (16) in the direction of increasing the volume of the storage chamber (15).
Bremsanlage nach einem der Ansprüche 2 und 3, dadurch g e k e n n z e i c h n e t, daß die der Speicherkammer (15) abgewandte Seite der Tellermembran (16) über eine Drosselstelle (Kolben 27/Gehäuseeinsatz 18) mit Atmosphärendruck in Verbindung steht.Brake system according to one of claims 2 and 3, characterized in that the side of the plate membrane (16) facing away from the storage chamber (15) is connected to atmospheric pressure via a throttle point (piston 27/housing insert 18).
Bremsanlage nach einem der Ansprüche 3 und 4, dadurch g e k e n n z e i c h n e t, daß die der Speicherkammer (15) abgewandte Seite der Tellermembran (16) zentral an einer Stirnseite eines Kolbens (27) anliegt, welche von der Tellermembran (16) durch die Kraft der Druckfeder (29) gegen einen gehäusefesten Anschlag gedrückt wird, welcher die Ruhelage von Tellermembran (16) und Kolben (27) bestimmt. Brake system according to one of claims 3 and 4, characterized in that the side of the plate membrane (16) facing away from the storage chamber (15) rests centrally on an end face of a piston (27), which is supported by the plate membrane (16) by the force of the compression spring ( 29) is pressed against a stop fixed to the housing, which determines the rest position of the plate membrane (16) and piston (27).
PCT/EP1995/000265 1994-01-29 1995-01-25 Brake system with skid and traction control WO1995020511A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19944402734 DE4402734C2 (en) 1994-01-29 1994-01-29 Brake slip and traction slip controlled brake system
DEP4402734.6 1994-01-29

Publications (1)

Publication Number Publication Date
WO1995020511A1 true WO1995020511A1 (en) 1995-08-03

Family

ID=6509030

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1995/000265 WO1995020511A1 (en) 1994-01-29 1995-01-25 Brake system with skid and traction control

Country Status (2)

Country Link
DE (1) DE4402734C2 (en)
WO (1) WO1995020511A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009030707A1 (en) * 2007-09-05 2009-03-12 Continental Teves Ag & Co. Ohg Brake system for a motor vehicle

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19544443A1 (en) * 1995-11-29 1997-06-05 Teves Gmbh Alfred Hydraulic twin-circuit brake system with pedal-operated tandem main cylinder
DE19601268A1 (en) * 1996-01-16 1997-07-17 Teves Gmbh Alfred Hydraulic brake system with traction control
DE19626305A1 (en) * 1996-07-01 1998-01-08 Teves Gmbh Alfred Hydraulic braking system with a device for active braking
DE19841152A1 (en) * 1998-04-07 1999-10-14 Continental Teves Ag & Co Ohg Anti-lock motor vehicle brake system
DE19850910A1 (en) * 1998-11-05 2000-05-11 Bosch Gmbh Robert Pressure fluid accumulator for vehicle brake systems
DE19953001A1 (en) * 1999-11-04 2001-05-10 Continental Teves Ag & Co Ohg Hydraulic motor vehicle braking system with wheel slip regulation and brake pressure transmitter connected hydraulically with at least one pair of wheel brakes also pressure modulation
DE102014221544A1 (en) 2014-10-23 2016-04-28 Continental Teves Ag & Co. Ohg Hydraulic unit for a slip-controlled brake system
DE102021202290A1 (en) 2021-03-09 2022-09-15 Continental Teves Ag & Co. Ohg pulsation dampener

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0281754A (en) * 1988-09-16 1990-03-22 Akebono Brake Res & Dev Center Ltd Combined antilock and traction controller for vehicle
DE4128386A1 (en) * 1991-08-27 1993-03-04 Bosch Gmbh Robert Vehicular hydraulic braking system with wheel-slip control arrangement - has unpressurised passive brake fluid reservoirs connected on master cylinder side to wheel brake supply lines
EP0539898A1 (en) * 1991-10-30 1993-05-05 Sumitomo Electric Industries, Limited Brake fluid pressure control device
WO1993009010A1 (en) * 1991-11-02 1993-05-13 Alfred Teves Gmbh Regulated slip hydraulic brake system
DE4138027A1 (en) * 1991-11-19 1993-05-27 Teves Gmbh Alfred Brake pressure regulator for vehicle hydraulic braking system - has electromagnetically-operated blocking device for low pressure reservoir coupled to brake fluid return line
JPH05178180A (en) * 1991-12-26 1993-07-20 Aisin Seiki Co Ltd Controller for braking and driving force
WO1993019960A1 (en) * 1992-04-03 1993-10-14 Itt Automotive Europe Gmbh Hydraulic switch valve for a vehicle brake system
DE4213205A1 (en) * 1992-04-22 1993-10-28 Teves Gmbh Alfred Braking pressure regulating system for hydraulic braking system of motor vehicle - has main braking cylinder and at least one wheel brake cylinder connected to main cylinder and braking pressure control circuit between main and wheel cylinders
DE4336464A1 (en) * 1993-10-26 1995-04-27 Bosch Gmbh Robert Hydraulic brake system

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3709265A1 (en) * 1987-03-20 1988-09-29 Teves Gmbh Alfred Hydraulic brake system with brake slip control
DE3940177C2 (en) * 1989-12-05 1999-03-18 Teves Gmbh Alfred Slip-controlled hydraulic vehicle brake system
DE4014052A1 (en) * 1990-05-02 1991-11-07 Teves Gmbh Alfred Electronic pressure regulator for vehicular hydraulic braking system - establishes corrective connection between brake fluid reservoirs serving master cylinder and two-pump fluid pressure modulator
DE4102864A1 (en) * 1990-05-18 1991-11-21 Bosch Gmbh Robert HYDRAULIC TWO-CIRCUIT BRAKE SYSTEM
DE4039661A1 (en) * 1990-12-12 1992-06-17 Bosch Gmbh Robert Hydraulic braking system with antilock and wheel-slip control - has energy storage spring in fluid cylinder supplying high-pressure pump in driven-wheel braking circuit
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
DE4218402B4 (en) * 1992-06-04 2005-08-18 Fte Automotive Gmbh & Co. Kg Anti-lock control system
DE4219450A1 (en) * 1992-06-13 1993-12-16 Teves Gmbh Alfred Hydraulic servo brakes with ABS control - has variable flow restriction to modulate inlet side of servo pump to reduce brake pedal vibrations.

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0281754A (en) * 1988-09-16 1990-03-22 Akebono Brake Res & Dev Center Ltd Combined antilock and traction controller for vehicle
DE4128386A1 (en) * 1991-08-27 1993-03-04 Bosch Gmbh Robert Vehicular hydraulic braking system with wheel-slip control arrangement - has unpressurised passive brake fluid reservoirs connected on master cylinder side to wheel brake supply lines
EP0539898A1 (en) * 1991-10-30 1993-05-05 Sumitomo Electric Industries, Limited Brake fluid pressure control device
WO1993009010A1 (en) * 1991-11-02 1993-05-13 Alfred Teves Gmbh Regulated slip hydraulic brake system
DE4138027A1 (en) * 1991-11-19 1993-05-27 Teves Gmbh Alfred Brake pressure regulator for vehicle hydraulic braking system - has electromagnetically-operated blocking device for low pressure reservoir coupled to brake fluid return line
JPH05178180A (en) * 1991-12-26 1993-07-20 Aisin Seiki Co Ltd Controller for braking and driving force
WO1993019960A1 (en) * 1992-04-03 1993-10-14 Itt Automotive Europe Gmbh Hydraulic switch valve for a vehicle brake system
DE4213205A1 (en) * 1992-04-22 1993-10-28 Teves Gmbh Alfred Braking pressure regulating system for hydraulic braking system of motor vehicle - has main braking cylinder and at least one wheel brake cylinder connected to main cylinder and braking pressure control circuit between main and wheel cylinders
DE4336464A1 (en) * 1993-10-26 1995-04-27 Bosch Gmbh Robert Hydraulic brake system

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 14, no. 276 (M - 984)<4219> 14 June 1990 (1990-06-14) *
PATENT ABSTRACTS OF JAPAN vol. 17, no. 598 (M - 1504) 2 November 1993 (1993-11-02) *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009030707A1 (en) * 2007-09-05 2009-03-12 Continental Teves Ag & Co. Ohg Brake system for a motor vehicle
US8840196B2 (en) 2007-09-05 2014-09-23 Continental Teves Ag & Co. Ohg Brake system for a motor vehicle

Also Published As

Publication number Publication date
DE4402734A1 (en) 1995-08-03
DE4402734C2 (en) 2003-06-05

Similar Documents

Publication Publication Date Title
DE4035527C2 (en) Hydraulic brake system
DE4128386C2 (en) Hydraulic brake system for motor vehicles with a traction control system
EP0324103B1 (en) Brake installation with antilock and driving slip regulation
DE3433345C2 (en)
EP0817738A2 (en) Hydraulic vehicle brake system
WO1998012434A1 (en) Piston pump
DE102010064035A1 (en) Method for controlling a wheel brake pressure of a hydraulic vehicle brake system
WO1993009010A1 (en) Regulated slip hydraulic brake system
DE4402734C2 (en) Brake slip and traction slip controlled brake system
DE3511972A1 (en) PRESSURE MODULATOR DEVICE FOR BRAKING REINFORCEMENT AND ANTI-BLOCKING CONTROL
EP0586625A1 (en) Hydraulic switch valve for a vehicle brake system.
EP1090228A1 (en) Piston pump
DE4011329A1 (en) HYDRAULIC TWO-CIRCUIT BRAKE SYSTEM
DE19626304A1 (en) Hydraulic brake system with a pre-charging device
DE3603742C2 (en)
DE19527402A1 (en) pump
DE4020450A1 (en) HYDRAULIC TWO-CIRCUIT BRAKE SYSTEM
DE19738524C5 (en) Piston pump for generating a fluid pressure
DE3804851A1 (en) HYDRAULIC AMPLIFIER AND PRESSURE SOURCE FOR A HYDRAULIC AMPLIFIER
DE1947846B2 (en) Hydraulic brake system for vehicles
EP0447796B1 (en) Hydraulic circuit brake system
EP0749380A1 (en) Hydraulic braking system with brake and drive slip control
EP0918158A2 (en) Piston pump
DE102013222949B4 (en) Piston pump
EP0625106A1 (en) Slip-controlled brake system.

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): CZ JP KR SK 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