WO2008061719A1 - Électroaimant pour l'actionnement de soupapes - Google Patents

Électroaimant pour l'actionnement de soupapes Download PDF

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Publication number
WO2008061719A1
WO2008061719A1 PCT/EP2007/010070 EP2007010070W WO2008061719A1 WO 2008061719 A1 WO2008061719 A1 WO 2008061719A1 EP 2007010070 W EP2007010070 W EP 2007010070W WO 2008061719 A1 WO2008061719 A1 WO 2008061719A1
Authority
WO
WIPO (PCT)
Prior art keywords
cone
central bore
valve
electromagnet according
electromagnet
Prior art date
Application number
PCT/EP2007/010070
Other languages
German (de)
English (en)
Inventor
Axel MÜLLER
Stefan Quast
Original Assignee
Thomas Magnete 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 Thomas Magnete Gmbh filed Critical Thomas Magnete Gmbh
Publication of WO2008061719A1 publication Critical patent/WO2008061719A1/fr

Links

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
    • F16K31/0686—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
    • 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
    • H01F7/1607—Armatures entering the winding
    • 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
    • H01F7/1607—Armatures entering the winding
    • H01F2007/163—Armatures entering the winding with axial bearing
    • 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
    • H01F2007/1661—Electromagnets or actuators with anti-stick disc

Definitions

  • the invention relates to an electromagnet for actuating valves, according to the preamble of claim 1.
  • a valve which is actuated by an electromagnet, flows through a fluid in the form of hydraulic oil, gas, air, brake fluid or other fluids or is filled with such a medium.
  • a pressure equalization is necessary, which takes place via holes or openings not only within the valve, but also takes place between the valve and the electromagnet. Therefore, both are connected via pressure equalization openings.
  • anti-sling discs are provided, which are arranged on the radial impact surface of the cone of the electromagnet by means of press fit.
  • the press fit of the anti-adhesive disc usually extends over the entire radial surface of the cone.
  • the anti-stick disc is made of a sturdy, non-magnetic material.
  • the actuator of the valve in the form of a valve spool or cone, connected to a Hubankerkolben the magnet via an actuating rod which protrudes through a central bore in the cone of the armature piston.
  • the compensation openings are designed as axially parallel bore in the cone. Due to the arrangement of the anti-stick disc on the inner end wall of the cone, these compensation openings are laid on the radial outer edge. Thus, the magnetic force effective area of the cone is reduced, resulting in a weakening of the magnetic force. The aim is therefore, in particular, to obtain this area of the cone, if possible, as solid material.
  • DE 197 17 445 C2 shows an electromagnet, in particular for actuating valves, with a Hubankerkolben and projecting therefrom actuating rod, which is connected by a central bore of the cone with an actuating element of the valve. Between the armature piston and the associated impact wall of the cone a circular anti-stick disc is provided with a central opening to the passage for the actuating rod. The pressure equalization between the interior of the electromagnet and the valve via the central bore of the cone, which has an enlarged diameter, so that a gap between the rod diameter and the bore diameter.
  • DE 90 05 411 U1 which is considered to be generic, shows a further electromagnet for actuating a valve, wherein the actuating rod is guided in a sliding bush, which simultaneously performs storage function for the rod.
  • the anti-stick disc is press-fitted on the actuating rod.
  • the required pressure equalization between the magnet and the valve takes place via axially parallel holes in the cone of the magnet.
  • the distance between the compensation bore and the central bore is determined by the diameter of the anti-slump disc, so that it is predominantly in the Outside of the cone are arranged. This in turn leads to a weakening of the magnetic flux in this area.
  • DE 10 2004 028 871 A1 shows a further generic electromagnet with a sleeve-shaped anti-adhesive disk, which comprises a rod-shaped actuating part of the magnet armature at a radial distance.
  • the bush is arranged with its radial region on the radial impact wall of the cone for the anchor. Its axial region extends into an opening bore of the cone for the actuating rod. Between the diameter of the rod and the opening bore of the cone, pressure compensation openings are provided.
  • DE 42 15 237 A1 shows another generic electromagnet with a sleeve-shaped anti-stick disc, which, however, is arranged on a radial impact wall of the magnet armature with the cone and not on that of the cone.
  • the armature has on the impact wall on an axial blind hole for receiving a return spring, which is surrounded at a radial distance from the socket.
  • the axial region of the bushing is arranged in the blind hole.
  • the radial portion of the sleeve extends to near the outer radial edge of the armature piston, are arranged in the axis-parallel pressure equalization holes.
  • the invention uses a pressure-compensating press-fit bushing as an anti-sticking disk
  • the component fulfills the functionality of an anti-sticking disk, but prevents the pressure equalization in the magne- not.
  • the bushing has a radially directed to the axis collar with recesses, which presses radially against the armature piston directed end wall of the cone and thus keeps the armature piston and the cone at a distance.
  • the pressure equalization openings can now be arranged closer in the direction of the axis of the magnet.
  • the axis-axial distance is limited only by the diameter of the central bore for the actuating rod.
  • the pressure compensation openings can even be arranged directly in the central bore for the actuating rod.
  • the proposed solution has the potential to be very cost effective. Because additional required grooves or holes can be reduced to a minimum, so that space can be designed to save space.
  • the socket itself can be inexpensively manufactured as a converted component.
  • the bush is press-fitted with its axial region in the central bore of the cone, through which the projecting from the armature piston actuating rod is slidably guided.
  • the bush does not rest with its entire axial circumference at the diameter of the central bore, but advantageously only at specially provided radially outward outlets. These bulges are designed so that the interference fit is ensured by their elastic or plastic deformation.
  • the pressure-compensating bushing in its axially extending portion lent additional as a guide or sliding bearing for the actuating rod in the centric bore in the cone can be used, which eliminates additional storage and management of the rod in the conical bore.
  • the bushing has at its axial end facing away from the cone a deflection of its outer wall directed radially inwards on the rod diameter. The deflection can also be designed as a slide bearing.
  • Pressure compensation openings arranged as separate, axially parallel and through holes in the cone, which open into the region of the recesses of the socket.
  • the recesses make it possible to arrange the additional pressure compensation bores with a minimum axis-parallel distance to the central bore.
  • the minimum radial distance to the axis of the cone is determined by the diameter of the centric bore or cavity in the central bore.
  • pelg is provided to arrange the pressure equalization openings in the central bore of the cone, wherein between the rod diameter and the bore diameter, an axially extending gap is provided through which the fluid flows to equalize the pressure.
  • the bulges of the press fit of the bushing are designed so that although their press fit is ensured by their deformation, but at the same time between the bulges creates a further gap through which the fluid can flow to equalize the pressure.
  • the gap opens advantageously in the region of the recesses on the collar of the bushing.
  • the actuating rod has running surfaces in the form of flats or a polygonal profile on its axial length. Column formation occurs here between the axial flattening of the rod and the central bore diameter. The uplifting running surfaces on the rod circumference can also be used as additional guide or sliding bearings of the rod in the cone area. Further advantageous embodiments of the invention will become apparent from the dependent claims and the drawings described below.
  • Fig. 1 shows a schematic side view of an electromagnet with flanged valve.
  • Fig. 2 shows a perspective view of Einpressbuchse.
  • Fig. 3 shows in a perspective view a variant of the invention.
  • FIG. 1 shows a schematic side view of an electric magnet 1 in the design of a cylindrical lifting magnet which actuates a valve 2.
  • the valve 2 is a 2/2 directional seat valve, which is arranged in a fluidic flow, wherein the fluid flows through an inflow or outflow 3.
  • the hydraulic inlet and outlet 3 is controlled by a seat body 4 in the form of a blunt cone (see FIG. 3) in a valve seat 5.
  • a seat body 4 contacted in the axial direction of an actuating rod 6, which in turn abuts the end face of a Hubankerkolbens 7 of the electromagnet 1.
  • the seat body 4 is pushed back into its seat 5 by means of a radially arranged flat spring 18 after actuation by the electromagnet 1. Shown is the normally closed embodiment of the valve. 2
  • the lifting armature piston 7 is arranged in a bearing sleeve 8, which is arranged in a coil body which consists of a current-carrying cylindrical coil 9, the yoke 10 and a rear cover 19 with a plug 11 for the power connection.
  • the electromagnet 1 is covered to the outside by a jacket 13.
  • a cone 12 is provided, which is part of the valve sleeve 14 of the valve 2.
  • the cone 12 or the valve sleeve 14 has a continuous axial centric bore 15, through which the actuating rod 6 protrudes.
  • the rod 6 has a circular cross-section.
  • the bore 15 opens at its end directed to the Hubankerkolben 7 to a cylindrical cavity 16, at the axial Wan PHg a bushing 17 is clamped in a press fit.
  • One of the two inflows and outflows 3 is arranged axially on the end face of the valve 2, the corresponding part extends radially and opens into the central bore 15 of the cone 12 or the valve sleeve 14.
  • the circular actuating rod 6 a reduced cross-section in order to ensure a sufficient ensure proper flow of the fluid and center the cone in the seat.
  • the bushing 17 which is shown separately in FIG. 2 in a perspective view, has a cylindrical axial region, on the circumferential wall of which bulges 20 directed radially outwards are arranged, which ensure a secure press fit in the wall of the cavity 16.
  • the bushing 17 additionally has a radially protruding collar 21, on whose circumference radially inwardly directed recesses 22 are provided.
  • the collar 21 is arranged with its recesses 22 on the radial end wall of the cone 12, and serves in this way as stroke limiting the armature piston 7. It thus fulfills the function of an anti-slump disc in this position to avoid the hyperbolic increase in the magnetic force in Endhub Brady the armature piston 7 on the cone 12 of the magnet. 1
  • the axial region of the bushing 17 has, at its end remote from the collar 21, a deflection 24, directed radially inwards towards the actuating rod 6 (see FIG. 1), of its circumferential wall, which serves as a guide or sliding bearing for the rod 6. Otherwise, the rod is guided over the central bore 15.
  • the pressure effects caused by the flow through the valve 2 must also be able to be conducted from the valve side into the interior of the electromagnet 1.
  • the arrangement according to FIG. 1 has an additional axially parallel bore in the cone 12 as a pressure compensation opening 23.
  • the pressure compensation bore 23 is continuous and extends from the region of the valve seat 5 to the radial end wall of the cone 12, on which the collar 21 of the bushing 17 rests.
  • the pressure compensation bore 23 opens in the stroke region of the armature piston 7 in the region of the recesses 22 of the collar 21 of the bushing 17.
  • the bore 23 can now be arranged as close as possible to the central bore 15.
  • Fig. 3 shows in a perspective longitudinal sectional view of a variant of the invention, in which the pressure compensation openings 23 are arranged in the central bore 15, that is dispensed with an additional bore for pressure equalization.
  • the actuating rod 6 in the region of the bearing of the bushing 17 does not have a uniform circular cross-section, but has a tangential flattening 28 extending in the axial direction or a polygonal cross-section.
  • the further region of the rod 6 extending in the direction of the valve seat 5 furthermore has a circular cross section.
  • a gap 25 is thus created between the rod diameter and the diameter of the central bore, via which connection can take place from the valve 2 to the interior of the electromagnet 1.
  • the gap 25 is in the cavity 16, in the storage area of the bushing 17, in a further gap 27, which is formed between the bulges 20 of the bush 17.
  • the extending through the entire central bore 15 gap 25 opens, which is not apparent from Fig. 3, in the region of the radial recesses 22 of the collar 21 of the bushing 17th
  • the profiled portion of the rod has at its outer edge region running surfaces 26 in the form of flats, curves or chamfers. These meet the Guiding or sliding function for the rod 6 in the central bore 15 of the cone 12 or the valve sleeve 14th
  • a sufficient pressure equalization in the central bore can, in a modification of the representation of FIG. 3, also take place in the case of a circular rod cross-section. It only has to be ensured that the fluid in the gap 25 after sealing by the valve seat 5 can flow into the interior of the electromagnet 1 and thus generates the pressure compensation.
  • the diameter of the central bore 15 is accordingly to be increased for the gap formation.
  • additional radially extending holding elements in the form of slide bearings with an axial passage for the fluid flow are to be provided at an axial distance from each other.

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

Abstract

L'invention concerne un électroaimant destiné à actionner une soupape (2) et qui présente un corps d'aimant creux, de forme cylindrique, rempli d'un fluide de la soupape (2) et doté d'un cône (12) et d'un piston d'induit (7) déplacé axialement et muni d'une tige d'actionnement (6) de la soupape (2) qui fait saillie dans la direction d'actionnement. Le cône (12) présente un alésage central (15) traversé par la tige d'actionnement (6) ainsi qu'une plaque anti-adhésive sur sa surface frontale tournée vers le piston d'induit (7). Au moins une ouverture (23) d'équilibrage de pression est prévue pour équilibrer la pression entre l'intérieur du corps d'aimant et la soupape. L'invention est caractérisée en ce que le disque anti-adhésif est configuré comme une douille (17), en ce que la douille (17) présente un collet (21) orienté dans la direction radiale et doté à sa périphérie de découpes (22) orientées radialement vers l'axe, en ce que le collet repousse radialement la paroi frontale du cône (12) tournée vers le piston d'induit (7) et en ce que l'ouverture d'équilibrage de pression débouche dans la zone des découpes (22) et est disposée aussi proche que possible dans la direction radiale dans la zone occupée par l'alésage central (15) du cône (12).
PCT/EP2007/010070 2006-11-22 2007-11-21 Électroaimant pour l'actionnement de soupapes WO2008061719A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006054942.2 2006-11-22
DE200610054942 DE102006054942B3 (de) 2006-11-22 2006-11-22 Elektromagnet zur Betätigung von Ventilen

Publications (1)

Publication Number Publication Date
WO2008061719A1 true WO2008061719A1 (fr) 2008-05-29

Family

ID=38650819

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/010070 WO2008061719A1 (fr) 2006-11-22 2007-11-21 Électroaimant pour l'actionnement de soupapes

Country Status (2)

Country Link
DE (1) DE102006054942B3 (fr)
WO (1) WO2008061719A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008029979B4 (de) 2008-06-24 2024-02-29 Robert Bosch Gmbh Betätigungsmagnet mit Antiklebescheibe
DE102009049109A1 (de) 2009-10-12 2011-04-14 Hydraulik-Ring Gmbh Elektromagnet sowie hydraulisches Ventil mit einem Elektromagnet
DE102018000449A1 (de) * 2018-01-19 2019-07-25 Hydac Fluidtechnik Gmbh Betätigungsmagnet

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4215237A1 (de) * 1992-05-09 1993-11-11 Thomas Technik Kg Ges Fuer Mag Elektromagnetisch betätigbares Hydraulik-Regelventil
DE19700405A1 (de) * 1997-01-09 1998-07-16 Teves Gmbh Alfred Magnetventil
US6053473A (en) * 1997-11-12 2000-04-25 Keihin Corporation Valve apparatus
WO2002027226A1 (fr) * 2000-09-29 2002-04-04 Nok Corporation Solenoide lineaire et vanne a solenoide
WO2004072566A1 (fr) * 2003-02-12 2004-08-26 Robert Bosch Gmbh Organe d'expansion pour systeme de climatisation

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19717445C2 (de) * 1997-04-25 1999-11-18 Bso Steuerungstechnik Gmbh Elektromagnet, insbesondere zum Betätigen von Ventilen
DE19934846A1 (de) * 1999-07-24 2001-01-25 Hydraulik Ring Gmbh Elektromagnet und hydraulisches Ventil mit einem Elektromagneten
DE102004028871A1 (de) * 2004-06-15 2006-01-05 Hydac Electronic Gmbh Betätigungsvorrichtung, insbesondere zum Betätigen von Ventilen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4215237A1 (de) * 1992-05-09 1993-11-11 Thomas Technik Kg Ges Fuer Mag Elektromagnetisch betätigbares Hydraulik-Regelventil
DE19700405A1 (de) * 1997-01-09 1998-07-16 Teves Gmbh Alfred Magnetventil
US6053473A (en) * 1997-11-12 2000-04-25 Keihin Corporation Valve apparatus
WO2002027226A1 (fr) * 2000-09-29 2002-04-04 Nok Corporation Solenoide lineaire et vanne a solenoide
WO2004072566A1 (fr) * 2003-02-12 2004-08-26 Robert Bosch Gmbh Organe d'expansion pour systeme de climatisation

Also Published As

Publication number Publication date
DE102006054942B3 (de) 2007-12-06

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