WO2011098468A1 - Pressure control valve assembly comprising a bypass duct for cooling the solenoid of a pilot valve - Google Patents

Pressure control valve assembly comprising a bypass duct for cooling the solenoid of a pilot valve Download PDF

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Publication number
WO2011098468A1
WO2011098468A1 PCT/EP2011/051867 EP2011051867W WO2011098468A1 WO 2011098468 A1 WO2011098468 A1 WO 2011098468A1 EP 2011051867 W EP2011051867 W EP 2011051867W WO 2011098468 A1 WO2011098468 A1 WO 2011098468A1
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WO
WIPO (PCT)
Prior art keywords
pressure
valve
solenoid
brake
diaphragm
Prior art date
Application number
PCT/EP2011/051867
Other languages
German (de)
French (fr)
Inventor
Martin Bohley
Original Assignee
Knorr-Bremse Systeme für Nutzfahrzeuge GmbH
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Filing date
Publication date
Application filed by Knorr-Bremse Systeme für Nutzfahrzeuge GmbH filed Critical Knorr-Bremse Systeme für Nutzfahrzeuge GmbH
Publication of WO2011098468A1 publication Critical patent/WO2011098468A1/en

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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
    • B60T8/36—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 including a pilot valve responding to an electromagnetic force
    • B60T8/3605—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 including a pilot valve responding to an electromagnetic force wherein the pilot valve is mounted in a circuit controlling the working fluid system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/48—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
    • B60T8/4818—Traction control, stability control, using both the wheel brakes and other automatic braking systems in pneumatic brake systems

Definitions

  • the invention relates to a pressure control valve arrangement for controlling the fluid pressure in a fluid-actuated and slip-controlled brake system of a vehicle such that in the context of the brake slip control, the brake pressure in at least one brake cylinder is increased, maintained or lowered, according to the preamble of Claim 1.
  • a slip-controlled braking system such as ABS (Anti-lock Braking System) prevents the wheels from locking and acts when a greater traction is required between a tire and the road surface than is transferable, i. when overbraking by the driver.
  • ABS Anti-lock Braking System
  • the central electronic control unit recognizes the
  • ABS brake system from Drehbaumtolersignalen the Blockierne Trent one or more wheels and calculates the control of the force acting on the associated brake cylinder pressure control valve assembly.
  • the brake pressure is then by means of the pressure control valve assembly by pressure lowering, pressure holding or
  • Pressure climbers set according to the wheel behavior and thus the friction conditions between the tire and the road to an optimal slip.
  • ABS pressure control valve arrangements without relay effect can be found on vehicles such as commercial vehicles, buses and coaches,
  • Pressure control valve assemblies without relay action usually have 3/2-way solenoid valves as pilot valves of diaphragm valves, wherein an electronic control device controls the 3/2-way solenoid valves to the necessary functions for the ABS operation
  • the pressure medium usually air in the bleeding and bleeding of the brake cylinder, flows through the pressure control valve assemblies unhindered in both directions it is ensured that the function of the service brake system is not influenced by the ABS pressure control valve arrangement.
  • Pressure control valves of the generic type as 1-channel pressure control valves for anti-lock systems of motor vehicles have within the housing depending on a diaphragm valve as a holding valve and as an exhaust valve and an electromagnetic control valve for the membrane holding valve and the membrane outlet valve.
  • the two diaphragm valves each contain a membrane which can be acted upon by the pressure in a pilot control chamber, and the electromagnetic control valves each have an armature which can be actuated by means of an electric solenoid and which cooperates with two solenoid valve seats in each case.
  • a generic pressure control valve assembly of an ABS brake system is known for example from EP 0266555 A1 or from DE-A 2855876.
  • pressure hold that is, when the pressure set by the pressure control valve set brake pressure is maintained, the solenoid coil of the membrane holding valve associated electromagnetic pilot valve is energized, whereby the armature of the pilot valve is urged sealingly against the action of spring means against the associated solenoid valve seat.
  • the problem is that for a longer "pressure holding" as it is necessary, for example, in the context of a long downhill or ACC (Adaptive Cruise Control) to keep the distance to a vehicle in front and braking, the magnetic coil of the retaining diaphragm valve associated This overheating can lead to damage to the solenoid coil, which is why in practice the ABS control unit only allows a certain maximum activation or energization time of the solenoid coil, when this maximum value is exceeded When the solenoid is again cooled after a time known from experience, it is energized by the ABS control unit again energizing the solenoid coil is stopped, whereby the pressure holding state can not be maintained.
  • ACC Adaptive Cruise Control
  • the invention has the object of providing a pressure control valve arrangement of the type mentioned in such a way that the temperature load of the solenoid coil of the retaining diaphragm valve associated pilot valve is reduced during energization.
  • the invention achieves this object by proposing, on the one hand, that a pressure medium flow of .beta., Which is forced against the solenoid valve seat when the solenoid is energized against the magnet valve seat, of the electromagnetic pilot control valve assigned to the holding diaphragm valve the chamber along at least a part of the magnetic coil to the
  • Pressure sink enabling bypass means are provided.
  • the arranged in the housing chamber is connected in the context of the function "pressure risers" by opening the holding diaphragm valve to the pressure medium connection and thereby pressurized or aerated, whereby the chamber under a relation to the function "pressure risers"
  • Atmospheric pressure is set higher brake pressure. This pressure or the amount of air generating this pressure is then enclosed in the chamber during the transition from the state of "pressure increase” to the state “pressure hold” during the closing of the membrane holding valve and can generate via the bypass means the pressure of the solenoid coil cooling fluid flow.
  • the by-pass means then effectively bridge the flow cross-section closed by the magnet armature sealingly abutting the magnet valve seat and thereby permit a flow of pressure medium along at least part of the magnet coil.
  • this magnetic coil Due to this pressure medium flow, this magnetic coil is cooled in the state "pressure keeping" in which the flow cross section through the magnetic valve seat is actually closed
  • the bypass means are designed such that the volume flow of the pressure medium flow is smaller than an upper limit volume flow through which the holding diaphragm valve is switchable from a closed position to an open position. This prevents the volume flow of the bypass flow from becoming so great that it can influence the (switching) state of the membrane holding valve. Because the volume flow of the bypass flow flowing through the bypass means to serve only the cooling of the magnetic coil of the diaphragm holding valve associated pilot valve.
  • the bypass means are formed by a trained on the circumference of the solenoid valve seat bypass channel so that remains at least partially open when sealed against the magnetic valve seat armature of the flow cross section of the bypass channel.
  • a bypass channel on the circumference of the solenoid valve seat is in a simple manner producible bar, in particular by a local recess on the circumference of the solenoid valve seat.
  • FIG. 1 is a schematic diagram of an ABS brake system as a general diagram of a 4S / 4K ABS brake system of a vehicle
  • 2a is a schematic representation of a brake cylinder an mortupressure control valve a north n i ng i m state "pressure risers",
  • FIG. 2b is a schematic representation of the pressure control valve arrangement of Figure 2a in the state "pressure lowering”,
  • Fig. 2c is a schematic representation of the pressure control valve assembly of Figure 2a in the "hold pressure".
  • a vehicle equipped with an ABS brake system has a front axle 1 and a rear axle 2.
  • wheels 3a and 3b are arranged;
  • the rear axle 2 has wheels 4a and 4b each equipped with twin tires.
  • the braking system for these wheels 3a, 3b and 4a, 4b serving ABS brake system is designed here in the manner of a 4S / 4K system (four sensors, four channels). This means that a total of four speed sensors 5a-5d and four pressure control valve arrangements 7a-7d are available here.
  • the pressure control valve assemblies 7a-7d are used to control each associated brake cylinders 6a-6d.
  • About a branching pneumatic brake pressure line 8 are all pressure control valve assemblies 7a-7d with a foot brake valve 9 in conjunction.
  • the driver When the foot brake valve 9 is actuated, the driver generates a brake pressure which, via the pneumatic brake pressure line 8, passes the pressure control valve arrangements 7a-7d to the wheels 3a, 3b and the wheels 4a, 4b associated brake cylinders 6a-6d is forwarded.
  • the pressure control valve arrangements 7a-7d can be actuated via integrated solenoid valves 15a, 15b shown in FIGS. 2a, 2b and 2c and are electrically connected for this purpose to a central electronic control unit, in particular an ABS control device 10.
  • the electronic control unit 10 communicates with the four speed sensors 5 a - 5 b determining the wheel speeds.
  • the brake pressure applied by the driver via the foot brake valve 9 is reduced by the corresponding pressure control valve arrangement 7a-7d in accordance with an ABS control in accordance with the electronic control unit 10 until the blocking has been eliminated.
  • the ABS brake system of the present embodiment further includes an ASR function that includes an ASR unit 11 for reducing engine torque such as an ASR solenoid valve 12 and a shuttle valve 13.
  • the pressure control valve arrangement 7 used according to FIG. 2a in the context of the ABS brake system for the purpose of ABS regulation is constructed here in the manner of a 1-channel pressure control valve arrangement and consists essentially of two integrated diaphragm valves 14a and 14b and two actuated by spring elements 17a, 17b in one of two closing directions biased solenoid valves 15a, 15b.
  • Diaphragms 18a, 18b of the diaphragm valves 14a and 14b are each provided by spring elements 16a, 16b loaded in the single closing direction and are piloted via the respectively associated solenoid valves 15a and 15b.
  • the diaphragm valves 1 4a, 1 4b one is a holding or inlet diaphragm valve 14a and the other is an outlet diaphragm valve 14b.
  • a housing 21 of the pressure control valve arrangement 7 furthermore has a pressure medium connection 23 for pressurizing and / or depressurizing the pressure control valve arrangement 7 and a working connection 24 for connecting the brake cylinder 6.
  • the pressure medium connection 23 is aerated or vented via the brake pressure line 8 to the foot or service brake valve 9 of the pressure-medium-actuated brake device in accordance with actuation of the foot brake valve 9.
  • the two electromagnetic valves 15a, 15b each have a magnetic coil 19a, 19b, whereby solenoid coils 19a, 19b with magnetic valve seats 20a, 20b or 29a, 29b of the electromagnetic valves 1 5a, 1 5 b to sa mmen wi rke nd e magnet armature 22 a, 22 b are operated as valve closing members.
  • the magneto-anchors 22a, 22b cooperate with two solenoid valve seats 20a, 20b and 29a, 29b, respectively.
  • the armature 22a, 22b are pressed against the upper magnetic valve seats 29a, 29b due to the bias by the spring means 17a, 17b in the de-energized state of the magnetic coils 19a, 19b.
  • the spring means 17a, 17b then bias the armature 22a in particular into a position raised from the lower magnetic valve seat 20a, in which a flow cross-section is released, the a chamber 26a formed in the housing 21 communicates with a pressure sink 27a in the form of a vent port.
  • the magnet armatures 22a, 22b are urged against the action of the spring means 17a, 17b against the lower magnet valve seats 20a, 20b.
  • the chamber 26a is connected to the pressure medium connection 23 and thus to the foot brake valve 9 when the diaphragm 18a of the holding diaphragm valve 14a lifts off from its associated diaphragm valve seat 28a.
  • the working port 24 and thus the brake cylinder 6 gets in communication with another pressure sink 30 when the diaphragm 18b of the outlet diaphragm valve 14b lifts from its associated diaphragm valve seat 28b.
  • the second electromagnetic valve 15b which is opened in its spring-loaded basic position, receives the brake pressure from the foot brake valve 9 on the diaphragm 18b of the outlet diaphragm valve 14b from the right and urges them against their diaphragm valve seat 28b, leaving the outlet diaphragm valve 14b closed.
  • the pressurized air under brake pressure passes through the pressure control valve 7.
  • the pressure control valve arrangement 7 is in the state where the pressure control valve arrangement 7 is not in the ABS control mode.
  • the braking pressure applied by the foot brake valve 9 via the old diaphragm valve 14a arrives in a chamber 26a formed in the housing 21 and can also act on the diaphragm 18a from the left side.
  • the pressure on the right and left side of the diaphragm 18a of the diaphragm valve 14a is the same size.
  • the holding diaphragm valve 14a is closed, that is, the diaphragm 18a is urged against the diaphragm valve seat 28a.
  • the pressure control valve arrangement 7 closes the pneumatic brake pressure line 8 extending from the foot brake valve 9 to the brake cylinder 6 in order to keep the pressure constant.
  • a bypass passage 31 is formed, through which a compressed air flow from the chamber 26a along at least a portion of the solenoid coil 19a of the membrane holding valve 14a associated solenoid valve 15a can flow to the pressure sink 27a. This compressed air flow can then cool the energized solenoid 19a.
  • the bypass channel 31 bridges the flow cross-section closed by the magnet armature 22a sealingly seated on the magnet valve seat 20a and allows compressed-air flow along at least part of the magnet coil 19a, preferably along its entire longitudinal extension and parallel to it, as indicated by the arrow 32 in FIG ,
  • the bypass channel 31 is designed in particular with respect to its cross section such that the volume flow of compressed air flow through the bypass channel 31 is smaller than an upper limit flow rate through which the holding diaphragm valve 14a could be switched from its closed position back to its open position. Because due to the bypass channel 31 through and to the Drucksen ke 27a flowing compressed air sin kt the pressure in the chamber 26a and thus the pressure on the left effective surface of Me mb ra ne 1 8 ad H al te diaphragm valve 14 a. This prevents the volume flow of the bypass flow from becoming so great that it influences the (switching) state of the membrane holding valve 14a is able to take.
  • bypass channel 31 is preferably formed on the circumference of the solenoid valve seat 20a and parallel to the central axis of the magnet armature 22a and to the coil 19a, and leaves despite of the magnetic valve seat 20a sealing magnet armature 36a a certain flow cross section open.
  • a pressure reduction (“pressure lowering") is achieved in the brake cylinder 6 by energizing both solenoid valves 15a and 15b the magnet armature 22b of the other solenoid valve 15b is lifted from the lower solenoid valve seat 20b against the action of the spring means 17b due to the energization of its solenoid coil 19b and urged against the upper solenoid valve seat 29b the membrane 1 8b of the outlet diaphragm valve 14b can lift off from the diaphragm valve seat 28b, so that the working port 24 and thus the brake cylinder 6 is connected to the pressure sink 30 for venting.

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

Abstract

The invention relates to a pressure control valve assembly (7) for controlling the fluid pressure in a pressure medium-actuated and slip-regulated brake system of a vehicle, wherein as part of the brake slip regulation the brake pressure in at least a brake cylinder (6) is retained, wherein bypass means (31), which make a pressure medium flow possible from the chamber (26a) along at least a part of the solenoid (19a) as far as the pressure sink (27a), are provided by an armature (22a) of the electromagnetic pilot valve (15a) that is associated with the retaining membrane valve (14a) being pressed against the solenoid valve seat (20a) when the solenoid (19a) is energised, and wherein the bypass means (31) are designed such that the volumetric flow of the pressure medium flow is less than an upper limit volumetric flow, by means of which the retaining membrane valve (14a) can be switched from a closed position to an open position.

Description

Drucksteuerventilanordnung mit Bypasskanal zur Kühlung der Magnetspule eines Vorsteuerventils Die Erfindung betrifft eine Drucksteuerventilanordnung zur Steuerung des Fluiddrucks in einer druckmittelbetätigten und schlupfgeregelten Bremsanlage eines Fahrzeugs derart, dass im Rahmen der Bremsschlupfregelung der Bremsdruck in wenigstens einem Bremszylinder gesteigert, gehalten oder gesenkt wird, gemäß dem Oberbegriff von Anspruch 1.  The invention relates to a pressure control valve arrangement for controlling the fluid pressure in a fluid-actuated and slip-controlled brake system of a vehicle such that in the context of the brake slip control, the brake pressure in at least one brake cylinder is increased, maintained or lowered, according to the preamble of Claim 1.
Ein schlupfgeregeltes Bremssystem wie ABS (Antiblockiersystem) verhindert ein Blockieren der Räder und tritt in Funktion, wenn zwischen einem Reifen und der Fahrbahn ein größerer Kraftschluss beansprucht wird, als übertragbar ist, d.h. wenn durch den Fahrer überbremst wird. Bei Überbremsung erkennt das zentrale elektronische Steuergerät der A slip-controlled braking system, such as ABS (Anti-lock Braking System) prevents the wheels from locking and acts when a greater traction is required between a tire and the road surface than is transferable, i. when overbraking by the driver. During overbraking the central electronic control unit recognizes the
ABS-Bremsanlage aus Drehzahlfühlersignalen die Blockierneigung eines oder mehrerer Räder und berechnet daraus die Ansteuerung der auf den zugeordneten Bremszylinder einwirkenden Drucksteuerventilanordnung. Der Bremsdruck wird dann mittels der Drucksteuerventilanordnung durch Drucksenken, Druckhalten oderABS brake system from Drehzahlfühlersignalen the Blockierneigung one or more wheels and calculates the control of the force acting on the associated brake cylinder pressure control valve assembly. The brake pressure is then by means of the pressure control valve assembly by pressure lowering, pressure holding or
Drucksteigern nach Maßgabe des Radverhaltens und damit der Reibungsverhältnisse zwischen Reifen und Fahrbahn auf einen optimalen Schlupf eingestellt. Pressure climbers set according to the wheel behavior and thus the friction conditions between the tire and the road to an optimal slip.
ABS-Drucksteuerventilanordnungen ohne Relaiswirkung finden bei Fahrzeugen wie beispielsweise Nutzfahrzeugen, Omnibussen,ABS pressure control valve arrangements without relay effect can be found on vehicles such as commercial vehicles, buses and coaches,
Sattelzugmaschinen wie auch bei Anhängern Verwendung. Drucksteuerventilanordnungen ohne Relaiswirkung verfügen meist über 3/2-Wege-Magnetventile als Vorsteuerventile von Membranventilen, wobei eine elektronische Steuereinrichtung die 3/2-Wege-Magnetventile ansteuert, um die für den ABS-Betrieb notwendigen Funktionen „Druckhalten", „Drucksenken" und „Drucksteigern" durchführen zu können. Während einer Bremsung ohne Ansprechen des ABS (keine Blockierneigung eines Rades) durchströmt das Druckmittel, meist Luft be i m Be- und Entlüften der Bremszylinder die Drucksteuerventilanordnungen ungehindert in beiden Richtungen. Damit ist sichergestellt, dass die Funktion der Betriebsbremsanlage nicht durch die ABS-Drucksteuerventilanordnung beeinflusst wird. Semitrailer tractors as well as trailers use. Pressure control valve assemblies without relay action usually have 3/2-way solenoid valves as pilot valves of diaphragm valves, wherein an electronic control device controls the 3/2-way solenoid valves to the necessary functions for the ABS operation During braking without ABS response (no tendency to lock a wheel), the pressure medium, usually air in the bleeding and bleeding of the brake cylinder, flows through the pressure control valve assemblies unhindered in both directions it is ensured that the function of the service brake system is not influenced by the ABS pressure control valve arrangement.
Drucksteuerventile der gattungsgemäßen Art als 1 -Kanal- Drucksteuerventile für Blockierschutzanlagen von Kraftfahrzeugen weisen innerhalb des Gehäuses je ein Membranventil als Halteventil und als Auslassventil auf sowie je ein elektromagnetisches Steuerventil für das Membran-Halteventil und das Membran-Auslassventil auf. Die beiden Membranventile beinhalten jeweils eine mit dem Druck in einem Vorsteuerraum beaufschlagbare Membrane und die elektromagnetischen Steuerventile jeweils einen mittels einer elektrischen Magnetspule betätigbaren Magnetanker, welcher mit jeweils zwei Magnetventilsitzen zusammen wirkt. Pressure control valves of the generic type as 1-channel pressure control valves for anti-lock systems of motor vehicles have within the housing depending on a diaphragm valve as a holding valve and as an exhaust valve and an electromagnetic control valve for the membrane holding valve and the membrane outlet valve. The two diaphragm valves each contain a membrane which can be acted upon by the pressure in a pilot control chamber, and the electromagnetic control valves each have an armature which can be actuated by means of an electric solenoid and which cooperates with two solenoid valve seats in each case.
Eine gattungsgemäße Drucksteuerventilanordnung einer ABS- Bremsanlage ist beispielsweise aus der EP 0266555 A1 oder aus der DE-A 2855876 bekannt. Im Betriebsmodus„Druckhalten", d.h. wenn der von der Drucksteuerventilanordnung gerade eingestellte Bremsdruck aufrechterhalten werden soll, ist die Magnetspule des dem Membran-Halteventil zugeordneten elektromagnetischen Vorsteuerventils bestromt, wodurch der Magnetanker des Vorsteuerventils gegen die Wirkung von Federmitteln gegen den zugeordneten Magnetventilsitz dichtend gedrängt ist. Problematisch ist dabei, dass für ein längeres „Druckhalten" wie es beispielsweise Im Rahmen einer langen Bergabfahrt oder im Rahmen einer ACC (Adaptive Cruise Control) zum Konstanthalten des Abstands zu einem vorausfahrenden und bremsenden Fahrzeug notwendig ist, die Magnetspule des dem Halte-Membranventil zugeordneten Vorsteuerventils ständig bestromt werden muss, was eine gewisse Temperaturbelastung der Magnetspule mit sich bringt. Diese Überhitzung kann zu Schäden der Magnetspule führen, weshalb aus der Praxis das ABS-Steuergerät nur eine gewisse maximale Ansteuer- oder Bestromungszeit der Magnetspule zulässt. Bei einem Überschreiten dieser maximalen Ansteuerzeit wird dann die Bestromung der Magnetspule gestoppt, wodurch der Druckhaltezustand allerdings nicht aufrechterhalten werden kann. Erst wenn die Magnetspule nach einer aus Erfahrung bekannten Zeit wieder abgekühlt ist, wird sie vom ABS-Steuergerät wieder bestromt. A generic pressure control valve assembly of an ABS brake system is known for example from EP 0266555 A1 or from DE-A 2855876. In the operating mode "pressure hold", that is, when the pressure set by the pressure control valve set brake pressure is maintained, the solenoid coil of the membrane holding valve associated electromagnetic pilot valve is energized, whereby the armature of the pilot valve is urged sealingly against the action of spring means against the associated solenoid valve seat. The problem is that for a longer "pressure holding" as it is necessary, for example, in the context of a long downhill or ACC (Adaptive Cruise Control) to keep the distance to a vehicle in front and braking, the magnetic coil of the retaining diaphragm valve associated This overheating can lead to damage to the solenoid coil, which is why in practice the ABS control unit only allows a certain maximum activation or energization time of the solenoid coil, when this maximum value is exceeded When the solenoid is again cooled after a time known from experience, it is energized by the ABS control unit again energizing the solenoid coil is stopped, whereby the pressure holding state can not be maintained.
Der Erfindung liegt die Aufgabe zugrunde, eine Drucksteuerventilanordnung der eingangs erwähnten Art derart weiter zu bilden, dass die Temperaturbelastung der Magnetspule des dem Halte-Membranventil zugeordneten Vorsteuerventils beim Bestromen herabgesetzt wird. The invention has the object of providing a pressure control valve arrangement of the type mentioned in such a way that the temperature load of the solenoid coil of the retaining diaphragm valve associated pilot valve is reduced during energization.
Diese Aufgabe wird erfindungsgemäß durch die Merkmale von Anspruch 1 gelöst. This object is achieved by the features of claim 1.
Offenbarung der Erfindung Disclosure of the invention
Die Erfindung löst diese Aufgabe, indem sie einerseits vorschlägt, dass durch bei Bestromung der Magnetspule gegen den Magnetventilsitz gedrängten Magnetanker des dem Halte-Membranventil zugeordneten elektromagnetischen Vorsteuerventils eine Druckmittelströmung von der Kammer entlang zumindest eines Teils der Magnetspule bis zurThe invention achieves this object by proposing, on the one hand, that a pressure medium flow of .beta., Which is forced against the solenoid valve seat when the solenoid is energized against the magnet valve seat, of the electromagnetic pilot control valve assigned to the holding diaphragm valve the chamber along at least a part of the magnetic coil to the
Drucksenke ermöglichende Bypass-Mittel vorgesehen sind. Pressure sink enabling bypass means are provided.
Von den beiden Magnetventilsitzen, mit welchen der Magnetanker des dem Membran-Halteventil zugeordneten Steuerventils zusammen wirkt, ist dabei der Magnetventilsitz betroffen, gegen welchen der Magnetanker durch die bestromte Magnetspule im ZustandOf the two solenoid valve seats, with which the armature of the membrane holding valve associated control valve cooperates, while the magnetic valve seat is affected, against which the armature by the energized magnetic coil in the state
„Druckhalten" dichtend gedrängt wird. "Pressure keeping" is urged sealingly.
Die im Gehäuse angeordnete Kammer wird im Rahmen der Funktion „Drucksteigern" durch Öffnen des Halte-Membranventils mit dem Druckmittelanschluss verbunden und dadurch druckbeaufschlagt bzw. belüftet, wodurch die Kammer unter einen gegenüber demThe arranged in the housing chamber is connected in the context of the function "pressure risers" by opening the holding diaphragm valve to the pressure medium connection and thereby pressurized or aerated, whereby the chamber under a relation to the
Atmosphärendruck höheren Bremsdruck gesetzt wird. Dieser Druck bzw. die diesen Druck erzeugende Luftmenge wird beim Schließen des Membran-Halteventils während des Übergangs vom Zustand „Drucksteigern" auf den Zustand„Druckhalten" dann in der Kammer eingeschlossen und kann über den Bypass-Mittel die die Magnetspule kühlende Druckmittelströmung erzeugen. Atmospheric pressure is set higher brake pressure. This pressure or the amount of air generating this pressure is then enclosed in the chamber during the transition from the state of "pressure increase" to the state "pressure hold" during the closing of the membrane holding valve and can generate via the bypass means the pressure of the solenoid coil cooling fluid flow.
Die Bypass-Mittel überbrücken dann gewissermaßen den durch den am Magnetventilsitz dichtend anliegenden Magnetanker verschlossenen Strömungsquerschnitt und ermöglichen dadurch eine Druckmittelströmung entlang wenigstens eines Teils der Magnetspule.The by-pass means then effectively bridge the flow cross-section closed by the magnet armature sealingly abutting the magnet valve seat and thereby permit a flow of pressure medium along at least part of the magnet coil.
Bedingt durch diese Druckmittelströmung wird diese Magnetspule in dem Zustand „Druckhalten" gekühlt, in welchem der Strömungsquerschnitt durch den Magnetventilsitz eigentlich verschlossen ist. Bedingt durch diese Maßnahme kann einerseits die Zeitdauer der Bestromung der Magnetspule und damit auch dieDue to this pressure medium flow, this magnetic coil is cooled in the state "pressure keeping" in which the flow cross section through the magnetic valve seat is actually closed
Zeitdauer verlängert werden, mit der die Drucksteuerventilanordnung im Zustand„Druckhalten" betrieben werden kann. Weiterhin erhöht sich auch die Lebensdauer der Magnetspule. Duration be extended, with which the pressure control valve arrangement in In addition, the service life of the solenoid coil is increased.
Andererseits sind die Bypass-Mittel derart ausgeführt, dass der Volumenstronn der Druckmittelströmung kleiner als ein oberer Grenz- Volumenstrom ist, durch welchen das Halte-Membranventil von einer Schließstellung in eine Öffnungsstellung schaltbar ist. Dadurch wird verhindert, dass der Volumenstrom der Bypass-Strömung so groß wird, dass sie Einfluss auf den (Schalt-) Zustand des Membran-Halteventils zu nehmen vermag. Denn der Volumenstrom der durch die Bypass-Mittel strömenden Bypass-Strömung soll ausschließlich der Kühlung der Magnetspule des dem Membran-Halteventil zugeordneten Vorsteuerventils dienen. On the other hand, the bypass means are designed such that the volume flow of the pressure medium flow is smaller than an upper limit volume flow through which the holding diaphragm valve is switchable from a closed position to an open position. This prevents the volume flow of the bypass flow from becoming so great that it can influence the (switching) state of the membrane holding valve. Because the volume flow of the bypass flow flowing through the bypass means to serve only the cooling of the magnetic coil of the diaphragm holding valve associated pilot valve.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der in Anspruch 1 angegebenen Erfindung möglich.  The measures listed in the dependent claims advantageous refinements and improvements of claim 1 invention are possible.
Besonders bevorzugt werden die Bypass-Mittel durch einen am Umfang des Magnetventilsitzes ausgebildeten Bypasskanal derart gebildet, dass bei gegen den Magnetventilsitz dichtendem Magnetanker der Strömungsquerschnitt des Bypasskanals wenigstens teilweise geöffnet bleibt. Ein solcher Bypasskanal am Umfang des Magnetventilsitzes ist auf einfache Weise herstell bar, insbesondere durch eine lokale Ausnehmung am Umfang des Magnetventilsitzes. Particularly preferably, the bypass means are formed by a trained on the circumference of the solenoid valve seat bypass channel so that remains at least partially open when sealed against the magnetic valve seat armature of the flow cross section of the bypass channel. Such a bypass channel on the circumference of the solenoid valve seat is in a simple manner producible bar, in particular by a local recess on the circumference of the solenoid valve seat.
Weitere die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Zeichn ung näher dargestellt. In der Zeichnung zeigt Fig. 1 eine Prinzipdarstellung einer ABS-Bremsanlage als allgemeines Schema einer 4S/4K-ABS-Bremsanlage eines Fahrzeugs, Further measures improving the invention will be described in more detail below together with the description of a preferred embodiment of the invention with reference to the drawing. In the drawing shows 1 is a schematic diagram of an ABS brake system as a general diagram of a 4S / 4K ABS brake system of a vehicle,
Fig. 2a eine schematische Darstellung einer einen Bremszyl inder ansteuernden Drucksteuerventil a nord n u ng i m Zustand „Drucksteigern", 2a is a schematic representation of a brake cylinder ansteuernden pressure control valve a north n i ng i m state "pressure risers",
Fig. 2b eine schematische Darstellung der Drucksteuerventilanordnung von Figur 2a im Zustand„Drucksenken", 2b is a schematic representation of the pressure control valve arrangement of Figure 2a in the state "pressure lowering",
Fig. 2c eine schematische Darstellung der Drucksteuerventilanordnung von Figur 2a im Zustand "Druckhalten". Fig. 2c is a schematic representation of the pressure control valve assembly of Figure 2a in the "hold pressure".
Beschreibung des Ausführungsbeispiels Description of the embodiment
Gemäß Fig . 1 weist ein m it einer ABS-Bremsanlage ausgestattetes Fahrzeug eine Vorderachse 1 sowie eine Hinterachse 2 auf. An der Vorderachse 1 sind Räder 3a und 3b angeordnet; die Hinterachse 2 weist beispielsweise jeweils mit Zwillingsbereifung ausgestattete Räder 4a und 4b auf. Die zur Bremsung dieser Räder 3a, 3b und 4a, 4b dienende ABS-Bremsanlage ist hier nach Art einer 4S/4K-Anlage (vier Sensoren, vier Kanäle) ausgebildet. Dies bedeutet, dass hier insgesamt vier Drehzahlsensoren 5a-5d sowie vier Drucksteuerventilanordnungen 7a-7d zur Verfügung stehen. Die Drucksteuerventilanordnungen 7a-7d dienen der Ansteuerung von jeweils zugeordneten Bremszylindern 6a- 6d. Über eine sich verzweigende pneumatische Bremsdruckleitung 8 stehen alle Drucksteuerventilanordnungen 7a-7d mit einem Fußbremsventil 9 in Verbindung.  According to FIG. 1, a vehicle equipped with an ABS brake system has a front axle 1 and a rear axle 2. On the front axle 1 wheels 3a and 3b are arranged; For example, the rear axle 2 has wheels 4a and 4b each equipped with twin tires. The braking system for these wheels 3a, 3b and 4a, 4b serving ABS brake system is designed here in the manner of a 4S / 4K system (four sensors, four channels). This means that a total of four speed sensors 5a-5d and four pressure control valve arrangements 7a-7d are available here. The pressure control valve assemblies 7a-7d are used to control each associated brake cylinders 6a-6d. About a branching pneumatic brake pressure line 8 are all pressure control valve assemblies 7a-7d with a foot brake valve 9 in conjunction.
Der Fahrer erzeugt bei Betätigung des Fußbremsventils 9 einen Bremsdruck, der über die pneumatische Bremsdruckleitung 8 die Drucksteuerventilanordnungen 7a-7d passierend an die den Rädern 3a, 3b sowie den Rädern 4a, 4b zugeordneten Bremszylindern 6a-6d weitergeleitet wird. When the foot brake valve 9 is actuated, the driver generates a brake pressure which, via the pneumatic brake pressure line 8, passes the pressure control valve arrangements 7a-7d to the wheels 3a, 3b and the wheels 4a, 4b associated brake cylinders 6a-6d is forwarded.
Die Drucksteuerventilanordnungen 7a-7d sind über integrierte, in Fig.2a, Fig.2b und Fig.2c gezeigte Elektromagnetventile 15a, 15b ansteuerbar und sind zu diesem Zwecke mit einer zentralen elektronischen Steuereinheit, insbesondere einer ABS- Steuereinrichtung 10 elektrisch verbunden. The pressure control valve arrangements 7a-7d can be actuated via integrated solenoid valves 15a, 15b shown in FIGS. 2a, 2b and 2c and are electrically connected for this purpose to a central electronic control unit, in particular an ABS control device 10.
Eingangsseitig steht die elektronische Steuereinheit 10 mit den vier die Radgeschwindigkeiten ermittelnden Drehzahlsensoren 5a-5b in Verbindung. Im Falle des Blockierens eines Rades 3a-3d, d.h. bei einem Überschreiten eines optimalen Bremsschlupfes wird entsprechend einer ABS-Regelung nach Maßgabe der elektronischen Steuereinheit 10 der vom Fahrer über das Fußbremsventil 9 eingesteuerte Bremsdruck durch die entsprechende Drucksteuerventilanordnung 7a-7d soweit herabgesetzt, bis das Blockieren beseitigt ist. Die ABS-Bremsanlage des vorliegenden Ausführungsbeispiels umfasst weiterhin eine ASR-Funktion, welche eine ASR-Einheit 11 zum Reduzieren des Motormoments wie ein ASR- Magnetventil 12 und ein Wechselventil 13 umfasst. On the input side, the electronic control unit 10 communicates with the four speed sensors 5 a - 5 b determining the wheel speeds. In the case of blocking a wheel 3a-3d, i. when an optimum brake slip is exceeded, the brake pressure applied by the driver via the foot brake valve 9 is reduced by the corresponding pressure control valve arrangement 7a-7d in accordance with an ABS control in accordance with the electronic control unit 10 until the blocking has been eliminated. The ABS brake system of the present embodiment further includes an ASR function that includes an ASR unit 11 for reducing engine torque such as an ASR solenoid valve 12 and a shuttle valve 13.
Die gemäß Figur 2a im Rahmen der ABS-Bremsanlage zum Zwecke der ABS-Regelung eingesetzte Drucksteuerventilanordnung 7 ist hier nach Art einer 1-Kanal-Drucksteuerventilanordnung aufgebaut und besteht im Wesentlichen aus zwei integrierten Membranventilen 14a und 14b und zwei diese ansteuernden, durch Federelemente 17a, 17b in der einen von zwei Schließrichtungen vorgespannte Elektromagnetventilen 15a, 15b. Membrane 18a, 18b der Membranventile 14a und 14b sind jeweils durch Federelemente 16a, 16b in die einzige Schließrichtung belastet und werden über die jeweils zugeordneten Elektromagnetventile 15a und 15b vorgesteuert. Von den Membran ventilen 1 4a, 1 4b ist das eine ein Halte- oder Einlass- Membranventil 14a und das andere ein Auslass-Membranventil 14b. The pressure control valve arrangement 7 used according to FIG. 2a in the context of the ABS brake system for the purpose of ABS regulation is constructed here in the manner of a 1-channel pressure control valve arrangement and consists essentially of two integrated diaphragm valves 14a and 14b and two actuated by spring elements 17a, 17b in one of two closing directions biased solenoid valves 15a, 15b. Diaphragms 18a, 18b of the diaphragm valves 14a and 14b are each provided by spring elements 16a, 16b loaded in the single closing direction and are piloted via the respectively associated solenoid valves 15a and 15b. Of the diaphragm valves 1 4a, 1 4b, one is a holding or inlet diaphragm valve 14a and the other is an outlet diaphragm valve 14b.
Ein Gehäuse 21 der Drucksteuerventilanordnung 7 weist weiterhin einen Druckmittelanschluss 23 zur Druckbeaufschlagung und/oder Druckentlastung der Drucksteuerventilanordnung 7 sowie einen in Arbeitsanschluss 24 zum Anschluss des Bremszylinders 6 auf. Der Druckmittelanschluss 23 ist, wie Fig.2a bis Fig.2c zeigen, über die Bremsdruckleitung 8 mit dem Fuß- oder Betriebsbremsventil 9 der druckmittelbetätigten Bremseinrichtung v e r b u n d e n u n d w i rd entsprechend einer Betätigung des Fußbremsventils 9 be- oder entlüftet. A housing 21 of the pressure control valve arrangement 7 furthermore has a pressure medium connection 23 for pressurizing and / or depressurizing the pressure control valve arrangement 7 and a working connection 24 for connecting the brake cylinder 6. As shown in FIGS. 2a to 2c, the pressure medium connection 23 is aerated or vented via the brake pressure line 8 to the foot or service brake valve 9 of the pressure-medium-actuated brake device in accordance with actuation of the foot brake valve 9.
Wie am besten im Detail aus Fig .2c hervorgeht, weisen die beiden Elektromagnetventile 15a, 15b jeweils eine Magnetspule 19a, 19b auf, wobei durch B est ro m u n g d er Magnetspulen 19a, 19b mit Magnetventilsitzen 20a, 20b bzw. 29a, 29b der Elektromagnetventile 1 5a , 1 5 b zu sa m m e n wi rke nd e Magnetanker 22a, 22b als Ventilschließglieder betätigt werden. Dabei wirken die Magentanker 22a, 22b je nach Schaltstellung mit jeweils zwei Magnetventilsitzen 20a, 20b bzw. 29a, 29b zusammen. As best shown in detail in FIG. 2c, the two electromagnetic valves 15a, 15b each have a magnetic coil 19a, 19b, whereby solenoid coils 19a, 19b with magnetic valve seats 20a, 20b or 29a, 29b of the electromagnetic valves 1 5a, 1 5 b to sa mmen wi rke nd e magnet armature 22 a, 22 b are operated as valve closing members. Depending on the switching position, the magneto-anchors 22a, 22b cooperate with two solenoid valve seats 20a, 20b and 29a, 29b, respectively.
Dabei werden die Magnetanker 22a, 22b infolge der Vorspannung durch die Federmittel 17a, 17b im unbestromten Zustand der Magnetspulen 19a, 1 9b gegen die oberen Magnetventilsitze 29a, 29b gedrückt. Die Federmittel 17a, 17b spannen die Magnetanker 22a dann insbesondere in eine vom unteren Magnetventilsitz 20a abgehobene Lage vor, in welcher ein Strömungsquerschnitt freigegeben wird, der eine im Gehäuse 21 ausgebildete Kammer 26a mit einer Drucksenke 27a in Form eines Entlüftungsanschlusses in Verbindung bringt. Bei Bestromung der Magnetspulen 19a, 19b werden die Magnetanker 22a, 22b gegen die Wirkung der Federmittel 1 7a, 17b gegen die unteren Magnetventilsitze 20a, 20b gedrängt. In this case, the armature 22a, 22b are pressed against the upper magnetic valve seats 29a, 29b due to the bias by the spring means 17a, 17b in the de-energized state of the magnetic coils 19a, 19b. The spring means 17a, 17b then bias the armature 22a in particular into a position raised from the lower magnetic valve seat 20a, in which a flow cross-section is released, the a chamber 26a formed in the housing 21 communicates with a pressure sink 27a in the form of a vent port. When current is applied to the magnet coils 19a, 19b, the magnet armatures 22a, 22b are urged against the action of the spring means 17a, 17b against the lower magnet valve seats 20a, 20b.
Die Kammer 26a wird mit dem Druckmittelanschluss 23 und damit mit dem Fußbremsventil 9 verbunden, wenn die Membrane 18a des Halte- Membranventils 14a von seinem zugeordneten Membranventilsitz 28a abhebt. Der Arbeitsanschluss 24 und damit der Bremszylinder 6 gerät mit einer weiteren Drucksenke 30 in Verbindung, wenn die Membrane 18b des Auslass-Membranventils 14b von ihrem zugeordneten Membranventilsitz 28b abhebt. The chamber 26a is connected to the pressure medium connection 23 and thus to the foot brake valve 9 when the diaphragm 18a of the holding diaphragm valve 14a lifts off from its associated diaphragm valve seat 28a. The working port 24 and thus the brake cylinder 6 gets in communication with another pressure sink 30 when the diaphragm 18b of the outlet diaphragm valve 14b lifts from its associated diaphragm valve seat 28b.
Die Drucksteuerventilanordnung 7 ist in Fig.2a in ihrer Offenstellung gezeigt, bei der ein Druckaufbau zum angeschlossenen Bremszylinder 6 erfolgt („Drucksteigern"). Hierbei wird keines der Elektromagnetventile 15a und 15b elektrisch angesteuert. In der gezeigten Stellung drückt die vom Fußbremsventil 9 kommende Druckluft das als Einlass- oder Halteventil ausgebildete Membranventil 14a auf, d.h . aufgrund des an der rechten Wirkfläche der Membrane 18a vom Anschluss 23 her anstehenden Bremsdrucks wird diese vom Membranventilsitz 28a gegen die Wirkung der Federmittel 16a abgehoben. Durch das in seiner federbelasteten Grundstellung gegen den oberen Magnetventilsitz 29a geschlossene Elektromagnetventil 1 5a wird verh indert, dass das zugeordnete Halte-Membranventil 14a wieder verschlossen wird. Durch das in seiner federbelasteten Grundstellung geöffnete zweite Elektromagnetventil 15b steht der vom Fußbremsventil 9 kommende Bremsdruck an der Membrane 18b des Auslass-Membranventils 14b von rechts her an und drängt diese gegen ihren Membranventilsitz 28b, wodurch das das Auslass-Membranventil 14b verschlossen bleibt. Somit durchläuft die unter Bremsdruck stehende Druckluft ungehindert d ie Dru cksteu erventi l a nord n u ng 7. I n d iesem die Druckluft durchleitenden Zustand befindet sich die Drucksteuerventilanordnung 7 auch dann, wenn keine ABS-Regelung erfolgt. 2a in its open position, in which a pressure build-up to the connected brake cylinder 6 takes place ("pressure increase") .Thereby, none of the solenoid valves 15a and 15b are electrically actuated In the position shown, the compressed air coming from the foot brake valve 9 presses the diaphragm valve 14a designed as an inlet or holding valve, ie due to the brake pressure applied from the port 23 on the right-hand effective surface of the diaphragm 18a, is lifted from the diaphragm valve seat 28a against the action of the spring means 16a The associated retaining diaphragm valve 14a is closed again by the solenoid valve seat 29a. The second electromagnetic valve 15b, which is opened in its spring-loaded basic position, receives the brake pressure from the foot brake valve 9 on the diaphragm 18b of the outlet diaphragm valve 14b from the right and urges them against their diaphragm valve seat 28b, leaving the outlet diaphragm valve 14b closed. Thus, the pressurized air under brake pressure passes through the pressure control valve 7. In this state, the pressure control valve arrangement 7 is in the state where the pressure control valve arrangement 7 is not in the ABS control mode.
Ausgehend von dem in Fig.2a gezeigten Zustand „Drucksteigern" ist zum Konstanthalten des Bremsdrucks in einem Bremszylinder 6a bis 6d („Druckhalten") gemäß Fig .2c lediglich die Magnetspul e 1 9a d es Elektromagnetventils 15a zu bestromen. Das Elektromagnetventil 15b bleibt hingegen unbestromt, wodurch das auslassseitige Membranventil 14b weiterhin geschlossen bleibt. Durch Bestromen der Magnetspule 19a des Elektromagnetventils 15a hebt dessen Magnetanker 22a vom oberen Magnetventilsitz 29a gegen die Wirkung der Federmittel 17a ab und drängt gegen den unteren Magnetventilsitz 20a. Dann steht der vom Fußbremsventil 9 ü ber d as zu n ächst noch offene H alte- Membranventil 14a herangeführte Bremsdruck in einer im Gehäuse 21 ausgebildeten Kammer 26a an und kann auf die Membrane 18a auch von der linken Seite her wirken. Nun ist der Druck auf der rechten und linken Seite der Membrane 18a des Membranventils 14a gleich groß. Da aber die Wirkfläche auf der linken Seite der Membrane 18a größer ist, wird das Halte-Membranventil 14a geschlossen, d.h. die Membrane 18a wird gegen den Membranventilsitz 28a gedrängt. Die Drucksteuerventilanordnung 7 verschließt zum Konstanthalten des Dru cks a l so d ie vom Fu ßbremsventi l 9 zu m Brem szyl i nd er 6 verlaufende pneumatische Bremsdruckleitung 8. Dabei steht der vom Fußbremsventil 9 herangeführte Bremsdruck aber weiterhin in der nun geschlossenen Kammer 26a an. Im Bereich des unteren Magnetventilsitzes 20a, gegen welchen der Magnetanker 22a des Elektromagnetventils 15a im bestromten Zustand der Magnetspule 22a gedrängt ist, ist ein Bypasskanal 31 ausgebildet, durch welche eine Druckluftströmung von der Kammer 26a entlang zumindest eines Teils der Magnetspule 19a des dem Membran-Halteventil 14a zugeordneten Elektromagnetventils 15a bis zur Drucksenke 27a strömen kann. Diese Druckluftströmung kann dann die unter Bestromung stehende Magnetspule 19a kühlen. Starting from the state shown in Fig.2a "pressure risers" is to keep the brake pressure in a brake cylinder 6a to 6d ("pressure hold") according to Fig .2c is constant, only the Magnetspul e 1 9a d it solenoid valve 15a to energize. The solenoid valve 15b, however, remains de-energized, whereby the outlet-side diaphragm valve 14b remains closed. By energizing the solenoid coil 19a of the electromagnetic valve 15a, its armature 22a lifts off from the upper solenoid valve seat 29a against the action of the spring means 17a and urges against the lower solenoid valve seat 20a. Then the braking pressure applied by the foot brake valve 9 via the old diaphragm valve 14a, which is still open, arrives in a chamber 26a formed in the housing 21 and can also act on the diaphragm 18a from the left side. Now, the pressure on the right and left side of the diaphragm 18a of the diaphragm valve 14a is the same size. However, since the effective area on the left side of the diaphragm 18a is larger, the holding diaphragm valve 14a is closed, that is, the diaphragm 18a is urged against the diaphragm valve seat 28a. The pressure control valve arrangement 7 closes the pneumatic brake pressure line 8 extending from the foot brake valve 9 to the brake cylinder 6 in order to keep the pressure constant. However, the braking pressure brought up by the foot brake valve 9 continues to be present in the now closed chamber 26a. In the region of the lower solenoid valve seat 20a, against which the armature 22a of the solenoid valve 15a is urged in the energized state of the solenoid 22a, a bypass passage 31 is formed, through which a compressed air flow from the chamber 26a along at least a portion of the solenoid coil 19a of the membrane holding valve 14a associated solenoid valve 15a can flow to the pressure sink 27a. This compressed air flow can then cool the energized solenoid 19a.
Der Bypasskanal 31 überbrückt den durch den am Magnetventilsitz 20a dichtend anliegenden Magnetanker 22a verschlossenen Strömungsquerschnitt und ermöglicht eine Druckluftströmung entlang wenigstens eines Teils der Magnetspule 19a, bevorzugt entlang deren gesamter Längserstreckung und parallel zu ihr, wie durch den Pfeil 32 in Fig.2 c angedeutet ist. The bypass channel 31 bridges the flow cross-section closed by the magnet armature 22a sealingly seated on the magnet valve seat 20a and allows compressed-air flow along at least part of the magnet coil 19a, preferably along its entire longitudinal extension and parallel to it, as indicated by the arrow 32 in FIG ,
Andererseits ist der Bypasskanal 31 insbesondere hinsichtlich seines Querschnitts derart ausgeführt, dass der Volumenstrom der Druckluftströmung durch den Bypasskanal 31 kleiner als ein oberer Grenz-Volumenstrom ist, durch welchen das Halte-Membranventil 14a von seiner Schließstellung wieder in seine Öffnungsstellung geschaltet werden könnte. Denn bedingt durch die den Bypasskanal 31 durch- und zur Drucksen ke 27a strömende Druckluft sin kt der Druck in der Kammer 26a und damit auch der Druck auf die linke Wirkfläche der Me m b ra n e 1 8 a d es H a l te-Membranventils 14a. Dadurch wird verhindert, dass der Volumenstrom der Bypass-Strömung so groß wird, dass sie Einfluss auf den (Schalt-) Zustand des Membran-Halteventils 14a zu nehmen vermag . Denn der Vol umenstrom der durch den Bypasskanal 31 strömenden Bypass-Strömung soll ausschließlich der Kühlung der Magnetspule 19a dienen. Der Bypasskanal 31 ist bevorzugt am Umfang des Magnetventilsitzes 20a ausgebildet und parallel zur Mittelachse des Magnetankers 22a bzw. zur Spule 19a, und lässt trotz gegen den Magnetventilsitz 20a dichtenden Magnetanker 36a einen gewissen Strömungsquerschnitt offen. On the other hand, the bypass channel 31 is designed in particular with respect to its cross section such that the volume flow of compressed air flow through the bypass channel 31 is smaller than an upper limit flow rate through which the holding diaphragm valve 14a could be switched from its closed position back to its open position. Because due to the bypass channel 31 through and to the Drucksen ke 27a flowing compressed air sin kt the pressure in the chamber 26a and thus the pressure on the left effective surface of Me mb ra ne 1 8 ad H al te diaphragm valve 14 a. This prevents the volume flow of the bypass flow from becoming so great that it influences the (switching) state of the membrane holding valve 14a is able to take. Because the vol umenstrom flowing through the bypass channel 31 bypass flow is intended to serve only the cooling of the solenoid 19a. The bypass channel 31 is preferably formed on the circumference of the solenoid valve seat 20a and parallel to the central axis of the magnet armature 22a and to the coil 19a, and leaves despite of the magnetic valve seat 20a sealing magnet armature 36a a certain flow cross section open.
Gemäß Figur 2b wird ein Druckabbau („Drucksenken") im Bremszylinder 6 dadurch erzielt, dass beide Elektromagnetventile 15a und 15b bestromt werden. Für das Elektromagnetventil 15a und das zugeordnete Halte-Mem branventil 1 5a g ilt das vorstehend zu m Druckhalten Beschriebene. Hingegen wird der Magnetanker 22b des anderen Elektromagnetventils 15b wegen der Bestromung seiner Magnetspule 19b gegen die Wirkung der Federmittel 17b vom unteren Magnetventilsitz 20b abgehoben und gegen den oberen Magnetventilsitz 29 b gedrängt. Deshalb sinkt der Druck in der Kammer 26b, so dass der vom Bremszylinder 6 kommende Druck die Membrane 1 8b des Auslass-Membranventils 14b vom Membranventilsitz 28b abheben kann, so dass der Arbeitsanschluss 24 und damit der Bremszylinder 6 zum Entlüften mit der Drucksenke 30 verbunden wird. According to Figure 2b, a pressure reduction ("pressure lowering") is achieved in the brake cylinder 6 by energizing both solenoid valves 15a and 15b the magnet armature 22b of the other solenoid valve 15b is lifted from the lower solenoid valve seat 20b against the action of the spring means 17b due to the energization of its solenoid coil 19b and urged against the upper solenoid valve seat 29b the membrane 1 8b of the outlet diaphragm valve 14b can lift off from the diaphragm valve seat 28b, so that the working port 24 and thus the brake cylinder 6 is connected to the pressure sink 30 for venting.
Die vorstehend beschriebenen Funktionen der Drucksteuerventilanordnung 7 werden nach Maßgabe der elektronischen Steuereinheit 10 im Rahmen einer ABS/ASR-Regelung im eingangs beschriebenen Sinne durchgeführt. Bezuqszeichenliste The above-described functions of the pressure control valve assembly 7 are performed in accordance with the electronic control unit 10 as part of an ABS / ASR control in the sense described above. LIST OF REFERENCES
1 Vorderachse 1 front axle
2 Hinterachse  2 rear axle
3 Rad  3 wheel
4 Rad  4 wheel
5 Drehzahlsensor  5 speed sensor
6 Bremszylinder  6 brake cylinders
7 Drucksteuerventilanordnung  7 pressure control valve arrangement
8 Bremsdruckleitung  8 brake pressure line
9 Fußbremsventil  9 foot brake valve
10 Steuereinheit  10 control unit
1 1 ASR-Einheit  1 1 ASR unit
12 ASR-Magnetventil  12 ASR solenoid valve
13 Wechselventil  13 shuttle valve
14 a/b Membranventil  14 a / b diaphragm valve
15 a/b Elektromagnetventil  15 a / b solenoid valve
16 a/b Federelement  16 a / b spring element
17 a/b Federelement  17 a / b spring element
18 a/b Membrane  18 a / b membrane
19 a/b Magnetspulen  19 a / b solenoid coils
20 a/b Magnetventilsitze  20 a / b solenoid valve seats
21 Gehäuse  21 housing
22 a/b Magnetanker  22 a / b magnetic armature
23 Druckmittelanschluss  23 pressure medium connection
24 Arbeitsanschluss  24 work connection
26 a/b Kammer  26 a / b chamber
27 a/b Drucksenke  27 a / b pressure sink
28 a/b Membranventilsitz Magnetventilsitz Drucksenke Bypasskanal Pfeil 28 a / b Diaphragm valve seat Solenoid valve seat Pressure sink Bypass channel arrow

Claims

Patentansprüche claims
1. Drucksteuerventilanordnung (7) zur Steuerung des Fluiddrucks in einer druckmittelbetätigten und schlupfgeregelten Bremsanlage eines Fahrzeugs, wobei im Rahmen der Bremsschlupfregelung der Bremsdruck in wenigstens einem Bremszylinder (6) gesteigert, gehalten oder gesenkt wird, wobei a) in einem Gehäuse (21) der Drucksteuerventilanordnung (7) zwei Membranventile (14a, 14b), ein Halte-Membranventil (14a) und ein Auslass- Membranventil (14b) sowie zwei von einer elektronischen Steuereinrichtung (10) ansteuerbare elektromagnetische Vorsteuerventile (15a, 15b) zum Vorsteuern der Membranventile (14a, 14b) vorgesehen sind,  1. Pressure control valve arrangement (7) for controlling the fluid pressure in a pressure-medium-operated and slip-controlled brake system of a vehicle, wherein in the context of the brake slip control, the brake pressure in at least one brake cylinder (6) is increased, maintained or lowered, wherein a) in a housing (21) of Pressure control valve assembly (7) has two diaphragm valves (14a, 14b), a holding diaphragm valve (14a) and an outlet diaphragm valve (14b) and two controllable by an electronic control device (10) electromagnetic pilot valves (15a, 15b) for piloting the diaphragm valves (14a , 14b) are provided,
b) die beiden elektromagnetischen Vorsteuerventile (15a, 15b) je eine Magnetspule (19a, 19b) sowie mit Magnetventilsitzen (20a, 20b, 29a, 29b) zusammen wirkende und durch Bestromung der Magnetspulen (19a, 19b) gegen Federmittel (17a, 17b) betätigbare Magnetanker (22a, 22b) aufweisen, b) the two electromagnetic pilot valves (15a, 15b) each have a magnetic coil (19a, 19b) and solenoid valve seats (20a, 20b, 29a, 29b) acting together and by energizing the magnetic coils (19a, 19b) against spring means (17a, 17b) having actuatable armature (22a, 22b),
c) der Magnetanker (22a) des dem Halte-Membranventil (14a) zugeordneten elektromagnetischen Vorsteuerventils (15a) durch Bestromen der Magnetspule (19a) gegen einen Magnetventilsitz (20a) der Magnetventilsitze (20a, 29a) gedrängt ist, welcher eine durch Öffnen des Halte-Membranventils (14a) druckbeaufschlagbare Kammer (26a) im Gehäuse (21) mit einer Drucksenke (27a) verbindet, c) the magnet armature (22a) of the retaining diaphragm valve (14a) associated electromagnetic pilot valve (15a) is urged by energizing the solenoid (19a) against a solenoid valve seat (20a) of the solenoid valve seats (20a, 29a), which one by opening the holding Diaphragm valve (14a) pressurizable chamber (26a) in the housing (21) connects to a pressure sink (27a),
dadurch gekennzeichnet, dass  characterized in that
d) durch bei Bestromung der Magnetspule (19a) gegen den Magnetventilsitz (20a) gedrängtem Magnetanker (22a) des dem Halte- Membranventil (14a) zugeordneten elektromagnetischen Vorsteuerventils (15a) eine Druckmittelströmung von der Kammer (26a) entlang zumindest eines Teils der Magnetspule (19a) bis zur Drucksenke (27a) ermöglichende Bypass-Mittel (31 ) vorgesehen sind, wobei d) by when the solenoid coil (19 a) against the solenoid valve seat (20 a) urged armature (22 a) of the holding diaphragm valve (14 a) associated electromagnetic pilot valve (15 a) a flow of pressure medium from the chamber (26 a) along at least a portion of the magnetic coil ( 19a) to the Pressure sink (27 a) enabling bypass means (31) are provided, wherein
e) die Bypass-Mittel (31 ) derart ausgeführt sind, dass der Volumenstrom der Druckmittelströmung kleiner als ein oberer Grenz-Volumenstrom ist, durch welchen das Halte-Membranventil (14a) von einer Schließstellung in eine Öffnungsstellung schaltbar ist. e) the bypass means (31) are designed such that the volume flow of the pressure medium flow is smaller than an upper limit volume flow through which the holding diaphragm valve (14a) can be switched from a closed position to an open position.
Drucksteuerventilanordnung nach Anspruch 1 , dadurch gekennzeichnet, dass die Bypass-Mittel durch einen am Umfang des Magnetventilsitzes (20a) ausgebildeten Bypasskanal (31 ) gebildet werden, derart, dass bei gegen den Magnetventilsitz (20a) gedrängtem Magnetanker (22a) der Strömungsquerschnitt des Bypasskanals (31 ) wenigstens teilweise geöffnet bleibt. Pressure control valve arrangement according to Claim 1, characterized in that the bypass means are formed by a bypass channel (31) formed on the circumference of the magnet valve seat (20a), such that when the magnet armature (22a) is pushed against the magnet valve seat (20a), the flow cross section of the bypass channel ( 31) remains at least partially open.
Drucksteuerventilanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass d a s G e h ä u s e ( 2 1 ) we n i g ste n s e i n e n Druckmittelanschluss (23) zur Druckbeaufschlagung oder Druckentlastung sowie wenigstens einen Arbeitsanschluss (24) zum Anschluss an den Bremszylinder (6) aufweist. Pressure control valve arrangement according to claim 1 or 2, characterized in that there is a pressure medium connection (23) for pressurizing or depressurizing and at least one working connection (24) for connection to the brake cylinder (6).
Drucksteuerventilanordnung nach Anspruch 3, dadurch gekennzeichnet, dass der Druckmittelanschluss (23) zur Verbindung mit einem Betriebsoder Fußbremsventil (9) einer druckmittelbetätigten Bremseinrichtung des Fahrzeugs vorgesehen ist. Pressure control valve arrangement according to claim 3, characterized in that the pressure medium connection (23) is provided for connection to an operating or foot brake valve (9) of a pressure-medium-operated braking device of the vehicle.
Drucksteuerventilanordnung nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die im Gehäuse (21 ) angeordnete Kammer (26a) durch Öffnen des M e m b ra n-Halteventils (14a) mit dem Druckmittelanschluss (23) verbunden ist. Pressure control valve arrangement according to claim 3 or 4, characterized in that in the housing (21) arranged chamber (26 a) is connected by opening the M embra n-holding valve (14 a) with the pressure medium connection (23).
6. Bremsschlupfgeregelte und druckmittelbetätigte Bremseinrichtung eines Fahrzeugs, beinhaltend wenigstens eine Drucksteuerventilanordnung (7) nach einem der vorhergehenden Ansprüche. 6. Brake-slip-controlled and pressure-medium-operated braking device of a vehicle, comprising at least one pressure control valve arrangement (7) according to one of the preceding claims.
PCT/EP2011/051867 2010-02-10 2011-02-09 Pressure control valve assembly comprising a bypass duct for cooling the solenoid of a pilot valve WO2011098468A1 (en)

Applications Claiming Priority (2)

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DE102010007407.1 2010-02-10
DE201010007407 DE102010007407B4 (en) 2010-02-10 2010-02-10 Pressure control valve assembly

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DE102017106555A1 (en) * 2017-03-27 2018-09-27 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Diaphragm valve without support ring and without support plate
DE102018202055A1 (en) * 2018-02-09 2019-08-14 Volkswagen Aktiengesellschaft Brake system, motor vehicle and method for braking a motor vehicle
DE102018124179B3 (en) * 2018-10-01 2019-09-19 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH ABS pressure control valve assembly
CN109204285B (en) * 2018-10-30 2023-10-27 宁波佳尔灵气动机械有限公司 Auxiliary brake valve

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