EP0898531A1 - Hydraulically actuated stop valve and hydraulic brake system for a vehicle - Google Patents

Hydraulically actuated stop valve and hydraulic brake system for a vehicle

Info

Publication number
EP0898531A1
EP0898531A1 EP98902944A EP98902944A EP0898531A1 EP 0898531 A1 EP0898531 A1 EP 0898531A1 EP 98902944 A EP98902944 A EP 98902944A EP 98902944 A EP98902944 A EP 98902944A EP 0898531 A1 EP0898531 A1 EP 0898531A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
shut
actuating element
brake cylinder
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP98902944A
Other languages
German (de)
French (fr)
Inventor
Norbert Alaze
Heinz Siegel
Rolf Hummel
Thomas Michl
Martin Maier
Günther HOHL
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 claimed from DE19732988A external-priority patent/DE19732988A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0898531A1 publication Critical patent/EP0898531A1/en
Withdrawn legal-status Critical Current

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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/341—Systems characterised by their valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7835—Valve seating in direction of flow

Definitions

  • the invention relates to a hydraulically actuated shut-off valve with the features of the preamble of claim 1 and to a hydraulic vehicle brake system that can be equipped with such a shut-off valve with the features of the preamble of claim 7.
  • Such a valve is known from EP 0 606 840 B1.
  • the known valve has a valve housing with an intermediate wall on which a valve seat is formed.
  • a piston is arranged as an actuating element on one side of the intermediate wall, said piston being pressed in the direction of the intermediate wall by a valve opening spring and being displaceable away from the intermediate wall by pressurization.
  • On the other side of the intermediate wall there is a valve ball as a valve closing body, which is lifted off the valve seat by the piston and is pressed in the direction of the valve seat by a valve closing spring which is weaker than the valve opening spring.
  • the well-known valve is in opened in its basic position and is closed by applying a pressure that is above a closing pressure.
  • the known valve has the disadvantage that its production is complex.
  • the valve housing must be machined on both sides of the valve seat. It is large and requires two springs that are matched to one another to set the desired switching pressures. By using two springs working against each other, there is a great risk that the switching pressures will change in the course of valve use.
  • This valve is part of a hydraulic vehicle brake system which is set up to limit drive slip by automatically braking drive wheels and for this purpose has at least one self-priming feed pump which is supplied with brake fluid from the reservoir by the open valve and by a master brake cylinder.
  • the hydraulic vehicle brake system also contains pressure build-up and pressure relief valve arrangements connected to wheel brake cylinders, by means of which brake fluid delivered by the feed pump for generating brake pressure, for example in traction control mode, can be supplied to at least one wheel brake cylinder.
  • the shut-off valve according to the invention with the features of claim 1 has only three moving parts, namely the valve closing body, the actuating element and a rocker element which transmits a movement of the actuating element to the valve closing body.
  • the geometry of these parts is simple and therefore inexpensive to manufacture. They can be accommodated in a cylindrical bore, which can have a cone on a ring step as a valve seat.
  • the shut-off valve according to the invention can be produced inexpensively with little effort, it is maintenance-free and is subject to only slight wear, so that it has a long service life.
  • the shut-off valve according to the invention is intended in particular for use as an intake valve for a hydraulic vehicle brake system having a pump, that is to say, for example, an anti-lock device, a traction slip device, a vehicle dynamics control device and / or an external vehicle brake system.
  • the shut-off valve is interposed between a master brake cylinder and a suction side of the pump, it is preferably open in its basic position and has a large flow cross-section in order to throttle as little as possible a brake fluid flow sucked in from a reservoir through the master brake cylinder when the master brake cylinder is not activated and thereby ensure a quick build-up of pressure.
  • the shut-off valve Due to the pressure build-up when the master brake cylinder is actuated, the shut-off valve is closed that the suction side of the pump is hydraulically separated from the master cylinder and brake fluid from wheel brake cylinders through a brake pressure reduction valve during an anti-lock control system or the like. can flow freely.
  • Driving dynamics control operation and / or power brake operation with the brake pedal actuated.
  • the characterizing features of claim 10 result in an embodiment which is more advantageous for driving dynamics control operation and / or power brake operation.
  • the configuration according to the characterizing feature of claim 11 results in an inexpensive design.
  • FIG. 1 shows an axial section of a shut-off valve according to the invention
  • Figure 2 is a hydraulic circuit diagram of a vehicle brake system according to the invention.
  • Figure 3 shows another hydraulic circuit diagram of a vehicle brake system according to the invention.
  • the hydraulically actuated shut-off valve according to the invention shown in FIG. 1, designated overall by 10, is a 2/2-way valve. It is inserted into a hydraulic block, of which only a fragment containing the shut-off valve 10 is shown in the drawing.
  • the shut-off valve 10 is hydraulically connected to other components of a vehicle brake system, such as solenoid valves, a master brake cylinder or a pump, via the hydraulic block.
  • the hydraulic block forms a valve housing 12 and is referred to below in this way.
  • the valve housing 12 has a cylindrical bore which forms a valve chamber 14. At the bottom of the valve chamber 14 there is an annular step with a conical valve seat 16, on which an axial fluid channel 18 opens.
  • a spherical valve closing body 20 is axially displaceably mounted in the valve chamber 14. This has longitudinal ribs 22 on its circumference. The longitudinal ribs 22 serve for the axial guidance of the valve closing body 20 in the valve chamber 14 and enable an almost unrestricted flow around the valve closing body 20.
  • valve closing body 20 is in one piece with a valve tappet 24 which is arranged axially in the valve chamber 14 and projects from the valve closing body 20 on a side facing away from the valve seat 16.
  • the valve lifter 24 projects through an annular actuating element 26 with an essentially rectangular ring cross section, which is located on one of the valve seats 16 facing end of the valve chamber 14 is located.
  • the actuating element 26 fills a space between the valve tappet 24 and a wall of the valve chambers 14, it has a clearance fit both with the valve tappet 24 and with the wall of the valve chamber 14. As a result, it guides the valve tappet 24 in the axial direction and is itself axially displaceably guided in the valve chamber 14.
  • a sleeve sealing ring 28 is arranged on an end face of the actuating element 26 which faces the valve seat 16 and which seals between the wall of the valve chamber 14 and the valve tappet 24.
  • sleeve sealing ring 28 it is also possible, for example, to provide a seal between the outer circumference of the actuating element 26 and the wall of the valve chamber 14 and a seal between the inner circumference of the actuating element 26 and the valve tappet 24 (not shown).
  • These seals are e.g. B. in grooves of the actuator 26 inserted sealing rings, preferably O-rings.
  • the valve chamber 14 is closed by means of a sealing plug 30 inserted into its mouth and caulked in a fluid-tight manner.
  • a rocker element 34 in the form of a plate spring is arranged between the sealing plug 30 and the actuating element 26. With slits running inwards from the outer circumference and / or outwards from the inner circumference, the elasticity of the seesaw element 34 can be influenced.
  • the rocker element 34 engages in a groove 36 of the valve stem 24.
  • the actuating element 26 is close to one Outer circumference on the rocker element 34.
  • the rocker element 34 5 lies on a circular edge which is formed by a cup-shaped recess 38 on an end face of the closure plug 30 facing the rocker element 34.
  • the annular edge forms a pivot bearing 40 for the rocker element 34.
  • a radial, second fluid channel 42 opens into the valve chamber 14 in the area between the sleeve seal 28 and the valve closing body 20.
  • the valve seat 16 is therefore located between the two fluid channels 18, 42.
  • shut-off valve 10 The function of the shut-off valve according to the invention is as follows: In a basic position of the shut-off valve 10 according to the invention shown in the left half of FIG. 1, the rocker element 34 designed as a disk spring lifts the valve closing body 20 from the valve seat 16, so that the shut-off valve 10 can be flowed through in both directions.
  • the embodiment shown in the drawing of a shut-off valve 10 according to the invention is therefore open in its basic position.
  • the rocker element 34 designed as a plate spring is elastically flattened by the actuating element 26, its outer edge moving in the direction of the sealing plug 30 and an inner edge which engages with the groove 36 of the valve tappet 24 in the direction of the valve seat 16. If the pressure in the valve chamber 14 drops below the switching pressure determined by the elastic spring force of the rocker element 34, the spring force of the rocker element 34 returns the shut-off valve 10 to its open basic position.
  • the shut-off valve 10 (FIG. 1) is provided according to the invention for use as a hydraulically actuated intake valve 44 in the vehicle brake system shown in FIG. 2.
  • FIG. 2 shows a brake circuit I of a two-circuit vehicle brake system 46.
  • the brake circuit II is constructed in accordance with the brake circuit I shown and functions in the same way.
  • the vehicle brake system 46 has a tandem master brake cylinder 48 with a reservoir 50.
  • a branching main brake line 52 leads from the main brake cylinder 48 to wheel brake cylinder 54 connected to this brake circuit I.
  • a changeover valve 56 which is open in its basic position, with an integrated pressure relief valve 58 is switched on.
  • a pressure build-up valve 60 which is open in its basic position is connected upstream of each wheel brake cylinder 54.
  • each wheel brake cylinder 54 has a pressure reduction valve 62 which is closed in its basic position, from which a common return line 64 leads to the main brake line 52 and opens between the changeover valve 56 and the pressure build-up valves 60.
  • a feed pump 66 is switched on, a storage 68 upstream and a damper 70 are connected downstream.
  • the pressure build-up and the pressure reduction valve 60, 62 form a brake pressure modulation valve arrangement of the respective wheel brake cylinder 54, with which the brake pressure in the wheel brake cylinder 54 can be modulated in a manner known per se in order to slip the corresponding vehicle wheel when braking (anti-lock control) when starting
  • the brake pressure modulation takes place with the aid of the feed pump 66.
  • the changeover valve 56 can be closed during the brake pressure modulation in order to have repercussions to prevent the master cylinder 48.
  • Pressure build-up and pressure reduction valves 60, 62 can, for example, also be combined to form a 3/3 valve instead of the separate 2/2 valves shown.
  • An intake line 72 leads from the master brake cylinder 48 to a suction side of the feed pump 66.
  • An intake valve 74 which is closed in its basic position is arranged in the intake line 72. Through the intake line 72, the feed pump 66 sucks brake fluid directly from the master brake cylinder 48 when the intake valve 74 is open, which is a prerequisite for rapid pressure build-up.
  • the suction valve 74 like the changeover valve 56 and the pressure build-up and pressure reduction valves 60, 62, is designed as a solenoid valve.
  • a flow cross section of the intake valve 74 is limited for design reasons; the intake valve 74 represents a throttle point when brake fluid is drawn in from the master brake cylinder 48 with the feed pump 66.
  • the hydraulically actuated shutoff valve 10 (FIG. 1) ) as an additional suction valve 44 (FIG. 2) connected in parallel to the suction valve 74, which is designed as a solenoid valve.
  • the flow resistance during the intake of brake fluid from the master brake cylinder 48 by means of the feed pump 66 is thereby further reduced and the pressure build-up is accelerated. Since the hydraulically actuated intake valve 44 has a constructional design, it is considerably easier larger flow cross-section than the electromagnetically operated suction valve 74 allows, the suction resistance can be significantly reduced with little effort.
  • the additional intake valve 44 is open in its basic position, so that the feed pump 66 can draw from the reservoir 50 when the master brake cylinder 48 is not actuated. If the master cylinder 48 is actuated, the valve chamber 14 of the shut-off valve 10 (FIG. 1) is pressurized via the intake line 72 and closed, i.e. H. the additional suction valve 44 ( Figure 2) switches automatically hydraulically controlled and does not need to be controlled electrically.
  • the hydraulically actuated, additional suction valve 44 can also replace the suction valve 74 designed as a solenoid valve in embodiments of the invention.
  • the axial fluid channel 18 shown in FIG. 1 connects the intake valve 44 to the low-pressure side of the feed pump 66 in the application example shown in FIG. 2.
  • the second fluid channel 42 opening radially into the valve chamber 14 (FIG. 1) connects the master brake cylinder 48 in the application example according to FIG with the intake valve 44.
  • the intake valve 44 shown symbolically in FIG. 2 can be designed according to the invention like the shut-off valve 10 shown in FIG.
  • the additional intake valve can also deviate from the Figure 1 be formed and selected for example from the prior art.
  • intake valves or at least intake valve elements according to the publications WO 94/29149 and WO 97/10132 or alternatively, for example, a copy of the intake valve 74 designed as a solenoid valve, which is represented by symbols in the alternative hydraulic circuit diagram of FIG. 3 at reference numeral 44a.
  • the dual-circuit vehicle brake system of FIG. 3 is given the reference symbol 46a.
  • a copy of the suction valve 74 can be carried out, for example, on a scale of 1: 1 in the sense of identical construction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

The invention relates to a hydraulically actuated stop valve (10) serving as a suction valve positioned between a master brake cylinder and the suction side of a supply pump of an antiskid braking system for motor vehicles. According to the invention, the stop valve (10) is provided with a closing element (20) having a valve lifter (24). Said closing element passes through a ring-shaped actuating element (26) and engages with a rocking element (34) configured as a spring washer which rests on a ring-shaped swivel bearing (40). When pressure is applied to the actuating element (26) it presses down an outer edge of the rocking element. As a result, one half of the actuating element (26) carries out a turning movement in the opposite direction, which movement closes the stop valve (10). The advantages of this stop valve (10) are that it is cost-effective, consists of only a limited number of components and can be used in a hydraulic brake system for motor vehicles. The invention also relates to a hydraulic brake system for motor vehicles comprising a master brake cylinder (48), wheel brake cylinders (54) supplied with brake pressure by said master brake cylinder (48), pressure build-up and pressure cut-back valve systems (60, 62) assigned to said wheel brake cylinders, one self-priming supply pump (66) for each braking circuit, a suction valve (74) positioned between the master brake cylinder and an inlet (64) of the supply pump (66) which is connected to the pressure build-up and pressure cut-back valve systems (60, 62), and a reversing valve (56) positioned between an outlet of the supply pump (66) and the master brake cylinder (48). This hydraulic brake system for motor vehicles is characterized in that a second suction valve (44, 44a) is mounted parallel to the suction valve (74) and allows for better filling of the supply pump (66).

Description

Hydraulisch betätigbares Absperrventil und hydraulische FahrzeugbremsanlageHydraulically operated shut-off valve and hydraulic vehicle brake system
Stand der TechnikState of the art
Die Erfindung betrifft ein hydraulisch betätigbares Absperrventil mit den Merkmalen des Oberbegriffs des Anspruchs 1 sowie eine mit einem solchen Absperrventil ausrüstbare hydraulische Fahrzeugbremsanlage mit den Merkmalen des Oberbegriffes des Anspruchs 7.The invention relates to a hydraulically actuated shut-off valve with the features of the preamble of claim 1 and to a hydraulic vehicle brake system that can be equipped with such a shut-off valve with the features of the preamble of claim 7.
Ein derartiges Ventil ist bekannt aus der EP 0 606 840 Bl. Das bekannte Ventil weist ein Ventilgehäuse mit einer Zwischenwand auf, an der ein Ventilsitz ausgebildet ist. Auf einer Seite der Zwischenwand ist ein Kolben als Betätigungselement angeordnet, der von einer Ventilöffnungsfeder in Richtung der Zwischenwand gedrückt und durch Druckbeaufschlagung von der Zwischenwand weg verschiebbar ist. Auf der anderen Seite der Zwischenwand befindet sich eine Ventilkugel als Ventilschließkörper, die von dem Kolben vom Ventilsitz abgehoben und von einer Ventilschließfeder, die schwächer als die Ventilöffnungsfeder ist, in Richtung des Ventilsitzes gedrückt wird. Das bekannte Ventil ist in seiner Grundstellung geöffnet und wird durch Beaufschlagung mit einem Druck, der über einem Schließdruck liegt, geschlossen.Such a valve is known from EP 0 606 840 B1. The known valve has a valve housing with an intermediate wall on which a valve seat is formed. A piston is arranged as an actuating element on one side of the intermediate wall, said piston being pressed in the direction of the intermediate wall by a valve opening spring and being displaceable away from the intermediate wall by pressurization. On the other side of the intermediate wall there is a valve ball as a valve closing body, which is lifted off the valve seat by the piston and is pressed in the direction of the valve seat by a valve closing spring which is weaker than the valve opening spring. The well-known valve is in opened in its basic position and is closed by applying a pressure that is above a closing pressure.
Das bekannte Ventil hat den Nachteil, daß seine Herstellung aufwendig ist. Insbesondere muß das Ventilgehäuse auf beiden Seiten des Ventilsitzes bearbeitet werden. Es ist groß und benötigt zwei Federn, die zur Einstellung gewünschter Schaltdrücke aufeinander abgestimmt werden. Durch die Verwendung zweier gegeneinander arbeitender Federn ist die Gefahr groß, daß sich die Schaltdrücke im Laufe der Ventilbenutzung verändern.The known valve has the disadvantage that its production is complex. In particular, the valve housing must be machined on both sides of the valve seat. It is large and requires two springs that are matched to one another to set the desired switching pressures. By using two springs working against each other, there is a great risk that the switching pressures will change in the course of valve use.
Dieses Ventil ist Bestandteil einer hydraulischen Fahrzeugbremsanlage, die zum Begrenzen von Antriebsschlupf durch automatisches Bremsen von Antriebsrädern eingerichtet ist und dafür wenigstens eine selbstsaugende Förderpumpe hat, die sich durch das offen stehende Ventil und durch einen Hauptbremszylinder aus dessen Vorratsbehälter mit Bremsflüssigkeit versorgt. Die hydraulische Fahrzeugbremsanlage enthält des weiteren noch mit Radbremszylindem verbundene Druckaufbau- und Druckabbauventilanordnungen, mittels denen beispielsweise im Antriebsschlupfregelbetrieb von der Förderpumpe zur Bremsdruckerzeugung geförderte Bremsflüssigkeit wenigstens einem Radbremszylinder zuleitbar ist.This valve is part of a hydraulic vehicle brake system which is set up to limit drive slip by automatically braking drive wheels and for this purpose has at least one self-priming feed pump which is supplied with brake fluid from the reservoir by the open valve and by a master brake cylinder. The hydraulic vehicle brake system also contains pressure build-up and pressure relief valve arrangements connected to wheel brake cylinders, by means of which brake fluid delivered by the feed pump for generating brake pressure, for example in traction control mode, can be supplied to at least one wheel brake cylinder.
Vorteile der Erfindung Das erfindungsgemäße Absperrventil mit den Merkmalen des Anspruchs 1 weist lediglich drei bewegliche Teile, nämlich den Ventilschließkörper, das Betätigungselement und ein Wippelement, das eine Bewegung des Betätigungselements auf den Ventilschließkörper überträgt, auf. Diese Teile sind einfach in ihrer Geometrie und dadurch kostengünstig herstellbar. Sie lassen sich in einer zylindrischen Bohrung unterbringen, die einen Konus an einer Ringstufe als Ventilsitz aufweisen kann. Das erfindungsgemäße Absperrventil ist mit geringem Aufwand preisgünstig herstellbar, es ist wartungsfrei und unterliegt nur geringem Verschleiß, so daß es eine lange Nutzungsdauer hat.Advantages of the invention The shut-off valve according to the invention with the features of claim 1 has only three moving parts, namely the valve closing body, the actuating element and a rocker element which transmits a movement of the actuating element to the valve closing body. The geometry of these parts is simple and therefore inexpensive to manufacture. They can be accommodated in a cylindrical bore, which can have a cone on a ring step as a valve seat. The shut-off valve according to the invention can be produced inexpensively with little effort, it is maintenance-free and is subject to only slight wear, so that it has a long service life.
Das erfindungsgemäße Absperrventil ist insbesondere zur Verwendung als Ansaugventil für eine hydraulische, eine Pumpe aufweisende Fahrzeugbremsanlage, also beispielsweise eine Blockierschutz-, eine Antriebsschlupf-, eine Fahrdynamikregeleinrichtung aufweisende und/oder eine Fremdkraft-Fahrzeugbremsanlage vorgesehen. Das Absperrventil wird einem Hauptbremszylinder und einer Saugseite der Pumpe zwischengeschaltet, es ist vorzugsweise in seiner Grundstellung offen und verfügt über einen großen Strömungsquerschnitt, um bei nicht betätigtem Hauptbremszylinder und eingeschalteter Pumpe einen aus einem Vorratsbehälter durch den Hauptbremszylinder hindurch angesaugten Bremsflüssigkeitsstrom möglichst wenig zu drosseln und dadurch einen schnellen Druckaufbau sicherzustellen. Durch den Druckaufbau bei Betätigung des HauptbremsZylinders wird das Absperrventil geschlossen, so daß die Saugseite der Pumpe vom Hauptbremszylinder hydraulisch getrennt ist und Bremsflüssigkeit aus Radbremszylindern durch ein Bremsdruckabsenkventil während einer Blockierschutzregelung oder dgl . ungehindert ausströmen kann.The shut-off valve according to the invention is intended in particular for use as an intake valve for a hydraulic vehicle brake system having a pump, that is to say, for example, an anti-lock device, a traction slip device, a vehicle dynamics control device and / or an external vehicle brake system. The shut-off valve is interposed between a master brake cylinder and a suction side of the pump, it is preferably open in its basic position and has a large flow cross-section in order to throttle as little as possible a brake fluid flow sucked in from a reservoir through the master brake cylinder when the master brake cylinder is not activated and thereby ensure a quick build-up of pressure. Due to the pressure build-up when the master brake cylinder is actuated, the shut-off valve is closed that the suction side of the pump is hydraulically separated from the master cylinder and brake fluid from wheel brake cylinders through a brake pressure reduction valve during an anti-lock control system or the like. can flow freely.
Die Unteransprüche haben vorteilhafte Ausgestaltungen und Weiterbildungen des im Anspruch 1 angegebenen Absperrventils zum Gegenstand.The dependent claims relate to advantageous refinements and developments of the shut-off valve specified in claim 1.
Die kennzeichnenden Merkmale des unabhängigen Anspruchs 7 ergeben in einer gattungsgemäßen hydraulischen Fahrzeugbremsanlage den Vorteil, daß beim automatischen Bremsen zwischen dem Hauptbremszylinder und einem Eingang einer Förderpumpe zwei geöffnete Ventilquerschnitte in Parallelschaltung zur Verfügung stehen, so daß sich die selbstansaugende Förderpumpe gut zu füllen vermag und demgemäß gut zu fördern vermag.The characterizing features of independent claim 7 result in a generic hydraulic vehicle brake system the advantage that two automatic valve cross sections are available in parallel connection during automatic braking between the master brake cylinder and an input of a feed pump, so that the self-priming feed pump can fill well and is accordingly good able to promote.
Die kennzeichnenden Merkmale des Anspruchs 8 ergeben ein Ausführungsbeispiel, bei dem eines der Ansaugventile elektrisch steuerbar ist und demgemäß die hydraulische Fahrzeugbremsanlage tauglich macht fürThe characterizing features of claim 8 result in an embodiment in which one of the intake valves is electrically controllable and accordingly makes the hydraulic vehicle brake system suitable for
Fahrdynamikregelbetrieb oder/und Fremdkraftbremsbetrieb bei betätigtem Bremspedal.Driving dynamics control operation and / or power brake operation with the brake pedal actuated.
Die kennzeichnenden Merkmale des Anspruchs 9 ergeben ein Ausführungsbeispiel, das im Antriebsschlupfregelungsbetrieb per automatisches Bremsen mittels des hydraulisch steuerbaren Ansaugventils in preisgünstiger und dabei raumsparender Weise einen großen Ventilquerschnitt zur Verfügung stellt .The characterizing features of claim 9 result in an embodiment, which in the traction control mode by automatic braking by means of the hydraulic controllable intake valve provides a large valve cross-section in an inexpensive and space-saving manner.
Die kennzeichnenden Merkmale des Anspruchs 10 ergeben ein Ausführungsbeispiel, das für Fahrdynamikregelbetrieb oder/und Fremdkraftbremsbetrieb vorteilhafter ist. Dabei ergibt die Ausgestaltung gemäß dem kennzeichnenden Merkmal des Anspruchs 11 eine preisgünstige Bauart.The characterizing features of claim 10 result in an embodiment which is more advantageous for driving dynamics control operation and / or power brake operation. The configuration according to the characterizing feature of claim 11 results in an inexpensive design.
Zeichnungdrawing
Die Erfindung wird nachfolgend anhand eines in der Zeichnung dargestellten Ausführungsbeispiels näher erläutert. Es zeigen:The invention is explained in more detail below with reference to an embodiment shown in the drawing. Show it:
Figur 1 einen Achsschnitt eines erfindungsgemäßen Absperrventi1s ,FIG. 1 shows an axial section of a shut-off valve according to the invention,
Figur 2 einen Hydraulikschaltplan einer Fahrzeugbremsanlage gemäß der Erfindung undFigure 2 is a hydraulic circuit diagram of a vehicle brake system according to the invention and
Figur 3 einen weiteren Hydraulikschaltplan einer Fahrzeugbremsanlage gemäß der Erfindung.Figure 3 shows another hydraulic circuit diagram of a vehicle brake system according to the invention.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Das in Figur 1 dargestellte, insgesamt mit 10 bezeichnete, erfindungsgemäße, hydraulisch betätigbare Absperrventil ist ein 2/2-Wegeventil . Es ist in einen Hydraulikblock eingesetzt, von dem in der Zeichnung nur ein das Absperrventil 10 enthaltendes Bruchstück dargestellt ist. Über den Hydraulikblock ist das Absperrventil 10 hydraulisch mit weiteren Bauelementen einer Fahrzeugbremsanlage wie beispielsweise Magnetventilen, einem Hauptbremszylinder oder einer Pumpe verschaltet. Der Hydraulikblock bildet ein Ventilgehäuse 12 und wird nachfolgend so bezeichnet.The hydraulically actuated shut-off valve according to the invention shown in FIG. 1, designated overall by 10, is a 2/2-way valve. It is inserted into a hydraulic block, of which only a fragment containing the shut-off valve 10 is shown in the drawing. The shut-off valve 10 is hydraulically connected to other components of a vehicle brake system, such as solenoid valves, a master brake cylinder or a pump, via the hydraulic block. The hydraulic block forms a valve housing 12 and is referred to below in this way.
Das Ventilgehäuse 12 weist eine zylindrische Bohrung auf, die eine Ventilkammer 14 bildet. Am Grund der Ventilkammer 14 ist eine Ringstufe mit einem konischen Ventilsitz 16 angebracht, an dem ein axialer Fluidkanal 18 mündet.The valve housing 12 has a cylindrical bore which forms a valve chamber 14. At the bottom of the valve chamber 14 there is an annular step with a conical valve seat 16, on which an axial fluid channel 18 opens.
In der Ventilkammer 14 ist ein balliger Ventilschließkörper 20 axial verschieblich gelagert. Dieser weist Längsrippen 22 an seinem Umfang auf. Die Längsrippen 22 dienen der Axialführung des Ventilschließkörpers 20 in der Ventilkammer 14 und ermöglichen eine nahezu ungedrosselte Umströmung des Ventilschließkörpers 20.A spherical valve closing body 20 is axially displaceably mounted in the valve chamber 14. This has longitudinal ribs 22 on its circumference. The longitudinal ribs 22 serve for the axial guidance of the valve closing body 20 in the valve chamber 14 and enable an almost unrestricted flow around the valve closing body 20.
Der Ventilschließkörper 20 ist einstückig mit einem Ventilstößel 24, der axial in der Ventilkammer 14 angeordnet ist und auf einer dem Ventilsitz 16 abgewandten Seite vom Ventilschließkörper 20 absteht.The valve closing body 20 is in one piece with a valve tappet 24 which is arranged axially in the valve chamber 14 and projects from the valve closing body 20 on a side facing away from the valve seat 16.
Der Ventilstößel 24 ragt durch ein ringförmiges Betätigungselement 26 mit im wesentlichen rechteckförmigem Ringquerschnitt hindurch, das sich auf einer dem Ventilsitz 16 abgewandten Stirnende der Ventilkammer 14 befindet. Das Betätigungselement 26 füllt einen Zwischenraum zwischen dem Ventilstδßel 24 und einer Wandung der Ventilkämmer 14 aus, es weist eine Spielpassung sowohl mit Ventilstößel 24 als auch mit der Wandung der Ventilkammer 14 auf. Es führt dadurch den Ventilstößel 24 in axialer Richtung und ist selbst axial verschieblich in der Ventilkammer 14 geführt. Zur Abdichtung ist ein Manschettendichtring 28 auf einer dem Ventilsitz 16 zugewandten Stirnseite des Betätigungselements 26 angeordnet, das zwischen der Wandung der Ventilkammer 14 und dem Ventilstößel 24 abdichtet. Anstelle des Manschettendichtrings 28 können beispielsweise auch eine Dichtung zwischen dem Außenumfang des Betätigungselements 26 und der Wandung der Ventilkammer 14 sowie eine Dichtung zwischen dem Innenumfang des Betätigungselements 26 und dem Ventilstößel 24 vorgesehen werden (nicht dargestellt) . Diese Dichtungen sind z. B. in Nuten des Betätigungselements 26 eingelegte Dichtringe, vorzugsweise O-Ringe.The valve lifter 24 projects through an annular actuating element 26 with an essentially rectangular ring cross section, which is located on one of the valve seats 16 facing end of the valve chamber 14 is located. The actuating element 26 fills a space between the valve tappet 24 and a wall of the valve chambers 14, it has a clearance fit both with the valve tappet 24 and with the wall of the valve chamber 14. As a result, it guides the valve tappet 24 in the axial direction and is itself axially displaceably guided in the valve chamber 14. For sealing purposes, a sleeve sealing ring 28 is arranged on an end face of the actuating element 26 which faces the valve seat 16 and which seals between the wall of the valve chamber 14 and the valve tappet 24. Instead of the sleeve sealing ring 28, it is also possible, for example, to provide a seal between the outer circumference of the actuating element 26 and the wall of the valve chamber 14 and a seal between the inner circumference of the actuating element 26 and the valve tappet 24 (not shown). These seals are e.g. B. in grooves of the actuator 26 inserted sealing rings, preferably O-rings.
Verschlossen ist die Ventilkammer 14 mittels eines in ihre Mündung eingesetzten und fluiddicht verstemmten 32 Verschlußstopfens 30. Zwischen dem Verschlußstopfen 30 und dem Betätigungselement 26 ist ein Wippelement 34 in Form einer Tellerfeder angeordnet. Mit vom Außenumfang nach innen und/oder vom Innenumfang nach außen verlaufenden Schlitzen kann die Elastizität des Wippelements 34 beeinflußt werden.The valve chamber 14 is closed by means of a sealing plug 30 inserted into its mouth and caulked in a fluid-tight manner. A rocker element 34 in the form of a plate spring is arranged between the sealing plug 30 and the actuating element 26. With slits running inwards from the outer circumference and / or outwards from the inner circumference, the elasticity of the seesaw element 34 can be influenced.
Das Wippelement 34 greift in eine Nut 36 des Ventilstδßels 24 ein. Das Betätigungselement 26 liegt nahe einem Außenumfang am Wippelement 34 an. In einem Mittelbereich zwischen dem Ventilstößel 24 und dem Außenumfang liegt das Wippelement 34 5 auf einer kreisförmigen Kante auf, die an einer dem Wippelement 34 zugewandten Stirnfläche des Verschlußstopfens 30 durch eine napfförmige Ausnehmung 38 gebildet ist. Die ringförmige Kante bildet ein Schwenklager 40 für das Wippelement 34.The rocker element 34 engages in a groove 36 of the valve stem 24. The actuating element 26 is close to one Outer circumference on the rocker element 34. In a central region between the valve tappet 24 and the outer circumference, the rocker element 34 5 lies on a circular edge which is formed by a cup-shaped recess 38 on an end face of the closure plug 30 facing the rocker element 34. The annular edge forms a pivot bearing 40 for the rocker element 34.
Im Bereich zwischen der Manschettendichtung 28 und dem Ventilschließkörper 20 mündet ein radialer, zweiter Fluidkanal 42 in die Ventilkammer 14. Der Ventilsitz 16 befindet sich also zwischen den beiden Fluidkanälen 18, 42.A radial, second fluid channel 42 opens into the valve chamber 14 in the area between the sleeve seal 28 and the valve closing body 20. The valve seat 16 is therefore located between the two fluid channels 18, 42.
Die Funktion des erfindungsgemäßen Absperrventils ist folgende: In einer in der linken Bildhälfte von Figur 1 dargestellten Grundstellung des erfindungsgemäßen Absperrventils 10 hebt das als Tellerfeder ausgebildete Wippelement 34 den Ventilschließkörper 20 vom Ventilsitz 16 ab, so daß das Absperrventil 10 in beiden Richtungen durchströmbar ist. Das in der Zeichnung dargestellte Ausführungsbeispiel eines erfindungsgemäßen Absperrventils 10 ist also in seiner Grundstellung offen.The function of the shut-off valve according to the invention is as follows: In a basic position of the shut-off valve 10 according to the invention shown in the left half of FIG. 1, the rocker element 34 designed as a disk spring lifts the valve closing body 20 from the valve seat 16, so that the shut-off valve 10 can be flowed through in both directions. The embodiment shown in the drawing of a shut-off valve 10 according to the invention is therefore open in its basic position.
Wird die Ventilkammer 14 und damit über die Manschettendichtung 28 das Betätigungselement 26 mit einem Druck beaufschlagt, der über einem Schaltdruck liegt, verschiebt sich das Betätigungselement 26 zusammen mit der Manschettendichtung 28 in axialer Richtung gegen die Federkraft des Wippelements 34 und drückt dieses an seinem Außenumfang gegen den Verschlußstopfen 30 nieder. Dadurch wird das Wippelement 34 im Querschnitt gesehen um das Schwenklager 40 verschwenkt und drückt den Ventilschließkörper 20 über den Ventilstößel 24 dichtend gegen den Ventilsitz 16, so daß das Absperrventil 10 geschlossen ist. Die geschlossene Schaltstellung des Absperrventils 10 ist in der rechten Bildhälfte von Figur 1 dargestellt. Tatsächlich wird das als Tellerfeder ausgebildete Wippelement 34 vom Betätigungselement 26 elastisch flachgedrückt, wobei sein Außenrand sich in Richtung des Verschlußstopfens 30 und ein Innenrand, der mit der Nut 36 des Ventilstößels 24 in Eingriff steht, in Richtung des Ventilsitzes 16 bewegt. Sinkt der Druck in der Ventilkammer 14 unter den von der elastischen Federkraft des Wippelements 34 bestimmten Schaltdruck ab, stellt die Federkraft des Wippelements 34 das Absperrventil 10 wieder in seine offene Grundstellung zurück.If the valve chamber 14 and thus via the sleeve seal 28, the actuating element 26 is subjected to a pressure which is above a switching pressure, the actuating element 26 together with the sleeve seal 28 moves in the axial direction against the spring force of the rocker element 34 and presses it against it Outer circumference against the stopper 30 down. As a result, seen in cross section, the rocker element 34 is pivoted about the pivot bearing 40 and presses the valve closing body 20 sealingly against the valve seat 16 via the valve tappet 24, so that the shut-off valve 10 is closed. The closed switching position of the shut-off valve 10 is shown in the right half of Figure 1. In fact, the rocker element 34 designed as a plate spring is elastically flattened by the actuating element 26, its outer edge moving in the direction of the sealing plug 30 and an inner edge which engages with the groove 36 of the valve tappet 24 in the direction of the valve seat 16. If the pressure in the valve chamber 14 drops below the switching pressure determined by the elastic spring force of the rocker element 34, the spring force of the rocker element 34 returns the shut-off valve 10 to its open basic position.
Das Absperrventil 10 (Figur 1) ist erfindungsgemäß zur Verwendung als hydraulisch betätigbares Ansaugventil 44 in der in Figur 2 dargestellten Fahrzeugbremsanlage vorgesehen. In Figur 2 ist ein Bremskreis I einer Zweikreis-Fahrzeugbremsanlage 46 dargestellt. Der nicht dargestellte Bremskreis II ist übereinstimmend mit dem dargestellten Bremskreis I aufgebaut und funktioniert in gleicher Weise.The shut-off valve 10 (FIG. 1) is provided according to the invention for use as a hydraulically actuated intake valve 44 in the vehicle brake system shown in FIG. 2. FIG. 2 shows a brake circuit I of a two-circuit vehicle brake system 46. The brake circuit II, not shown, is constructed in accordance with the brake circuit I shown and functions in the same way.
Die Fahrzeugbremsanlage 46 weist einen Tandem-Hauptbrems- zylinder 48 mit einem Vorratsbehälter 50 auf. Eine sich verzweigende Hauptbremsleitung 52 führt vom Hauptbrems- zylinder 48 zu an diesen Bremskreis I angeschlossene Radbremszylinder 54. In die Hauptbremsleitung 52 ist ein in seiner Grundstellung geöffnetes Umschaltventil 56 mit integriertem Druckbegrenzungsventil 58 eingeschaltet. Jedem Radbremszylinder 54 ist ein in seiner Grundstellung geöffnetes Druckaufbauventil 60 vorgeschaltet.The vehicle brake system 46 has a tandem master brake cylinder 48 with a reservoir 50. A branching main brake line 52 leads from the main brake cylinder 48 to wheel brake cylinder 54 connected to this brake circuit I. In the main brake line 52, a changeover valve 56, which is open in its basic position, with an integrated pressure relief valve 58 is switched on. A pressure build-up valve 60 which is open in its basic position is connected upstream of each wheel brake cylinder 54.
Des weiteren weist jeder Radbremszylinder 54 ein in seiner Grundstellung geschlossenes Druckabsenkventil 62 auf, von denen eine gemeinsame Rückleitung 64 zur Hauptbremsleitung 52 führt und zwischen dem Umschaltventil 56 und den Druckaufbauventilen 60 mündet. In die Rückleitung 64 ist eine Förderpumpe 66 eingeschaltet, der ein Speicher 68 vor- und ein Dämpfer 70 nachgeschaltet sind.Furthermore, each wheel brake cylinder 54 has a pressure reduction valve 62 which is closed in its basic position, from which a common return line 64 leads to the main brake line 52 and opens between the changeover valve 56 and the pressure build-up valves 60. In the return line 64, a feed pump 66 is switched on, a storage 68 upstream and a damper 70 are connected downstream.
Das Druckaufbau- und das Druckabsenkventil 60, 62 bilden eine Bremsdruckmodulationsventilanordnung des jeweiligen RadbremsZylinders 54, mit denen in an sich bekannter Weise der Bremsdruck im Radbremszylinder 54 modulierbar ist, um Schlupf des entsprechenden Fahrzeugrades beim Bremsen (Blockierschutzregelung) , beim AnfahrenThe pressure build-up and the pressure reduction valve 60, 62 form a brake pressure modulation valve arrangement of the respective wheel brake cylinder 54, with which the brake pressure in the wheel brake cylinder 54 can be modulated in a manner known per se in order to slip the corresponding vehicle wheel when braking (anti-lock control) when starting
(Antriebsschlupfregelung) zu verhindern bzw. zu begrenzen oder um durch gezieltes Bremsen eines Fahrzeugrades dessen Seitenführung zu beeinflussen, um ein Schleudern des Fahrzeugs zu verhindern (Fahrdynamikregelunq) .To prevent or limit (traction control) or to influence the lateral guidance of a vehicle wheel by targeted braking in order to prevent the vehicle from skidding (driving dynamics control).
Die Bremsdruckmodulation erfolgt mit Hilfe der Förderpumpe 66. Das Umschaltventil 56 kann während der Bremsdruckmodulation geschlossen werden, um Rückwirkungen auf den Hauptbremszylinder 48 zu unterbinden. Druckaufbau- und Druckabsenkventil 60, 62 können beispielsweise auch zu einem 3/3-Ventil anstelle der dargestellten, separaten 2/2- Ventile zusammengefaßt werden.The brake pressure modulation takes place with the aid of the feed pump 66. The changeover valve 56 can be closed during the brake pressure modulation in order to have repercussions to prevent the master cylinder 48. Pressure build-up and pressure reduction valves 60, 62 can, for example, also be combined to form a 3/3 valve instead of the separate 2/2 valves shown.
Eine Ansaugleitung 72 führt vom Hauptbremszylinder 48 zu einer Saugseite der Förderpumpe 66. In der Ansaugleitung 72 ist ein in seiner Grundstellung geschlossenes Ansaugventil 74 angeordnet . Durch die Ansaugleitung 72 saugt die Förderpumpe 66 bei geöffnetem Ansaugventil 74 Bremsflüssigkeit unmittelbar aus dem Hauptbremszylinder 48 an, was Voraussetzung für einen schnellen Druckaufbau ist.An intake line 72 leads from the master brake cylinder 48 to a suction side of the feed pump 66. An intake valve 74 which is closed in its basic position is arranged in the intake line 72. Through the intake line 72, the feed pump 66 sucks brake fluid directly from the master brake cylinder 48 when the intake valve 74 is open, which is a prerequisite for rapid pressure build-up.
Das Ansaugventil 74 ist, ebenso wie das Umschaltventil 56 und die Druckaufbau- und Druckabsenkventile 60, 62 als Magnetventil ausgebildet. Ein Durchströmquerschnitt des Ansaugventils 74 ist aus konstruktiven Gründen begrenzt, das Ansaugventil 74 stellt eine Drosselstelle beim Ansaugen von Bremsflüssigkeit aus dem Hauptbremszylinder 48 mit der Förderpumpe 66 dar. Um den verfügbaren Gesamtströmungs- querschnitt zu vergrößern, ist erfindungsgemäß das hydraulisch betätigbare Absperrventil 10 (Figur 1 ) als zusätzliches Ansaugventil 44 (Figur 2) dem als Magnetventil ausgebildeten Ansaugventil 74 parallel geschaltet. Der Strömungswiderstand beim Ansaugen von Bremsflüssigkeit aus dem Hauptbremszylinder 48 mittels der Förderpumpe 66 wird dadurch weiter herabgesetzt und der Druckaufbau beschleunigt. Da das hydraulisch betätigbare Ansaugventil 44 konstruktionsbedingt auf einfache Weise einen erheblich größeren Durchströmquerschnitt als das elektromagnetisch betätigte Ansaugventil 74 ermöglicht, läßt sich der Ansaugwiderstand mit wenig Aufwand wesentlich verringern.The suction valve 74, like the changeover valve 56 and the pressure build-up and pressure reduction valves 60, 62, is designed as a solenoid valve. A flow cross section of the intake valve 74 is limited for design reasons; the intake valve 74 represents a throttle point when brake fluid is drawn in from the master brake cylinder 48 with the feed pump 66. In order to enlarge the available total flow cross section, the hydraulically actuated shutoff valve 10 (FIG. 1) ) as an additional suction valve 44 (FIG. 2) connected in parallel to the suction valve 74, which is designed as a solenoid valve. The flow resistance during the intake of brake fluid from the master brake cylinder 48 by means of the feed pump 66 is thereby further reduced and the pressure build-up is accelerated. Since the hydraulically actuated intake valve 44 has a constructional design, it is considerably easier larger flow cross-section than the electromagnetically operated suction valve 74 allows, the suction resistance can be significantly reduced with little effort.
Das zusätzliche Ansaugventil 44 ist, wie anhand des in Figur 1 dargestellten Absperrventils 10 erläutert, in seiner Grundstellung geöffnet, so daß die Förderpumpe 66 bei nicht betätigtem Hauptbremszylinder 48 aus dem Vorratsbehälter 50 ansaugen kann. Wird der Hauptbremszylinder 48 betätigt, so wird über die Ansaugleitung 72 die Ventilkammer 14 des Absperrventils 10 (Figur 1) mit Druck beaufschlagt und dieses geschlossen, d. h. das zusätzliche Ansaugventil 44 (Figur 2) schaltet selbsttätig hydraulisch gesteuert und braucht nicht elektrisch gesteuert zu werden.As explained with reference to the shut-off valve 10 shown in FIG. 1, the additional intake valve 44 is open in its basic position, so that the feed pump 66 can draw from the reservoir 50 when the master brake cylinder 48 is not actuated. If the master cylinder 48 is actuated, the valve chamber 14 of the shut-off valve 10 (FIG. 1) is pressurized via the intake line 72 and closed, i.e. H. the additional suction valve 44 (Figure 2) switches automatically hydraulically controlled and does not need to be controlled electrically.
Das hydraulisch betätigbare, zusätzliche Ansaugventil 44 kann bei Ausgestaltungen der Erfindung auch das als Magnetventil ausgebildete Ansaugventil 74 ersetzen.The hydraulically actuated, additional suction valve 44 can also replace the suction valve 74 designed as a solenoid valve in embodiments of the invention.
Der in Figur 1 gezeigte axiale Fluidkanal 18 verbindet bei dem in Figur 2 dargestellten Anwendungsbeispiel das Ansaugventil 44 mit der Niederdruckseite der Förderpumpe 66. Der radial in die Ventilkammer 14 (Figur 1) mündende zweite Fluidkanal 42 verbindet bei dem Anwendungsbeispiel gemäß Figur 2 den Hauptbremszylinder 48 mit dem Ansaugventil 44. Wie bereits erwähnt, kann das in der Figur 2 symbolhaft dargestellte Ansaugventil 44 erfindungsgemäß wie das in der Figur l gezeigte Absperrventil 10 ausgeführt sein. Das zusätzliche Ansaugventil kann also auch abweichend von der Figur 1 ausgebildet sein und dabei beispielsweise aus dem Stand der Technik ausgewählt werden. Hierfür kommen beispielsweise in Betracht Ansaugventile oder wenigstens Ansaugventilelemente gemäß den Druckschriften WO 94/29149 und WO 97/10132 oder alternativ beispielsweise eine Kopie des als Magnetventil ausgebildeten Ansaugventils 74, was per Symbolik im alternativen Hydraulikschaltplan der Figur 3 dargestellt ist bei dem Bezugszeichen 44a. Daran angepaßt erhält die Zweikreis-Fahrzeugbremsanlage der Figur 3 das Bezugszeichen 46a. Eine Kopie des Ansaugventils 74 ist beispielsweise im Maßstab 1:1 durchführbar im Sinne von Baugleichheit . The axial fluid channel 18 shown in FIG. 1 connects the intake valve 44 to the low-pressure side of the feed pump 66 in the application example shown in FIG. 2. The second fluid channel 42 opening radially into the valve chamber 14 (FIG. 1) connects the master brake cylinder 48 in the application example according to FIG with the intake valve 44. As already mentioned, the intake valve 44 shown symbolically in FIG. 2 can be designed according to the invention like the shut-off valve 10 shown in FIG. The additional intake valve can also deviate from the Figure 1 be formed and selected for example from the prior art. For example, intake valves or at least intake valve elements according to the publications WO 94/29149 and WO 97/10132 or alternatively, for example, a copy of the intake valve 74 designed as a solenoid valve, which is represented by symbols in the alternative hydraulic circuit diagram of FIG. 3 at reference numeral 44a. Adapted to this, the dual-circuit vehicle brake system of FIG. 3 is given the reference symbol 46a. A copy of the suction valve 74 can be carried out, for example, on a scale of 1: 1 in the sense of identical construction.

Claims

Patentansprüche claims
1. Hydraulisch betätigbares Absperrventil mit einem in eine Schließstellung und in eine Öffnungsstellung verstellbaren Ventilschließkörper und mit einem durckbeaufschlagbaren Betätigungselement, dadurch gekennzeichnet, daß das Absperrventil (10, 44) ein Wippelement (34) aufweist, das bei Beaufschlagung des Betätigungselements (26) mit einem über einem Schaltdruck liegenden Druck von dem Betätigungselement (26) verschwenkt wird und dadurch den Ventilschließkörper (20) betätigt.1. Hydraulically actuated shut-off valve with a valve closing body adjustable in a closed position and in an open position and with an actuating element which can be pressurized, characterized in that the shut-off valve (10, 44) has a rocker element (34) which, when the actuating element (26) is acted upon with a pressure above the switching pressure is pivoted by the actuating element (26) and thereby actuates the valve closing body (20).
2. Hydraulisch betätigbares Absperrventil nach Anspruch 1, dadurch gekennzeichnet, daß das Wippelement (34) ein Rückstellfederelement aufweist, das den Ventilschließkörper (20) in eine Grundstellung drückt. 2. Hydraulically actuated shut-off valve according to claim 1, characterized in that the rocker element (34) has a return spring element which presses the valve closing body (20) into a basic position.
3. Hydraulisch betätigbares Absperrventil nach Anspruch 2, dadurch gekennzeichnet, daß das Wippelement (34) als Tellerfeder ausgebildet ist.3. Hydraulically actuated shut-off valve according to claim 2, characterized in that the rocker element (34) is designed as a plate spring.
4. Hydraulisch betätigbares Absperrventil nach Anspruch 2, dadurch gekennzeichnet, daß das Wippelement (34) als Blattfeder ausgebildet ist.4. Hydraulically actuated shut-off valve according to claim 2, characterized in that the rocker element (34) is designed as a leaf spring.
5. Hydraulisch betätigbares Absperrventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Betätigungselement (26) ringförmig ausgebildet und axial verschieblich in einer druckbeaufschlagbaren Ventilkammer5. Hydraulically actuated shut-off valve according to one of the preceding claims, characterized in that the actuating element (26) is annular and axially displaceable in a pressurizable valve chamber
(14) aufgenommen ist, daß der Ventilschließkörper (20) einen Ventilstößel (24) aufweist, der das Betätigungselement (26) durchgreift, wobei das Betätigungselement (26) abgedichtet ist gegenüber der Ventilkammer (14) und gegenüber dem Ventilstößel (24) , daß der Ventilstößel (24) mit dem als Tellerfeder ausgebildeten Wippelement (34) in Eingriff steht, das im Bereich zwischen seiner Mitte und seinem Außenumfang auf einem ringförmigen Schwenklager (40) aufliegt, und daß das Betätigungselement (26) bei Beaufschlagung der Ventilkammer (14) mit Druck radial außerhalb des Schwenklagers (40) an dem Wippelement (34) anliegt .(14) that the valve closing body (20) has a valve tappet (24) which passes through the actuating element (26), the actuating element (26) being sealed off from the valve chamber (14) and from the valve tappet (24), that the valve tappet (24) engages with the rocker element (34) designed as a plate spring, which rests in the area between its center and its outer circumference on an annular pivot bearing (40), and that the actuating element (26) when the valve chamber (14) is acted upon with pressure radially outside the pivot bearing (40) on the rocker element (34).
6. Hydraulisch betätigbares Absperrventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Absperrventil (10, 44) einen Ventilsitz (16) aufweist, gegen den das Rückstellfederelement (34) den Ventilschließkörper (20) drückt .6. Hydraulically actuated shut-off valve according to claim 1 or 2, characterized in that the shut-off valve (10, 44) has a valve seat (16) against which the Return spring element (34) presses the valve closing body (20).
7. Hydraulische Fahrzeugbremsanlage mit einem Hauptbremszylinder, mit aus diesem mit Bremsdruck versorgbaren RadbremsZylindern, mit den RadbremsZylindern zugeordneten Druckaufbau- und Druckabsenkventilanordnungen, mit einer selbstansaugenden Förderpumpe je Bremskreis, mit einem Ansaugventil zwischen dem Hauptbremszylinder und einem Eingang der Förderpumpe, die mit den Druckaufbau- und Druckabsenkventilanordnungen verbunden ist, und mit einem Umschaltventil zwischen einem Ausgang der Förderpumpe und dem Hauptbremszylinder, dadurch gekennzeichnet, daß dem Ansaugventil ein zweites Ansaugventil parallel geschaltet ist .7.Hydraulic vehicle brake system with a master brake cylinder, with wheel brake cylinders which can be supplied with brake pressure from it, with the pressure build-up and pressure reduction valve arrangements associated with the wheel brake cylinders, with a self-priming feed pump per brake circuit, with a suction valve between the master brake cylinder and an input of the feed pump, which with the pressure build-up and Pressure reduction valve arrangements is connected, and with a changeover valve between an output of the feed pump and the master brake cylinder, characterized in that the intake valve is connected in parallel with a second intake valve.
8. Hydraulische Fahrzeugbremsanlage nach Anspruch 7, dadurch gekennzeichnet, daß ein Ansaugventil (74) als Magnetventil und das andere Ansaugventil (44) als ein hydraulisch steuerbares Ventil ausgebildet ist.8. Hydraulic vehicle brake system according to claim 7, characterized in that an intake valve (74) is designed as a solenoid valve and the other intake valve (44) as a hydraulically controllable valve.
9. Hydraulische Fahrzeugbremsanlage nach Anspruch 8, dadurch gekennzeichnet, daß das hydraulisch steuerbare Ansaugventil9. Hydraulic vehicle brake system according to claim 8, characterized in that the hydraulically controllable intake valve
(44) als ein mittels Druck aus dem Hauptbremszylinder (40) schließbares Absperrventil (10 in Figur 1) ausgebildet ist.(44) is designed as a shut-off valve (10 in FIG. 1) which can be closed by pressure from the master brake cylinder (40).
10. Hydraulische Fahrzeugbremsanlage nach Anspruch 7, dadurch gekennzeichnet, daß beide Ansaugventile (74, 44a) als Magnetventile ausgebildet sind. 10. Hydraulic vehicle brake system according to claim 7, characterized in that both intake valves (74, 44a) are designed as solenoid valves.
11. Hydraulische Fahrzeugbremsanlage nach Anspruch 10, dadurch gekennzeichnet, daß die beiden Ansaugventile (74, 44a) baugleich ausgebildet sind. 11. Hydraulic vehicle brake system according to claim 10, characterized in that the two intake valves (74, 44a) are constructed identically.
EP98902944A 1997-03-13 1998-01-09 Hydraulically actuated stop valve and hydraulic brake system for a vehicle Withdrawn EP0898531A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19710426 1997-03-13
DE19710426 1997-03-13
DE19732988 1997-07-31
DE19732988A DE19732988A1 (en) 1997-03-13 1997-07-31 Hydraulically operated shut-off valve and hydraulic vehicle brake system
PCT/DE1998/000054 WO1998040257A1 (en) 1997-03-13 1998-01-09 Hydraulically actuated stop valve and hydraulic brake system for a vehicle

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EP0898531A1 true EP0898531A1 (en) 1999-03-03

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EP98902944A Withdrawn EP0898531A1 (en) 1997-03-13 1998-01-09 Hydraulically actuated stop valve and hydraulic brake system for a vehicle

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US (1) US6189984B1 (en)
EP (1) EP0898531A1 (en)
JP (1) JP2000511491A (en)
WO (1) WO1998040257A1 (en)

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DE10327567B4 (en) * 2003-06-18 2014-07-10 Robert Bosch Gmbh Method for actuating a foreign-power parking brake system
DE102011089956A1 (en) * 2011-12-27 2013-06-27 Robert Bosch Gmbh Hydraulically controlled storage chamber valve
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WO1998040257A1 (en) 1998-09-17
JP2000511491A (en) 2000-09-05
US6189984B1 (en) 2001-02-20

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