WO1998033688A1 - Pressure control valve - Google Patents

Pressure control valve Download PDF

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Publication number
WO1998033688A1
WO1998033688A1 PCT/EP1998/000444 EP9800444W WO9833688A1 WO 1998033688 A1 WO1998033688 A1 WO 1998033688A1 EP 9800444 W EP9800444 W EP 9800444W WO 9833688 A1 WO9833688 A1 WO 9833688A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
slide
wheel brake
control valve
way control
Prior art date
Application number
PCT/EP1998/000444
Other languages
German (de)
French (fr)
Inventor
Johann Jungbecker
Manfred Rüffer
Original Assignee
Itt Manufacturing Enterprises, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Itt Manufacturing Enterprises, Inc. filed Critical Itt Manufacturing Enterprises, Inc.
Publication of WO1998033688A1 publication Critical patent/WO1998033688A1/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
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3655—Continuously controlled electromagnetic valves
    • B60T8/366—Valve details
    • B60T8/367—Seat valves, e.g. poppet valves
    • 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
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B60T15/02—Application and release valves
    • B60T15/025—Electrically controlled valves
    • B60T15/028—Electrically controlled valves in hydraulic 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
    • B60T8/36—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
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3655—Continuously controlled electromagnetic valves
    • B60T8/366—Valve details
    • B60T8/3665—Sliding valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5087—Pressure release using restrictions
    • B60T8/5093—Pressure release using restrictions in hydraulic brake systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors

Definitions

  • the invention relates to an electromagnetically controllable multi-way control valve for slip-controlled hydraulic motor vehicle brake systems for establishing a pressure medium connection between at least one wheel brake and a high-pressure source or a low-pressure accumulator, comprising a slide guided in a sleeve-shaped housing body, which is biased in the longitudinal direction of displacement and one extending in the longitudinal direction Opening, wherein in normal braking operation the bias towards a first end position dominates, in which the wheel brake is fluidly connected to the high-pressure source and is fluidly separated from the low-pressure accumulator, and a valve provided between the wheel brake and the low-pressure accumulator, which is used to reduce pressure in the wheel brake is opened.
  • Such a multi-way valve is known for example from DE 44 41 150 AI.
  • The is in normal braking mode Slider in such a position that a radial opening in the sleeve-shaped housing body, which forms a connection for the high-pressure source, is in pressure medium connection with another opening located in the region of the slide end, which forms a connection for a wheel brake.
  • the slide is designed as a hollow slide, so that the fluid connection of the high pressure source and the wheel brake leads through the longitudinal opening of the slide. If measured wheel sensors of the electrical control and regulating unit of a slip-controlled motor vehicle brake system determine that the wheel is locked, an electromagnetic actuator is energized so that an armature of the electromagnetic actuator is moved in the longitudinal direction of the slide.
  • the armature acts on the slide via a push rod and adjusts it in such a way that the pressure medium connection between the high pressure source and the wheel brake is interrupted. Then the plunger which engages through the slide strikes against a spherical valve closing member and lifts it off its sealing seat, whereby a pressure medium connection between the wheel brake and the low-pressure accumulator is opened to reduce the pressure in the wheel brake.
  • the slide In multi-way valves of the type mentioned at the beginning, as well as in the multi-way valve described above, the slide remains in the above-described position in normal braking operation. Because sometimes it takes a very long time can, until the normal brake operation is exited via the control or regulating device of the brake system and the wheel brake is to be connected to the low-pressure accumulator in order to reduce the pressure, there is sometimes the risk that the slide sticks in its normal brake position, so that rapid pressure reduction in the wheel brake does not occur can be achieved without delay in the desired manner.
  • the above invention is therefore based on the object of eliminating the risk of the slide sticking in its normal braking position for a multi-way pressure control valve of the type described in the introduction.
  • a multi-way pressure control valve of the type mentioned according to the invention in that a slowly displaceable pressure piston is provided in the opening of the slide, which counteracts the bias directed into the first end position with its free end in normal braking operation, so that the slide depends on Pressure of the high pressure source is reciprocable in the longitudinal direction.
  • the pressure piston which is displaceable in the longitudinal opening, is displaced with ever increasing force in the direction of the mouth of the opening and can thus counteract the preload directed in the direction of the first end position, so that the slide is moved slightly counter to the preload, for that to apply the appropriate equilibrium position. If the control pressure is reduced, the spool is slightly moved back under the effect of the preload. According to the invention, a slight back and forth movement of the slide is achieved in normal braking operation, so that there is no risk that the slide will become stuck.
  • the bias in the direction of the first end position is transmitted from a spring means via a mediator element to the slide, and the pressure piston which is longitudinally displaceable in the slide opening is supported against the mediator element.
  • the pressure piston With increasing control pressure in the longitudinal opening of the slide, the pressure piston now presses with increasing force against the mediator element, so that the slide with the mediator element moves against the force of the spring means.
  • the mediator element is formed by an armature of an electromagnetic actuating device, which in the de-energized state of the actuating device, i. H. in normal braking operation, is biased towards an end position.
  • the longitudinal opening of the slide opens at its end facing away from the pressure piston on the end face of the slide there, and in the mouth region of the opening, a pin which moves to a limited extent engages, which connects the valve mentioned above between the wheel brake and Low pressure accumulator keeps closed during normal braking. Due to the limited longitudinal displaceability of the pin, the valve remains closed in normal braking operation even when the slide is moved back and forth in the inventive manner described above.
  • the longitudinally displaceable pin is biased in the closing direction of the valve in normal braking operation by the pressure of the high-pressure source in the opening and is supported against the housing body via the valve.
  • the valve is preferably between the wheel brake and Low-pressure accumulator designed as a seat valve and the valve body of the seat valve can be actuated from the free end of the longitudinally displaceable pin which projects from the longitudinal opening.
  • the free end of the longitudinally displaceable pin itself forms the valve body of the seat valve and, in normal braking operation, lies sealingly against a sealing seat of the seat valve.
  • the free end of the longitudinally displaceable pin is designed in the form of a sealing pin.
  • the longitudinal displaceability of the pin could in any way be limited in order to prevent the pin from sliding out of the longitudinal opening of the slide.
  • the pin has a radial projection which can be placed against a stop to limit the longitudinal displacement.
  • the projection is preferably arranged such that it comes to lie outside the opening.
  • the stop which is also to be provided in this case outside the opening can then be achieved in a technically simple manner by a cup-shaped element placed against the end face of the slide, which has a bottom opening through which the pin slidably engages, but which are not passed by the radial projection of the pin can.
  • a longitudinally displaceable piston-like pressure transmission part bearing against the inwardly facing end face of the longitudinally displaceable pin.
  • the multi-way pressure control valve shown in longitudinal section in the figure comprises a sleeve-shaped housing body 2 and a slide 6 which is displaceable therein in the longitudinal direction 4.
  • the slide 6 is prestressed in the longitudinal direction 4 in opposite directions, namely in the direction of the first end position shown by a first spring 8 and in the opposite direction by a second spring 10.
  • the first spring 8 is supported at one end against a core 12 and at the other end against an armature 14 of an electromagnetic actuating device 16.
  • the armature 14 bears with its side facing away from the spring 8 against an end face 18 of the slide 6.
  • the core 12 of the electromagnetic actuator 16 is held in a press fit by means of a pot-shaped holding element 20, which is placed over a free end 22 of the sleeve-shaped housing body 2 and is sealed off from it.
  • a coil holder 24 with a coil 26 of the electromagnetic actuating device 16 is arranged on the circumference of the cup-shaped element 20.
  • the armature 14, which is displaceable in the longitudinal direction 4 within the cylindrical end section 22 of the housing body 2 is moved against the core 12 against the bias by the spring 8.
  • openings 28, 30, 32 which are spaced apart in the radial direction and form a pressure medium connection to a low-pressure accumulator, a wheel brake or a high-pressure source in the form of a tandem master cylinder.
  • the slide 6 is designed as a hollow slide and has an inner opening 33 which extends in the longitudinal direction 4.
  • the slide 6 has on its outer circumference a first control edge 34 which interacts with a corresponding control edge 36 of the sleeve-shaped housing body 2 and thereby releases or closes a variable throttle cross section 38 between the connection 32 for the high pressure source and the inner longitudinal opening 33 of the slide 6.
  • the control edge 34 delimits an annular groove 40, which is provided concentrically in the outer peripheral surface of the slide 6.
  • the groove 40 communicates via two radial bores 42 with the inner longitudinal opening 33 of the Slide 6.
  • a slowly displaceable pressure piston 48 is provided in the inner longitudinal opening 33, which is acted upon at one end by the pressure of the high-pressure source prevailing in the inner longitudinal opening 33 and at the other end - like the slide 6 - with its end face 50 against the armature 14 supports.
  • a slowly displaceable pin 52 engages from the outside in the inner longitudinal opening 33 of the slide 6.
  • the pin 52 has at its free end 54 a sealing pin 56 which, in the illustrated normal braking position, bears against a sealing seat 58 of a seat valve 60 which closes the pressure medium connection 28 of the low-pressure accumulator.
  • the pin 52 has a radial collar 62 located outside the longitudinal opening 33.
  • a spiral spring 64 surrounding the pin 52 is supported at one end against this collar 62 and at the other end against the end face 66 of the slide 6, so that the pin 52 in Direction is biased to the sealing seat 58.
  • Spring 64 and collar 62 are located within a cup-shaped element 68, which rests with a collar-shaped flange section 70 against the end face 66 of the slide 6 and has a bottom opening 72 through which the pin extends so as to be longitudinally displaceable.
  • the bottom region 74 of the cup-shaped element 68 forms a stop 76 for the radial collar 62 of the pin 52 and therefore forms a displacement end position for the pin 52.
  • a slowly displaceable pressure and sealing piston 78 which is acted upon at one end by the pressure prevailing in the inner opening 33 and at the other end abuts against the end 80 of the pin 52 which engages in the longitudinal opening 33.
  • the illustrated multi-way pressure regulating valve works as follows: In the drawing of the figure, the armature 14 and thus the slide 6 are under the pretension of the spring 8 in their first end position. There is a pressure medium connection between the connection 32 of the high-pressure source and the connection 30 of the wheel brake, in which the variable throttle cross-section 38 is opened to a maximum in the area of the connection 32, so that pressure medium via the annular groove 40, the transverse bores 42 into the inner longitudinal opening 33 and over the inclined holes 46 to the annular groove 44 and Pressure medium connection 30 of the wheel brake can reach.
  • the pressure and sealing piston 78 is also moved back and forth under the effect of the control pressure and holds the sealing pin 56 of the pin 52 in sealing contact with the sealing seat 58 by pressing on the pin 52 Seat valve 60.
  • the pin 52 is therefore supported on the sealing seat 58.
  • a control edge 82 which is formed by the end face 66 of the slide 6, passes over a corresponding control edge 84 of the housing body 2, whereby a throttle cross-section, not shown in the figure but easily imaginable, is opened between the pressure medium connection 30 of the wheel brake and the opened seat valve 60 to cause a pressure reduction in the wheel brake to the low pressure accumulator.
  • control edge 82 of the slide 6 passes over the control edge 84 in the opposite direction, so that the throttle cross section between the wheel brake and the low-pressure accumulator is interrupted again, the seat valve 60 still remaining open. If the pressure in the wheel brake is to be increased again, the current in is controlled accordingly the coil 26, the armature 14 is moved so far to the left under the action of the spring 8 until the control edge 34 of the slide opens the control edge 36 again in the region of the pressure medium connection 32 to the high pressure source.
  • the sealing and pressure piston 78 is supported on the housing via the pin 52, the collar 62, the stop 64, the collar 70 and the spring 10.

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

Abstract

An electromagnetically controllable multiple way control valve for hydraulic, anti-lock motor vehicle brake systems puts at least one wheel brake (wheel) in hydraulic communication with a high-pressure source (THZ) or a low-pressure reservoir (NDS) and comprises a slide (6) guided in a cylindrical housing body (2) prestressed in both directions in the longitudinal direction of displacement (4), as well as an elongate opening (33) in the longitudinal direction. During normal operation of the brakes, the slide is prestressed towards a first end position in which the wheel brake is in fluid communication with the high-pressure source and cut off from the low-pressure reservoir. A valve (60) provided between the wheel brake and the low-pressure reservoir is opened to reduce pressure in the wheel brake. To prevent the slide (6) from getting stuck during normal brake operation, the multiple way control valve has a longitudinally movable pressure piston (48) arranged in the opening (33) of the slide (6). During normal brake operation, the pressure piston (48) acts with its free end (50) against the force that prestresses the slide towards the first end position, so that the slide (6) can move back and forth in the longitudinal direction depending on the pressure of the high-pressure source.

Description

DruckregelventilPressure control valve
Die Erfindung betrifft ein elektromagnetisch ansteuerbares Mehrwege-Regelventil für schlupfgeregelte hydraulische Kraftfahrzeugbremssysteme zum Herstellen einer Druckmittelverbindung zwischen wenigstens einer Radbremse und einer Hochdruckquelle oder einem Niederdruckspeicher, umfassend einen in einem hülsenförmigen Gehäusekörper geführten Schieber, der in Verschiebelängsrichtung in beiden Richtungen vorgespannt ist und eine in Längsrichtung verlaufende Öffnung aufweist, wobei im Normalbremsbetrieb die Vorspannung in Richtung auf eine erste Endlage hin dominiert, in welcher die Radbremse mit der Hochdruckquelle strömungsmäßig verbunden und vom Niederdruckspeicher strömungsmäßig getrennt ist, und ein zwischen der Radbremse und dem Niederdruckspeicher vorgesehenes Ventil, welches zum Druckabbauen in der Radbremse geöffnet wird.The invention relates to an electromagnetically controllable multi-way control valve for slip-controlled hydraulic motor vehicle brake systems for establishing a pressure medium connection between at least one wheel brake and a high-pressure source or a low-pressure accumulator, comprising a slide guided in a sleeve-shaped housing body, which is biased in the longitudinal direction of displacement and one extending in the longitudinal direction Opening, wherein in normal braking operation the bias towards a first end position dominates, in which the wheel brake is fluidly connected to the high-pressure source and is fluidly separated from the low-pressure accumulator, and a valve provided between the wheel brake and the low-pressure accumulator, which is used to reduce pressure in the wheel brake is opened.
Ein derartiges Mehrwegeventil ist beispielsweise aus der DE 44 41 150 AI bekannt. Im Normalbremsbetrieb befindet sich der Schieber in einer solchen Stellung, dass eine radiale Öffnung in dem hülsenförmigen Gehäusekörper, welche einen Anschluss für die Hochdruckquelle bildet, in Druckmittelverbindung mit einer weiteren im Bereich des Schieberendes liegenden Öffnung steht, welche einen Anschluss für eine Radbremse bildet. Der Schieber ist als Hohlschieber ausgebildet, so dass die strömungsmäßige Verbindung von Hochdruckquelle und Radbremse durch die Längsöffnung des Schiebers führt. Wenn von Messwert- aufnehmern der elektrischen Steuer- und Regeleinheit eines schlupfgeregelten Kraftfahrzeugbremssystems ein Blockieren des Rades festgestellt wird, so wird eine elektromagnetische Stelleinrichtung bestromt, so dass ein Anker der elektromagnetischen Stelleinrichtung in Verschiebelängsrichtung des Schiebers bewegt wird. Der Anker wirkt über eine Stößelstange auf den Schieber ein und verstellt diesen derart, dass die Druckmittelverbindung zwischen Hochdruckquelle und Radbremse unterbrochen wird. Anschließend schlägt der den Schieber durchgreifende Stößel gegen ein kugelförmiges Ventilschließglied an und hebt dieses von seinem Dichtsitz ab, wodurch eine Druckmittelverbindung zwischen der Radbremse und dem Niederdruckspeicher zum Verringern des Drucks in der Radbremse geöffnet wird.Such a multi-way valve is known for example from DE 44 41 150 AI. The is in normal braking mode Slider in such a position that a radial opening in the sleeve-shaped housing body, which forms a connection for the high-pressure source, is in pressure medium connection with another opening located in the region of the slide end, which forms a connection for a wheel brake. The slide is designed as a hollow slide, so that the fluid connection of the high pressure source and the wheel brake leads through the longitudinal opening of the slide. If measured wheel sensors of the electrical control and regulating unit of a slip-controlled motor vehicle brake system determine that the wheel is locked, an electromagnetic actuator is energized so that an armature of the electromagnetic actuator is moved in the longitudinal direction of the slide. The armature acts on the slide via a push rod and adjusts it in such a way that the pressure medium connection between the high pressure source and the wheel brake is interrupted. Then the plunger which engages through the slide strikes against a spherical valve closing member and lifts it off its sealing seat, whereby a pressure medium connection between the wheel brake and the low-pressure accumulator is opened to reduce the pressure in the wheel brake.
Bei Mehrwegeventilen der eingangs genannten Art wie auch bei dem vorstehend beschriebenen Mehrwegeventil verbleibt der Schieber im Normalbremsbetrieb in der vorausgehend beschriebenen Stellung. Da mitunter sehr lange Zeit vergehen kann, bis über die Steuer- bzw. Regeleinrichtung des Bremssystems der Normalbremsbetrieb verlassen und die Radbremse zum Druckabbau mit dem Niederdruckspeicher verbunden werden soll, besteht mitunter die Gefahr, dass sich der Schieber in seiner Normalbremsstellung festsetzt, so dass ein rascher Druckabbau in der Radbremse nicht in der gewünschten Weise verzögerungsfrei erreicht werden kann.In multi-way valves of the type mentioned at the beginning, as well as in the multi-way valve described above, the slide remains in the above-described position in normal braking operation. Because sometimes it takes a very long time can, until the normal brake operation is exited via the control or regulating device of the brake system and the wheel brake is to be connected to the low-pressure accumulator in order to reduce the pressure, there is sometimes the risk that the slide sticks in its normal brake position, so that rapid pressure reduction in the wheel brake does not occur can be achieved without delay in the desired manner.
Der vorstehenden Erfindung liegt daher die Aufgabe zugrunde, für ein Mehrwege-Druckregelventil der eingangs beschriebenen Art die Gefahr des Festsetzens des Schiebers in seiner Normalbremsstellung auszuschließen.The above invention is therefore based on the object of eliminating the risk of the slide sticking in its normal braking position for a multi-way pressure control valve of the type described in the introduction.
Diese Aufgabe wird bei einem Mehrwege-Druckregelventil der genannten Art erfindungsgemäß dadurch gelöst, dass in der Öffnung des Schiebers ein langsverschieblicher Druckkolben vorgesehen ist, der im Normalbremsbetrieb mit seinem freien Ende der in die erste Endlage gerichteten Vorspannung entgegenwirkt, so dass der Schieber in Abhängigkeit vom Druck der Hochdruckquelle in Längsrichtung hin- und herbewegbar ist.This object is achieved in a multi-way pressure control valve of the type mentioned according to the invention in that a slowly displaceable pressure piston is provided in the opening of the slide, which counteracts the bias directed into the first end position with its free end in normal braking operation, so that the slide depends on Pressure of the high pressure source is reciprocable in the longitudinal direction.
Bei sich aufbauendem Steuerdruck der Hochdruckquelle wird der in der Längsöffnung verschiebliche Druckkolben mit immer stärkerer Kraft in Richtung auf die Mündung der Öffnung verschoben und kann so der in Richtung auf die erste Endlage gerichteten Vorspannung entgegenwirken, so dass der Schieber geringfügig entgegen der Vorspannung bewegt wird, um die dem gerade anliegenden Druck entsprechende Gleichgewichtslage einzunehmen. Wird der Steuerdruck herabgesetzt, so wird der Schieber unter der Wirkung der Vorspannung wieder geringfügig zurückbewegt. Es wird also erfindungsgemäß ein geringfügiges Hin- und Herbewegen des Schiebers im Normalbremsbetrieb erreicht, so dass nicht die Gefahr besteht, dass sich der Schieber festsetzt.When the control pressure of the high-pressure source builds up, the pressure piston, which is displaceable in the longitudinal opening, is displaced with ever increasing force in the direction of the mouth of the opening and can thus counteract the preload directed in the direction of the first end position, so that the slide is moved slightly counter to the preload, for that to apply the appropriate equilibrium position. If the control pressure is reduced, the spool is slightly moved back under the effect of the preload. According to the invention, a slight back and forth movement of the slide is achieved in normal braking operation, so that there is no risk that the slide will become stuck.
Bei einer bevorzugten Ausführungsform der Erfindung wird die Vorspannung in Richtung auf die erste Endlage von einem Federmittel über ein Vermittlerelement auf den Schieber übertragen, und der in der Schieberöffnung längsverschiebliche Druckkolben ist gegen das Vermittlerelement abgestützt. Bei zunehmendem Steuerdruck in der Schieberlängsöffnung drückt nun der Druckkolben mit zunehmender Kraft gegen das Vermittlerelement, so dass sich der Schieber mit dem Vermittlerelement entgegen der Kraft des Federmittels verschiebt.In a preferred embodiment of the invention, the bias in the direction of the first end position is transmitted from a spring means via a mediator element to the slide, and the pressure piston which is longitudinally displaceable in the slide opening is supported against the mediator element. With increasing control pressure in the longitudinal opening of the slide, the pressure piston now presses with increasing force against the mediator element, so that the slide with the mediator element moves against the force of the spring means.
In bevorzugter Weise ist das Vermittlerelement von einem Anker einer elektromagnetischen Stelleinrichtung gebildet, welcher im unbestromten Zustand der Stelleinrichtung, d. h. im Normalbremsbetrieb, in Richtung auf eine Endlage hin vorgespannt ist.Preferably, the mediator element is formed by an armature of an electromagnetic actuating device, which in the de-energized state of the actuating device, i. H. in normal braking operation, is biased towards an end position.
Zum Verlassen des Normalbremsbetriebs - wenn also der Druck in der Radbremse abgebaut werden soll - wird die in Richtung auf die erste Endlage gerichtete Vorspannung des Schiebers weggenommen, indem beispielsweise über die elektromagnetische Stelleinrichtung ein Anker bewegt wird, so dass der Schieber in eine die Druckmittelverbindung zwischen Hochdruckquelle und Radbremse verschließende und zwischen Radbremse und Niederdruckspeicher öffnende Stellung verschoben wird.To exit normal braking operation - if the pressure is in the wheel brake is to be removed - the bias of the slide directed towards the first end position is removed, for example by moving an anchor via the electromagnetic actuating device, so that the slide closes the pressure medium connection between the high-pressure source and the wheel brake and between the wheel brake and low-pressure accumulator opens Position is shifted.
Bei einer besonders vorteilhaften Ausführungsform des erfindungsgemäßen Mehrwegeventils mündet die in Längsrichtung verlaufende Öffnung des Schiebers an ihrem vom Druckkolben abgewandten Ende an der dortigen Stirnseite des Schiebers, und in den Mündungsbereich der Öffnung greift ein beschränkt langsverschieblicher Stift ein, welcher das eingangs erwähnte Ventil zwischen Radbremse und Niederdruckspeicher im Normalbremsbetrieb geschlossen hält. Durch die beschränkte Längsverschieblichkeit des Stifts bleibt das Ventil im Normalbremsbetrieb auch dann geschlossen, wenn der Schieber in der vorstehend beschriebenen erfindungsgemäßen Weise hin- und herbewegt wird.In a particularly advantageous embodiment of the multi-way valve according to the invention, the longitudinal opening of the slide opens at its end facing away from the pressure piston on the end face of the slide there, and in the mouth region of the opening, a pin which moves to a limited extent engages, which connects the valve mentioned above between the wheel brake and Low pressure accumulator keeps closed during normal braking. Due to the limited longitudinal displaceability of the pin, the valve remains closed in normal braking operation even when the slide is moved back and forth in the inventive manner described above.
Der längsverschiebliche Stift ist im Normalbremsbetrieb durch den in der Öffnung anstehenden Druck der Hochdruckquelle in Schließrichtung des Ventils vorgespannt und über das Ventil gegen den Gehäusekörper abgestützt.The longitudinally displaceable pin is biased in the closing direction of the valve in normal braking operation by the pressure of the high-pressure source in the opening and is supported against the housing body via the valve.
In bevorzugter Weise ist das Ventil zwischen Radbremse und Niederdruckspeicher als Sitzventil ausgebildet und der Ventilkörper des Sitzventils ist von dem freien aus der Längsöffnung ragenden Ende des längsverschieblichen Stifts betätigbar. In ganz besonders vorteilhafter Weise bildet das freie Ende des längsverschieblichen Stifts selbst den Ventilkörper des Sitzventils und liegt im Normalbremsbetrieb gegen einen Dichtsitz des Sitzventils dichtend an. Hierfür ist das freie Ende des längsverschieblichen Stifts in der Form eines Dichtpins ausgebildet.The valve is preferably between the wheel brake and Low-pressure accumulator designed as a seat valve and the valve body of the seat valve can be actuated from the free end of the longitudinally displaceable pin which projects from the longitudinal opening. In a very particularly advantageous manner, the free end of the longitudinally displaceable pin itself forms the valve body of the seat valve and, in normal braking operation, lies sealingly against a sealing seat of the seat valve. For this purpose, the free end of the longitudinally displaceable pin is designed in the form of a sealing pin.
Die Längsverschieblichkeit des Stifts könnte in an sich beliebiger Weise begrenzt werden, um zu verhindern, dass der Stift aus der Längsöffnung des Schiebers herausgleiten kann. Es hat sich jedoch in herstellungstechnischer Hinsicht als besonders einfach und daher vorteilhaft erwiesen, wenn der Stift einen radialen Vorsprung aufweist, der zum Begrenzen der Längsverschieblichkeit gegen einen Anschlag anlegbar ist. Der Vorsprung ist vorzugsweise so angeordnet, dass er außerhalb der Öffnung zu liegen kommt. Der solchenfalls ebenfalls außerhalb der Öffnung vorzusehende Anschlag kann dann in herstellungstechnisch einfacher Weise durch ein gegen die Stirnseite des Schiebers gelegtes topfförmiges Element erreicht werden, welches eine Bodenöffnung aufweist, durch die der Stift verschieblich hindurchgreift, die jedoch von dem radialen Vorsprung des Stifts nicht passiert werden kann.The longitudinal displaceability of the pin could in any way be limited in order to prevent the pin from sliding out of the longitudinal opening of the slide. In terms of production technology, however, it has proven to be particularly simple and therefore advantageous if the pin has a radial projection which can be placed against a stop to limit the longitudinal displacement. The projection is preferably arranged such that it comes to lie outside the opening. The stop which is also to be provided in this case outside the opening can then be achieved in a technically simple manner by a cup-shaped element placed against the end face of the slide, which has a bottom opening through which the pin slidably engages, but which are not passed by the radial projection of the pin can.
Nach einer weiteren besonders bevorzugten Ausführungsform der Erfindung ist im Inneren der Längsöffnung des Schiebers ein gegen die nach innen gewandte Stirnseite des längsverschieblichen Stifts anliegendes längsverschiebliches kolbenartiges Druckübermittlungsteil vorgesehen. Hierdurch kann die Dichtwirkung des in der Öffnung längsverschieblichen Stifts verbessert werden.According to a further particularly preferred embodiment of the Invention is provided in the interior of the longitudinal opening of the slide, a longitudinally displaceable piston-like pressure transmission part bearing against the inwardly facing end face of the longitudinally displaceable pin. As a result, the sealing effect of the pin which is longitudinally displaceable in the opening can be improved.
Weitere Merkmale, Einzelheiten und Vorteile der Erfindung ergeben sich aus den beigefügten Schutzansprüchen und der zeichnerischen Darstellung und nachfolgenden Beschreibung einer bevorzugten Ausführungsform des erfindungsgemäßen Mehrwege- Druckregelventils. In der Zeichnung zeigt die Figur einen Längsschnitt durch ein erfindungsgemäß ausgebildetes Mehrwege- Druckregelventil in der Normalbremsstellung.Further features, details and advantages of the invention result from the appended protection claims and the drawing and the following description of a preferred embodiment of the multi-way pressure control valve according to the invention. In the drawing, the figure shows a longitudinal section through an inventive multi-way pressure control valve in the normal braking position.
Das in der Figur im Längsschnitt dargestellte Mehrwege- Druckregelventil umfasst einen hülsenförmigen Gehäusekörper 2 und einen darin in Längsrichtung 4 verschieblichen Schieber 6. Der Schieber 6 ist in Längsrichtung 4 in entgegengesetzten Richtungen vorgespannt, und zwar in Richtung auf die dargestellte erste Endstellung durch eine erste Feder 8 und in Gegenrichtung durch eine zweite Feder 10. Die erste Feder 8 stützt sich einenends gegen einen Kern 12 und anderenends gegen einen Anker 14 einer elektromagnetischen Stelleinrichtung 16 ab. Der Anker 14 liegt mit seiner von der Feder 8 abgewandten Seite gegen eine endseitige Stirnseite 18 des Schiebers 6 an. Der Kern 12 der elektromagnetischen Stelleinrichtung 16 ist mittels eines topfförmigen Halteelements 20 im Presssitz gehalten, welches über ein freies Ende 22 des hülsenförmigen Gehäusekörpers 2 gestülpt und gegenüber diesem abgedichtet ist. Am Umfang des topfförmigen Elements 20 ist ein Spulenhalter 24 mit einer Spule 26 der elektromagnetischen Stelleinrichtung 16 angeordnet. Im bestromten Zustand wird der Anker 14, der innerhalb des zylindrischen Endabschnitts 22 des Gehäusekörpers 2 in Längsrichtung 4 verschieblich ist, entgegen der Vorspannung durch die Feder 8 gegen den Kern 12 bewegt.The multi-way pressure control valve shown in longitudinal section in the figure comprises a sleeve-shaped housing body 2 and a slide 6 which is displaceable therein in the longitudinal direction 4. The slide 6 is prestressed in the longitudinal direction 4 in opposite directions, namely in the direction of the first end position shown by a first spring 8 and in the opposite direction by a second spring 10. The first spring 8 is supported at one end against a core 12 and at the other end against an armature 14 of an electromagnetic actuating device 16. The armature 14 bears with its side facing away from the spring 8 against an end face 18 of the slide 6. The core 12 of the electromagnetic actuator 16 is held in a press fit by means of a pot-shaped holding element 20, which is placed over a free end 22 of the sleeve-shaped housing body 2 and is sealed off from it. A coil holder 24 with a coil 26 of the electromagnetic actuating device 16 is arranged on the circumference of the cup-shaped element 20. In the energized state, the armature 14, which is displaceable in the longitudinal direction 4 within the cylindrical end section 22 of the housing body 2, is moved against the core 12 against the bias by the spring 8.
In dem hülsenförmigen Gehäusekörper 2 sind in Längsrichtung 4 voneinander beabstandete in radialer Richtung erstreckte Öffnungen 28, 30, 32 vorgesehen, welche einen Druckmittelanschluss zu einem Niederdruckspeicher, einer Radbremse bzw. einer Hochdruckquelle in Form eines Tandemhauptzylinders bilden. Der Schieber 6 ist als Hohlschieber ausgebildet und weist eine in Längsrichtung 4 erstreckte innere Öffnung 33 auf. Der Schieber 6 weist an seinem Außenumfang eine erste Steuerkante 34 auf, die mit einer korrespondierenden Steuerkante 36 des hülsenförmigen Gehäusekörpers 2 zusammenwirkt und dabei einen veränderbaren Drosselquerschnitt 38 zwischen dem Anschluss 32 für die Hochdruckquelle und der inneren Längsöffnung 33 des Schiebers 6 freigibt oder verschließt. Die Steuerkante 34 begrenzt eine Ringnut 40, welche in der Außenumfangsflache des Schiebers 6 konzentrisch vorgesehen ist. Die Nut 40 kommuniziert über zwei radiale Bohrungen 42 mit der inneren Längsöffnung 33 des Schiebers 6 .Provided in the sleeve-shaped housing body 2 in the longitudinal direction 4 are openings 28, 30, 32 which are spaced apart in the radial direction and form a pressure medium connection to a low-pressure accumulator, a wheel brake or a high-pressure source in the form of a tandem master cylinder. The slide 6 is designed as a hollow slide and has an inner opening 33 which extends in the longitudinal direction 4. The slide 6 has on its outer circumference a first control edge 34 which interacts with a corresponding control edge 36 of the sleeve-shaped housing body 2 and thereby releases or closes a variable throttle cross section 38 between the connection 32 for the high pressure source and the inner longitudinal opening 33 of the slide 6. The control edge 34 delimits an annular groove 40, which is provided concentrically in the outer peripheral surface of the slide 6. The groove 40 communicates via two radial bores 42 with the inner longitudinal opening 33 of the Slide 6.
In der dargestellten Normalbremsstellung befindet sich eine ebenfalls konzentrische Ringnut 44 im Bereich des Druckmittelanschlusses 30 zur Radbremse. Zwei geneigte Bohrungen 46 verbinden die Nut 44 mit der inneren Längsöffnung 33 des Schiebers 6. Es besteht daher eine Druckmittelverbindung zwischen Hochdruckquelle und Radbremse.In the normal braking position shown, there is a likewise concentric annular groove 44 in the region of the pressure medium connection 30 to the wheel brake. Two inclined bores 46 connect the groove 44 to the inner longitudinal opening 33 of the slide 6. There is therefore a pressure medium connection between the high pressure source and the wheel brake.
Am ankerseitigen Ende des Schiebers 6 ist in der inneren Längsöffnung 33 ein langsverschieblicher Druckkolben 48 vorgesehen, der einenends mit dem in der inneren Längsöffnung 33 herrschenden Druck der Hochdruckquelle beaufschlagt ist und sich anderenends - wie der Schieber 6 - mit seiner Stirnseite 50 gegen den Anker 14 abstützt.At the armature-side end of the slide 6, a slowly displaceable pressure piston 48 is provided in the inner longitudinal opening 33, which is acted upon at one end by the pressure of the high-pressure source prevailing in the inner longitudinal opening 33 and at the other end - like the slide 6 - with its end face 50 against the armature 14 supports.
An dem vom Anker 14 abgewandten Ende des Schiebers 6 greift ein langsverschieblicher Stift 52 von außen in die innere Längsöffnung 33 des Schiebers 6 ein. Der Stift 52 weist an seinem freien Ende 54 einen Dichtpin 56 auf, der in der dargestellten Normalbremsstellung gegen einen Dichtsitz 58 eines den Druckmittelanschluss 28 des Niederdruckspeichers abschließenden Sitzventils 60 an. Der Stift 52 weist einen außerhalb der Längsöffnung 33 gelegenen radialen Bund 62 auf. Eine den Stift 52 umgebende Spiralfeder 64 stützt sich einenends gegen diesen Bund 62 und anderenends gegen die Stirnseite 66 des Schiebers 6 ab, so dass der Stift 52 in Richtung auf den Dichtsitz 58 vorgespannt ist. Feder 64 und Bund 62 befinden sich innerhalb eines topfförmigen Elements 68, welches mit einem kragenformigen Flanschabschnitt 70 gegen die Stirnseite 66 des Schiebers 6 anliegt und eine Bodenöffnung 72 aufweist, durch welche sich der Stift längsverschieblich hindurch erstreckt. Der Bodenbereich 74 des topfförmigen Elements 68 bildet einen Anschlag 76 für den radialen Bund 62 des Stifts 52 und bildet daher eine Verschiebeendstellung für den Stift 52.At the end of the slide 6 facing away from the armature 14, a slowly displaceable pin 52 engages from the outside in the inner longitudinal opening 33 of the slide 6. The pin 52 has at its free end 54 a sealing pin 56 which, in the illustrated normal braking position, bears against a sealing seat 58 of a seat valve 60 which closes the pressure medium connection 28 of the low-pressure accumulator. The pin 52 has a radial collar 62 located outside the longitudinal opening 33. A spiral spring 64 surrounding the pin 52 is supported at one end against this collar 62 and at the other end against the end face 66 of the slide 6, so that the pin 52 in Direction is biased to the sealing seat 58. Spring 64 and collar 62 are located within a cup-shaped element 68, which rests with a collar-shaped flange section 70 against the end face 66 of the slide 6 and has a bottom opening 72 through which the pin extends so as to be longitudinally displaceable. The bottom region 74 of the cup-shaped element 68 forms a stop 76 for the radial collar 62 of the pin 52 and therefore forms a displacement end position for the pin 52.
In der inneren Längsöffnung 33 ist des Weiteren ein langsverschieblicher Druck- und Dichtkolben 78 vorgesehen, welcher einenends mit dem in der inneren Öffnung 33 herrschenden Druck beaufschlagt ist und sich anderenends gegen das in die Längsöffnung 33 eingreifende Ende 80 des Stifts 52 anlegt.In the inner longitudinal opening 33 there is further provided a slowly displaceable pressure and sealing piston 78 which is acted upon at one end by the pressure prevailing in the inner opening 33 and at the other end abuts against the end 80 of the pin 52 which engages in the longitudinal opening 33.
Das dargestellte Mehrwege-Druckregelventil funktioniert wie folgt: In der zeichnerischen Darstellung der Figur befindet sich der Anker 14 und damit der Schieber 6 unter Vorspannung der Feder 8 in ihrer ersten Endstellung. Es besteht eine Druckmittelverbindung zwischen dem Anschluss 32 der Hochdruckquelle und dem Anschluss 30 der Radbremse, in dem der veränderbare Drosselquerschnitt 38 im Bereich des Anschlusses 32 maximal geöffnet ist, so dass Druckmittel über die Ringnut 40, die Querbohrungen 42 in die innere Längsöffnung 33 und über die geneigten Bohrungen 46 zur Ringnut 44 und zum Druckmittelanschluss 30 der Radbremse gelangen kann. Bei zunehmendem Steuerdruck über den Druckmittelanschluss 32 drückt der Druckkolben 48 mit seiner Stirnseite 50 mit entsprechend größerer Kraft gegen den Anker 14, so dass die Kraft der Feder 10 zuzüglich der Kraft des Druckkolbens 48 geringfügig größer ist als die entgegengesetzte Kraft der Feder 8. Schieber 6, Druckkolben 48 und Anker 14 werden sich daher entgegen der Kraft der Feder 8 geringfügig nach rechts bewegen bis wieder ein Kräftegleichgewicht erreicht ist. Wird der über den Anschluss 32 anliegende Steuerdruck weiter erhöht, so werden Schieber 6 samt Druckkolben 48 und Anker 14 noch weiter nach rechts bewegt. Bei abnehmendem Steuerdruck werden sich Schieber 6, Druckkolben 48 und Anker 14 wieder nach links bewegen. Der Schieber 6 wird also im Normalbremsbetrieb entsprechend dem anliegenden Steuerdruck ständig hin- und herbewegt, wodurch die Gefahr, dass sich der Schieber festsetzt, ausgeschlossen wird. Während des Hin- und Herbewegens des Schiebers 6 im Normalbremsbetrieb wird auch der Druck- und Dichtkolben 78 unter der Wirkung des Steuerdrucks hin- und herbewegt und hält durch Druck auf den Stift 52 den Dichtpin 56 des Stifts 52 in dichtender Anlage an dem Dichtsitz 58 des Sitzventils 60. Der Stift 52 stützt sich also auf dem Dichtsitz 58 ab.The illustrated multi-way pressure regulating valve works as follows: In the drawing of the figure, the armature 14 and thus the slide 6 are under the pretension of the spring 8 in their first end position. There is a pressure medium connection between the connection 32 of the high-pressure source and the connection 30 of the wheel brake, in which the variable throttle cross-section 38 is opened to a maximum in the area of the connection 32, so that pressure medium via the annular groove 40, the transverse bores 42 into the inner longitudinal opening 33 and over the inclined holes 46 to the annular groove 44 and Pressure medium connection 30 of the wheel brake can reach. With increasing control pressure via the pressure medium connection 32, the pressure piston 48 presses with its end face 50 with a correspondingly greater force against the armature 14, so that the force of the spring 10 plus the force of the pressure piston 48 is slightly greater than the opposite force of the spring 8. Slide 6 The pressure piston 48 and armature 14 will therefore move slightly to the right against the force of the spring 8 until an equilibrium of forces is reached again. If the control pressure present via the connection 32 is increased further, the slide 6 together with the pressure piston 48 and armature 14 are moved further to the right. When the control pressure decreases, slide 6, pressure piston 48 and armature 14 will again move to the left. The slider 6 is therefore constantly moved back and forth in normal braking operation in accordance with the control pressure present, thereby eliminating the risk that the slider will get stuck. During the back and forth movement of the slide 6 in normal braking operation, the pressure and sealing piston 78 is also moved back and forth under the effect of the control pressure and holds the sealing pin 56 of the pin 52 in sealing contact with the sealing seat 58 by pressing on the pin 52 Seat valve 60. The pin 52 is therefore supported on the sealing seat 58.
Wenn nun der Normalbremsbetrieb bei anliegendem Bremsdruck verlassen werden soll, weil das Blockieren eines Rades von der Steuer- und Regeleinrichtung des Bremssystems festgestellt wurde, so wird die elektromagnetische Stelleinrichtung 16 bestromt und der Anker 14 in Richtung auf den Kern 12 bewegt und in diesem ABS-Fall bestimmen die Kräfte zwischen Anker 14 und Kern 12, in welche Position der Schieber 6 unter der Wirkung der Feder 10 geschoben wird. Bei dieser Verschiebung überfährt zuerst die Steuerkante 34 des Schiebers 6 die korrespondierende Steuerkante 36 des Gehäusekörpers 2, so dass die Druckmittelverbindung zwischen innerer Schieberöffnung 33 und Hochdruckquelle getrennt ist. Währenddessen wird der Stift 52 aus der inneren Längsöffnung 33 des Schiebers 6 herausbewegt, bis sein radialer Bund 62 gegen den Anschlag 76 anschlägt. Hiernach wird der Dichtpin 56 vom Dichtsitz 58 abgehoben, so dass das Sitzventil 60 zum Druckmittelanschluss 28 des Niederdruckspeichers öffnet. Schließlich wird eine Steuerkante 82, welche von der Stirnseite 66 des Schiebers 6 gebildet ist, eine korrespondierende Steuerkante 84 des Gehäusekörpers 2 überfahren, wodurch ein in der Figur nicht dargestellter aber leicht vorstellbarer Drosselquerschnitt zwischen dem Druckmittelanschluss 30 der Radbremse und dem geöffneten Sitzventil 60 geöffnet wird, um einen Druckabbau in der Radbremse zum Niederdruckspeicher hin zu bewirken.If normal braking operation is now to be exited when the brake pressure is applied because the locking of a wheel has been determined by the control and regulating device of the brake system, then the electromagnetic actuating device 16 energized and the armature 14 moves in the direction of the core 12 and in this ABS case, the forces between armature 14 and core 12 determine the position into which the slide 6 is pushed under the action of the spring 10. During this displacement, the control edge 34 of the slide 6 first passes over the corresponding control edge 36 of the housing body 2, so that the pressure medium connection between the inner slide opening 33 and the high-pressure source is separated. In the meantime, the pin 52 is moved out of the inner longitudinal opening 33 of the slide 6 until its radial collar 62 abuts against the stop 76. The sealing pin 56 is then lifted off the sealing seat 58, so that the seat valve 60 opens to the pressure medium connection 28 of the low-pressure accumulator. Finally, a control edge 82, which is formed by the end face 66 of the slide 6, passes over a corresponding control edge 84 of the housing body 2, whereby a throttle cross-section, not shown in the figure but easily imaginable, is opened between the pressure medium connection 30 of the wheel brake and the opened seat valve 60 to cause a pressure reduction in the wheel brake to the low pressure accumulator.
Zum Druckhalten überfährt die Steuerkante 82 des Schiebers 6 die Steuerkante 84 in umgekehrter Richtung, so dass der Drosselquerschnitt zwischen Radbremse und Niederdruckspeicher wieder unterbrochen wird, wobei nach wie vor das Sitzventil 60 geöffnet bleibt. Soll der Druck in der Radbremse wieder erhöht werden, wird durch entsprechende Steuerung der Stromstärke in der Spule 26 der Anker 14 unter der Wirkung der Feder 8 so weit nach links bewegt, bis die Steuerkante 34 des Schiebers wieder die Steuerkante 36 im Bereich des Druckmittelanschlusses 32 zur Hochdruckquelle öffnet.To maintain pressure, the control edge 82 of the slide 6 passes over the control edge 84 in the opposite direction, so that the throttle cross section between the wheel brake and the low-pressure accumulator is interrupted again, the seat valve 60 still remaining open. If the pressure in the wheel brake is to be increased again, the current in is controlled accordingly the coil 26, the armature 14 is moved so far to the left under the action of the spring 8 until the control edge 34 of the slide opens the control edge 36 again in the region of the pressure medium connection 32 to the high pressure source.
In dieser aktivierten ABS-Regelstellung stützt sich der Dicht- und Druckkolben 78 über den Stift 52, den Bund 62, den Anschlag 64, den Kragen 70 und die Feder 10 auf das Gehäuse ab. In this activated ABS control position, the sealing and pressure piston 78 is supported on the housing via the pin 52, the collar 62, the stop 64, the collar 70 and the spring 10.

Claims

Patentansprücheclaims
1. Elektromagnetisch ansteuerbares Mehrwege-Regelventil für schlupfgeregelte hydraulische Kraftfahrzeugbremssysteme, zum Herstellen einer Druckmittelverbindung zwischen wenigstens einer Radbremse (Rad) und einer Hochdruckquelle (THZ) oder einem Niederdruckspeicher (NDS), umfassend1. Electromagnetically controllable multi-way control valve for slip-controlled hydraulic motor vehicle brake systems, for establishing a pressure medium connection between at least one wheel brake (wheel) and a high pressure source (THZ) or a low pressure accumulator (NDS), comprising
einen in einem hülsenförmigen Gehäusekörper (2) geführten Schieber (6), der ina slide (6) which is guided in a sleeve-shaped housing body (2) and which
Verschiebelängsrichtung (4) in beiden Richtungen vorgespannt ist und eine in Längsrichtung verlaufende Öffnung (33) aufweist, wobei im Normalbremsbetrieb die Vorspannung in Richtung auf eine erste Endlage hin dominiert, in welcher die Radbremse mit der Hochdruckquelle strömungsmäßig verbunden und vom Niederdruckspeicher strömungsmäßig getrennt ist, undThe longitudinal direction of displacement (4) is biased in both directions and has an opening (33) running in the longitudinal direction, the bias predominating towards a first end position in normal braking operation, in which the wheel brake is fluidly connected to the high-pressure source and is fluidly separated from the low-pressure accumulator, and
ein zwischen der Radbremse und demone between the wheel brake and the
Niederdruckspeicher vorgesehenes Ventil (60), welches zum Druckabbauen in der Radbremse geöffnet wird,Low-pressure accumulator provided valve (60), which is opened to reduce pressure in the wheel brake,
dadurch gekennzeichnet,characterized,
dass in der Öffnung (33) des Schiebers (6) ein langsverschieblicher Druckkolben (48) vorgesehen ist, der im Normalbremsbetrieb mit seinem freien Ende (50) der in die erste Endlage gerichteten Vorspannung entgegenwirkt, so daß der Schieber (6) in Abhängigkeit vom Druck der Hochdruckquelle in Längsrichtung hin- und herbewegbar ist.that in the opening (33) of the slide (6) a slowly displaceable pressure piston (48) is provided, which in normal braking operation with its free end (50) in the first end position counteracts bias, so that the slide (6) can be moved in the longitudinal direction depending on the pressure of the high pressure source.
!. Mehrwege-Regelventil nach Anspruch 1, dadurch gekennzeichnet, dass die Vorspannung in Richtung auf die erste Endlage von einem Federmittel (8) über ein Vermittlerelement auf den Schieber (6) übertragen wird und der längsverschiebliche Druckkolben (48) gegen das Vermittlerelement abgestützt ist.!. Multi-way control valve according to claim 1, characterized in that the bias towards the first end position is transmitted from a spring means (8) via a mediator element to the slide (6) and the longitudinally displaceable pressure piston (48) is supported against the mediator element.
) . Mehrwege-Regelventil nach Anspruch 2, dadurch gekennzeichnet, dass das Vermittlerelement vom Anker (14) einer elektromagnetischen Stelleinrichtung (16) gebildet ist.). Multi-way control valve according to claim 2, characterized in that the mediator element is formed by the armature (14) of an electromagnetic actuating device (16).
1. Mehrwege-Regelventil nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, dass die in Längsrichtung verlaufenden Öffnung (33) des Schiebers (6) an ihrem vom Druckkolben (48) abgewandten Ende an der dortigen Stirnseite (66) des Schiebers (6) mündet und dass in den Mündungsbereich der Öffnung (33) ein beschränkt langsverschieblicher Stift (52) eingreift, welcher das Ventil (60) zwischen Radbremse und Niederdruckspeicher im Normalbremsbetrieb geschlossen hält. Mehrwege-Regelventil nach Anspruch 4, dadurch gekennzeichnet, dass der längsverschiebliche Stift (52) durch den in der Öffnung (33) anstehenden Druck der Hochdruckquelle in Schließrichtung des Ventils (60) vorgespannt ist.1. Multi-way control valve according to claim 1, 2 or 3, characterized in that the longitudinal opening (33) of the slide (6) at its end facing away from the pressure piston (48) on the end face (66) of the slide (6 ) opens and that in the mouth area of the opening (33) engages a pin (52) which can be moved slowly and which keeps the valve (60) between the wheel brake and the low-pressure accumulator closed in normal braking mode. Multi-way control valve according to claim 4, characterized in that the longitudinally displaceable pin (52) is biased in the closing direction of the valve (60) by the pressure of the high pressure source present in the opening (33).
>. Mehrwege-Regelventil nach Anspruch 5, dadurch gekennzeichnet, dass das Ventil (60) zwischen Radbremse und Niederdruckspeicher als Sitzventil ausgebildet ist und dass der Ventilkörper des Sitzventils von dem freien aus der Längsöffnung ragenden Ende (54) des längsverschieblichen Stifts (52) betätigbar ist.>. Multi-way control valve according to claim 5, characterized in that the valve (60) between the wheel brake and low-pressure accumulator is designed as a seat valve and that the valve body of the seat valve can be actuated by the free end (54) of the longitudinally displaceable pin (52) which projects from the longitudinal opening.
1 . Mehrwege-Regelventil nach Anspruch 5, dadurch gekennzeichnet, dass das Ventil (60) zwischen Radbremse und Niederdruckspeicher als Sitzventil ausgebildet ist und das freie Ende (54) des längsverschieblichen Stifts (52) den Ventilkörper des Sitzventils bildet und im Normalbremsbetrieb gegen einen Dichtsitz (58) des Sitzventils dichtend anliegt.1 . Multi-way control valve according to claim 5, characterized in that the valve (60) between the wheel brake and the low pressure accumulator is designed as a seat valve and the free end (54) of the longitudinally displaceable pin (52) forms the valve body of the seat valve and in normal braking operation against a sealing seat (58 ) of the seat valve lies tight.
Mehrwege-Regelventil nach einem der Ansprüche 5 - 7 , dadurch gekennzeichnet, dass der längsverschiebliche Stift (52) einen radialen Vorsprung (62) aufweist, der zur Begrenzung der Längsverschieblichkeit gegen einen Anschlag (76) anlegbar ist. Multi-way control valve according to one of claims 5-7, characterized in that the longitudinally displaceable pin (52) has a radial projection (62) which can be placed against a stop (76) to limit the longitudinal displaceability.
9. Mehrwege-Regelventil nach Anspruch 8, dadurch gekennzeichnet, dass der radiale Vorsprung (62) des Stifts (52) und der mit diesem zusammenwirkende Anschlag (76) außerhalb des Schiebers (6) angeordnet sind.9. Multi-way control valve according to claim 8, characterized in that the radial projection (62) of the pin (52) and the stop (76) cooperating therewith are arranged outside the slide (6).
10. Mehrwege-Regelventil nach einem der Ansprüche 5 - 9, dadurch gekennzeichnet, dass im Inneren der Öffnung (33) ein gegen die Stirnseite (66) des Stifts (52) anliegendes längsverschiebliches Druckübermittlungsteil (78) vorgesehen ist.10. Multi-way control valve according to one of claims 5-9, characterized in that in the interior of the opening (33) against the end face (66) of the pin (52) adjacent longitudinally displaceable pressure transmission part (78) is provided.
11. Mehrwege-Regelventil nach wenigstens einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Schieber (6) eine erste Steuerkante (34) aufweist und zusammen mit einer korrespondierenden Steuerkante (36) an dem Gehäusekörper (2) einen ersten veränderbaren Drosselquerschnitt (38) in der hydraulischen Druckmittelverbindung zwischen der Hochdruckquelle und der Radbremse bildet.11. Multi-way control valve according to at least one of the preceding claims, characterized in that the slide (6) has a first control edge (34) and together with a corresponding control edge (36) on the housing body (2) a first variable throttle cross-section (38) in the hydraulic pressure medium connection between the high pressure source and the wheel brake.
12. Mehrwege-Regelventil nach wenigstens einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Schieber (6) eine zweite Steuerkante (82) aufweist, die mit einer korrespondierenden zweiten Steuerkante (84) an dem Gehäusekörper (2) einen zweiten veränderbaren Drosselquerschnitt in der hydraulischen Druckmittelverbindung zwischen Radbremse und Niederdruckspeicher bildet.12. Multi-way control valve according to at least one of the preceding claims, characterized in that the slide (6) has a second control edge (82) which with a corresponding second control edge (84) on the housing body (2) has a second variable throttle cross section in the hydraulic pressure medium connection between wheel brake and Low pressure accumulator forms.
13. Mehrwege-Regelventil nach den Ansprüchen 12 und 13, dadurch gekennzeichnet, dass die ersten (34, 36) und zweiten (82, 84) Steuerkanten derart angeordnet sind, dass beim Verschieben des Schiebers (6) in Richtung eines Druckabbaus an der Radbremse zuerst der erste Strömungsquerschnitt (38) geschlossen und dann erst der zweite Strömungsquerschnitt geöffnet wird. 13. Multi-way control valve according to claims 12 and 13, characterized in that the first (34, 36) and second (82, 84) control edges are arranged such that when the slide (6) is moved in the direction of a pressure reduction on the wheel brake first the first flow cross section (38) is closed and only then is the second flow cross section opened.
PCT/EP1998/000444 1997-02-01 1998-01-28 Pressure control valve WO1998033688A1 (en)

Applications Claiming Priority (2)

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DE19703775.5 1997-02-01
DE1997103775 DE19703775A1 (en) 1997-02-01 1997-02-01 Pressure control valve

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008143188A1 (en) 2007-05-17 2008-11-27 Bridgestone Corporation Radial tire for heavy load

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005038215A1 (en) * 2005-05-06 2006-11-09 Continental Teves Ag & Co. Ohg Electromagnetic multi-way valve for non-slip vehicle braking systems has first valve closing component passing through second valve closing component and fits against its seat, regardless of tolerance of second component in valve casing
DE102015223833A1 (en) * 2015-12-01 2017-06-01 Continental Teves Ag & Co. Ohg braking system

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US3832010A (en) * 1971-12-13 1974-08-27 Citroen Sa Brake control devices for preventing locking a braked wheel
JPH072076A (en) * 1993-06-21 1995-01-06 Hitachi Ltd Flow rate control valve for antilock brake device
DE4441150A1 (en) 1994-11-18 1996-05-23 Teves Gmbh Alfred Pressure control valve

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Publication number Priority date Publication date Assignee Title
FR2669883B1 (en) * 1990-11-29 1993-01-29 Bendix Europ Services Tech AUTOMATIC BRAKING DEVICE FOR VEHICLE.
FR2691690B1 (en) * 1992-05-26 1994-07-22 Bendix Europ Services Tech BRAKING DEVICE WITH SINGLE DISTRIBUTOR FOR ANTI - LOCK AND ANTI - SKATING.

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Publication number Priority date Publication date Assignee Title
US3832010A (en) * 1971-12-13 1974-08-27 Citroen Sa Brake control devices for preventing locking a braked wheel
JPH072076A (en) * 1993-06-21 1995-01-06 Hitachi Ltd Flow rate control valve for antilock brake device
DE4441150A1 (en) 1994-11-18 1996-05-23 Teves Gmbh Alfred Pressure control valve

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Title
PATENT ABSTRACTS OF JAPAN vol. 095, no. 004 31 May 1995 (1995-05-31) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008143188A1 (en) 2007-05-17 2008-11-27 Bridgestone Corporation Radial tire for heavy load

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