DE4332820A1 - Hydraulic brake system with slip control - Google Patents

Hydraulic brake system with slip control

Info

Publication number
DE4332820A1
DE4332820A1 DE19934332820 DE4332820A DE4332820A1 DE 4332820 A1 DE4332820 A1 DE 4332820A1 DE 19934332820 DE19934332820 DE 19934332820 DE 4332820 A DE4332820 A DE 4332820A DE 4332820 A1 DE4332820 A1 DE 4332820A1
Authority
DE
Germany
Prior art keywords
valve
pressure
brake system
annular piston
central body
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
DE19934332820
Other languages
German (de)
Inventor
Juergen Rausch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
ITT Automotive Europe GmbH
Alfred Teves GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE4319227A external-priority patent/DE4319227A1/en
Application filed by ITT Automotive Europe GmbH, Alfred Teves GmbH filed Critical ITT Automotive Europe GmbH
Priority to DE19934332820 priority Critical patent/DE4332820A1/en
Priority to CZ1996592A priority patent/CZ289322B6/en
Priority to KR1019960700972A priority patent/KR100314299B1/en
Priority to SK273-96A priority patent/SK27396A3/en
Priority to JP51010395A priority patent/JP3905122B2/en
Priority to EP94928802A priority patent/EP0720553B1/en
Priority to PCT/EP1994/003183 priority patent/WO1995009098A1/en
Priority to US08/619,745 priority patent/US5887956A/en
Priority to DE59408550T priority patent/DE59408550D1/en
Publication of DE4332820A1 publication Critical patent/DE4332820A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • B60T8/5037—Pressure reapplication using restrictions in hydraulic brake systems closed systems
    • 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
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems 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
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B60T8/365—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems combining a plurality of functions in one unit, e.g. pressure relief
    • 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
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/42—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having expanding chambers for controlling pressure, i.e. closed systems
    • B60T8/4275—Pump-back systems
    • B60T8/4291—Pump-back systems having means to reduce or eliminate pedal kick-back
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—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

Landscapes

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

Abstract

The invention relates to a brake system with slip control, which is provided with digital-controlled solenoid inlet and outlet valves (1, 17), a volume control valve varying as a function of differential pressures being assigned to the inlet valve (1) in order to reduce the valve noises. <IMAGE>

Description

Die Erfindung betrifft eine hydraulische Bremsanlage mit Schlupfregelung nach dem Oberbegriff des Anspruchs 1 und stellt eine weitere Ausgestaltung des Gegenstandes der Er­ findung nach Patent (Patentanmeldung Akten­ zeichen: P 43 19 227.0) dar.The invention relates to a hydraulic brake system Slip control according to the preamble of claim 1 and represents a further embodiment of the subject of Er invention after patent (patent application files characters: P 43 19 227.0).

Die diskontinuierliche Druckmittelsteuerung bei schlupfge­ regelten Bremsanlagen mittels digital schaltbaren Ein­ laß- und Auslaßventilen führt infolge des impulsartigen Druckverlaufs zur unerwünschten Schallemission.The discontinuous pressure medium control at schlupfge controlled braking systems using digitally switchable on Let and exhaust valves result from the pulse-like Pressure curve for undesirable noise emission.

Bei der in der Hauptanmeldung beschriebenen Bremsanlage hat es sich gezeigt, daß die vorgeschlagenen konstruktiven Lö­ sungen zur Anordnung des mit der schaltbaren Blende verse­ henen Ringkolbens sowie die mit dem Ringkolben korrespon­ dierenden Einzelheiten im Einlaßmagnetventil einer weiteren baulichen Vereinfachung bedürfen, um eine möglichst einfach bauende und miniaturisierte Ausführung des Einlaßventils zu erhalten.In the brake system described in the main application it has been shown that the proposed constructive Lö solutions to the arrangement of the verse with the switchable aperture the annular piston and the one corresponding to the annular piston details in the inlet solenoid valve another Structural simplifications need to be as simple as possible building and miniaturized version of the inlet valve receive.

Daher ist es die Aufgabe der Erfindung, unter Beibehaltung eines unveränderten schaltungstechnischen Aufbaus der aus der Hauptanmeldung hervorgegangenen Bremsanlage, Lösungs­ vorschläge zur Miniaturisierung des Einlaßventils auf zuzei­ gen, die ohne Einschränkung der Funktionsfähigkeit kosten­ günstig zu realisieren sind.Therefore, it is the object of the invention while maintaining an unchanged circuit design from the main application of the braking system, solution Suggestions for miniaturization of the intake valve on time conditions that cost without restriction of functionality are cheap to implement.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnen­ den Merkmale des Patentanspruchs 1 gelöst, wonach der die schaltbare Blende aufnehmende Ringkolben im Ventilträger, innerhalb eines Ringraums, konzentrisch zum Ventilschließ­ glied des Einlaßventils geführt ist.According to the invention, this object is characterized by the solved the features of claim 1, according to which the switchable orifice-receiving ring pistons in the valve carrier,  within an annulus, concentric with valve closing member of the inlet valve is guided.

Hierdurch dient gleichzeitig der ursprünglich einen Ring­ filter und das Ventilschließglied aufnehmende Ringraum vor­ teilhaft zur Integration des Ringkolbens, womit die Außen­ maße des Ventilträgers und die Maße der Stufenbohrung des Ventilaufnahmekörpers beibehalten werden können. Ferner kann der Ringbereich zwischen dem Ventilaufnahmekörper und dem Ventilträger zur Anordnung des Ringfilters verwendet werden, wodurch sich eine vorteilhafte Vergrößerung der Filterfläche zur Filtrierung der u. a. auch zwischen der Radbremse und der Rückschlagmanschette strömenden Flüssig­ keit ergibt.This also serves as the original ring filter and the valve closing member receiving annulus part of the integration of the ring piston, with which the outside dimensions of the valve carrier and the dimensions of the stepped bore of the Valve receiving body can be retained. Further can the ring area between the valve body and the valve carrier used to arrange the ring filter be, which is an advantageous increase in Filter surface for filtering the u. a. also between the Wheel brake and the non-return sleeve flowing fluid results.

Weitere Merkmale, Vorteile und Anwendungsmöglichkeiten der Erfindung gehen aus der nachfolgenden Beschreibung mehrerer Ausführungsbeispiele hervor.Other features, advantages and possible uses of the Invention will emerge from the following description of several Embodiments emerge.

Es zeigen:Show it:

Fig. 1 eine Teilansicht eines Einlaßventils in vergrößer­ ter Darstellung, mit der erfindungsgemäßen Anord­ nung des Ringkolbens im Bereich des Ventilschließ­ gliedes, Fig. 1 is a partial view of an inlet valve member in Enlarge ter representation, with the inventive Anord voltage of the annular piston in the area of the valve closing,

Fig. 2 eine weitere alternative Ausführungsform von Ein­ zelheiten innerhalb eines Einlaßventils, Fig. 2 shows a further alternative embodiment of a zelheiten within an intake valve,

Fig. 3 einen Querschnitt an der Stelle A-A des Ventilträ­ gers im vergrößerten Maßstab. Fig. 3 shows a cross section at the location AA of the Ventilträ gers on an enlarged scale.

Die Fig. 1 zeigt ein konstruktives Ausführungsbeispiel zum Gesamtaufbau des Einlaßventils 1. Das Einlaßventil 1 weist einen Ventilträger 10 auf, der das Ventilschließglied 11 und die Kanalführung der vom Bremsdruckgeber 5 und der Hilfsdruckpumpe 18 kommenden Hauptdruckleitung 2 beinhal­ tet. Der Ventilträger 10 ist vorzugsweise in Patronenbau­ weise (Einschraubpatrone, Verstemmpatrone, Patrone mit Spreizring) in einem Ventilaufnahmekörper 9 integriert. In der gewählten Darstellung des Ventilbefestigungssystems ist der Ventilträger 10 im konisch verjüngten Außenbereich mit einem Spreizring 128 im Ventilaufnahmekörper 9 befestigt, dessen Öffnung zur Aufnahme des Spreizrings 128 mit einer konischen Hinterschneidung versehen ist. Die Abdichtung des Ventilträgers 10 im Ventilaufnahmekörper 9 ist durch eine unterhalb des konisch geformten Ventilträgers 10 angeordne­ te Dichtung gewährleistet. Es besteht eine Druckmittelver­ bindung der Hauptdruckleitung 2, die am Bremsdruckgeber 5 und der Hilfsdruckpumpe 18 angeschlossen ist, durch einen am Fortsatz des Ventilträgers 10 aufgeclipsten Plattenfil­ ter 21 und über das in der Grundstellung offengeschaltete Ventilschließglied 11 zum Ringkolben 8. Von dort gelangt Druckmittel über den offenen Ringspalt am Magnetkern 127 sowie auch im geringen Umfang über die Blende 4 zu einer im Ventilträger 10 eingearbeiteten Festblende 31, die zum Zwecke der Verbesserung der ABS-Regelgüte verwendet wird, in Richtung des dem Anschluß zur Radbremse 3 vorgeschalte­ ten Ringfilters 22. Fig. 1 shows a constructive embodiment of the overall configuration of the intake valve 1. The inlet valve 1 has a valve carrier 10 , which includes the valve closing member 11 and the channel guide of the main pressure line 2 coming from the brake pressure transmitter 5 and the auxiliary pressure pump 18 . The valve carrier 10 is preferably integrated in a cartridge construction (screw-in cartridge, caulking cartridge, cartridge with expansion ring) in a valve receiving body 9 . In the selected representation of the valve fastening system, the valve carrier 10 is fastened in the conically tapered outer region with an expansion ring 128 in the valve receiving body 9 , the opening for receiving the expansion ring 128 is provided with a conical undercut. The sealing of the valve carrier 10 in the valve receiving body 9 is ensured by a TE below the conically shaped valve carrier 10 . There is a Druckmittelver connection of the main pressure line 2 , which is connected to the brake pressure sensor 5 and the auxiliary pressure pump 18 , by a clipped on the extension of the valve support 10 Plattenfil ter 21 and via the valve closing member 11 open in the basic position to the annular piston 8th From there, pressure medium passes through the open annular gap on the magnetic core 127 and also to a small extent via the orifice 4 to a fixed orifice 31 incorporated in the valve carrier 10 , which is used for the purpose of improving the ABS control quality, in the direction of the connection to the wheel brake 3 ring filter 22 .

Der Ringkolben 8 übernimmt infolge einer Querbohrung in der Ringkolbenwandung die schaltbare Blendenfunktion. Dieser ist auf dem im Durchmesser verkleinerten Fortsatz des den Ventilsitz 116 aufweisenden rotationssymmetrischen Zentral­ körpers 114 im Ringraum 126 axial beweglich geführt. Der Ringkolben 8 stützt sich unter Wirkung einer Druckfeder 7 mit seinem als Anschlag wirksamen äußeren Bund 119 an der Bohrungsstufe des Ringraums 126 im Ventilträger 10 ab. Der Ringkolben 8 weist im wesentlichen die Form einer Hülse auf, die an ihrer dem Magnetkern 127 zugewandten Stirn­ fläche mit einem trichterförmigen Gummidichtsitz 115 verse­ hen ist, der dem kegelförmig gestalteten Stirnbereich des Magnetkerns 127 gegenüberliegt. Bei Wunsch oder Bedarf kann die Kegelabdichtung auch als metallische Flachdichtung oder mit einem im Stirnflächenbereich des Ringkolben 8 einge­ faßten O-Ring ausgeführt sein.The annular piston 8 takes over the switchable diaphragm function as a result of a transverse bore in the annular piston wall. This is on the reduced diameter extension of the valve seat 116 having rotationally symmetrical central body 114 in the annular space 126 axially movable. The annular piston 8 is supported under the action of a compression spring 7 with its outer collar 119 , which acts as a stop, on the bore step of the annular space 126 in the valve carrier 10 . The annular piston 8 has essentially the shape of a sleeve, the face on its end facing the magnetic core 127 is hen with a funnel-shaped rubber sealing seat 115 , which is opposite the conical end region of the magnetic core 127 . If desired or required, the cone seal can also be designed as a metallic flat seal or with an O-ring encased in the end face area of the annular piston 8 .

Auf der zum Magnetkern 127 abgewandten Stirnseite des Ring­ kolbens 8 befindet sich ein Dichtring 124, der in der Schließstellung des Einlaßventils 1 ein Überströmen von Druckmittel vom Bremsdruckgeber 5 in Richtung der Radbremse 3 verhindert. Der sich mit seinem Fortsatz in den Innenraum erstreckende rotationssymmetrische Zentralkörper 114 ist in die Stufenbohrung des Ventilträgers 10 eingepreßt und ggf. im Stirnflächenbereich verstemmt. In der gezeigten Ausfüh­ rungsform ist der Ventilsitz 116 als gestuftes Hülsenteil in die koaxial zum Ventilschließglied 11 verlaufende Boh­ rung des Zentralkörpers 114 eingepreßt.On the end of the ring piston 8 facing away from the magnetic core 127 there is a sealing ring 124 which , in the closed position of the inlet valve 1, prevents overflow of pressure medium from the brake pressure transmitter 5 in the direction of the wheel brake 3 . The rotationally symmetrical central body 114 , which extends into the interior with its extension, is pressed into the stepped bore of the valve carrier 10 and, if necessary, caulked in the end face region. In the embodiment shown, the valve seat 116 is pressed as a stepped sleeve part into the bore of the central body 114 which runs coaxially to the valve closing member 11 .

Eine am Außenumfang des Ventilträgers 10 auf Höhe des Zen­ tralkörpers 114 gelegene Ringnut nimmt eine in Richtung der Radbremse 3 sperrende Dichtmanschette 112 auf, die über ei­ nen zwischen dem Ventilträger 10 und dem Ventilaufnahmekör­ per 9 beabstandeten Ringfilter 22 sowie mittels wenigstens einer in der Abbildung erkennbaren seitlichen Ausnehmung 120 am Plattenfilter 21 eine die Flüssigkeit filtrierende Druckmittelverbindung zwischen der Radbremse 3 und dem Bremsdruckgeber 5, bzw. der Hilfsdruckpumpe 18, ermöglicht. An on the outer circumference of the valve support 10 at the level of the Zen tralkörpers 114 annular groove receives a locking in the direction of the wheel brake 3 sealing sleeve 112 , the egg filter between egg valve 10 and the valve receptacle by 9 spaced ring filter 22 and by means of at least one recognizable in the figure lateral recess 120 on the plate filter 21 enables a fluid filtering pressure medium connection between the wheel brake 3 and the brake pressure sensor 5 , or the auxiliary pressure pump 18 .

Die Fig. 2 zeigt abweichend von Fig. 1 gleichfalls im er­ heblich vergrößerten Maßstab den Ventilsitz 116 als homoge­ nes Bestandteil im Zentralkörper 114 integriert, so daß die in Fig. 1 erläuterte separate Anordnung eines den Ventil­ sitz 116 aufweisenden weiteren hülsenförmigen Einpreßteils entfällt. Zur Druckbeaufschlagung des am Ringkolben 8 ange­ ordneten Dichtrings 124 ist lediglich ein Durchbruch 118 im Zentralkörper 114 vorgesehen, der entsprechend groß dimen­ sioniert ist und als eine Bohrung kostengünstig hergestellt werden kann. Zur Feinabstimmung der Durchflußmenge zur Rad­ bremse 3 im ABS-Betrieb, ist zusätzlich im Ventilträger 10 eine Festblende 31 als Einsatzteil in die den Ringraum 126 mit der Radbremse 3 hydraulisch verbindenden Querbohrung 13 des Ventilträgers 10 eingepreßt, wobei bei Bedarf, entspre­ chend der Darstellung in Fig. 1, auch durch kalibriertes Feinbohren der Querbohrung die Funktion der Festblende mög­ lich ist. Der Ventilträger 10 ist mittels einer im Ventil­ aufnahmekörper 9 selbsteinscherenden Befestigung gehalten, so daß auf den aus Fig. 1 bekannten Dichtring verzichtet werden kann. Fig. 2 shows, deviating from Fig. 1 also on a considerably enlarged scale, it integrates the valve seat 116 as a homogeneous component in the central body 114 , so that the separate arrangement of a valve seat 116 having a further sleeve-shaped press-in part eliminated in Fig. 1 is omitted. For pressurizing is disposed on the annular piston 8 sealing ring 124, only one aperture 118 is provided in the central body 114 which is sioned correspondingly large dimen and can be manufactured inexpensively as a bore. To fine-tune the flow rate to the wheel brake 3 in ABS operation, a fixed orifice 31 is additionally pressed in the valve carrier 10 as an insert into the annular space 126 with the wheel brake 3 hydraulically connecting transverse bore 13 of the valve carrier 10 , if necessary, corresponding to the representation in Fig. 1, the function of the fixed aperture is possible by calibrated fine drilling of the cross hole. The valve carrier 10 is held by means of a self-reinserting mounting body 9 in the valve, so that the sealing ring known from FIG. 1 can be dispensed with.

Alle aus der bildlichen Darstellung von Fig. 2 ersicht­ lichen weiteren Elemente entsprechen im wesentlichen dem Aufbau und der Funktion nach Fig. 1.All of the other elements shown in the pictorial representation of FIG. 2 essentially correspond to the structure and function of FIG. 1.

Die Fig. 3 zeigt eine Draufsicht auf das in Fig. 1 darge­ stellte Einlaßventil 1 an der Schnittstelle A-A, woraus hervorgeht, daß der Zentralkörper 114 durch die Ausführung als Vierkantprofil gegenüber der Innenwandung des Ventil­ trägers 10 entsprechend große Druckmitteldurchlässe in Richtung des dem Ringkolben 8 vorgeordneten Dichtrings 124 aufweist. Die Schnittebene durchdringt den unteren Endab­ schnitt des Ventilträgers 10, an dem der Plattenfilter 21 aufgeclipst ist. Der Plattenfilter 21 weist über den Umfang verteilt mehrere Ausnehmungen 120 auf, die den Druckmittel­ durchlaß aus Richtung der Dichtmanschette 112 ermöglichen. Alle zur Schnittebene A-A beschriebenen Elemente befinden sich somit zueinander in einer rotationssymmetrischen koaxialen Anordnung. Fig. 3 shows a plan view of the inlet valve 1 shown in Fig. 1 Darge at the interface AA, which shows that the central body 114 by execution as a square profile against the inner wall of the valve carrier 10 correspondingly large pressure medium passages in the direction of the annular piston 8th upstream sealing ring 124 . The sectional plane penetrates the lower Endab section of the valve support 10 on which the plate filter 21 is clipped. The plate filter 21 has a plurality of recesses 120 distributed over the circumference, which allow the pressure medium passage from the direction of the sealing sleeve 112 . All the elements described for the section plane AA are thus in a rotationally symmetrical coaxial arrangement with respect to one another.

Nachfolgend wird die Funktionsweise der Erfindung erläutert:The mode of operation of the invention is explained below:

Während einer nicht geregelten, schlupffreien Normalbrems­ phase befindet sich das Einlaßventil 1 in der elektromagne­ tisch nicht erregten offenen Grundstellung. Bei der Betäti­ gung des Bremsdruckgebers 5 entsteht kein Staudruck im Ven­ tileingang des Einlaßventils 1, da der Ventilsitz 116 keine maßgebliche Drossel- bzw. Blendenwirkung verursacht, wo­ durch auch keine nennenswerte Druckdifferenz zwischen dem Ventileingang und Ventilausgang entsteht. Der Ringkolben 8 bleibt in der abbildungsgemäßen Ausgangsstellung an der Bohrungsstufe auf Anschlag, so daß der Bremsdruck über den Ventilsitz 116 sowie über den Ringspalt zwischen dem Ring­ kolben 8 und dem Magnetkern 127 auf die Radbremse 3 wirken kann.During an uncontrolled, slip-free normal braking phase, the inlet valve 1 is in the electromagnetic non-energized open basic position. When actuating the brake pressure transducer 5 , there is no back pressure in the valve inlet of the inlet valve 1 , since the valve seat 116 does not cause any significant throttling or orifice effect, where there is also no significant pressure difference between the valve inlet and valve outlet. The annular piston 8 remains in the illustrated initial position at the bore step to the stop, so that the brake pressure via the valve seat 116 and the annular gap between the ring piston 8 and the magnetic core 127 can act on the wheel brake 3 .

Beim Lösen des Bremspedals wird der Bremsdruck in umgekehr­ ter Richtung über das offene Ventilschließglied 11 und über die Dichtmanschette 112 in Richtung des Bremsdruckgebers 5 wieder abgebaut.When the brake pedal is released, the brake pressure is reduced again in the opposite direction via the open valve closing member 11 and the sealing collar 112 in the direction of the brake pressure transmitter 5 .

Überschreitet bei geschlossenem Einlaßventil 1 während ei­ ner Bremsschlupfregelung die Druckdifferenz zwischen dem Ventileinlaß (Hauptzylinder-/Pumpendruck) und Ventilausgang (Radbremsdruck) einen durch die Druckfeder 7 eingestellten Wert, so wird der Ringkolben 8 infolge der resultierenden Druckkraft am Dichtring 124 gegen die Federkraft verschoben und kommt am Magnetkern 127 dichtend zur Anlage. Eine Druckmittelverbindung zur Radbremse 3 besteht somit aus­ schließlich über die Blende 4 des Ringkolbens 8. Öffnet das Einlaßventil 1 wieder seinen regulären Durchgang über das Ventilschließglied 11, so gelangt das von der in Betrieb befindlichen Hilfsdruckpumpe 18 nachströmende Fluid aus­ schließlich über die Blende 4 im Ringkolben 8 zur Radbremse und wird derart abgebremst, daß beim nachfolgenden wieder­ holten Schließen des Einlaßventils 1 der Druckstoß und da­ mit das Geräusch reduziert ist. Beim Unterschreiten der zur Betätigung des Ringkolbens 8 notwendigen Schaltdruckdiffe­ renz sowie beim Unterbrechen des Bremsvorgangs gelangt der Ringkolben 8 in die den Strömungsdurchlaß vergrößernde Aus­ gangsstellung zurück.Exceeds with closed inlet valve 1 during egg brake slip control, the pressure difference between the valve inlet (master cylinder / pump pressure) and valve outlet (wheel brake pressure) a value set by the compression spring 7 , the annular piston 8 is displaced as a result of the resulting pressure force on the sealing ring 124 against the spring force and comes into contact with the 127 magnetic core. A pressure medium connection to the wheel brake 3 thus finally consists of the orifice 4 of the annular piston 8 . If the inlet valve 1 opens its regular passage again via the valve closing member 11 , the fluid flowing in from the auxiliary pressure pump 18 in operation finally reaches the wheel brake via the orifice 4 in the annular piston 8 and is braked in such a way that when the inlet valve 1 is subsequently closed again the pressure surge and therefore the noise is reduced. When falling below the necessary for the actuation of the annular piston 8 Schaltdruckdiffe limit and when interrupting the braking process, the annular piston 8 comes back into the starting position increasing the flow passage.

BezugszeichenlisteReference list

1 Einlaßventil
2 Hauptdruckleitung
3 Radbremse
4 Blende
5 Bremsdruckgeber
7 Druckfeder
8 Ringkolben
9 Ventilaufnahmekörper
10 Ventilträger
11 Ventilschließglied
13 Querbohrung
21 Plattenfilter
22 Ringfilter
31 Festblende
112 Dichtmanschette
114 Zentralkörper
115 Dichtsitz
116 Ventilsitz
117 Zwischenraum
118 Durchbruch
119 Bund
120 Ausnehmung
124 Dichtring
126 Ringraum
127 Magnetkern
128 Spreizring 1 inlet valve
2 main pressure line
3 wheel brake
4 aperture
5 brake pressure sensors
7 compression spring
8 ring pistons
9 valve body
10 valve supports
11 valve closing member
13 cross hole
21 plate filters
22 ring filter
31 fixed aperture
112 sealing sleeve
114 central body
115 sealing seat
116 valve seat
117 space
118 breakthrough
119 fret
120 recess
124 sealing ring
126 annulus
127 magnetic core
128 expansion ring

Claims (7)

1. Hydraulische Bremsanlage mit Schlupfregelung, mit einem Bremsdruckgeber, der über eine Hauptdruckleitung mit we­ nigstens einer Radbremse hydraulisch in Verbindung steht, mit einer an der Radbremse angeschlossenen Rück­ laufleitung, die mit einem Druckmittelsammler in Verbindung steht, mit einer Hilfsdruckpumpe, die eine Hilfsdruckleitung aufweist und die mit dem Bremsdruckgeber hydraulisch verbunden ist, sowie mit in der Hauptdruckleitung und in der Rücklaufleitung einge­ setzten Einlaß- und Auslaßventilen, die den Druckmittel­ durchlaß in der Hauptdruckleitung und in der Rücklauf­ leitung entweder sperren oder geöffnet halten, mit einer in der Hauptdruckleitung zwischen dem Einlaßventil und der Radbremse angeordneten schaltbaren Blende, die in einer ersten Schaltstellung einen ungehinderten hydrau­ lischen Durchlaß der Hauptdruckleitung zur Radbremse herstellt und die in einer weiteren Schaltstellung den Druckmitteldurchlaß zur Radbremse begrenzt, dadurch gekennzeichnet, daß ein die schaltbare Blende (4) aufnehmender Ringkolben (8) innerhalb eines Ringraums (126) im Ventilträger (10) konzentrisch zum Ventilschließglied (11) des Einlaßventils (1) geführt ist.1.Hydraulic brake system with slip control, with a brake pressure transmitter which is hydraulically connected to at least one wheel brake via a main pressure line, with a return line connected to the wheel brake, which is connected to a pressure medium collector, with an auxiliary pressure pump which has an auxiliary pressure line and which is hydraulically connected to the brake pressure transducer, and with inlet and outlet valves inserted in the main pressure line and in the return line, which either block or hold the pressure passage in the main pressure line and in the return line, with one in the main pressure line between the Inlet valve and the wheel brake arranged switchable orifice, which produces an unimpeded hydraulic passage of the main pressure line to the wheel brake in a first switching position and which limits the pressure medium passage to the wheel brake in a further switching position, characterized in that an annular piston ( 8 ) receiving the switchable diaphragm ( 4 ) is guided concentrically to the valve closing member ( 11 ) of the inlet valve ( 1 ) within an annular space ( 126 ) in the valve carrier ( 10 ). 2. Hydraulische Bremsanlage nach Anspruch 1, dadurch ge­ kennzeichnet, daß der Ringraum (126) als Stu­ fenbohrung ausgebildet ist, die auf der einen Stirnseite vom Magnetkern (127) des Einlaßventils (1) und auf der anderen Stirnseite von einem den Ventilsitz (116) auf­ nehmenden Zentralkörper (114) begrenzt ist. 2. Hydraulic brake system according to claim 1, characterized in that the annular space ( 126 ) is designed as Stu fenbohrung on one end of the magnetic core ( 127 ) of the inlet valve ( 1 ) and on the other end of one of the valve seat ( 116 ) is limited to the receiving central body ( 114 ). 3. Hydraulische Bremsanlage nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Ringkolben (8) zwischen dem den Ventilsitz (116) aufweisenden Zentral­ körper (114) und der Wandung des Ringraums (126) geführt ist.3. Hydraulic brake system according to claim 1 or 2, characterized in that the annular piston ( 8 ) between the valve seat ( 116 ) having the central body ( 114 ) and the wall of the annular space ( 126 ) is guided. 4. Hydraulische Bremsanlage nach mindestens einem der vor­ hergehenden Ansprüche, dadurch gekennzeich­ net, daß die dem Magnetkern (127) zugewandte Stirn­ fläche des Ringkolbens (8) mit einem an der Stirnfläche des Magnetkerns (127) anlegbaren Dichtsitz (115) verse­ hen ist.4. Hydraulic braking system according to at least one of the preceding claims, characterized in that the magnetic core ( 127 ) facing the end face of the annular piston ( 8 ) with a sealing face ( 115 ) which can be placed on the end face of the magnetic core ( 127 ) is hen. 5. Hydraulische Bremsanlage nach mindestens einem der vor­ hergehenden Ansprüche, dadurch gekennzeich­ net, daß zwischen einer Stirnfläche am Zentralkörper (114) und der dem Zentralkörper (114) zugewandten Stirn­ fläche des Ringkolbens (8) ein Zwischenraum (117) zur Aufnahme eines Dichtrings (124) vorgesehen ist.5. Hydraulic brake system according to at least one of the preceding claims, characterized in that between an end face on the central body ( 114 ) and the central body ( 114 ) facing the end face of the annular piston ( 8 ) an intermediate space ( 117 ) for receiving a sealing ring ( 124 ) is provided. 6. Hydraulische Bremsanlage nach mindestens einem der vor­ hergehenden Ansprüche, dadurch gekennzeich­ net, daß der Zentralkörper (114) in Richtung seiner Symmetrieachse mit wenigstens einem Durchbruch (118) versehen ist, der eine permanente Druckmittelverbindung zwischen der aus Richtung des Bremsdruckgebers (5) kom­ menden Hauptdruckleitung (2) und dem den Dichtring (124) aufweisenden Zwischenraum (117) herstellt. 6. Hydraulic brake system according to at least one of the preceding claims, characterized in that the central body ( 114 ) is provided in the direction of its axis of symmetry with at least one opening ( 118 ), the permanent pressure medium connection between the direction of the brake pressure sensor ( 5 ) com menden main pressure line ( 2 ) and the space ( 117 ) having the sealing ring ( 124 ). 7. Hydraulische Bremsanlage nach einem der vorhergehenden Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Ringkolben (8) einen Bund (119) aufweist, der an der Bohrungsstufe des Ringraums (126) unter Abstützung einer am Magnetkern (127) angebrachten Druckfeder (7) grundpositioniert ist.7. Hydraulic brake system according to one of the preceding claims 1 to 6, characterized in that the annular piston ( 8 ) has a collar ( 119 ) on the bore step of the annular space ( 126 ) with the support of a compression spring ( 7 ) attached to the magnetic core ( 127 ) ) is in the basic position.
DE19934332820 1993-06-09 1993-09-28 Hydraulic brake system with slip control Withdrawn DE4332820A1 (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
DE19934332820 DE4332820A1 (en) 1993-06-09 1993-09-28 Hydraulic brake system with slip control
DE59408550T DE59408550D1 (en) 1993-09-28 1994-09-23 HYDRAULIC BRAKE SYSTEM WITH SLIP CONTROL
JP51010395A JP3905122B2 (en) 1993-09-28 1994-09-23 Hydraulic brake system with slip control
KR1019960700972A KR100314299B1 (en) 1993-09-28 1994-09-23 Hydraulic braking system with slip control
SK273-96A SK27396A3 (en) 1993-09-28 1994-09-23 Hydraulic braking system with skid control
CZ1996592A CZ289322B6 (en) 1993-09-28 1994-09-23 Electromagnetic inlet valve
EP94928802A EP0720553B1 (en) 1993-09-28 1994-09-23 Hydraulic braking system with skid control
PCT/EP1994/003183 WO1995009098A1 (en) 1993-09-28 1994-09-23 Hydraulic braking system with skid control
US08/619,745 US5887956A (en) 1993-09-28 1994-09-23 Hydraulic brake system with slip control

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4319227A DE4319227A1 (en) 1993-06-09 1993-06-09 Hydraulic brake system with slip control
DE19934332820 DE4332820A1 (en) 1993-06-09 1993-09-28 Hydraulic brake system with slip control

Publications (1)

Publication Number Publication Date
DE4332820A1 true DE4332820A1 (en) 1995-03-30

Family

ID=25926646

Family Applications (1)

Application Number Title Priority Date Filing Date
DE19934332820 Withdrawn DE4332820A1 (en) 1993-06-09 1993-09-28 Hydraulic brake system with slip control

Country Status (1)

Country Link
DE (1) DE4332820A1 (en)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19628979A1 (en) * 1996-07-18 1998-01-22 Teves Gmbh Alfred Process for improving the control behavior of an ABS
DE19628981A1 (en) * 1996-07-18 1998-01-22 Teves Gmbh Alfred Process for improving the control behavior of an ABS
DE19628972A1 (en) * 1996-07-18 1998-01-22 Teves Gmbh Alfred Process for improving the control behavior of an ABS
DE19710175A1 (en) * 1997-03-12 1998-09-17 Itt Mfg Enterprises Inc Seat valve for slip-controlled electrohydraulic braking systems
US5929014A (en) * 1993-09-27 1999-07-27 Henkel-Ecolab Gmbh & Co. Ohg Paste-form detergent
DE19947900A1 (en) * 1999-05-11 2000-11-16 Continental Teves Ag & Co Ohg Valve assembly, especially for hydraulic braking system with wheel slip regulation, has flow cross-section between valve pin piston that is closed by electrical actuation of valve pin
DE10007349A1 (en) * 1999-08-25 2001-03-01 Continental Teves Ag & Co Ohg Continuous valve
WO2001014196A1 (en) * 1999-08-25 2001-03-01 Continental Teves Ag & Co. Ohg Proportional valve
US7341320B2 (en) 2003-05-19 2008-03-11 Hitachi, Ltd. Electromagnetically actuated valve
DE102007013984A1 (en) * 2006-10-11 2008-04-17 Continental Teves Ag & Co. Ohg Cylindrical component holding device for cylindrical housing, has fastening unit formed by inner and outer eccentric rings, where outer eccentric ring is tight-fitted at inner eccentric ring, and inner cone attached at outer cone

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DE3836112A1 (en) * 1988-10-22 1990-04-26 Teves Gmbh Alfred Control valve, especially for hydraulic brake systems with slip control
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DE4141546A1 (en) * 1991-12-17 1993-06-24 Teves Metallwaren Alfred Electromagnetic valve esp. for hydraulic anti-skid braking system - has sleeve secured tightly into stepped bore contg. funnel=shaped insert for centring needle on seating
DE4211307A1 (en) * 1992-04-04 1993-10-07 Teves Gmbh Alfred Solenoid valve, in particular for hydraulic brake systems with slip control

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US4555766A (en) * 1981-10-09 1985-11-26 General Signal Corporation Brake control system for vehicles
DE3437834A1 (en) * 1984-10-16 1986-04-17 Alfred Teves Gmbh, 6000 Frankfurt Multi-way valve, in particular a brake valve controlled by external force
FR2591678A1 (en) * 1985-10-26 1987-06-19 Teves Gmbh Alfred AUXILIARY PRESSURE SUPPLY SYSTEM FOR A HYDRAULIC BRAKING SYSTEM
DE3836112A1 (en) * 1988-10-22 1990-04-26 Teves Gmbh Alfred Control valve, especially for hydraulic brake systems with slip control
DE3934771C1 (en) * 1989-10-18 1991-03-28 Lucas Industries P.L.C., Birmingham, West Midlands, Gb
DE4010842A1 (en) * 1990-04-04 1991-10-10 Teves Gmbh Alfred Motor vehicle hydraulic braking system with slip regulation - has auxiliary pump coupled to brake fluid reservoir with pressure-equalising pump valve
DE4112920A1 (en) * 1991-04-19 1992-10-22 Teves Gmbh Alfred ELECTROMAGNETIC VALVE, ESPECIALLY FOR SLIP-CONTROLLED MOTOR VEHICLE BRAKING SYSTEMS
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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5929014A (en) * 1993-09-27 1999-07-27 Henkel-Ecolab Gmbh & Co. Ohg Paste-form detergent
US6208928B1 (en) 1996-07-18 2001-03-27 Continental Teves Ag & Co., Ohg Method of improving ABS control behavior
DE19628981A1 (en) * 1996-07-18 1998-01-22 Teves Gmbh Alfred Process for improving the control behavior of an ABS
DE19628972A1 (en) * 1996-07-18 1998-01-22 Teves Gmbh Alfred Process for improving the control behavior of an ABS
DE19628979A1 (en) * 1996-07-18 1998-01-22 Teves Gmbh Alfred Process for improving the control behavior of an ABS
DE19628979B4 (en) * 1996-07-18 2008-11-13 Continental Teves Ag & Co. Ohg Method for improving the control behavior of an ABS
US6295499B1 (en) 1996-07-18 2001-09-25 Continental Teves Ag & Co., Ohg Method of improving ABS control behavior
DE19710175A1 (en) * 1997-03-12 1998-09-17 Itt Mfg Enterprises Inc Seat valve for slip-controlled electrohydraulic braking systems
DE19947900A1 (en) * 1999-05-11 2000-11-16 Continental Teves Ag & Co Ohg Valve assembly, especially for hydraulic braking system with wheel slip regulation, has flow cross-section between valve pin piston that is closed by electrical actuation of valve pin
WO2001014196A1 (en) * 1999-08-25 2001-03-01 Continental Teves Ag & Co. Ohg Proportional valve
DE10007349A1 (en) * 1999-08-25 2001-03-01 Continental Teves Ag & Co Ohg Continuous valve
US7341320B2 (en) 2003-05-19 2008-03-11 Hitachi, Ltd. Electromagnetically actuated valve
DE102004024673B4 (en) * 2003-05-19 2012-01-12 Hitachi, Ltd. Electromagnetically actuated valve
DE102007013984A1 (en) * 2006-10-11 2008-04-17 Continental Teves Ag & Co. Ohg Cylindrical component holding device for cylindrical housing, has fastening unit formed by inner and outer eccentric rings, where outer eccentric ring is tight-fitted at inner eccentric ring, and inner cone attached at outer cone

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