DE10114299A1 - Valve for regulated slip braking system controls liquid flow between first and second fluid connection, rate of flow through valve being regulated independently of its direction - Google Patents
Valve for regulated slip braking system controls liquid flow between first and second fluid connection, rate of flow through valve being regulated independently of its directionInfo
- Publication number
- DE10114299A1 DE10114299A1 DE10114299A DE10114299A DE10114299A1 DE 10114299 A1 DE10114299 A1 DE 10114299A1 DE 10114299 A DE10114299 A DE 10114299A DE 10114299 A DE10114299 A DE 10114299A DE 10114299 A1 DE10114299 A1 DE 10114299A1
- Authority
- DE
- Germany
- Prior art keywords
- valve
- pressure
- pressure medium
- seat
- medium connection
- 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- Withdrawn
Links
- 230000001105 regulatory effect Effects 0.000 title abstract 4
- 239000012530 fluid Substances 0.000 title abstract 2
- 239000007788 liquid Substances 0.000 title abstract 2
- 238000007789 sealing Methods 0.000 claims description 11
- 230000001419 dependent effect Effects 0.000 claims 1
- 230000000694 effects Effects 0.000 claims 1
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000005347 demagnetization Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000002085 persistent effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0655—Lift 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
- B60T8/363—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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
- F16K31/0665—Lift valves with valve member being at least partially ball-shaped
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Electromagnetism (AREA)
- Transportation (AREA)
- Fluid Mechanics (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
Description
Die Erfindung betrifft ein Sitzventil, insbesondere für schlupfgeregelte Bremsanlagen, nach dem Oberbegriff des Pa tentanspruchs 1.The invention relates to a seat valve, in particular for slip-controlled braking systems, according to the generic term of Pa claim 1.
Aus der DE 40 28 447 A1 ist bereits ein derartiges Sitzventil bekannt geworden. Die Durchströmung des Ventils ist auf gro ße Volumina ausgelegt, um den Volumenbedarf als auch die ge wünschten Druckaufbaugradienten in den Radbremsen einer schlupfgeregelte Bremsanlage zu erreichen. Dies hat aller dings den Nachteil, dass zwangsläufig auch bei umgekehrter Durchströmungsrichtung des Sitzventils, das heißt von den Radbremsen zurück in Richtung des Hauptzylinders ein Druck gefälle wirksam ist, das aus komfort- und regelungstechni schen Gründen unerwünscht ist.Such a seat valve is already known from DE 40 28 447 A1 known. The flow through the valve is large Large volumes designed to meet the volume requirements as well as the ge wanted pressure build-up gradient in the wheel brakes one to achieve slip-controlled braking system. Everyone has this dings the disadvantage that inevitably even with the reverse Flow direction of the seat valve, that is from the Wheel brakes back towards the master cylinder gradient is effective, which is due to comfort and control technology reasons is undesirable.
Daher ist es die Aufgabe der vorliegenden Erfindung, ein Sitzventil der angegebenen Art derart auszubilden, dass vor genannte Nachteile vermieden werden.It is therefore the object of the present invention to provide a Train seat valve of the type specified in such a way that before mentioned disadvantages are avoided.
Diese Aufgabe wird erfindungsgemäß für ein Sitzventil der gattungsbildenden Art mit den kennzeichnenden Merkmalen des Patentanspruchs 1 gelöst.This object is achieved for a seat valve generic species with the characteristic features of the Claim 1 solved.
Weitere Merkmale, Vorteile und Anwendungsmöglichkeiten der Erfindung gehen im folgenden aus der Beschreibung eines Aus führungsbeispieles nach Fig. 2 hervor. Further features, advantages and possible uses of the invention will become apparent in the following from the description of an exemplary embodiment according to FIG. 2.
Es zeigen:Show it:
Fig. 1 ein Sitzventil zum Stand der Technik, das mit einer Überdruckventilfunktion versehen ist, Fig. 1 a seat valve to the prior art, which is provided with a pressure relief valve function,
Fig. 2 eine gegenüber dem Sitzventil nach Fig. 1 verbesserte Ausführungsform mit den erfindungswesentlichen Merkmalen. FIG. 2 shows an embodiment improved over the seat valve according to FIG. 1 with the features essential to the invention.
Die Fig. 1 zeigt im Längsschnitt ein in Grundstellung strom los offenes 2/2-Wege-Sitzventil, dessen Ventilstößel 4 über den Magnetanker 11 und über einen tief im Ventilgehäuse 10 angeordneten Führungsabschnitt 12 zentriert ist. Der Magne tanker 11 ist als steifes Rohr- bzw. Hülsenteil ausgeführt, in dem der Ventilstößel 4 entgegen der Wirkung einer Über druckventilfeder 7 relativ beweglich zur Einstellhülse 13 im Magnetanker 11 angeordnet ist. Die Druckmittelkanäle zwi schen den beiden Druckmittelanschlüssen 1, 2 im Ventilgehäuse 10 sind in beiden Durchströmungsrichtungen im Querschnitt als auch bezüglich ihrer Lage auf möglichst großen Volumen durchsatz und kleinen Staudruck ausgelegt. Fig. 1 shows in longitudinal section, a current-in basic position los open 2/2-way seat valve, the valve stem 4 is centered over the armature 11 and a deep arranged in the valve housing 10, the guide portion 12. The Magne tanker 11 is designed as a rigid pipe or sleeve part in which the valve tappet 4 against the action of a pressure valve spring 7 is arranged relatively movable to the adjusting sleeve 13 in the armature 11 . The pressure medium channels between the two pressure medium connections 1 , 2 in the valve housing 10 are designed in both flow directions in cross section and in terms of their position for the largest possible volume flow and low dynamic pressure.
Dies führt unter bestimmten Betriebsbedingungen zu den be reits eingangs erwähnten Nachteilen, so dass sich bei einem entsprechend großen hydraulischen Druckgefälle zwischen den Druckmittelanschlüssen 1, 2 nach dem Abheben des Ventilstö ßels 4 vom Ventilsitz 6 eine unerwünschte Rückwirkung der Druckmittelsäule in Richtung des ersten Druckmittelanschlus ses 1 bemerkbar machen kann, und zwar unabhängig davon, ob der Ventilstößel 4 durch die Überdruckventilfunktion oder die Entmagnetisierung in die Offenstellung bewegt wird. Au ßer der unkomfortablen Rückwirkung der Druckmittelsäule kann es zu einer unerwünschten Geräuschentwicklung kommen, die es gleichfalls zu verhindern gilt.Under certain operating conditions, this leads to the disadvantages already mentioned at the outset, so that there is an undesirable reaction of the pressure medium column in the direction of the first pressure medium connection 1 in the event of a correspondingly large hydraulic pressure drop between the pressure medium connections 1 , 2 after the valve tappet 4 is lifted off the valve seat 6 can make noticeable, regardless of whether the valve tappet 4 is moved into the open position by the pressure relief valve function or the demagnetization. In addition to the uncomfortable reaction of the pressure medium column, it can lead to undesirable noise, which must also be prevented.
Diese Nachteile werden erfindungsgemäß durch das nachfolgend vorgestellte Sitzventil nach Fig. 2 vermieden, das in einer vergrößerten Darstellung in elektromagnetisch unerregter, offener Schaltstellung im Längsschnitt gezeigt ist. Der Ak tuator 5 des Sitzventils besteht im Wesentlichen aus einer am Ventilgehäuse 10 angebrachten Magnetspule 14 und einem den Ventilstößel 4 tragenden Magnetanker 11. Der Ventilstö ßel 4 ist zur Realisierung einer Überdruckventilfunktion im hülsenförmigen Magnetanker 11 axial beweglich. Eine Über druckventilfeder 7 im Magnetanker 11 hält den Ventilstößel 4 abbildungsgemäß auf Anschlag an einer im Magnetanker 11 ver pressten Einstellhülse 13, so dass das Ende des Ventilstö ßels 4 unter Wirkung einer zwischen der Einstellhülse 13 und einem Gehäusekernteil 9 eingespannten Rückstellfeder 15 in einem definierten Abstand zum Ventilsitz 6 positioniert ist, was der abbildungsgemäßen offenen Ventilgrundstellung ent spricht. Damit unterscheidet sich das Sitzventil nach Fig. 2 zunächst nicht von dem Sitzventil nach Fig. 1.These disadvantages are avoided according to the invention by the seat valve according to FIG. 2 presented below, which is shown in a longitudinal section in an enlarged view in an electromagnetically unexcited, open switching position. The actuator 5 of the seat valve essentially consists of a magnet coil 14 attached to the valve housing 10 and a magnet armature 11 carrying the valve tappet 4 . The valve tappet 4 is axially movable to realize a pressure relief valve function in the sleeve-shaped armature 11 . An over pressure valve spring 7 in the magnet armature 11 holds the valve tappet 4 as shown in the figure on a stop in a magnet sleeve 11 ver pressed adjusting sleeve 13 , so that the end of the valve tappet 4 under the action of a return spring 15 clamped between the adjusting sleeve 13 and a housing core part 9 at a defined distance is positioned to the valve seat 6 , which speaks ent the open valve basic position shown in the figure. The seat valve according to FIG. 2 does not initially differ from the seat valve according to FIG. 1.
Als wesentlicher Unterschied gegenüber dem eingangs erwähn ten Stand der Technik weist das Sitzventil nach Fig. 2 je doch einen zusätzlichen Dichtsitz 8 am rohrförmigen Gehäuse kernteil 9 auf, der in einem Axialabstand oberhalb des Ven tilsitzes 6 angeordnet ist. Der Dichtsitz 8 dient als Anla gefläche für eine hydraulisch betätigbare Schalthülse 3. Zwischen der Schalthülse 3 und dem Gehäusekernteil 9 ist ei ne Druckfeder 25 angeordnet, die in der abbildungsgemäßen Ventilgrundstellung die Schalthülse 3 in einer Stufenbohrung 16 auf Abstand vom kegelförmigen Dichtsitz 8 des Gehäuse kernteils 9 hält. Alle vorgenannten Teile befinden sich hierzu in koaxialer Anordnung zueinander. Der Ventilsitz 6 ist als Kegeldichtsitz in der Stirnfläche einer sich in die Stufenbohrung 16 erstreckenden Buchse 17 eingearbeitet, an deren Mantelfläche die Schalthülse 3 präzise geführt ist. Die Buchse 17 ist am Ende der Stufenbohrung 16 in das Ven tilgehäuse 10 eingestemmt und vom Hauptkanal des zweiten Druckmittelanschlusses 2 koaxial durchdrungen. Die Abdich tung der Schalthülse 3 in der Stufenbohrung 16 erfolgt mit tels eines unterhalb der Schalthülse 3 angeordneten O-Rings 18, der von unten über den koaxial in das Ventilgehäuse 10 gerichteten zweiten Druckmittelanschluss 2 beaufschlagt wird. Hierzu erstreckt sich der zweite Druckmittelanschluß 2 als Bypasskanal 26 des koaxial in das Ventilgehäuse 10 ein mündenden Hauptkanals in den von der Schalthülse 3 und von dem O-Ring 18 in der Stufenbohrung 16 abgetrennten Druck raum. Der zweite Druckmittelanschluss 2 ist in vorliegendem Beispiel über einen Plattenfilter 19 an eine Radbremse einer schlupfgeregelten Bremsanlage angeschlossen, während der er ste Druckmittelanschluss 1 mit einem Hauptbremszylinder der Bremsanlage verbunden ist, wobei der Druckmittelanschluss 1 über den abbildungsgemäßen Ringfilter 20 zu beiden Seiten des Ventilgehäuses 10 auf Höhe des Ventilsitzes 6 näherungs weise radial in die Stufenbohrung 16 einmündet. Beiderseits der Stufenbohrung 16 ist das Ventilgehäuse 10 von Bypassboh rungen 21 durchdrungen, die den ersten Druckmittelanschluss 1 differenzdruckabhängig mit dem zweiten Druckmittelan schluss 2 verbinden, wenn der Ventilsitz 6 vom Ventilstößel 4 verschlossen ist. Hierzu sind in die Bypassbohrungen 21 in Richtung des ersten Druckmittelanschlusses 1 hydraulisch sperrbare Kugelrückschlagventile 22 eingesetzt, die entweder von einem Halteblech 23 oder vom Plattenfilter 19 selbst in den Bypassbohrungen 21 fixiert sind.As a significant difference from the prior art mentioned at the outset, the seat valve according to FIG. 2 each has an additional sealing seat 8 on the tubular housing core part 9 , which is arranged at an axial distance above the Ven valve seat 6 . The sealing seat 8 serves as a contact surface for a hydraulically actuated switching sleeve 3 . Between the switching sleeve 3 and the housing core part 9 , a pressure spring 25 is arranged, which holds the switching sleeve 3 in a stepped bore 16 at a distance from the conical sealing seat 8 of the housing core part 9 in the valve basic position shown in the illustration. For this purpose, all of the aforementioned parts are in a coaxial arrangement with one another. The valve seat 6 is incorporated as a conical sealing seat in the end face of a bushing 17 extending into the stepped bore 16 , on the outer surface of which the switching sleeve 3 is guided precisely. The socket 17 is caulked at the end of the stepped bore 16 into the valve housing 10 and coaxially penetrated by the main channel of the second pressure medium connection 2 . The sealing device of the switching sleeve 3 in the stepped bore 16 is carried out by means of an O-ring 18 arranged below the switching sleeve 3 , which is acted upon from below via the second pressure medium connection 2 directed coaxially into the valve housing 10 . For this purpose, the second pressure medium connection 2 extends as a bypass channel 26 of the coaxially into the valve housing 10, a main channel opening into the pressure chamber separated from the switching sleeve 3 and from the O-ring 18 in the stepped bore 16 . The second pressure medium connection 2 is connected in the present example a plate filter 19 to a wheel brake of a slip-controlled brake system while it is 1 connected to a master brake cylinder of the brake system ste pressure medium connection, wherein the pressure medium connection 1 via the image-wise ring-shaped filter 20 on both sides of the valve housing 10 on Height of the valve seat 6 approximately radially opens into the stepped bore 16 . On both sides of the stepped bore 16 , the valve housing 10 is penetrated by bypass bores 21 which connect the first pressure medium connection 1 depending on the differential pressure to the second pressure medium connection 2 when the valve seat 6 is closed by the valve tappet 4 . For this purpose, hydraulically lockable ball check valves 22 are inserted into the bypass bores 21 in the direction of the first pressure medium connection 1 and are either fixed in the bypass bores 21 by a holding plate 23 or by the plate filter 19 itself.
Nachfolgend wird die Funktionsweise des erfindungsgemäßen Sitzventils nach Fig. 2 beschrieben. In der abbildungsgemä ßen elektromagnetisch nicht erregten, offenen Ventilschalt stellung besteht einerseits eine ungehinderte hydraulische Verbindung beider Druckmittelanschlüsse 1, 2 über den offenen Dichtsitz 8 und den Ventilsitz 6, andererseits herrscht zu nächst auch eine ungehinderte hydraulische Verbindung zwi schen beiden Druckmittelanschlüssen 1, 2 über die Bypassboh rungen 21. Konstruktiv sind die Kanäle des Sitzventils auf den erforderlich hohen Volumenstrom und den entsprechend ge ringen Staudruck ausgelegt, so dass beim Einsatz des Sitz ventiles in Antriebsschlupf- als auch mit Fahrdynamikrege lung versehenen Bremsanlagen bei Bedarf der relativ hohe Vo lumenstrom für beide Radbremsen eines Bremskreises durch das abbildungsgemäße Sitzventil strömen kann. Die großzügig be messenen, drosselfreien Strömungswege ermöglichen somit ei nen möglichst raschen Bremsdruckaufbau.The mode of operation of the seat valve according to the invention according to FIG. 2 is described below. In the open valve switching position, which is not electromagnetically excited, there is on the one hand an unimpeded hydraulic connection between the two pressure medium connections 1 , 2 via the open sealing seat 8 and the valve seat 6 , and on the other hand there is also an unimpeded hydraulic connection between the two pressure medium connections 1 , 2 via the Bypass holes 21 . The ducts of the seat valve are designed for the required high volume flow and the corresponding low dynamic pressure, so that when using the seat valve in traction slip as well as with vehicle dynamics control, the relatively high volume flow for both wheel brakes of a brake circuit is required seat valve according to the illustration can flow. The generously dimensioned, throttle-free flow paths thus enable the brake pressure to build up as quickly as possible.
Sobald das Sitzventil jedoch elektromagnetisch erregt wird, legt sich der Ventilstößel 4 am Ventilsitz 6 an, so dass die Druckmittelverbindung zwischen beiden Druckmittelanschlüssen 1, 2 über die Stufenbohrung 16 unterbrochen ist und allen falls ein geringfügiges Nachströmen von Druckmittel aus Richtung des ersten Druckmittelanschlusses 1 über die Bypassbohrungen 21 zum zweiten Druckmittelanschluss 2 er folgt, bis durch den Druckanstieg im zweiten Druckmittelan schluss 2 die Kugelrückschlagventile 22 die Bypassbohrungen 21 verschließen. As soon as the poppet valve is energized electromagnetically, the valve tappet 4 rests on the valve seat 6 , so that the pressure medium connection between the two pressure medium connections 1 , 2 via the stepped bore 16 is interrupted and, if so, a slight inflow of pressure medium from the direction of the first pressure medium connection 1 via the Bypass holes 21 to the second pressure medium connection 2 it follows until the ball check valves 22 close the bypass holes 21 due to the pressure increase in the second pressure medium connection 2 .
In dem Anwendungsfall, dass der hydraulische Druck im zwei ten Druckmittelanschluss 2 noch zunimmt, was beispielsweise durch den Anschluss einer Pumpe (oder durch eine alternative Energieversorgung, z. B. Hochdruckspeicher) an dem zweiten Druckmittelanschluss 2 regelmäßig geschieht, pflanzt sich der im zweiten Druckmittelanschluss 2 anstehende Druck in die mit dem O-Ring 18 versehene Stufenbohrung 16 fort, so dass durch den Aufbau einer definierten Druckdifferenz an den Stirnflächen der Schalthülse 3 diese von der abbildungs gemäßen Anschlagstellung an der Gehäusestufe nach oben gegen den Dichtsitz 8 bewegt wird. Damit verbleibt zwischen dem Dichtsitz 8 und der Schalthülse 3 lediglich ein kleiner Blendenquerschnitt, der in vorliegendem Beispiel durch eine in die Stirnfläche der Schalthülse 3 eingearbeitete Kerbe 24 dargestellt ist.In the application that the hydraulic pressure in the second pressure medium connection 2 still increases, which happens, for example, by connecting a pump (or by an alternative energy supply, e.g. high-pressure accumulator) to the second pressure medium connection 2 , the plant in the second pressure medium connection 2 pressure present in the stepped bore 16 provided with the O-ring 18 , so that due to the build-up of a defined pressure difference on the end faces of the switching sleeve 3, this is moved upward from the stop position on the housing step according to the illustration against the sealing seat 8 . This leaves only a small diaphragm cross-section between the sealing seat 8 and the switching sleeve 3 , which in the present example is represented by a notch 24 machined into the end face of the switching sleeve 3 .
Bei einer anschließenden Unterbrechung der elektromagneti schen Erregung oder auch bei einer Ausführung der Überdruck ventilfunktion gibt der Ventilstößel 4 zwar wieder den groß zügigen Strömungsquerschnitt am Ventilsitz 6 frei, jedoch wird in Folge des Verharrungszustandes der Schalthülse 3 am Dichtsitz 8 nur ein kleiner Volumenstrom über den Blenden querschnitt in Richtung des dem kleinen Druckniveau ausge setzten ersten Druckmittelanschluss 1 abgelassen, so dass dann auch vorteilhaft bei großer Druckdifferenz zwischen den beiden Druckmittelanschlüssen 1, 2 zu Beginn der Druckredu zierung ein geräuscharmer und regelungstechnisch feinfühli ger Betrieb des Sitzventils erfolgt. Die Schalthülse 3 ge langt erst dann wieder in ihre abbildungsgemäße drosselfreie Stellung, wenn die an den Schalthülsenstirnflächen wirksamen Druckkräfte soweit ausgeglichen sind, dass die Kraft der Druckfeder 25 in der Kräftebilanz letztlich wieder über wiegt.In the event of a subsequent interruption of the electromagnetic excitation or also in the execution of the overpressure valve function, the valve tappet 4 again releases the generous flow cross-section at the valve seat 6 , but as a result of the persistent state of the switching sleeve 3 on the sealing seat 8, only a small volume flow over the orifices Cross section in the direction of the low pressure level set out first pressure medium connection 1 , so that then also advantageously with a large pressure difference between the two pressure medium connections 1 , 2 at the beginning of the pressure reduction, a low-noise and control-technically sensitive operation of the seat valve takes place. The switching sleeve 3 ge only then returns to its choke-free position, as shown, when the pressure forces acting on the switching sleeve end faces are balanced so far that the force of the compression spring 25 ultimately weighs in again in the balance of forces.
Das Sitzventil vereinigt somit die Vorteile, große Volumina rasch dem Verbraucher am zweiten Druckmittelanschluss 2 zur Verfügung zu stellen, ohne im Fall einer Druckreduzierung Einbußen hinsichtlich des Regel-, Schalt- und Geräuschver haltens hinnehmen zu müssen. Insbesondere bleibt die Über druckventilfunktion des Sitzventils von vorgenannten Maßnah men unberührt, so dass jederzeit beim Überschreiten des durch die Überdruckventilfeder 7 voreingestellten Öffnungs druck der Ventilstößel 4 aus der elektromagnetisch geschlos senen Ventilschaltstellung durch einen unzulässigen Anstieg des Systemdrucks am zweiten Druckmittelanschluss 2 vom Ven tilsitz 6 abgehoben werden kann. Die hinreichend große Druckreduzierung des Systemdrucks erfolgt sodann über die Blendenstellung der Schalthülse 3 in der bereite geschilder ten Weise. The poppet valve thus combines the advantages of quickly making large volumes available to the consumer at the second pressure medium connection 2 without having to accept losses in terms of control, switching and noise behavior in the event of a pressure reduction. In particular, the transfer remains pressure-valve function of the poppet valve of the aforementioned measures men untouched, so that upon exceeding the pre-set by the pressure relief valve spring 7 Opening the valve stem 4 out of the electromagnetically closed-end valve switching position printed by an unacceptable increase of the system pressure on the second pressure medium connection 2 tilsitz from Ven 6 lifted anytime can be. The sufficiently large pressure reduction of the system pressure then takes place via the diaphragm position of the switching sleeve 3 in the ready described manner.
11
erster Druckmittelanschluss
first pressure medium connection
22
zweiter Druckmittelanschluss
second pressure medium connection
33
Schalthülse
switching sleeve
44
Ventilstößel
tappet
55
Aktuator
actuator
66
Ventilsitz
valve seat
77
Überdruckventilfeder
Overpressure valve spring
88th
Dichtsitz
sealing seat
99
Gehäusekernteil
Housing core part
1010
Ventilgehäuse
valve housing
1111
Magnetanker
armature
1212
Führungsabschnitt
guide section
1313
Einstellhülse
adjusting
1414
Magnetspule
solenoid
1515
Rückstellfeder
Return spring
1616
Stufenbohrung
stepped bore
1717
Buchse
Rifle
1818
O-Ring
O-ring
1919
Plattenfilter
plate filters
2020
Ringfilter
ring filter
2121
Bypassbohrung
bypass bore
2222
Kugelrückschlagventil
Ball check valve
2323
Halteblech
Halteblech
2424
Kerbe
score
2525
Druckfeder
compression spring
2626
Bypasskanal
bypass channel
Claims (5)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10114299A DE10114299A1 (en) | 2000-10-20 | 2001-03-23 | Valve for regulated slip braking system controls liquid flow between first and second fluid connection, rate of flow through valve being regulated independently of its direction |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10051979 | 2000-10-20 | ||
DE10114299A DE10114299A1 (en) | 2000-10-20 | 2001-03-23 | Valve for regulated slip braking system controls liquid flow between first and second fluid connection, rate of flow through valve being regulated independently of its direction |
Publications (1)
Publication Number | Publication Date |
---|---|
DE10114299A1 true DE10114299A1 (en) | 2002-05-29 |
Family
ID=7660414
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
DE10114299A Withdrawn DE10114299A1 (en) | 2000-10-20 | 2001-03-23 | Valve for regulated slip braking system controls liquid flow between first and second fluid connection, rate of flow through valve being regulated independently of its direction |
Country Status (1)
Country | Link |
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DE (1) | DE10114299A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005014100A1 (en) * | 2004-07-15 | 2006-02-02 | Continental Teves Ag & Co. Ohg | Electromagnetic valve for use in anti-slip brake system of vehicle, has coaxial valve bodies mounted one above other, magnetic anchor being attached to upper valve body which has limited degree of movement |
DE102005022693A1 (en) * | 2005-05-18 | 2006-11-23 | Hydac Fluidtechnik Gmbh | Valve, in particular proportional pressure relief valve |
Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4339305A1 (en) * | 1993-06-09 | 1995-05-24 | Teves Gmbh Alfred | Solenoid valve for hydraulic brake system with feedback control |
DE4438334A1 (en) * | 1994-10-27 | 1996-05-02 | Bosch Gmbh Robert | Solenoid valve with pressure limitation for slip-controlled motor vehicle braking systems |
DE4441150A1 (en) * | 1994-11-18 | 1996-05-23 | Teves Gmbh Alfred | Pressure control valve |
DE19504246A1 (en) * | 1995-02-09 | 1996-08-14 | Teves Gmbh Alfred | Solenoid valve with pressure limiting function, especially for hydraulic motor vehicle brake systems with slip control and / or automatic brake intervention for driving dynamics control |
DE19700405A1 (en) * | 1997-01-09 | 1998-07-16 | Teves Gmbh Alfred | Solenoid valve for vehicle ABS braking systems |
DE19711442A1 (en) * | 1997-03-19 | 1998-09-24 | Itt Mfg Enterprises Inc | Solenoid inlet valve for motor vehicle hydraulic braking system |
DE19839224A1 (en) * | 1997-08-30 | 1999-03-04 | Hyundai Motor Co Ltd | Solenoid valve for adjusting hydraulic pressure flow |
DE19849877A1 (en) * | 1998-02-28 | 1999-09-02 | Continental Teves Ag & Co Ohg | Solenoid valve |
DE19836493A1 (en) * | 1998-03-31 | 1999-10-07 | Itt Mfg Enterprises Inc | Solenoid valve |
DE19943532A1 (en) * | 1999-05-14 | 2000-11-16 | Continental Teves Ag & Co Ohg | Electromagnetic valve has valve piston and valve seat body in form of cold-drawn components that are inserted into valve housing from direction remote from magnet armature |
DE10030659A1 (en) * | 1999-07-02 | 2001-01-04 | Continental Teves Inc | Switchable solenoid valve for use in braking system with anti-lock mode has valve disc movable between positions opening and closing seat bore, pin for opening and closing other bore |
DE19955884A1 (en) * | 1999-11-20 | 2001-05-23 | Bosch Gmbh Robert | Solenoid valve with a check valve |
-
2001
- 2001-03-23 DE DE10114299A patent/DE10114299A1/en not_active Withdrawn
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4339305A1 (en) * | 1993-06-09 | 1995-05-24 | Teves Gmbh Alfred | Solenoid valve for hydraulic brake system with feedback control |
DE4438334A1 (en) * | 1994-10-27 | 1996-05-02 | Bosch Gmbh Robert | Solenoid valve with pressure limitation for slip-controlled motor vehicle braking systems |
DE4441150A1 (en) * | 1994-11-18 | 1996-05-23 | Teves Gmbh Alfred | Pressure control valve |
DE19504246A1 (en) * | 1995-02-09 | 1996-08-14 | Teves Gmbh Alfred | Solenoid valve with pressure limiting function, especially for hydraulic motor vehicle brake systems with slip control and / or automatic brake intervention for driving dynamics control |
DE19700405A1 (en) * | 1997-01-09 | 1998-07-16 | Teves Gmbh Alfred | Solenoid valve for vehicle ABS braking systems |
DE19711442A1 (en) * | 1997-03-19 | 1998-09-24 | Itt Mfg Enterprises Inc | Solenoid inlet valve for motor vehicle hydraulic braking system |
DE19839224A1 (en) * | 1997-08-30 | 1999-03-04 | Hyundai Motor Co Ltd | Solenoid valve for adjusting hydraulic pressure flow |
DE19849877A1 (en) * | 1998-02-28 | 1999-09-02 | Continental Teves Ag & Co Ohg | Solenoid valve |
DE19836493A1 (en) * | 1998-03-31 | 1999-10-07 | Itt Mfg Enterprises Inc | Solenoid valve |
DE19943532A1 (en) * | 1999-05-14 | 2000-11-16 | Continental Teves Ag & Co Ohg | Electromagnetic valve has valve piston and valve seat body in form of cold-drawn components that are inserted into valve housing from direction remote from magnet armature |
DE10030659A1 (en) * | 1999-07-02 | 2001-01-04 | Continental Teves Inc | Switchable solenoid valve for use in braking system with anti-lock mode has valve disc movable between positions opening and closing seat bore, pin for opening and closing other bore |
DE19955884A1 (en) * | 1999-11-20 | 2001-05-23 | Bosch Gmbh Robert | Solenoid valve with a check valve |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005014100A1 (en) * | 2004-07-15 | 2006-02-02 | Continental Teves Ag & Co. Ohg | Electromagnetic valve for use in anti-slip brake system of vehicle, has coaxial valve bodies mounted one above other, magnetic anchor being attached to upper valve body which has limited degree of movement |
DE102005022693A1 (en) * | 2005-05-18 | 2006-11-23 | Hydac Fluidtechnik Gmbh | Valve, in particular proportional pressure relief valve |
US8807519B2 (en) | 2005-05-18 | 2014-08-19 | Hydac Fluidtechnik Gmbh | Valve in particular a proportional pressure relief valve |
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Legal Events
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OM8 | Search report available as to paragraph 43 lit. 1 sentence 1 patent law | ||
8130 | Withdrawal |