WO2017186449A1 - Soupape électromagnétique et procédé de fonctionnement - Google Patents

Soupape électromagnétique et procédé de fonctionnement Download PDF

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Publication number
WO2017186449A1
WO2017186449A1 PCT/EP2017/057595 EP2017057595W WO2017186449A1 WO 2017186449 A1 WO2017186449 A1 WO 2017186449A1 EP 2017057595 W EP2017057595 W EP 2017057595W WO 2017186449 A1 WO2017186449 A1 WO 2017186449A1
Authority
WO
WIPO (PCT)
Prior art keywords
pilot
closing body
valve
return spring
valve seat
Prior art date
Application number
PCT/EP2017/057595
Other languages
German (de)
English (en)
Inventor
Jörg BÜRSSNER
Peter Vincon
Sven Roos
Original Assignee
Eto Magnetic Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eto Magnetic Gmbh filed Critical Eto Magnetic Gmbh
Publication of WO2017186449A1 publication Critical patent/WO2017186449A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • 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
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/024—Devices for relieving the pressure on the sealing faces for lift valves using an auxiliary valve on the main valve

Definitions

  • the invention relates to a solenoid valve, more precisely a pilot switching valve, according to the preamble of claim 1, in particular in the form of a 2/3-way valve, preferably for use in a coolant circuit of a motor vehicle. Furthermore, the invention relates to a method for operating such a solenoid valve.
  • ⁇ / 3-solenoid valves in the center-centric slider design. In this case, two springs center the slide in a central position, wherein the slider is deflectable by two reluctance in both directions.
  • lever-operated slide valves are known which are pressed by a spring to a locking mechanism - by adjusting the catch, the various positions or switching positions are approached.
  • Switching valves with cascaded springs are likewise known from the prior art, for example from DE 42 364 82 A1, DE 199 08 102 C1, DE 1 0 2007 009 167 A1, DE 10 2013 217 580 A1, EP 0 595 014 A1 or DE 37 00 356 C2.
  • the disadvantage of a slide valve design is the function-related leakage in the closed position and also the sensitivity to contamination. In addition, the required high-precision and therefore cost-intensive production of the sliding pair is disadvantageous.
  • the disadvantage of the switching valves with cascaded springs as described for example in DE 10 2013 216 568 A1, is that the return springs act on each switching position to each other and thus add up the tolerances.
  • the present invention seeks to provide an improved switching valve, which is less critical to tolerance.
  • the pilot switching position (throttle position) and the closing switching position (closed valve position) should be able to be defined very precisely and with as little tolerance as possible.
  • the object is to provide a method for operating such an improved switching valve.
  • the object is achieved with the features of claim 12, i. in a generic operating method in that the adjustment of the armature from the open position into the intermediate switching position takes place exclusively against the spring force of the first return spring and / or that an adjusting movement of the armature against the spring force of both the first and the second return spring exclusively on the way of the Intermediate switching position takes place in the closed position, ie the second return spring is moved from the opening shaft position into the intermediate shaft division only along the adjustment direction, without a force being applied to the second return spring.
  • the solenoid valve according to the invention is a pilot switching valve, wherein the armature by energizing the coil means with different high (effective) coil currents between an open switch position, a closed switch position and an intermediate switch position (throttle switch position or pilot switch position) is adjustable, the armature both with a pilot-closing body as well as with a valve-closing body is operatively connected to these between a cooperating with the respective seat (valve seat or pilot valve seat) position in which the respective closing body rests against the associated seat and a position spaced from the respective seat position.
  • both the pilot-closing body and the valve-closing body are spaced apart from its valve seat, while in the closed switch position the pilot-closing body rests against its pilot valve seat and the valve-closing body against its valve seat in order to completely prevent a medium flow which can be controlled by the solenoid valve, while in the intermediate switching position located axially between the opening switching position and the closing switch position, the valve closing body is lifted off its valve seat and only the pilot closing body bears against its pilot valve seat and thereby keeps a throttle opening open, in order to flow through a reduced or throttled medium volume flow in relation to the opening switch position to let.
  • the coil means In order to move the armature from the opening switching position to the intermediate switching position, the coil means must be energized via a suitable control unit with a first coil current, which is dimensioned such that the spring force of the first return spring is overcome, so that the pilot closing body is in contact with its Pilot valve seat can come, wherein the first coil current is further dimensioned so that the generated electromagnetic force is not sufficient still plant of the pilot-closing body on the pilot valve seat to overcome the spring force of the second return spring.
  • the coil means To achieve this and also to bring the valve closing body to bear against its valve seat, the coil means must be energized via the control unit with a larger second coil current, which is so dimensioned to overcome the spring force of the second return spring in addition to the spring force of the first return spring.
  • the first spring force of the first return spring and the second spring force of the second return spring in the opening switch position and / or the intermediate switch position of the armature are matched to one another such that the first spring force is smaller than the second spring force.
  • the specification or setting of the first and second spring force in the opening switching position can be selected by selecting appropriate spring constants, wherein preferably the spring constant of the second return spring is larger, in particular significantly greater than the spring constant of the first return spring - additionally or alternatively, the different spring force be adjusted by appropriate choice of the spring preloads (springs with the same or different spring constant).
  • the second return spring the valve closing body axially in the direction of adjustment of the armature when energized the coil means is spring-loaded in the direction of its valve seat and is further arranged so that the spring force of the second return spring does not counteract an adjusting movement of the armature from the opening switching position to the intermediate switching position, so that the armature from the opening switching position until reaching the intermediate switching position exclusively against the spring force of Return spring (ie not additionally against the spring force of the second return spring) is adjustable.
  • the second return spring is arranged such that it is compressible only after installation of the pilot-closing body on the pilot valve seat and a corresponding application of force by the armature or an energization of the coil means with the second coil current.
  • the power is transmitted from the armature to the pilot-closing body on the way from the opening switching position to the intermediate switching position not via the second return spring, but exclusively via the first return spring.
  • the second return spring is thus displaced axially in the compression of the first return spring only between the open switch position and the intermediate switch position without resulting force application, ie the axially spaced abutment or support elements (for example, a bump-side abutment and the pilot closing body), in which the second Restored spring, are not subjected to force on this adjustment against each other.
  • This overcomes the disadvantage of the prior art that the springs do not interact with each other permanently, but only from the intermediate switching position into the closed switching position, so that tolerances do not add up to reaching the intermediate switching position in contrast to the prior art.
  • a lower tolerance dependence in the intermediate switching position (throttle position) is achieved than in the prior art.
  • a separate adjustment of the spring engagement points is possible, both geometrically and by the choice of a corresponding Vorstellkraft.
  • the throttle rate or throttle position (intermediate switching position) is defined as a whole comparatively tolerance-free.
  • the closed switching position is defined by interaction between the valve closing body and the associated valve closing body and the associated valve seat (stop).
  • first and the second return spring are axially spaced and are most preferably located on two spaced apart sides of the core, which in turn is preferably penetrated by a later to be explained plunger.
  • the first return spring is supported with an axial end directly or indirectly on the armature and with the opposite or remote from the further axial end directly or indirectly on the core, is thus sandwiched between armature and core, so that the first return spring in an adjustment the armature between opening switch position and intermediate switch position and between the intermediate switch position and the closed switch position is compressed.
  • both the valve closing body and the pilot closing body, in particular at the end, are arranged on an elongate plunger extending along the adjustment axis of the armature.
  • the ram and the armature are separate from one another but fixed to one another, for example, by screwing, welding or pressing.
  • the disturbance ßel at least in sections of the anchor itself that is monolithically formed with this.
  • the plunger is arranged such that it axially passes through the first return spring and / or the second return spring and / or the core preferably arranged between the return springs.
  • the second return spring together with the plunger is axially adjustable, in particular such that these only after reaching the intermediate switching position (starting from the opening switching position) by pressing the pilot-closing body against the pilot valve seat due to the corresponding energization of the coil means with the second (higher) coil current is compressible.
  • an abutment is formed or fixed on the plunger on which the second return spring is axially supported with an end remote from the pilot closing body.
  • the second return spring is supported with the axial end oriented in the direction of the pilot closing body indirectly or directly on the pilot closing body, in particular in such a way that the second return spring is compressed after contact of the pilot lock body with the pilot valve seat and an axial further movement of the armature and the plunger, since Distance between the valve closing body and the relative to the plunger fixed position abutment is reduced or seen relative to the plunger, the pilot-closing body is displaced away from the armature facing away from the axial end towards the anchor.
  • the abutment is arranged in all switching positions of the armature equidistant from the valve closing body, which is preferably arranged immovable or stationary in all switching positions relative to the plunger.
  • the valve closing body forms an indirect or immediate axial stop for the pilot valve body in the opening switching position until reaching the intermediate switching position and axially from the valve closing body Komprimi- tion of the second return spring when energized with the second coil current, ie on the way of the armature of the intermediate switching position in the closed switching position lifts.
  • valve seat and the pilot valve seat are arranged radially side by side, in particular in a common axial plane or axial position.
  • valve seat and the pilot valve seat are not or alternatively only slightly offset axially.
  • the valve seat and the pilot valve seat are arranged on a common valve seat component, which in the opening switching position both from the valve closing body and the pilot closing body and in the intermediate switching position exclusively from the valve closing body axially is spaced.
  • valve closing body and the pilot closing body are preferably at least one, preferably both cup-shaped, in particular to cooperate with a pot bottom axially spaced pot opening peripheral edge with the respectively associated seat. It is particularly expedient to arrange the valve closing body radially inside the pilot closing body. It has been found to be particularly expedient here, the valve closing body axially in the opening switching position and the intermediate switching position relative to the front acting end of the pilot closing body in Return to the direction of armature, this return offset is overcome by compressing the second return spring after passing through the Zwischschalt too.
  • the pilot-closing body and the valve-closing body are arranged axially outside a housing of the solenoid valve receiving the armature, the core and the coil means, preferably magnetically conducting, which is preferably axially penetrated by the aforementioned plunger.
  • the invention also leads to a method for operating a solenoid valve according to the invention.
  • the adjustment of the armature from the open position to the intermediate position is exclusively counter to the spring force of the first return spring, which does not additionally counter to the spring force of the second return spring and / or that an adjusting movement of the armature against the spring force both the first return spring and the second return spring takes place exclusively on the way from the intermediate switch position to the closed switch position.
  • the energization of the coil unit with different effective coil currents preferably takes place via a control unit assigned to the solenoid valve in the context of a valve system.
  • the system preferably comprises a coolant circuit of an internal combustion engine, in particular of a motor vehicle, within the scope of which the method according to the invention is used or the solenoid valve according to the invention fulfills its function.
  • FIG. 2 shows the electromagnetic valve according to FIG. 1 in its intermediate switching position
  • FIG. 1 designed as a 3/2-way valve electromagnetic pilot switching valve (solenoid valve) 1 is shown.
  • This comprises an axially along an adjustment axis V by energizing coil means 2 relative to a stationary core 3 adjustable armature 4.
  • the coil means 2 comprise a Bestrombare winding 5, which is arranged on a here formed as a plastic injection molded coil support 6, which radially outside the armature surrounds.
  • the armature 4 is assigned in the specific embodiment, an armature guide tube 7, within which the armature 4 is guided in its axial adjustment movement. Within the armature 4 is a through hole 8, to provide for axial pressure balance on both opposite axial sides of the armature 4 in an adjustment concern.
  • an elongated plunger 9 is set, which passes axially through the core 3 and protrudes axially from a housing 10 which receives the coil means, the armature 4 and the core 3 and also has flow-conducting properties to close the magnetic circuit.
  • a first return spring 16 is arranged, which has a smaller spring constant in the concrete embodiment than a second return spring 17, which is axially received between one on the plunger. 9 trained and permanently stationary to this arranged abutment 18 and the pilot closing body 1 1.
  • different spring forces can be achieved in the illustrated open switch position and the intermediate switch position (compare FIG. 2) by selecting corresponding spring voltages.
  • the first spring force of the first return spring 16, which momentarily acts on the respectively supporting components is less than the second spring force of the second return spring 17.
  • the second return spring 17 is supported directly on the plunger-fixed abutment 18 and opposite to the relative to the plunger 9 displaceable pilot-closing body 1 1.
  • This in turn is supported axially directly on the ram-proof or permanently fixed to the plunger 9 arranged valve closing body 12, which is clamped between a ram ring shoulder 19 and an end-side axial lock nut 20.
  • the illustrated opening switching position of the armature 4 the one in the Drawing plane upper or facing away from the core 3 end position, a maximum Medium volume flow through an area axially between the seats 14,
  • the armature 4 is supported on the bottom of the sleeve-shaped armature guide tube 7 via an elastomeric ring seal 22, which is accommodated in a retaining groove on the end face.
  • FIGS. 2 and 3 are explained, with only differences in the switching positions being discussed in order to avoid repetitions - with regard to similarities and in particular the design of the electromagnetic valve 1, reference is made to FIG. 1 with associated description of the figures.
  • the armature 4 moves into the intermediate switching position (throttle position) shown in FIG. 2, which is defined by abutment or abutment of the pilot closing body 1 1 on the pilot valve seat 15, with the exception of a pilot opening 23 (throttle opening) to ensure a pilot volume flow in the direction of arrows 24 or the opposite directions.
  • the first return spring 16 has been (further) compressed by this adjusting movement in comparison to the opening switching position, but the second return spring 17 is not.
  • the power transmission from the armature 4 to the pilot valve seat during this adjusting movement until reaching the intermediate switching position was effected exclusively via the first return spring 16 or by compression of the first return spring
  • the armature 4 is moved further in the direction of the core 3, specifically until the valve-closing body 12 abuts against its valve seat member 14 in a sealing manner As shown in FIG. 3, this end position is not quite reached.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une soupape électromagnétique (1), en particulier une soupape à 2/3 voies, comportant des moyens bobines (2) et un induit (4) déplaçable par rapport à un noyau (3) entre différentes positions de commutation à l'encontre de l'action d'un premier ressort de rappel (16) et d'un deuxième ressort de rappel (17) par alimentation en courant électrique des moyens bobines (2), lequel induit est en liaison fonctionnelle avec un corps de fermeture pilote (11) pour coopérer avec un siège de soupape pilote (15) et en liaison fonctionnelle avec un corps de fermeture de soupape (12) pour coopérer avec un siège de soupape (14), de telle sorte que, dans une position de commutation d'ouverture, le corps de fermeture pilote (11) est espacé de son siège de soupape pilote (15) et le corps de fermeture de soupape (11) est espacé de son siège de soupape (14) et, dans une position de commutation de fermeture, le corps de fermeture pilote (11) s'appuie contre son siège de soupape pilote (15) et le corps de fermeture de soupape (12) s'appuie contre son siège de soupape (14), et de telle sorte que, dans une position de commutation pilote située axialement entre la position de commutation d'ouverture et la position de commutation de fermeture, le corps de fermeture de soupape (12) est espacé du siège de soupape (14) et le corps de fermeture pilote (11) s'appuie contre le siège de soupape pilote (15) en dégageant une ouverture pilote (23) à travers laquelle un débit volumique pilote peut s'écouler, le premier ressort de rappel (16) et le deuxième ressort de rappel (17) étant conçus et disposés, en particulier précontraints, de telle sorte que, dans la position de commutation d'ouverture et/ou la position de commutation intermédiaire, une première force du premier ressort de rappel (16) est inférieure à une deuxième force du deuxième ressort de rappel (17).
PCT/EP2017/057595 2016-04-27 2017-03-30 Soupape électromagnétique et procédé de fonctionnement WO2017186449A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016107766.6 2016-04-27
DE102016107766.6A DE102016107766A1 (de) 2016-04-27 2016-04-27 Elektromagnetventil sowie Betriebsverfahren

Publications (1)

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WO2017186449A1 true WO2017186449A1 (fr) 2017-11-02

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WO (1) WO2017186449A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113135128A (zh) * 2021-05-14 2021-07-20 东风汽车集团股份有限公司 一种含有电磁阻尼调节装置的座椅

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0595014A1 (fr) 1992-10-29 1994-05-04 Robert Bosch Gmbh Electrovanne
DE3700356C2 (de) 1987-01-08 1995-07-06 Bosch Gmbh Robert Magnetventil zur Steuerung von Flüssigkeitsmengen
JPH08121635A (ja) * 1994-10-26 1996-05-17 Nippon Abs Ltd 電磁弁
DE19826076C1 (de) * 1998-06-12 1999-08-19 Dungs Karl Gmbh & Co Doppelsicherheitsventil
DE19908102C1 (de) 1999-02-25 2000-05-04 Daimler Chrysler Ag Ventil mit variablem Ventilquerschnitt
EP1278011A2 (fr) * 2001-07-19 2003-01-22 HeaTec Thermotechnik GmbH Insert de soupape et soupape pour des appareilles à gaz
US20050166979A1 (en) * 2004-01-30 2005-08-04 Karl Dungs Gmbh & Co. Solenoid valve
DE102007009167A1 (de) 2007-02-26 2008-08-28 Robert Bosch Gmbh Mehrwegeventil
US20110168931A1 (en) * 2010-01-13 2011-07-14 Aisan Kogyo Kabushiki Kaisha Solenoid valves capable of controlling valve-opening area
US20120255639A1 (en) * 2011-04-06 2012-10-11 Denso Corporation Solenoid valve
DE102013216568A1 (de) 2013-08-21 2015-02-26 Continental Teves Ag & Co. Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeug-Bremsanlagen
DE102013217580A1 (de) 2013-09-04 2015-03-05 Continental Teves Ag & Co. Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeug-Bremsanlage

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012011051B3 (de) * 2012-06-04 2013-03-28 A. Kayser Automotive Systems Gmbh Ventil mit Vorsteuerung insbesondere für Kraftstoffdampfrückhaltesystem
DE102013220593A1 (de) * 2013-10-11 2015-04-16 Robert Bosch Gmbh Elektromagnetisch ansteuerbares Saugventil

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3700356C2 (de) 1987-01-08 1995-07-06 Bosch Gmbh Robert Magnetventil zur Steuerung von Flüssigkeitsmengen
EP0595014A1 (fr) 1992-10-29 1994-05-04 Robert Bosch Gmbh Electrovanne
DE4236482A1 (de) 1992-10-29 1994-05-05 Bosch Gmbh Robert Magnetventil
JPH08121635A (ja) * 1994-10-26 1996-05-17 Nippon Abs Ltd 電磁弁
DE19826076C1 (de) * 1998-06-12 1999-08-19 Dungs Karl Gmbh & Co Doppelsicherheitsventil
DE19908102C1 (de) 1999-02-25 2000-05-04 Daimler Chrysler Ag Ventil mit variablem Ventilquerschnitt
EP1278011A2 (fr) * 2001-07-19 2003-01-22 HeaTec Thermotechnik GmbH Insert de soupape et soupape pour des appareilles à gaz
US20050166979A1 (en) * 2004-01-30 2005-08-04 Karl Dungs Gmbh & Co. Solenoid valve
DE102007009167A1 (de) 2007-02-26 2008-08-28 Robert Bosch Gmbh Mehrwegeventil
US20110168931A1 (en) * 2010-01-13 2011-07-14 Aisan Kogyo Kabushiki Kaisha Solenoid valves capable of controlling valve-opening area
US20120255639A1 (en) * 2011-04-06 2012-10-11 Denso Corporation Solenoid valve
DE102013216568A1 (de) 2013-08-21 2015-02-26 Continental Teves Ag & Co. Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeug-Bremsanlagen
DE102013217580A1 (de) 2013-09-04 2015-03-05 Continental Teves Ag & Co. Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeug-Bremsanlage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113135128A (zh) * 2021-05-14 2021-07-20 东风汽车集团股份有限公司 一种含有电磁阻尼调节装置的座椅

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