WO2007082816A1 - Soupape électromagnétique - Google Patents

Soupape électromagnétique Download PDF

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Publication number
WO2007082816A1
WO2007082816A1 PCT/EP2007/050171 EP2007050171W WO2007082816A1 WO 2007082816 A1 WO2007082816 A1 WO 2007082816A1 EP 2007050171 W EP2007050171 W EP 2007050171W WO 2007082816 A1 WO2007082816 A1 WO 2007082816A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
armature
closing member
valve closing
housing
Prior art date
Application number
PCT/EP2007/050171
Other languages
German (de)
English (en)
Inventor
Christoph Voss
Christian Courth
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 WO2007082816A1 publication Critical patent/WO2007082816A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—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

Definitions

  • the invention relates to a solenoid valve according to the preamble of patent claim 1.
  • a solenoid valve of the type specified is already known, with an externally mounted on the sleeve-shaped valve housing solenoid and a magnet armature extending between the valve spool in the valve housing to a valve housing closing magnetic core.
  • the valve housing consists of a material which does not conduct the magnetic flux, which results in a large contact resistance in the region of the magnetic disk pushed onto the valve housing for the magnetic flux.
  • the magnet armature is a rigidly mounted first valve closing member in the function of a pilot stage, which closes in the valve base position arranged in a second valve closing member valve seat.
  • the second valve closure member takes over the function of the valve main stage and is normally held by the first valve closure member to a valve seat which is arranged in the bottom of the valve housing.
  • the chosen design requires a correspondingly high electrical energy requirement for the magnetic drive in order to fully release the main valve stage, the armature over a relatively large stroke both against the action of a arranged between the armature and the magnetic core compression spring and taking into account the hydraulic see pressure differences on the magnetic core to move.
  • FIG. 1 shows an embodiment of a solenoid valve in longitudinal section in the closed, electromagnetically non-energized switching position
  • FIG. 2 shows the solenoid valve according to FIG. 1 in an electromagnetically excited switching position, which is advanced compared to FIG. 1, in which a magnet armature bears against a step of a first valve closing member after bridging an armature partial stroke;
  • FIG. 3 shows the electromagnetic valve according to FIG. 1 in an electromagnetic state which is advanced with respect to FIG. table excited switching position in which after Ü- exceeded the Ankerteilhubs the first valve closing member is lifted from its valve seat,
  • FIG. 4 shows the solenoid valve according to FIG. 1 in an electromagnetically excited switching position, which is advanced with respect to FIG. 3, in which the magnet armature rests against the magnet core and a driver mounted on the magnet armature lifts a second valve closing member from its valve seat;
  • Figure 5 shows the solenoid valve of Figure 1 in a comparison with Figure 4 advanced electromagnetically excited switching position, in which the second valve closing member occupies its maximum opening stroke after hydraulic pressure compensation under spring force.
  • valve housing 6 designed as a two-stage 2/2-way poppet valve solenoid valve has a cartridge designed in the valve housing 6, which has a received by a magnet armature 3 first and second valve closure member 24, 14.
  • Both valve closing members 14, 24 are arranged concentrically on the valve longitudinal axis, wherein the second valve closing member 14 is concentric with a valve seat 8 in the valve housing 6 and the first valve closure member 24 is directed to a provided on the second valve closure member 14 valve seat 12.
  • the invention Magnet armature 3 disc or plate-shaped and the required for the actuation of the magnet armature 3 solenoid 1 integrated directly in the valve housing 6.
  • the magnetic coil 1 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 the corresponding end face of the armature 3, a changeable by the armature stroke axial gap 2 is provided, which is bridged during an electromagnetic excitation of the magnet armature 3 only axially on and axially exiting magnetic field lines.
  • the magnetic coil 1 is designed as a partially immersed by the pressure medium plunger coil, which is immersed in electromagnetic excitation of the armature 3 in a ringnutförmige recess 31 of the armature 3.
  • 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, which in the lower part of the executed on a press-fit valve seat 8 and a few Pressure medium channels 9, 10 receives.
  • Both sections 5, 7 of the valve housing 6 are designed as mutually fixed by a press fit cartridge-shaped housing halves, in which advantageously the solenoid coil 1 as a plunger space and magnetic force optimized integrated.
  • the by means of a self-restraint in the valve block 11 completely sunk fastened, to the atmosphere as a press-fit sealing portion 5 of the valve housing 6 is designed for use in high-pressure hydraulic systems and for receiving the caulking thick-walled and has for partially receiving the magnetic coil 1 adapted to the magnetic coil contour recess in which the solenoid 1 is accurately recorded and securely attached.
  • the protruding from the section 5 in the direction of the axial gap 2 part of the solenoid coil 1 is acted upon directly by the liquid flowing through the valve housing 6, provided that a corresponding pressure supply into the valve housing 6 takes place.
  • the magnetic coil 1 is therefore designed to be pressure-resistant and thus immersed liquid-flushed sections in the recess 31 of the armature 1 a.
  • valve housing 6 thus consists only of two cartridge halves, the upper half of the housing is formed by the provided with the annular recess 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 the contact 23 of the magnetic coil 1 connected to the coil turns are liquid on all sides. impermeable sealed by a pressure-resistant housing (eg plastic), which forms the bobbin.
  • 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 individual components known from the cited prior art such as a magnetic core, a non-ferromagnetic annular disc and a yoke ring enclosing the magnetic coil 1, can thus be integrated much more easily in the two-part valve housing 6 as a predominantly homogeneous unit with a reduced number of parts.
  • the solenoid valve has a cup-shaped portion 7 arranged on the filter element 27, which is designed as a ring filter element and prevents dirt entering via the pressure medium channel 9 in the valve housing 6.
  • the magnetic core is defined by the area of the magnetic Coil 1 enclosing section 5 formed in the center of the direction of the axial gap 2, a blind bore 16 opens, which receives a compression spring 17 which is clamped between the end face of the armature 3 and the end of the blind bore 16, whereby in the basic valve position of the armature with the valve-closing members 14, 24 in the valve seats 8, 12 closing switch position is held.
  • both valve closing members 14, 24 are inserted in sections, wherein the second valve closing member 14 is accommodated in the region of its pipe section telescopically displaceable in the stepped bore 28.
  • the valve closing member 14 extends under the action of a spring used in the stepped bore 28 19 with its pipe section to a bore stage in the stepped bore 28, wherein the spring 19 is clamped between a collar 32 on the pipe section and a stop fixed to the armature 3 stop 33, the Preferably, a component of the fixedly connected to the armature 3 guide member 29 is. This results in a telescope-like interaction of magnetic armature and valve closure member, to be able to cover the largest possible armature stroke with the lowest possible magnetic power requirement.
  • the upper end of the pipe section on the second valve closing member 14 has the valve seat 12, which is closed by the first flap-shaped valve closure member 24.
  • the first valve closure member 24 is guided between a cap 20 and the stepped bore 28 as well as the second valve closure member 14 in the armature 3 telescopically.
  • the cap 20 is therefore fastened in the end region of the stepped bore 28 on the end face of the magnet armature 3 facing the axial gap 2.
  • the cap 20 is preferably made by deep drawing of thin sheet, provided with a pressure equalization hole and extends due to their height between the spring coils of the compression spring 17 space optimized in the blind bore 16th
  • the arranged between the sleeve-shaped driver 18 and the collar 26 spring 19 is dimensioned such that upon electromagnetic excitation of the armature 3, the valve closure member 14 remains on the valve seat 8, as long as the valve closure member 14 is not hydraulically pressure balanced.
  • the first valve closure member 24 acts as a pilot stage, the positively controlled by the Magnetankerhub the throttle bore 22 releases for pressure equalization.
  • the armature 3 is designed to be relatively movable in the region of a defined anchor stroke relative to the first valve closure member 24, wherein the magnetic coil 1 is designed as a plunger coil.
  • the magnet armature 3 is provided with a recess 31 adapted to the diameter of the magnet coil 1, into which part of the magnet coil 1 protruding inside the valve housing 6 can be immersed.
  • the recess 31 is designed as embedded in the end face of the armature 3 annular groove whose depth is selected to be greater by at least the dimension of the axial gap 2 as the supernatant of the magnetic coil 1 within the valve housing. 6
  • the magnet armature 3 is designed to be freely movable relative to the second valve closing member 14 via a defined armature stroke, to which end a driver 18 attached to the second valve closing member 14 with axial play is fastened to the magnet armature 3.
  • the driver 18 is designed as a fixed to the armature 3 sleeve through which the first valve closing member 14 extends in sections within a stepped bore 28 in the direction of the second valve closing body 8.
  • Both valve closing members 14, 24 are at least off taken in sections axially within a stepped bore 28 of the magnet armature 3, in which the driver 18 is attached.
  • a cap 20 is secured into which the first valve closing member 24 extends.
  • the driver 18 has a sleeve-shaped guide member 29 formed on the end portion which is guided centrally to the longitudinal axis of the valve housing 6, whereby the armature 3 is centered in the valve housing 6.
  • non-energized solenoid valve position of Figure 1 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, 24 their illustrated valve closing positions.
  • the push-type valve closure member 24 bears against the end wall on the inner wall of the cap 20 and presses the sleeve-shaped valve closure member 14 onto the valve seat 8.
  • the illustrated solenoid valve is preferably used in a slip-controlled brake system, there are generally no constant hydraulic pressures in the pressure medium inlet (horizon- Valve terminal 21) and pressure medium outlet (vertical valve connection 4), wherein the pressure in the pressure medium inlet generally predominates.
  • FIG. 2 shows the beginning of the electromagnetic excitation, according to which the armature 3 covers a partial lift until it contacts a step 30 provided on the first valve closing member 24. Both valve closing members 14, 24 initially remain in the closing pitch as a result of the magnetic armature partial stroke.
  • FIG. 5 shows the second valve closing member 14 after completed hydraulic pressure equalization, whereby the spring 19 forces a lifting of the valve closing member 14 from the valve seat 8, so that in the sense of the main stage of the large passage cross-section between the valve closing member 14 and the valve seat 8 is opened maximum.
  • the spring 19 moves via the second valve closing member 14, the first valve closure member 24 except for the upper stop in the cap 20th
  • the pressure fluid connection between the two valve ports 21, 4 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, 24 in the armature 3 is thus that in an electromagnetically initiated lifting movement of the armature 3 is initially covered to the concerns of the armature 3 at the plunger stage of the valve closure member 24 is already a partial lift from the armature 3, the the required to open the valve closing member 14 stroke and thus significantly reduced by the magnetic field to be bridged axial gap 2, so that after the pressure equalization through the throttle bore 22 with a relatively low magnetic force designed for a large volume flow valve closure member 14 via the driver 18 from the valve seat 8 accordingly can be easily lifted off.

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

Abstract

L'invention concerne une soupape électromagnétique avec un étage de soupape principal et un étage de soupape pilotée, ainsi qu'une bobine magnétique (1) et un noyau magnétique (3), la bobine (1) à l'intérieur du boîtier (6) de soupape étant réalisé sous forme de bobine à noyau plongeur et le noyau magnétique (3) étant réalisé sous forme de noyau plat afin de réduire la taille et la consommation énergétique, le noyau plat relevant de façon relativement mobile les éléments de fermeture (14, 24) de la soupape de l'étages de soupape principale et de l'étage de soupape pilot à l'intérieur d'une perforation d'étage (28).
PCT/EP2007/050171 2006-01-11 2007-01-09 Soupape électromagnétique WO2007082816A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102006001339.5 2006-01-11
DE102006001339 2006-01-11
DE102006013660.8 2006-03-24
DE102006013660A DE102006013660A1 (de) 2006-01-11 2006-03-24 Elektromagnetventil

Publications (1)

Publication Number Publication Date
WO2007082816A1 true WO2007082816A1 (fr) 2007-07-26

Family

ID=37891943

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/050171 WO2007082816A1 (fr) 2006-01-11 2007-01-09 Soupape électromagnétique

Country Status (2)

Country Link
DE (1) DE102006013660A1 (fr)
WO (1) WO2007082816A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007040691B4 (de) 2007-08-29 2019-02-07 Schaeffler Technologies AG & Co. KG Elektromagnetventil und Herstellungsverfahren für ein Elektromagnetventil
DE102009007675A1 (de) * 2009-02-05 2010-08-19 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Ventilbefestigung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1650574A1 (de) * 1967-11-15 1970-09-10 Teldix Gmbh Elektromagnetisch betaetigbares Miniaturventil mit Tauchankermagnetsystem
WO1997006040A1 (fr) * 1995-08-10 1997-02-20 Robert Bosch Gmbh Soupape regulable
DE19849667A1 (de) * 1998-10-28 2000-05-04 Bosch Gmbh Robert Elektromagnetische Vorrichtung, insbesondere für eine schlupfgeregelte, hydraulische Fahrzeugbremsanlage
DE10010734A1 (de) 2000-03-04 2001-09-06 Continental Teves Ag & Co Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeugbremsanlagen
WO2007014827A1 (fr) * 2005-08-04 2007-02-08 Continental Teves Ag & Co. Ohg Soupape hydraulique

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19626304A1 (de) * 1996-07-01 1998-01-08 Teves Gmbh Alfred Hydraulische Bremsanlage mit einer Vorladeeinrichtung
DE10200979A1 (de) * 2002-01-12 2003-08-07 Danfoss As Ventilanordnung zum Einsetzen in Vakuumanlagen
DE10252231A1 (de) * 2002-04-26 2003-11-06 Continental Teves Ag & Co Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeugbremsanlagen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1650574A1 (de) * 1967-11-15 1970-09-10 Teldix Gmbh Elektromagnetisch betaetigbares Miniaturventil mit Tauchankermagnetsystem
WO1997006040A1 (fr) * 1995-08-10 1997-02-20 Robert Bosch Gmbh Soupape regulable
DE19849667A1 (de) * 1998-10-28 2000-05-04 Bosch Gmbh Robert Elektromagnetische Vorrichtung, insbesondere für eine schlupfgeregelte, hydraulische Fahrzeugbremsanlage
DE10010734A1 (de) 2000-03-04 2001-09-06 Continental Teves Ag & Co Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeugbremsanlagen
WO2007014827A1 (fr) * 2005-08-04 2007-02-08 Continental Teves Ag & Co. Ohg Soupape hydraulique

Also Published As

Publication number Publication date
DE102006013660A1 (de) 2007-07-12

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