WO2007014827A1 - Hydraulic valve - Google Patents

Hydraulic valve Download PDF

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Publication number
WO2007014827A1
WO2007014827A1 PCT/EP2006/064081 EP2006064081W WO2007014827A1 WO 2007014827 A1 WO2007014827 A1 WO 2007014827A1 EP 2006064081 W EP2006064081 W EP 2006064081W WO 2007014827 A1 WO2007014827 A1 WO 2007014827A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
armature
magnetic
housing
coil
Prior art date
Application number
PCT/EP2006/064081
Other languages
German (de)
French (fr)
Inventor
Harald Biller
Original Assignee
Continental Teves Ag & Co. Ohg
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 Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2007014827A1 publication Critical patent/WO2007014827A1/en

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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • 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
    • 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
    • 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
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0693—Pressure equilibration of the armature
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/081—Magnetic constructions

Definitions

  • the invention relates to a hydraulic valve according to the preamble of patent claim 1.
  • a non-ferromagnetic disc located below the magnetic coil, so that the magnetic flux via a disposed between the armature and the cylindrical valve housing section axial gap and between the armature and the valve housing existing radial gap in a desired manner to a closed magnetic circuit.
  • Figure 1 shows an embodiment of the subject invention in the form of a closed in basic position, two-stage
  • Figure 2 shows an embodiment of the subject invention in the form of a closed in the basic position, single-stage
  • Each illustrated in longitudinal section, designed as a 2/2-way valve seat hydraulic valve has a designed in cartridge design valve housing 6 which receives a actuatable by a magnetic armature 3 valve closure member 14 which is concentrically directed to a valve seat 8 in the valve housing 6.
  • a magnetic coil 1 is integrated directly in the valve housing 6, which is arranged in a magnetic flux conducting portion 5 of the valve housing 6 and fixedly connected to this section 5.
  • a variably adjustable by the armature stroke axial gap 2 is provided, which is bridged as well as provided between a lateral surface of the armature 3 and the valve housing 6 constant radial gap 4 during electromagnetic excitation of magnetic field lines.
  • the magnet coil 1 is therefore inventively designed as a plunger coil partially immersed in the pressure medium and the armature 3 as a stepped armature whose provided with a smaller diameter relative to the magnetic coil 1 center portion has a directed into a gap 20 of the magnetic coil 1 extension 21 which passes through the axial gap 2 of the end face of the valve housing 6 is spaced.
  • the extension 21 of the step armature is opposite to the extension 21 in diameter enlarged annular disc portion 22 which covers the end face of the magnetic coil 1 at an axial distance to the coil so far that the lateral surface of the annular disc portion 22 only by the radial gap 4 from the magnetically conductive portion 5 of the valve housing 6 is disconnected.
  • armature and coil design of the magnetic force loss is advantageously reduced with increasing armature stroke, so that if desired or demand with unchanged electrical energy demand relatively large armature strokes are possible.
  • valve housing 6 has a magnetic flux non-conductive further portion 7, which bears liquid-tight at the periphery of the magnetic portion 5, to which the further portion 7 is formed as a cup-shaped deep-drawn part, the valve seat 8 and two pressure medium channels 9, 10 receives in the lower region ,
  • Both sections 5, 7 of the valve housing 6 are designed as firmly connected to each other cartridge-shaped housing halves, in which advantageously the magnetic coil 1 according to the principle of a plunger space-optimized and integrated low resistance with respect to the magnetic field.
  • the solenoid coil 1 is therefore exposed via the pressure medium channels 9, 10 of the in the valve housing 6 under pressure as well as outflowing liquid.
  • the fixed by means of a self-caulking in the valve block 11, to the atmosphere as Einpressstopfen sealing portion 5 of the valve housing 6 is designed thick-walled for use in Hochdruckhydrauliksystemen and has for partially receiving the solenoid 1 adapted to the magnetic coil recess in which the magnetic coil 1 recorded accurately and securely fastened.
  • the protruding from the section 5 part of the magnetic coil 1 is of the fluid flowing through the valve housing 6 is applied directly, provided that a corresponding pressure supply into the valve housing 6 takes place.
  • the magnet armature 3 thus immersed liquid-flushed in sections in the magnetic coil 1 a.
  • valve housing 6 inserted in the form of a cartridge in the valve block 11 thus consists only of two cartridge halves, wherein the upper half of the housing is formed by the recess provided with the plug-shaped portion 5 and the lower half of the housing through the cup-shaped portion 7 which carries the valve seat 8.
  • a sealing washer 15 is inserted, which advantageously the liquid-tight from the magnetic coil 1 protruding electrical contact 23 in the direction of the passage opening 13 in the valve housing 6 surrounds.
  • the coil turns and connected to the coil turns contact 23 of the magnetic coil 1 are on all sides liquid-tight enclosed by a pressure-resistant housing, which forms the coil carrier.
  • the magnetic coil 1 is either fixed in the recess of the section 5 or fixed non-positively or positively via a pressure-resistant plastic sheath of the contact 23 in the through hole 13 of the valve housing 6.
  • the recess 24 having portion 5 is formed as a cold impact part, the contour of which can be produced automatically by cold striking a magnetic flux conducting blank from which in a single operation advantageously the outside as well which is formed for receiving the magnetic coil 1 required inner contour.
  • the magnet armature 3 can also be produced in a simplified manner by extrusion or cold striking.
  • the hydraulic valves depicted in FIGS. 1 and 2 have a filter element 31 arranged on the pot-shaped section 7, which is embodied as a ring filter element and prevents dirt from entering the generally calibrated pressure medium channel 9.
  • the magnetic core is formed for each closed in the basic position hydraulic valves by the region of the directed into the magnetic coil 1 section 5, in the center of the direction of the axial gap 2, a blind bore 16 opens, which receives a compression spring 17, which between the end face of the armature. 3 and the end of the blind bore 16 is clamped, whereby in the valve base position of the Magnet armature 3 is held with the valve closing member 14 on the valve seat 8.
  • a sleeve-shaped guide member 29 is pressed into sections centrally from the bottom of the magnet armature 3, the sleeve end remote from the armature 3 is guided parallel to the valve seat body 35 pressed into the bottom of the cup-shaped section 7.
  • a plunger portion of the valve closure member 14 is also received telescopically slidably.
  • the valve closing member 14 extends with its tappet portion to a bore stage in the stepped bore 28, wherein the spring 19 is clamped between a collar 32 on the tappet portion and a stop fixed to the armature 3 stop 33, preferably a part of a fixedly connected to the armature 3 guide member 29 is. This results in a telescope-like interaction of armature and valve closure member to cover with minimal magnetic force required large armature strokes can.
  • the mentioned telescopic connection between the valve closing member 14 and the armature 3 has the advantage that at the beginning of electromagnetic excitation of the armature 3, the valve closing member 14 initially remains in the closed position on the valve seat 8 until the idle stroke (axial distance) between the collar 32 and the Driver 18 is completed as a result of the magnet armature. As soon as the driver 18 contacts the collar 32, the valve closing member 14 is lifted by its valve seat 8 and the pressure medium connection between the two pressure medium channels 9, 10 is released.
  • FIG. 1 shows a hydraulic valve designed as a two-stage valve and closed in the basic position.
  • valve closure member 14 of the plunger portion is designed as a sleeve with a throttle bore 36 which is closed by a further shock-shaped valve closure member 37 which is guided within a cap 38 which is fixed on the axial gap 2 facing end face of the armature 3 ,
  • the cap 38 is provided with a pressure equalization bore and extends between the spring coils of the compression spring 17 in the blind bore 16th
  • the further valve closing member 37 which is arranged in series with the valve closing member 14, closes in the electromagnetically non-excited magnet armature position under the action of the compression spring 17 a further valve seat 12 adjoining the throttle bore 36, which is thus a component of the sleeve-shaped valve closing member 14.
  • valve closing member 14 remains on the valve seat 8, as long as the valve closure member 14 is not hydraulically pressure balanced.
  • further valve closing member 37 acts as a pilot stage, by the Magnetankerhub positively controlled the throttle bore 36 releases pressure equalization.
  • non-energized solenoid valve position take due to the closing force of the compression spring 17 whose spring force is larger than the force of the oppositely acting spring 19, both arranged in series connection valve closure members 14, 37 their illustrated valve closing positions.
  • the push-type valve closure member 37 bears against the end wall on the inner wall of the cap 38 and presses the sleeve-shaped valve closure member 14 onto the valve seat 8.
  • the illustrated hydraulic valves are preferably used in a slip-controlled brake system, there are generally no constant hydraulic pressures in the pressure medium inlet (horizontal valve connection 39 ) and pressure medium outlet (vertical valve connection 34), wherein the pressure in the pressure medium inlet often predominates.
  • the armature 3 lays a partial stroke until the contacting of a step on the limit valve-shaped closing member 37.
  • the valve closing member 14 against the action of the spring 19 as a result of the hydraulic pressure first remains in the locked position until the meaning of Pilot stage via the throttle bore 36, a hydraulic pressure compensation takes place. Due to the hydraulic pressure compensation, the spring 19 can lift the valve closing 14 of the valve seat 8, whereby in the context of the main stage of the large passage cross-section between the valve closure member 14 and the valve seat 8 is opened.
  • the pressure fluid connection between the two valve ports 39, 41 is thus made resistant to resistance for a correspondingly large volume flow rate.
  • the advantage of the telescopic arrangement of the two valve closing members 14, 37 in the armature 3 is thus that in an electromagnetically initiated lifting movement of the armature 3 is initially covered until the armature 3 at the plunger stage of the valve closure member 37 is already a partial stroke of the armature 3, the considerably reduced to open the valve closing member 14 stroke and thus the magnetic field to be bridged axial gap 2, so that after pressure equalization via the throttle bore 36 with a relatively low magnetic force designed for a large volume flow rate valve member 14 via the driver 18 from the valve seat can be easily lifted accordingly.
  • the hydraulic valve of Figure 2 differs from the hydraulic valve of Figure 1 by the elimination of the elements of Vorordelcut, so that only necessary for the function of the main stage valve components are required, the known from Figure 1, essentially by the voltage applied in the basic position on the valve seat 8 valve closing member 14, the spring 19 and the driver 18 is formed.
  • valve closing member 14 is thus spring-loaded added in the stepped bore of the armature 3 in Figure 2. Due to the elimination of the pre-throttle stage, the valve closing member 14 in FIG. 2 has no throttle bore, so that the valve-closing member 14 has a closed Senen shaft portion which is supported by the already known from Figure 1 known spring 19 with its collar 32 in the stepped bore 28 of the magnet armature 3.
  • spring 19 and the driver 18 reference is made to FIG.
  • This further axial gap 26 is formed by a recess 24, which is arranged on the inner circumference of the magnetic section 5 and extends essentially in the shape of a groove, from the radial gap 4 spaced.
  • the recess 24 is to be understood as an example of a locally targeted cross-sectional weakening at the end portion of the section 5 (magnetic yoke). This cross-sectional weakening considerably reduces the leakage flux of the magnetic field in the transitional region between the radial gap 4 and the further axial gap 26 and thus contributes to an advantageous alignment or steering of the magnetic flux in the field line transition from the radial to the further axial gap 4, 26 during the magnetically initiated magnet armature stroke at.
  • the magnetic force effect with respect to the hydraulic valve of Figure 1 at a small axial gap 2 increases by at least 20 percent.
  • the electromagnetically initiated position of the magnet armature 3 with a small axial gap 2 can be seen from the right-hand half of the figure in FIG. In this position, the valve closing member 14 is located just before lifting from the valve seat 8 under exclusive axial magnetic force effect, since the annular disc portion 22 moves within the recess 24.
  • the left half of the picture illustrates the armature basic position in which both axial gaps 2, 26 represent a maximum in terms of magnitude.
  • the section 5 can be made in two parts as desired or required, which is shown by way of example in Figure 2, whereby the recess 24 and the housing projection 25 having lower part of the section 5 after assembly of the magnetic coil 1 in the upper part of the section. 5 can be joined easily with the top.
  • the presented hydraulic valves are preferably used in a slip-controlled vehicle brake system, for which the valve block 11 shown only in sections has a plurality of valve receiving bores 30, which are shown in several rows for receiving the illustrated two-stage valve and the illustrated normally closed and normally open hydraulic valves in the valve block 11th conceptually like the illustrated hydraulic valves. Ie can be executed. This results in a particularly compact braking device, the valve block 11 is particularly flat due to the low height of the illustrated hydraulic valves.
  • the illustrated hydraulic valves in this case fulfill the function of the suction side of a pump required for the brake pressure supply possible low resistance with a pressure medium source, preferably to be able to connect to the reservoir of a master cylinder.
  • the pump is electrically actuated for traction control or for automatic brake pressure control by means of a suitable control electronics, to which the control electronics preferably rests directly flat and thus extremely compact on the top of the hydraulic valves.

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

Abstract

The invention relates to a hydraulic valve comprising a body (6) provided with a closing element (14), which interacts with a magneto inductor (3) and is directed to a valve seat (8), and a magnet coil (1) which is used for actuating the magneto inductor (3) and is fixedly connected to the section (5) of the body (6) leading a magnetic flow. In order to reduce the valve height and the magnetic resistance, the magneto inductor (3) is embodied in the form of double-wound magneto inductor, whose central section, which has a diameter smaller than the diameter of the magnetic coil (1), comprises an extension (21) directed to the internal space (20) of the magnetic coil (1) and separated from the front surface of the body (6) by an axial gap (2). The magnetic coil (1) is placed in the valve body (6) in the form of a moving coil around which a liquid flows.

Description

Hydraulikventilhydraulic valve
Die Erfindung betrifft ein Hydraulikventil nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic valve according to the preamble of patent claim 1.
Aus der EP 1 124 714 Bl ist bereits ein derartiges Hydraulikventil bekannt geworden, dessen magnetisches Ventilgehäuse ein mit einem Magnetanker fest verbundenes Ventilschließglied aufnimmt, das auf einen Ventilsitz im Ventilgehäuse gerichtet ist. Zur Betätigung des Magnetankers ist eine Magnetspule vorgesehen, die entfernt vom Magnetanker außerhalb eines zylindrischen sowie magnetischen Kernabschnitts im Ventilgehäuse angeordnet ist.From EP 1 124 714 Bl, such a hydraulic valve has already become known, the magnetic valve housing of which accommodates a valve closing member which is fixedly connected to a magnet armature and which is directed onto a valve seat in the valve housing. For actuating the magnet armature, a magnet coil is provided, which is arranged away from the magnet armature outside of a cylindrical and magnetic core portion in the valve housing.
Zur Vermeidung eines magnetischen Kurzschlusses befindet sich unterhalb der Magnetspule eine nicht ferromagnetische Scheibe, sodass der Magnetfluss über einen zwischen dem Magnetanker und dem zylindrischen Ventilgehäuseabschnitt angeordneten Axialspalt und einem zwischen dem Magnetanker und dem Ventilgehäuse vorhandenen Radialspalt in gewünschter Weise zu einem geschlossenen Magnetkreis erfolgt.To avoid a magnetic short circuit is located below the magnetic coil, a non-ferromagnetic disc, so that the magnetic flux via a disposed between the armature and the cylindrical valve housing section axial gap and between the armature and the valve housing existing radial gap in a desired manner to a closed magnetic circuit.
Bezüglich des zum Stand der Technik zitierten Ventils ergibt sich infolge der gewählten Konstruktion ein Magnetkraftverlauf, der nur für kleine Magentankerhübe geeignet ist. Da der Magnetanker in Flach- bzw. Plattenankerbauweise ausgeführt ist, liegen der Axial- und Radialspalt sehr dicht beieinander, was wegen einem unerwünschten Streufluss für einen optimalen Verlauf der Magnetfeldlinien ungünstig ist. Daher ist es die Aufgabe der vorliegenden Erfindung, ein Hydraulikventil der angegebenen Art derart zu verbessern, dass die vorgenannten Nachteile vermieden werden.With regard to the valve cited in the prior art, as a result of the chosen design, a magnetic force profile which is suitable only for small magenta armature strokes results. Since the armature is designed in flat or plate anchor design, the axial and radial gap are very close to each other, which is unfavorable for an optimal course of the magnetic field lines due to an undesirable leakage flux. Therefore, it is the object of the present invention to improve a hydraulic valve of the specified type such that the aforementioned disadvantages are avoided.
Diese Aufgabe wird erfindungsgemäß für ein Hydraulikventil der angegebenen Art mit den kennzeichnenden Merkmalen des Patentanspruchs 1 gelöst.This object is achieved for a hydraulic valve of the type indicated with the characterizing features of claim 1.
Weitere Merkmale und Vorteile der Erfindung gehen im Folgenden aus der Beschreibung mehrerer Ausführungsbeispiele hervor.Further features and advantages of the invention will become apparent hereinafter from the description of several embodiments.
Es zeigen:Show it:
Figur 1 eine Ausführung des Erfindungsgegenstands in Form eines in Grundstellung geschlossenen, zweistufigenFigure 1 shows an embodiment of the subject invention in the form of a closed in basic position, two-stage
Hydraulikventils , Figur 2 eine Ausführung des Erfindungsgegenstands in Form eines in Grundstellung geschlossenen, einstufigenHydraulic valve, Figure 2 shows an embodiment of the subject invention in the form of a closed in the basic position, single-stage
Hydraulikventils .Hydraulic valve.
Bevor auf alle aus den Figuren 1, 2 ersichtlichen Details eingegangen wird, sollen zunächst die Gemeinsamkeiten der beiden abgebildeten Hydraulikventile und die wesentlichen Merkmale der Erfindung erläutert werden.Before discussing all the details shown in FIGS. 1, 2, the common features of the two illustrated hydraulic valves and the essential features of the invention will first be explained.
Jedes im Längsschnitt abgebildete, als 2/2-Wege-Sitzventil ausgelegte Hydraulikventil weist ein in Patronenbauweise ausgeführtes Ventilgehäuse 6 auf, welches ein von einem Magnetanker 3 betätigbares Ventilschließglied 14 aufnimmt, das konzentrisch auf einen Ventilsitz 8 im Ventilgehäuse 6 gerichtet ist.Each illustrated in longitudinal section, designed as a 2/2-way valve seat hydraulic valve has a designed in cartridge design valve housing 6 which receives a actuatable by a magnetic armature 3 valve closure member 14 which is concentrically directed to a valve seat 8 in the valve housing 6.
Um die Magnetkraftwirkung am Magnetanker 3 möglichst effektiv zu gestalten und die Bauhöhe des Hydraulikventils mög- liehst gering zu halten, ist erfindungsgemäß zur Betätigung des Magnetankers 3 eine Magnetspule 1 direkt im Ventilgehäuse 6 integriert, die in einem den Magnetfluss leitenden Abschnitt 5 des Ventilgehäuses 6 angeordnet ist und mit diesem Abschnitt 5 fest verbunden ist. Zwischen dem magnetischen Abschnitt 5 und einer Stirnfläche des Magnetankers 3 ist ein durch den Ankerhub variabel einstellbarer Axialspalt 2 vorgesehen, der ebenso wie ein zwischen einer Mantelfläche des Magnetankers 3 und dem Ventilgehäuse 6 vorgesehener konstanter Radialspalt 4 während einer elektromagnetischen Erregung von Magnetfeldlinien überbrückt wird.In order to make the magnetic force effect on the armature 3 as effective as possible and the height of the hydraulic valve possible lent to keep low, according to the invention for actuating the armature 3, a magnetic coil 1 is integrated directly in the valve housing 6, which is arranged in a magnetic flux conducting portion 5 of the valve housing 6 and fixedly connected to this section 5. Between the magnetic portion 5 and an end face of the magnet armature 3, a variably adjustable by the armature stroke axial gap 2 is provided, which is bridged as well as provided between a lateral surface of the armature 3 and the valve housing 6 constant radial gap 4 during electromagnetic excitation of magnetic field lines.
Die Magnetspule 1 ist daher erfindungsgemäß als eine vom Druckmittel teilweise umspülte Tauchspule und der Magnetanker 3 als Stufenanker ausgeführt, dessen mit kleinerem Durchmesser gegenüber der Magnetspule 1 versehene Mittenabschnitt einen in einen Zwischenraum 20 der Magnetspule 1 gerichteten Fortsatz 21 aufweist, der durch den Axialspalt 2 von der Stirnfläche des Ventilgehäuses 6 beabstandet ist.The magnet coil 1 is therefore inventively designed as a plunger coil partially immersed in the pressure medium and the armature 3 as a stepped armature whose provided with a smaller diameter relative to the magnetic coil 1 center portion has a directed into a gap 20 of the magnetic coil 1 extension 21 which passes through the axial gap 2 of the end face of the valve housing 6 is spaced.
An den Fortsatz 21 des Stufenankers schließt sich ein gegenüber dem Fortsatz 21 im Durchmesser vergrößerter Ringscheibenabschnitt 22 an, der die Stirnfläche der Magnetspule 1 in einem Axialabstand zur Spule so weit überdeckt, dass die Mantelfläche des Ringscheibenabschnitts 22 lediglich durch den Radialspalt 4 vom magnetisch leitenden Abschnitt 5 des Ventilgehäuses 6 getrennt ist.At the extension 21 of the step armature is opposite to the extension 21 in diameter enlarged annular disc portion 22 which covers the end face of the magnetic coil 1 at an axial distance to the coil so far that the lateral surface of the annular disc portion 22 only by the radial gap 4 from the magnetically conductive portion 5 of the valve housing 6 is disconnected.
Da infolge der vollständigen radialen Überdeckung der Magnetspule 1 durch den Ringscheibenabschnitt 22 der Außendurchmesser des Magnetanker 3 in Richtung des Radialspalts 4 zunimmt, vergrößert sich entsprechend die Querschnittsfläche des Magnetankers 3, während der Radialspalt 4 vorteilhaft möglichst weit nach außen verlegt ist. Durch diese Maßnahmen - A -As a result of the complete radial overlap of the magnetic coil 1 through the annular disc portion 22 of the outer diameter of the armature 3 increases in the direction of the radial gap 4, correspondingly increases the cross-sectional area of the armature 3, while the radial gap 4 is advantageously moved as far as possible to the outside. Through these measures - A -
lässt sich der durch den Radialspalt 4 verursachte magnetische Widerstand erheblich verkleinern und der magnetische Fluss über den Axialspalt 2 verstärken.can be significantly reduced by the magnetic gap caused by the radial gap 4 and increase the magnetic flux across the axial gap 2.
Durch die aus den Figuren ersichtliche Anker- und Spulengestaltung wird vorteilhaft der Magnetkraftverlust bei zunehmendem Ankerhub vermindert, sodass bei Wunsch oder Bedarf mit unverändertem elektrischen Energiebedarf verhältnismäßig große Ankerhübe möglich sind.By apparent from the figures armature and coil design of the magnetic force loss is advantageously reduced with increasing armature stroke, so that if desired or demand with unchanged electrical energy demand relatively large armature strokes are possible.
Ferner weist das Ventilgehäuse 6 einen den Magnetfluss nicht leitenden weiteren Abschnitt 7 auf, der am Umfang des magnetischen Abschnitts 5 flüssigkeitsdicht anliegt, wozu der weitere Abschnitt 7 als topfförmiges Tiefziehteil ausgebildet ist, das im unteren Bereich den Ventilsitz 8 und zwei Druckmittelkanäle 9, 10 aufnimmt.Furthermore, the valve housing 6 has a magnetic flux non-conductive further portion 7, which bears liquid-tight at the periphery of the magnetic portion 5, to which the further portion 7 is formed as a cup-shaped deep-drawn part, the valve seat 8 and two pressure medium channels 9, 10 receives in the lower region ,
Beide Abschnitte 5, 7 des Ventilgehäuses 6 sind als miteinander fest verbundene patronenförmige Gehäusehälften ausgeführt, in denen vorteilhaft die Magnetspule 1 nach dem Prinzip einer Tauchspule bauraumoptimiert und bezüglich dem Magnetfeld widerstandsarm integriert ist. Die Magnetspule 1 ist daher über die Druckmittelkanäle 9, 10 der in das Ventilgehäuse 6 unter Druck ein- als auch ausströmenden Flüssigkeit ausgesetzt .Both sections 5, 7 of the valve housing 6 are designed as firmly connected to each other cartridge-shaped housing halves, in which advantageously the magnetic coil 1 according to the principle of a plunger space-optimized and integrated low resistance with respect to the magnetic field. The solenoid coil 1 is therefore exposed via the pressure medium channels 9, 10 of the in the valve housing 6 under pressure as well as outflowing liquid.
Der mittels einer Selbstverstemmung im Ventilblock 11 befestigte, zur Atmosphäre hin als Einpressstopfen dichtende Abschnitt 5 des Ventilgehäuses 6 ist zum Einsatz in Hochdruckhydrauliksystemen dickwandig ausgeführt und weist zur teilweisen Aufnahme der Magnetspule 1 eine an die Magnetspulenkontur angepasste Ausnehmung auf, in der die Magnetspule 1 passgenau aufgenommen und sicher befestigt ist. Das aus dem Abschnitt 5 hervorstehende Teil der Magnetspule 1 ist von der das Ventilgehäuse 6 durchströmenden Flüssigkeit direkt beaufschlagt, sofern eine entsprechende Druckzufuhr in das Ventilgehäuse 6 erfolgt. Der Magnetanker 3 taucht somit flüssigkeitsumspült abschnittsweise in die Magnetspule 1 ein.The fixed by means of a self-caulking in the valve block 11, to the atmosphere as Einpressstopfen sealing portion 5 of the valve housing 6 is designed thick-walled for use in Hochdruckhydrauliksystemen and has for partially receiving the solenoid 1 adapted to the magnetic coil recess in which the magnetic coil 1 recorded accurately and securely fastened. The protruding from the section 5 part of the magnetic coil 1 is of the fluid flowing through the valve housing 6 is applied directly, provided that a corresponding pressure supply into the valve housing 6 takes place. The magnet armature 3 thus immersed liquid-flushed in sections in the magnetic coil 1 a.
Das in Form einer Patrone in den Ventilblock 11 eingesetzte Ventilgehäuse 6 besteht somit lediglich aus zwei Patronenhälften, wobei die obere Gehäusehälfte durch den mit der Ausnehmung versehene stopfenförmige Abschnitt 5 und die untere Gehäusehälfte durch den topfförmigen Abschnitt 7 gebildet ist, der den Ventilsitz 8 trägt.The valve housing 6 inserted in the form of a cartridge in the valve block 11 thus consists only of two cartridge halves, wherein the upper half of the housing is formed by the recess provided with the plug-shaped portion 5 and the lower half of the housing through the cup-shaped portion 7 which carries the valve seat 8.
Zur elektrischen Energieversorgung der Magnetspule 1 ist der die Magnetspule 1 aufnehmende Abschnitt 5 mit einer zur Atmosphäre gerichteten Durchgangsöffnung 13 versehen, durch die ein mit der Magnetspule 1 verbundener elektrischer Kontakt 23 gas- und flüssigkeitsdicht hindurchgeführt ist.For the electrical power supply of the solenoid coil 1 of the magnetic coil 1 receiving portion 5 is provided with an atmosphere-directed through hole 13 through which a connected to the magnetic coil 1 electrical contact 23 is passed gas and liquid tight.
Zwischen der Stirnfläche der Magnetspule 1 und der Stirnfläche der Ausnehmung 24 ist eine Dichtscheibe 15 eingefügt, welche vorteilhaft den aus der Magnetspule 1 hervorstehenden elektrischen Kontakt 23 flüssigkeitsdicht in Richtung der Durchgangsöffnung 13 im Ventilgehäuse 6 umschließt.Between the end face of the magnetic coil 1 and the end face of the recess 24, a sealing washer 15 is inserted, which advantageously the liquid-tight from the magnetic coil 1 protruding electrical contact 23 in the direction of the passage opening 13 in the valve housing 6 surrounds.
Die Spulenwindungen und der mit den Spulenwindungen verbundene Kontakt 23 der Magnetspule 1 sind allseitig flüssigkeitsdicht von einem druckfesten Gehäuse umschlossen, der den Spulenträger bildet. Die Magnetspule 1 ist entweder in der Ausnehmung des Abschnitts 5 fixiert oder über eine druckfeste Kunststoffummantelung des Kontakts 23 in der Durchgangsöffnung 13 des Ventilgehäuses 6 kraft- oder formschlüssig befestigt. Um für das Ventilgehäuse 6 eine möglichst kostengünstige Herstellung zu ermöglichen, ist der die Ausnehmung 24 aufweisende Abschnitt 5 als Kaltschlagteil ausgebildet, dessen Kontur sich automatengerecht durch Kaltschlagen eines den Magnetfluss leitenden Rohlings herstellen lässt, aus dem in einem einzigen Arbeitgang vorteilhaft die Außen- als auch die zur Aufnahme der Magnetspule 1 erforderliche Innenkontur geformt ist.The coil turns and connected to the coil turns contact 23 of the magnetic coil 1 are on all sides liquid-tight enclosed by a pressure-resistant housing, which forms the coil carrier. The magnetic coil 1 is either fixed in the recess of the section 5 or fixed non-positively or positively via a pressure-resistant plastic sheath of the contact 23 in the through hole 13 of the valve housing 6. In order to allow for the valve housing 6 as cost-effective production, the recess 24 having portion 5 is formed as a cold impact part, the contour of which can be produced automatically by cold striking a magnetic flux conducting blank from which in a single operation advantageously the outside as well which is formed for receiving the magnetic coil 1 required inner contour.
Ebenso lässt sich aufgrund des gewählten Aufbaus auch der Magnetanker 3 durch Fließpressen bzw. Kaltschlagen vereinfacht herstellen.Likewise, due to the chosen construction, the magnet armature 3 can also be produced in a simplified manner by extrusion or cold striking.
Die zum eingangs zitierten Stand der Technik bekannten Einzelkomponenten, wie beispielsweise der Magnetkern, die nicht ferromagnetische Ringscheibe und der die Magnetspule 1 umschließende Jochring lassen sich somit nunmehr erheblich einfacher durch Kaltschlagen eines Rohlings (Ventilgehäuse 6) herstellen und bilden eine überwiegend homogene Einheit bei reduzierter Teileanzahl.The well-known to the cited prior art individual components, such as the magnetic core, the non-ferromagnetic annular disc and the magnetic coil 1 enclosing yoke ring can thus now considerably easier by cold hammering a blank (valve housing 6) produce and form a predominantly homogeneous unit with a reduced number of parts ,
Ferner weisen die in den Figuren 1 und 2 abgebildeten Hydraulikventile ein am topfförmigen Abschnitt 7 angeordnetes Filterelement 31 auf, das als Ringfilterelement ausgeführt ist und Schmutzeintrag in den in der Regel kalibrierten Druckmittelkanal 9 verhindert.Furthermore, the hydraulic valves depicted in FIGS. 1 and 2 have a filter element 31 arranged on the pot-shaped section 7, which is embodied as a ring filter element and prevents dirt from entering the generally calibrated pressure medium channel 9.
Der Magnetkern ist für die in Grundstellung geschlossenen Hydraulikventile jeweils durch den Bereich des in die Magnetspule 1 gerichteten Abschnitts 5 gebildet, in den mittig aus der Richtung des Axialspalts 2 eine Sackbohrung 16 einmündet, die eine Druckfeder 17 aufnimmt, welche zwischen der Stirnfläche des Magnetankers 3 und dem Ende der Sackbohrung 16 eingespannt ist, wodurch in der Ventilgrundstellung der Magnetanker 3 mit dem Ventilschließglied 14 am Ventilsitz 8 gehalten wird.The magnetic core is formed for each closed in the basic position hydraulic valves by the region of the directed into the magnetic coil 1 section 5, in the center of the direction of the axial gap 2, a blind bore 16 opens, which receives a compression spring 17, which between the end face of the armature. 3 and the end of the blind bore 16 is clamped, whereby in the valve base position of the Magnet armature 3 is held with the valve closing member 14 on the valve seat 8.
Zur präzisen Zentrierung des Magnetankers 3 im Ventilgehäuse 6 ist in eine mittig den Magnetanker 3 durchdringende Stufenbohrung 28 abschnittsweise von unten ein hülsenförmiges Führungsglied 29 eingepresst, dessen vom Magnetanker 3 abgewandtes Hülsenende parallel zu dem im Boden des topfförmigen Abschnitts 7 eingepressten Ventilsitzkörper 35 geführt ist.For precise centering of the magnet armature 3 in the valve housing 6, a sleeve-shaped guide member 29 is pressed into sections centrally from the bottom of the magnet armature 3, the sleeve end remote from the armature 3 is guided parallel to the valve seat body 35 pressed into the bottom of the cup-shaped section 7.
In der Stufenbohrung 28 ist ferner ein Stößelabschnitt des Ventilschließgliedes 14 teleskopartig verschiebbar aufgenommen. Das Ventilschließglied 14 erstreckt sich mit seinem Stößelabschnitt auf eine Bohrungsstufe in der Stufenbohrung 28, wobei die Feder 19 zwischen einem Bund 32 am Stößelabschnitt und einem ortsfest am Magnetanker 3 ausgebildeten Anschlag 33 eingespannt ist, der vorzugsweise ein Bestandteil eines fest mit dem Magnetanker 3 verbundenen Führungsgliedes 29 ist. Es ergibt sich somit ein teleskopartiges Zusammenwirken von Magnetanker und Ventilschließglied, um mit möglichst geringem Magnetkraftbedarf große Ankerhübe zurücklegen zu können.In the stepped bore 28, a plunger portion of the valve closure member 14 is also received telescopically slidably. The valve closing member 14 extends with its tappet portion to a bore stage in the stepped bore 28, wherein the spring 19 is clamped between a collar 32 on the tappet portion and a stop fixed to the armature 3 stop 33, preferably a part of a fixedly connected to the armature 3 guide member 29 is. This results in a telescope-like interaction of armature and valve closure member to cover with minimal magnetic force required large armature strokes can.
Die erwähnte teleskopartige Verbindung zwischen dem Ventilschließglied 14 und dem Magnetanker 3 hat den Vorteil, dass zu Beginn einer elektromagnetischen Erregung des Magnetankers 3 das Ventilschließglied 14 zunächst in der geschlossenen Stellung am Ventilsitz 8 verharrt, bis der Leerhub (Axialabstand) zwischen dem Bund 32 und dem Mitnehmer 18 infolge des Magnetankerhubs zurückgelegt ist. Sobald der Mitnehmer 18 den Bund 32 kontaktiert, wird das Ventilschließglied 14 von seinem Ventilsitz 8 angehoben und die Druckmittelverbindung zwischen den beiden Druckmittelkanälen 9, 10 freigegeben. Auf Basis der bisher beschriebenen Merkmale, die außer der Vermeidung der zum Stand der Technik bereits beschriebenen Nachteile auch zu einer wesentlichen Vereinfachung des Ventilaufbaus führen, werden nunmehr die aus den Figuren 1 und 2 ersichtlichen weiteren vorteilhaften Einzelheiten und Unterschiede der Hydraulikventile erläutert.The mentioned telescopic connection between the valve closing member 14 and the armature 3 has the advantage that at the beginning of electromagnetic excitation of the armature 3, the valve closing member 14 initially remains in the closed position on the valve seat 8 until the idle stroke (axial distance) between the collar 32 and the Driver 18 is completed as a result of the magnet armature. As soon as the driver 18 contacts the collar 32, the valve closing member 14 is lifted by its valve seat 8 and the pressure medium connection between the two pressure medium channels 9, 10 is released. Based on the features described so far, which also lead to a significant simplification of the valve assembly in addition to avoiding the disadvantages already described in the prior art, the further advantageous details and differences of the hydraulic valves shown in FIGS. 1 and 2 will now be explained.
Die Figur 1 zeigt ein als Zweistufenventil ausgeführtes, in Grundstellung geschlossenes Hydraulikventil. Ergänzend zu den bisherigen Erläuterungen zum Ventilschließglied 14 ist der Stößelabschnitt als Hülse mit einer Drosselbohrung 36 ausgeführt, die von einem weiteren stößeiförmigen Ventilschließglied 37 verschlossen ist, das innerhalb einer Kappe 38 geführt ist, die auf der dem Axialspalt 2 zugewandten Stirnfläche des Magnetankers 3 befestigt ist.FIG. 1 shows a hydraulic valve designed as a two-stage valve and closed in the basic position. In addition to the previous explanations of the valve closure member 14 of the plunger portion is designed as a sleeve with a throttle bore 36 which is closed by a further shock-shaped valve closure member 37 which is guided within a cap 38 which is fixed on the axial gap 2 facing end face of the armature 3 ,
Die Kappe 38 ist mit einer Druckausgleichsbohrung versehen und erstreckt sich zwischen den Federwindungen der Druckfeder 17 in die Sackbohrung 16.The cap 38 is provided with a pressure equalization bore and extends between the spring coils of the compression spring 17 in the blind bore 16th
Das in Reihe zum Ventilschließglied 14 angeordnete weitere Ventilschließglied 37 verschließt in der elektromagnetisch nicht erregten Magnetankerstellung unter der Wirkung der Druckfeder 17 einen an die Drosselbohrung 36 angrenzenden weiteren Ventilsitz 12, der somit ein Bestandteil des hül- senförmigen Ventilschließgliedes 14 ist.The further valve closing member 37, which is arranged in series with the valve closing member 14, closes in the electromagnetically non-excited magnet armature position under the action of the compression spring 17 a further valve seat 12 adjoining the throttle bore 36, which is thus a component of the sleeve-shaped valve closing member 14.
Die zwischen dem Mitnehmer 18 und dem Bund 32 angeordnete Feder 19 ist derart bemessen, dass bei elektromagnetischer Erregung des Magnetankers 3 das Ventilschließglied 14 am Ventilsitz 8 verharrt, solange das Ventilschließglied 14 hydraulisch nicht druckausgeglichen ist. Um den Druckausgleich am Ventilschließglied 14 herzustellen, wirkt das weitere Ventilschließglied 37 als Vorsteuerstufe, das durch den Magnetankerhub zwangsgesteuert die Drosselbohrung 36 zum Druckausgleich freigibt.The arranged between the driver 18 and the collar 32 spring 19 is dimensioned such that upon electromagnetic excitation of the armature 3, the valve closing member 14 remains on the valve seat 8, as long as the valve closure member 14 is not hydraulically pressure balanced. In order to establish the pressure equalization on the valve closing member 14, the further valve closing member 37 acts as a pilot stage, by the Magnetankerhub positively controlled the throttle bore 36 releases pressure equalization.
Mit Blick auf die baulichen Besonderheiten des Hydraulikventils nach Figur 1 folgt hierzu eine Funktionsbeschreibung.With regard to the structural features of the hydraulic valve of Figure 1 follows a functional description.
In der abgebildeten, elektromagnetisch nicht erregten Ventilstellung nehmen infolge der Schließkraft der Druckfeder 17, deren Federkraft größer dimensioniert ist als die Kraft der entgegengesetzt wirkenden Feder 19, beide in Reihenschaltung angeordnete Ventilschließglieder 14, 37 ihre abgebildeten Ventilschließstellungen ein. Das stößeiförmige Ventilschließglied 37 liegt hierzu auf Endanschlag an der Innenwand der Kappe 38 an und drückt das hülsenförmigen Ventilschließgliedes 14 auf den Ventilsitz 8. Beim bevorzugten Einsatz der abgebildeten Hydraulikventile in einer schlupfgeregelten Bremsanlage liegen in der Regel keine konstanten hydraulischen Drücke im Druckmitteleinlass (horizontaler Ventilanschluss 39) und Druckmittelauslass (vertikaler Ven- tilanschluss 34) vor, wobei der Druck im Druckmitteleinlass häufig überwiegt.In the illustrated, non-energized solenoid valve position take due to the closing force of the compression spring 17 whose spring force is larger than the force of the oppositely acting spring 19, both arranged in series connection valve closure members 14, 37 their illustrated valve closing positions. For this purpose, the push-type valve closure member 37 bears against the end wall on the inner wall of the cap 38 and presses the sleeve-shaped valve closure member 14 onto the valve seat 8. When the illustrated hydraulic valves are preferably used in a slip-controlled brake system, there are generally no constant hydraulic pressures in the pressure medium inlet (horizontal valve connection 39 ) and pressure medium outlet (vertical valve connection 34), wherein the pressure in the pressure medium inlet often predominates.
Zu Beginn einer elektromagnetischen Erregung legt der Magnetanker 3 bis zur Kontaktierung einer Stufe am stößeiförmigen Ventilschließglied 37 einen Teilhub zurück. Infolge der Formschlussverbindung innerhalb der das stößeiförmige Ventilschließglied 37 aufnehmenden Stufenbohrung 28 nimmt der Magnetanker 3 nach der Überbrückung des Teilhubs das weitere Ventilschließglied 37 mit, während das Ventilschließglied 14 entgegen der Wirkung der Feder 19 infolge des hydraulischen Drucks zunächst in Sperrstellung verharrt, bis im Sinne der Vorsteuerstufe über die Drosselbohrung 36 ein hydraulischer Druckausgleich erfolgt. Durch den hydraulischen Druckausgleich kann die Feder 19 ein Abheben des Ventilschließglie- des 14 vom Ventilsitz 8 erzwingen, wodurch im Sinne der Hauptstufe der große Durchlassquerschnitt zwischen dem Ventilschließglied 14 und dem Ventilsitz 8 geöffnet wird. Die Druckmittelverbindung zwischen den beiden Ventilanschlüssen 39, 41 ist somit widerstandsarm für einen entsprechend großen Volumendurchsatz hergestellt.At the beginning of an electromagnetic excitation, the armature 3 lays a partial stroke until the contacting of a step on the limit valve-shaped closing member 37. As a result of the positive connection within the stoßiförmige valve closing member 37 receiving stepped bore 28 of the armature 3 takes after bridging the partial stroke with the other valve closing member 37, while the valve closing member 14 against the action of the spring 19 as a result of the hydraulic pressure first remains in the locked position until the meaning of Pilot stage via the throttle bore 36, a hydraulic pressure compensation takes place. Due to the hydraulic pressure compensation, the spring 19 can lift the valve closing 14 of the valve seat 8, whereby in the context of the main stage of the large passage cross-section between the valve closure member 14 and the valve seat 8 is opened. The pressure fluid connection between the two valve ports 39, 41 is thus made resistant to resistance for a correspondingly large volume flow rate.
Der Vorteil der teleskopischen Anordnung der beiden Ventilschließglieder 14, 37 im Magnetanker 3 besteht somit darin, dass bei einer elektromagnetisch initiierte Hubbewegung des Magnetankers 3 zunächst bis zum Anliegen des Magnetankers 3 an der Stößelstufe des Ventilschließgliedes 37 bereits ein Teilhub Xl vom Magnetanker 3 zurückgelegt ist, der den zum Öffnen des Ventilschließgliedes 14 erforderlichen Hub und damit auch den vom Magnetfeld zu überbrückende Axialspalt 2 erheblich reduziert, sodass nach dem Druckausgleich über die Drosselbohrung 36 mit einer verhältnismäßig geringen Magnetkraft das für einen großen Volumendurchsatz konzipierte Ventilschließglied 14 über den Mitnehmer 18 vom Ventilsitz 8 entsprechend leicht abgehoben werden kann.The advantage of the telescopic arrangement of the two valve closing members 14, 37 in the armature 3 is thus that in an electromagnetically initiated lifting movement of the armature 3 is initially covered until the armature 3 at the plunger stage of the valve closure member 37 is already a partial stroke of the armature 3, the considerably reduced to open the valve closing member 14 stroke and thus the magnetic field to be bridged axial gap 2, so that after pressure equalization via the throttle bore 36 with a relatively low magnetic force designed for a large volume flow rate valve member 14 via the driver 18 from the valve seat can be easily lifted accordingly.
Das Hydraulikventil nach Figur 2 unterscheidet sich vom Hydraulikventil nach Figur 1 durch den Entfall der Elemente der Vordrosselstufe, sodass lediglich die zur Funktion der Hauptstufe erforderlichen Ventilbauteile erforderlich sind, die den aus Figur 1 bekannten, im wesentlichen durch das in Grundstellung am Ventilsitz 8 anliegende Ventilschließglied 14, die Feder 19 und den Mitnehmer 18 gebildet ist.The hydraulic valve of Figure 2 differs from the hydraulic valve of Figure 1 by the elimination of the elements of Vorordelstufe, so that only necessary for the function of the main stage valve components are required, the known from Figure 1, essentially by the voltage applied in the basic position on the valve seat 8 valve closing member 14, the spring 19 and the driver 18 is formed.
Identisch zu Figur 1 ist somit auch in Figur 2 das Ventilschließglied 14 in der Stufenbohrung des Magnetankers 3 federbelastet aufgenommen. Durch den Entfall der Vordrosselstufe hat das Ventilschließglied 14 in Figur 2 keine Drosselbohrung, sodass das Ventilschließglied 14 einen geschlos- senen Schaftabschnitt aufweist, der sich durch die bereits aus Figur 1 bekannte Feder 19 mit seinem Bund 32 in der Stufenbohrung 28 des Magnetankers 3 abstützt. Bezüglich den weiteren Einzelheiten zum Aufbau und zur Wirkungsweise des Ventilschließgliedes 14, der Feder 19 und des Mitnehmers 18 wird auf Figur 1 verwiesen.Identical to Figure 1, the valve closing member 14 is thus spring-loaded added in the stepped bore of the armature 3 in Figure 2. Due to the elimination of the pre-throttle stage, the valve closing member 14 in FIG. 2 has no throttle bore, so that the valve-closing member 14 has a closed Senen shaft portion which is supported by the already known from Figure 1 known spring 19 with its collar 32 in the stepped bore 28 of the magnet armature 3. For further details on the structure and operation of the valve closure member 14, the spring 19 and the driver 18, reference is made to FIG.
Um ohne das Vorhandensein einer Vordrosselstufe im Ausführungsbeispiel nach Figur 2 das nicht druckausgeglichene Ventilschließglied 14 von seinem Ventilsitz 8 abheben zu können, ist außer dem aus Figur 1 bekannten Axial- und Radialspalt 2, 4 ein weiterer, für den Magnetfluss relevanter Axialspalt 26 vorgesehen, der zwischen dem Ringscheibenabschnitt 22 und einem unterhalb der Magnetspule 1 auf den Fortsatz 21 des Magnetankers 3 gerichteten Gehäusevorsprung 25 am Abschnitt 5 vorgesehen ist. Durch den magnetischen Gehäusevorsprung 25 ergibt sich eine zum Öffnen des Ventilschließgliedes 14 zusätzliche axiale Magnetkraftwirkung, die nach dem Überfahren des Radialspalts 4 zur Geltung kommt. Beim Überfahren des Radialspalts 4 bewegt sich der Magnetanker 3 relativ zum geschlossenen Ventilschließglied 14, bis der Mitnehmer 18 den Bund 32 des Ventilschließgliedes 14 kontaktiert. In diesem Zustand ist der Ringscheibenabschnitt 22 bereits so weit an den Gehäusevorsprung 25 angenähert, dass das Magnetfeld über den weiteren Axialspalt 26 zum Gehäusevorsprung 25 verlustarm umgelenkt wird. Infolge des sehr kleinen weiteren Axialspalts 26 ergibt sich eine hinreichend große Wirkung der Magnetkraft, um das hydraulisch nicht druckausgeglichene Ventilschließglied 14 von seinem Ventilsitz 8 abheben zu können.In order to be able to lift the non-pressure compensated valve closure member 14 from its valve seat 8 without the presence of a Vorordelstufe in the embodiment of Figure 2, except for the known from Figure 1 axial and radial gap 2, 4 another, relevant for the magnetic flux axial gap 26 is provided between the annular disc portion 22 and a directed below the magnetic coil 1 on the extension 21 of the armature 3 housing projection 25 is provided on section 5. By the magnetic housing projection 25 results in an opening of the valve closing member 14 additional axial magnetic force effect, which comes after passing over the radial gap 4 to advantage. When driving over the radial gap 4, the armature 3 moves relative to the closed valve closing member 14 until the driver 18 contacts the collar 32 of the valve closure member 14. In this state, the annular disk section 22 has already approached the housing projection 25 to such an extent that the magnetic field is diverted via the further axial gap 26 to the housing projection 25 with little loss. As a result of the very small further axial gap 26 results in a sufficiently large effect of the magnetic force in order to lift the hydraulically non-pressure compensated valve closure member 14 from its valve seat 8 can.
Dieser weitere Axialspalt 26 ist durch eine am Innenumfang des magnetischen Abschnitts 5 angeordnete, im wesentlichen nutförmig umlaufende Ausnehmung 24 vom Radialspalt 4 beabstandet. Die Ausnehmung 24 ist als Beispiel für eine örtlich gezielte Querschnittsschwächung am Endabschnitt des Abschnitts 5 (Magnetjoch) zu verstehen. Diese Querschnittsschwächung verringert den Streufluss des Magnetfeldes im Ü- bergangsbereich zwischen dem Radialspalt 4 und dem weiteren Axialspalt 26 erheblich und trägt damit während des elektromagnetisch initiierten Magnetankerhubs zu einer vorteilhaften Ausrichtung bzw. Lenkung des Magnetflusses im Feldlinienübergang vom Radial- auf den weiteren Axialspalt 4, 26 bei .This further axial gap 26 is formed by a recess 24, which is arranged on the inner circumference of the magnetic section 5 and extends essentially in the shape of a groove, from the radial gap 4 spaced. The recess 24 is to be understood as an example of a locally targeted cross-sectional weakening at the end portion of the section 5 (magnetic yoke). This cross-sectional weakening considerably reduces the leakage flux of the magnetic field in the transitional region between the radial gap 4 and the further axial gap 26 and thus contributes to an advantageous alignment or steering of the magnetic flux in the field line transition from the radial to the further axial gap 4, 26 during the magnetically initiated magnet armature stroke at.
Um mit zunehmender Annährung des Magnetankers 3 an den Gehäusevorsprung 25 den weiteren Feldlinienverlauf des Magnetfeldes über den Radialspalt 4 zu verhindern, weist der Ringscheibenabschnitt 22 auf der von der Magnetspule 1 abgewandten Seite eine umlaufende Schräge 27 (Trichterkontur) auf, wodurch sich der Radialspalt 4 mit zunehmenden Ankerhub vergrößern lässt und der Magnetfluß mit der Annährung an den Gehäusevorsprung 25 verstärkt auf den weiteren Axialspalt 26 umgelenkt wird.In order to prevent the further field line course of the magnetic field via the radial gap 4 with increasing approach of the armature 3 to the housing projection 25, the annular disc portion 22 on the side facing away from the magnetic coil 1 a circumferential bevel 27 (funnel contour), whereby the radial gap 4 with increase increasing armature stroke and the magnetic flux with the approximation to the housing projection 25 is increasingly deflected to the other axial gap 26.
Durch die voran geschilderten Maßnahmen lässt sich die Magnetkraftwirkung gegenüber dem Hydraulikventil nach Figur 1 bei kleinem Axialspalt 2 (Kontaktierung des Bunds 32 durch den Mitnehmer 18) um wenigstens 20 Prozent steigern. Die e- lektromagnetisch initiierte Stellung des Magnetankers 3 bei kleinem Axialspalt 2 ist aus der rechten Bildhälfte in Figur 2 ersichtlich. In dieser Stellung befindet sich das Ventilschließglied 14 kurz vor dem Abheben vom Ventilsitz 8 unter ausschließlicher axialer Magnetkraftwirkung, da sich der Ringscheibenabschnitt 22 innerhalb der Ausnehmung 24 bewegt. Hingegen verdeutlicht die linken Bildhälfte die Magnetankergrundstellung, in der beide Axialspalte 2, 26 vom Betrage her ein Maximum darstellen. Mit diesem Aufbau und dem damit verbundenen Magnetkreis ist es in Verbindung mit der teleskopischen Aufnahme des Ventilschließgliedes 14 im Stufenanker möglich, ohne Vorsteuerbzw. Vordrosselstufe über einen verhältnismäßig großen Arbeitshub (beispielsweise 2 Millimeter) einen großen Ventilquerschnitt zwischen dem Ventilsitz 8 und dem Ventilschließglied 14 mit einem verhältnismäßig kleinen Magnetantrieb und dem damit verbundenen geringem Energiebedarf zu öffnen.By the measures described above, the magnetic force effect with respect to the hydraulic valve of Figure 1 at a small axial gap 2 (contacting the collar 32 by the driver 18) increase by at least 20 percent. The electromagnetically initiated position of the magnet armature 3 with a small axial gap 2 can be seen from the right-hand half of the figure in FIG. In this position, the valve closing member 14 is located just before lifting from the valve seat 8 under exclusive axial magnetic force effect, since the annular disc portion 22 moves within the recess 24. On the other hand, the left half of the picture illustrates the armature basic position in which both axial gaps 2, 26 represent a maximum in terms of magnitude. With this structure and the associated magnetic circuit, it is possible in connection with the telescopic recording of the valve closure member 14 in the step armature, without Vorsteuerbzw. Vordrosslstufe over a relatively large stroke (for example, 2 millimeters) to open a large valve cross-section between the valve seat 8 and the valve closure member 14 with a relatively small magnetic drive and the associated low energy consumption.
Bezüglich der weiteren aus der Figur 2 ersichtlichen Einzelheiten und deren Funktion wird auf die Beschreibung des Hydraulikventils nach Figur 1 verwiesen.With respect to the further apparent from the figure 2 details and their function, reference is made to the description of the hydraulic valve of Figure 1.
Ergänzend zu den bisherigen Ausführungen kann der Abschnitt 5 nach Wunsch oder Bedarf zweiteilig ausgeführt sein, was beispielhaft in Figur 2 gezeigt ist, wodurch das die Ausnehmung 24 und den Gehäusevorsprung 25 aufweisende Unterteil des Abschnitts 5 nach der Montage der Magnetspule 1 im Oberteil des Abschnitts 5 sich unproblematisch mit dem Oberteil zusammenfügen lässt.In addition to the previous embodiments, the section 5 can be made in two parts as desired or required, which is shown by way of example in Figure 2, whereby the recess 24 and the housing projection 25 having lower part of the section 5 after assembly of the magnetic coil 1 in the upper part of the section. 5 can be joined easily with the top.
Wie aus den beiden Abbildungen nach Fig. 1, 2 ersichtlich ist, sind alle zitierten Bauteile rotationssymmetrisch zur Ventillängsachse ausgerichtet, wodurch eine automatengerechte Herstellung und Montage der Bauteile begünstigt wird.As can be seen from the two figures according to FIGS. 1, 2, all cited components are oriented rotationally symmetrical to the longitudinal axis of the valve, whereby a vending machine-compatible production and assembly of the components is favored.
Die vorgestellten Hydraulikventile kommen bevorzugt in einem schlupfgeregelten Kfz-Bremssystem zur Anwendung, wozu der nur abschnittsweise abgebildete Ventilblock 11 eine Vielzahl von Ventilaufnahmebohrungen 30 aufweist, die in mehreren Reihen zur Aufnahme des abgebildeten Zweistufenventils und der abgebildeten stromlos geschlossenen sowie stromlos geöffneten Hydraulikventile in den Ventilblock 11 eingelassen sind, die konzeptionell wie die abgebildeten Hydraulikventi- Ie ausgeführt werden können. Hierdurch ergibt sich ein besonders kompaktes Bremsgerät, dessen Ventilblock 11 aufgrund der geringen Bauhöhe der abgebildeten Hydraulikventile besonders flach baut. Die abgebildeten Hydraulikventile erfüllen hierbei die Funktion die Saugseite einer zur Bremsdruckversorgung erforderlichen Pumpe möglichst widerstandsarm mit einer Druckmittelquelle, vorzugsweise mit dem Nachlaufbehälter eines Hauptbremszylinders verbinden zu können. Die Pumpe wird zur Antriebschlupfregelung bzw. zur automatischen Bremsdruckregelung mittels einer geeigneten Steuerelektronik elektrisch betätigt, wozu die Steuerelektronik bevorzugt unmittelbar flach und damit äußerst kompakt auf der Oberseite der Hydraulikventile anliegt. The presented hydraulic valves are preferably used in a slip-controlled vehicle brake system, for which the valve block 11 shown only in sections has a plurality of valve receiving bores 30, which are shown in several rows for receiving the illustrated two-stage valve and the illustrated normally closed and normally open hydraulic valves in the valve block 11th conceptually like the illustrated hydraulic valves. Ie can be executed. This results in a particularly compact braking device, the valve block 11 is particularly flat due to the low height of the illustrated hydraulic valves. The illustrated hydraulic valves in this case fulfill the function of the suction side of a pump required for the brake pressure supply possible low resistance with a pressure medium source, preferably to be able to connect to the reservoir of a master cylinder. The pump is electrically actuated for traction control or for automatic brake pressure control by means of a suitable control electronics, to which the control electronics preferably rests directly flat and thus extremely compact on the top of the hydraulic valves.
BezugszeichenlisteLIST OF REFERENCE NUMBERS
1 Magnetspule1 solenoid
2 Axialspalt2 axial gap
3 Magnetanker3 magnetic armature
4 Radialspalt4 radial gap
5 Abschnitt5 section
6 Ventilgehäuse6 valve housing
7 Abschnitt7 section
8 Ventilsitz8 valve seat
9 Druckmittelkanal9 pressure medium channel
10 Druckmittelkanal10 pressure medium channel
11 Ventilblock11 valve block
12 Ventilsitz12 valve seat
13 Durchgangsöffnung13 passage opening
14 Ventilschließglied14 valve closure member
15 DichtScheibe15 sealing disc
16 Sackbohrung16 blind hole
17 Druckfeder17 compression spring
18 Mitnehmer18 drivers
19 Feder19 spring
20 Zwischenraum20 space
21 Fortsatz21 extension
22 Ringscheibenabschnitt22 ring disk section
23 Kontakt23 contact
24 Ausnehmung24 recess
25 Gehäusevorsprung25 housing projection
26 Axialspalt26 axial gap
27 Schräge27 slope
28 Stufenbohrung28 stepped bore
29 Führungsglied29 guide member
30 Ventilaufnahmebohrung30 valve receiving bore
31 Filterelement31 filter element
32 Bund Ans chlag Ventilanschluss Ventilsitzkörper Drosselbohrung Ventilschließglied Kappe Ventilanschluss 32 fret Ans chlag Valve connection Valve seat body Throttle bore Valve closure element Cap Valve connection

Claims

Patentansprüche claims
1. Hydraulikventil, insbesondere für schlupfgeregelte Bremsanlagen, mit einem vorzugsweise in Patronenbauweise ausgeführten Ventilgehäuse, welches zum Verbinden oder Trennen von Druckmittelkanälen im Ventilgehäuse ein mit einem Magnetanker zusammenwirkendes Ventilschließglied aufnimmt, das auf einen Ventilsitz im Ventilgehäuse gerichtet ist, mit einer Magnetspule zur Betätigung des Magnetankers, die mit einem den Magnet- fluss leitenden Abschnitt des Ventilgehäuses fest verbunden ist, mit einem von Magnetfeldlinien überbrückbaren, zwischen dem Ventilgehäuse und einer Stirnfläche des Magnetankers vorgesehenen Axialspalt und mit einem von Magnetfeldlinien überbrückbaren, zwischen einer Mantelfläche des Magnetankers und dem Ventilgehäuse vorgesehenen Radialspalt, dadurch gekennzeichnet, dass die Magnetspule (1) als eine vom Druckmittel umspülte Tauchspule und der Magnetanker (3) als Stufenanker ausgeführt ist, dessen mit kleinerem Durchmesser gegenüber der Magnetspule (1) versehener Mittenabschnitt einen in einen Zwischenraum (20) der Magnetspule (1) gerichteten Fortsatz (21) aufweist, der durch den Axialspalt (2) von der Stirnfläche des Ventilgehäuses (6) beabstandet ist .1. Hydraulic valve, in particular for slip-controlled brake systems, with a preferably designed in cartridge design valve housing which receives a connecting with a magnetic armature valve closure member for connecting or disconnecting pressure medium channels in the valve housing, which is directed to a valve seat in the valve housing, with a magnetic coil for actuating the armature which is fixedly connected to a magnetic flux conducting portion of the valve housing, with an axial gap bridged by magnetic field lines, provided between the valve housing and an end face of the magnet armature and with a magnetic field bridgeable, provided between a lateral surface of the armature and the valve housing radial gap, characterized in that the magnetic coil (1) is designed as a circulating from the pressure medium immersion coil and the armature (3) as a stepped armature whose smaller diameter relative to the magnetic coil (1) provided center portion in an intermediate space (20) of the magnetic coil (1) directed extension (21) which is spaced by the axial gap (2) from the end face of the valve housing (6).
2. Hydraulikventil nach Anspruch 1, dadurch gekennzeichnet, dass sich an den Fortsatz (21) des Magnetankers2. Hydraulic valve according to claim 1, characterized in that on the extension (21) of the magnet armature
(3) ein gegenüber dem Fortsatz (21) im Durchmesser vergrößerter Ringscheibenabschnitt (22) anschließt, der die Stirnfläche der Magnetspule (1) in einem Axialabstand so weit überdeckt, dass die Mantelfläche des Ringscheibenabschnitts (22) lediglich durch den Radialspalt (4) vom magnetisch leitenden Abschnitt (5) des Ventilgehäuses (6) beabstandet ist.(3) an enlarged relative to the extension (21) in diameter annular disc portion (22) adjoins the end face of the magnetic coil (1) in an axial distance so far covered that the lateral surface of the annular disc portion (22) only by the radial gap (4) from magnetically conductive portion (5) of Valve housing (6) is spaced.
3. Hydraulikventil nach Anspruch 2, dadurch gekennzeichnet:, dass zur Ausbildung eines weiteren Axialspalts3. Hydraulic valve according to claim 2, characterized in that, for the formation of a further axial gap
(26) zwischen dem Ringscheibenabschnitt (22) und der Stirnfläche der Magnetspule (1) der magnetische Abschnitt (5) des Ventilgehäuses (6) einen auf den Fortsatz (21) radial gerichteten Gehäusevorsprung (25) aufweist .(26) between the annular disc portion (22) and the end face of the magnetic coil (1), the magnetic portion (5) of the valve housing (6) on the extension (21) radially directed housing projection (25).
4. Hydraulikventil nach Anspruch 3, dadurch gekennzeichnet, dass zur Lenkung des Magnetflusses zwischen dem radialen Gehäusevorsprung (25) und dem Radialspalt (4) der Querschnitt des magnetischen Abschnitts (5) eine örtliche Schwächung aufweist, die vorzugsweise als eine am Innenumfang des magnetischen Abschnitts (5) nutför- mig umlaufende Ausnehmung (24) ausgeführt ist.4. A hydraulic valve according to claim 3, characterized in that for guiding the magnetic flux between the radial housing projection (25) and the radial gap (4), the cross section of the magnetic portion (5) has a local weakening, preferably as a on the inner circumference of the magnetic portion (5) groove-shaped circumferential recess (24) is executed.
5. Hydraulikventil nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, dass das Ventilschließglied (14) in einer mittig im Magnetanker (3) angeordneten Stufenbohrung (28) abschnittsweise aufgenommen und darin unter Wirkung einer Feder (19) axial verschiebbar angeordnet ist.5. Hydraulic valve according to one of the preceding claims, characterized in that the valve closure member (14) in a centrally in the armature (3) arranged stepped bore (28) partially received and therein under the action of a spring (19) is arranged axially displaceable.
6. Hydraulikventil nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, dass der Magnetanker (3) auf der vom Axialspalt (2) abgewandten Stirnseite ein vorzugsweise hülsenförmiges Führungsglied (29) aufweist, das den Magnetanker (3) mittig im Ventilgehäuse6. Hydraulic valve according to one of the preceding claims, characterized in that the magnet armature (3) facing away from the axial gap (2) end face a preferably sleeve-shaped guide member (29), the magnet armature (3) in the middle in the valve housing
(6) zentriert.(6) centered.
7. Hydraulikventil nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, dass sich das Ventil- schließglied (14) mit seinem Stößelabschnitt auf Anschlag in die Stufenbohrung (28) erstreckt, wobei die Feder (19) zwischen einem Bund (32) am Stößelabschnitt und einem ortsfest am Magnetanker (3) ausgebildeten Anschlag (33) eingespannt ist, der vorzugsweise ein Bestandteil des fest mit dem Magnetanker (3) verbundenen Führungsgliedes (29) ist.7. Hydraulic valve according to one of the preceding claims, characterized in that the valve closing member (14) with its plunger portion to stop in the stepped bore (28), wherein the spring (19) between a collar (32) on the plunger portion and a stationary on the armature (3) formed stop (33) is clamped, preferably a Part of the fixedly connected to the armature (3) guide member (29).
8. Hydraulikventil nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, dass sich zur Zwangsöffnung des zwischen dem Ventilsitz (8) und dem Ventilschließglied (14) gelegenen Ventildurchlasses ein Mitnehmer (18) in die Stufenbohrung (28) erstreckt, der vorzugsweise ein Bestandteil des Führungsgliedes (29) ist, an dem in der elektromagnetisch erregten Schaltstellung des Magnetankers (3) der Bund (32) anliegt. 8. Hydraulic valve according to one of the preceding claims, characterized in that for positive opening of the valve seat (8) and the valve closing member (14) located valve passage, a driver (18) in the stepped bore (28), preferably a part of the guide member (29) is, against which in the electromagnetically excited switching position of the armature (3) of the collar (32).
PCT/EP2006/064081 2005-08-04 2006-07-11 Hydraulic valve WO2007014827A1 (en)

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DE102005037341 2005-08-04
DE102005037341.0 2005-08-04
DE102006001924A DE102006001924A1 (en) 2005-08-04 2006-01-14 hydraulic valve
DE102006001924.5 2006-01-14

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WO2007082816A1 (en) * 2006-01-11 2007-07-26 Continental Teves Ag & Co. Ohg Solenoid valve
US9620274B2 (en) 2015-02-17 2017-04-11 Enfield Technologies, Llc Proportional linear solenoid apparatus

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DE102006027859B4 (en) * 2006-04-28 2015-05-21 Continental Teves Ag & Co. Ohg Solenoid valve
DE102008020101B4 (en) * 2008-04-22 2013-12-24 Staiger Gmbh & Co. Kg Valve
DE102008039421B4 (en) * 2008-08-13 2012-03-22 Rolf Prettl Solenoid valve and method for its production
DE102015105116B4 (en) 2015-04-02 2019-09-19 Eto Magnetic Gmbh Solenoid valve and safety-related pneumatic system with such a solenoid valve

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US4463332A (en) * 1983-02-23 1984-07-31 South Bend Controls, Inc. Adjustable, rectilinear motion proportional solenoid
DE19834303A1 (en) * 1998-07-30 2000-02-03 Lopic Michael Magnetic valve with magnet cage that carries housing and lid
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US4463332A (en) * 1983-02-23 1984-07-31 South Bend Controls, Inc. Adjustable, rectilinear motion proportional solenoid
DE19834303A1 (en) * 1998-07-30 2000-02-03 Lopic Michael Magnetic valve with magnet cage that carries housing and lid
EP1124714B1 (en) * 1998-10-28 2004-01-21 Robert Bosch Gmbh Electromagnetic device, especially for an anti-slip, hydraulic vehicle brake system
DE20001020U1 (en) * 2000-01-21 2001-06-07 Bosch Gmbh Robert Electromagnetically operated pressure control valve

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WO2007082816A1 (en) * 2006-01-11 2007-07-26 Continental Teves Ag & Co. Ohg Solenoid valve
US9620274B2 (en) 2015-02-17 2017-04-11 Enfield Technologies, Llc Proportional linear solenoid apparatus
US9704636B2 (en) 2015-02-17 2017-07-11 Enfield Technologies, Llc Solenoid apparatus

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