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WO2018007167A1 - Soupape à fluide pouvant être traversée axialement par un écoulement - Google Patents

Soupape à fluide pouvant être traversée axialement par un écoulement Download PDF

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Publication number
WO2018007167A1
WO2018007167A1 PCT/EP2017/065503 EP2017065503W WO2018007167A1 WO 2018007167 A1 WO2018007167 A1 WO 2018007167A1 EP 2017065503 W EP2017065503 W EP 2017065503W WO 2018007167 A1 WO2018007167 A1 WO 2018007167A1
Authority
WO
WIPO (PCT)
Prior art keywords
armature
core
valve
fluid valve
axial flow
Prior art date
Application number
PCT/EP2017/065503
Other languages
German (de)
English (en)
Inventor
Besart Sadiku
Original Assignee
Pierburg 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 Pierburg Gmbh filed Critical Pierburg Gmbh
Publication of WO2018007167A1 publication Critical patent/WO2018007167A1/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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/12—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with streamlined valve member around which the fluid flows when the valve is opened
    • F16K1/123—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with streamlined valve member around which the fluid flows when the valve is opened with stationary valve member and moving sleeve
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/029—Electromagnetically actuated 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
    • F16K31/0644—One-way valve
    • F16K31/0651—One-way valve the fluid passing through the solenoid coil

Definitions

  • the invention relates to an axial flow Bares fluid valve, in particulardeffenabsperrventil with an electromagnet having a coil, a core and a flow-through bare anchor unit and magnetic yokes, a housing in which the electromagnet is arranged, an inlet nozzle, at a first axial end the housing is mounted and in which a Umströmungs phenomenon is arranged, which has a valve seat, an outlet nozzle which is fixed to an opposite axial end of the housing and a bearing surface at an axial end portion of the anchor unit, which cooperates with the valve seat.
  • Such fluid valves are also referred to as coaxial valves, hydraulic valves ordeementabsperrventile. These fluid valves are used, for example, to shutdown or release a coolant path in a motor vehicle, on the one hand to ensure the fastest possible heating of the flow-through aggregates and on the other hand to prevent their overheating.
  • it is necessary to ensure the lowest possible flow through the fluid valve to minimize the pumping power to be applied and, secondly, to minimize the power consumption of the fluid valve, which is normally actuated electromagnetically To consume energy.
  • coaxial valves are used, which despite a small space requirement and low production costs due to reduced flow deflections produce a low pressure loss and simultaneously provide a sufficiently large flow area available. Due to the small sizes and consequent small and light moving parts, the power consumption of these fluid valves is relatively low.
  • Such a coaxial valve is known for example from EP 1 255 066 A2.
  • This valve has a tube serving as a closing body, which is fixed radially inside an armature of the electromagnet and extends through the core to the opposite axial end of the electromagnet.
  • an outlet connection piece is fastened to the housing of the electromagnet, in which a flow-around body with valve seat is formed, onto which the pipe can be placed for closing the flow cross-section.
  • the tube surrounding a compression spring is arranged, which is arranged in mutually facing formed on the inner circumference recesses of the armature and the core and the tube loaded via the armature in its closed position.
  • the armature has a relatively large mass for generating a sufficiently high magnetic force for switching the valve.
  • the axially souström bare armature unit has a constriction on the inner circumference, which has a continuously decreasing downstream inner diameter is created at constant Einströmquerites with very low pressure losses additional space to increase the armature mass and thus the acting magnetic force, whereby the fluid valve to be built smaller can.
  • the constriction immediately follows a cylindrical portion and largest inner diameter, which further downstream each further reduced until the portion of the constriction is completed and in the following extends a cylindrical portion with the smallest diameter of the constriction on.
  • it may thus be a conical constriction, but also slightly convex or concave constrictions are conceivable.
  • a circumferential extension is formed, which acts as a conical diffuser and thus leads to a pressure recovery from the kinetic energy increased in the narrow diameter. In this way, the total pressure loss can be reduced compared to a version without extension.
  • the armature unit comprises a magnetizable armature and a fixed to the anchor through-Bares tube which projects through the core.
  • This tube is not one magnetizable material so that it can be used for fluid guidance within the core of the electromagnet. This also facilitates the assembly and weight of the movable anchor unit.
  • the armature unit at its two axial end portions of a same diameter, wherein the two annular axial ends are usable as bearing surfaces which cooperate with the valve seat.
  • the inlet nozzle can optionally be arranged on both sides of the electromagnet, so that the valve can be constructed both as a normally open valve and as a normally closed valve. It is also conceivable to dimension the diameter of the two end sections differently and to set desired flow curves in this way.
  • the tube abuts axially against the armature and is secured in an annular receptacle on the inner circumference of the armature, providing a continuous linear transition between the tube and the armature, which avoids additional pressure losses.
  • the constriction in the anchor and the extension is formed in the pipe or the constriction in the pipe and the extension formed in the anchor.
  • a part of the core and the compression spring can be arranged radially within the largest diameter of the armature unit, namely in the area of the smaller diameter, and yet the armature unit can be mounted to the core, whereby the size can be reduced.
  • the armature unit is guided in a sleeve which surrounds the core, wherein an inner of the sleeve is sealed against the inlet port in the closed state of the fluid valve and a space between the armature and the core has a fluidic connection to the outlet port.
  • a sleeve which surrounds the core
  • an inner of the sleeve is sealed against the inlet port in the closed state of the fluid valve and a space between the armature and the core has a fluidic connection to the outlet port.
  • a contact surface facing the armature is formed on the core against which bears a compression spring whose opposite end bears against an axial end of the armature, wherein the compression spring is arranged axially between the extension and the constriction of the armature unit.
  • the spring can thus be arranged to save space on the smaller diameter of the anchor unit, whereby the radial space is reduced.
  • the tube can be used at the same time as a guide of the spring, so that a buckling of the spring can be excluded during operation.
  • the core has a radially inner annular recess in which the compression spring is arranged and which is axially limited by the contact surface of the compression spring on the core, whereby the spring for opening or closing the fluid valve requires no additional space.
  • the compression spring rests with its core to the opposite axial end against an annular projection at the end of the armature, which at least partially immersed in energizing the electromagnet in the annular recess of the core.
  • the armature preferably has a radial groove in which a non-magnetizable stop ring is arranged, against which the core rests in the energized state of the electromagnet. Accordingly, a small distance between the core and the armature is maintained even in the energized position, whereby a sticking of the armature to the core is reliably prevented regardless of the position of the valve seat to a closing member.
  • Figure 1 shows a side view of a fluid valve according to the invention in normally open version in a sectional view.
  • Figure 2 shows a side view of a fluid valve according to the invention in normally closed version in a sectional view.
  • Figure 3 shows a section of the anchor unit and the core of the fluid valve according to the invention in a sectional enlarged view.
  • the invention axially flow-through bare fluid valve, which is for cooling circuits of internal combustion engines, hybrid or electric vehicles can be used, has an electromagnet 10 which is arranged in a housing 12.
  • the electromagnet 10 consists of a coil 14, which is wound on a coil support 16, and return elements 18, 20, 22, which are formed by two arranged at the axial ends of the bobbin 16 return plates 18, 20 and a coil 14 surrounding the yoke 22 ,
  • a sleeve 24 is fixed, inside which a core 26 of the electromagnet 10 is fixed and in which an armature 28 of the electromagnet 10 is slidably mounted.
  • a plug 30 is formed on the housing 12, the electrical contact lugs 32 extend through the housing 12 to the coil 14.
  • the core 26 has a radially inner, open to the sleeve 24, circumferential recess 34 which viewed from the armature 28 extends to a contact surface 36 against which a compression spring 38 is applied, which biased at its opposite end against an annular projection 40 of the armature 28 rests and surrounds the sleeve 24 in this area.
  • the radially inner annular projection 40 at the axial end 41 of the armature 28 is formed corresponding to a conical projection 42 extending from the recess 34 of the core 26 in the radially outer region, whereby the armature 28 is partially immersed in the core 26 when the coil 14 is energized can.
  • a circumferential radial groove 44 is formed at the end of the projection 40 of the armature 28, in which a non-magnetizable stop ring 46 is disposed against the the core 26 is applied in the energized state.
  • the armature unit 49 viewed from the inlet connection 60, initially extends cylindrically, whereupon a conical section 50 follows, followed by a cylindrical section 51 of reduced diameter, in which the transition between the tube 48 and the armature 28 is formed.
  • a conical-section-shaped, circumferential extension 52 is formed, from the end of which the armature unit 49 continues cylindrically again with the diameter, which is also formed in the entrance area.
  • the design of the anchor unit is identical, but due to the reversed flow direction in the embodiment in Figure 1, the constriction 50 in the tube 48 and the extension 52 in the armature 28 is formed, while in Embodiment according to Figure 2, the constriction 50 in the armature 28 and the extension 52 in the tube 48 is formed.
  • the compression spring 38 respectively surrounds the cylindrical portion 51 of reduced diameter, which is formed on the tube 48 so that it serves as a guide of the compression spring 38.
  • the facing away end portions 54, 56 of the tube 48 and the armature 28 have in the present embodiments, the same inner diameter, which ends in an annular thin support surface 57, which can serve as a closing surface for a corresponding valve seat 58 which is arranged in an inlet port 60 is located and either opposite to the end portion 54 of the armature 28 or opposite to the end portion 56 of the tube 48.
  • This embodiment of the armature unit 47 is shown enlarged in FIG. It can be seen that due to the constriction 50, the anchor mass can be increased while the size of the sleeve 24 remains the same and thus the size of the coil 14 remains constant, as a result of which the magnetic forces can be increased significantly. Also, the required space for accommodating the compression spring 38 is minimized.
  • the housing 12 of the fluid valve has at its axial ends axially extending annular projections 62, 64, which are each surrounded by a corresponding annular projection 66, 68 of the inlet nozzle 60 and an outlet nozzle 70 directly with the interposition of an O-ring 72.
  • the inlet port 60 and the outlet port 70 can be secured, for example, by laser welding, respectively.
  • the outlet port 70 also has in its radially inner region an axially extending annular projection 74, which surrounds the projection 62 of the housing 12 from the inside and in the fluid valve shown in Figure 1 surrounds the axial end portion 54 of the armature 28 and radially inside the projection 64 is disposed, as well as in the fluid valve shown in Figure 2, the axial end portion 56 of the tube 48 immediately surrounds and is disposed radially within the projection 62.
  • the inlet port 60 has a shoulder 76 through which an outer peripheral ring 77 of a Umströmungsianus 78 and an outer circumference 79 of a support ring 80 in the attachment of the inlet nozzle 60 against the annular projection 62 of the housing 12 in the embodiment of Figure 1 and the projection 64 of Housing 12 is clamped in the embodiment of Figure 2, so that the support ring 80 and the Umströmungsêt 78, the same time Valve seat 58 forms or on which a corresponding valve seat 58 can be formed, are fixed in position.
  • the Umströmungs crusher 78 is formed axially symmetrical and has a central convex inflow surface 82, to which further radially outwardly a concave inflow surface 84 connects. This passes via a radius in a first in the radially outer region convex discharge surface 86 from which radially outward four webs 88 extend over which the Umströmungs Kunststoff the Umströmungs emotionss is attached to the peripheral ring 77 and between which the fluid flow from the inflow side to the downstream side and thus can reach into the interior of the anchor unit 49.
  • the convex discharge surface 86 is adjoined by a planar region, which forms the valve seat 58 and from which a concave discharge surface 88 extends up to the center axis of the flow body 78.
  • the bypass body 78 cooperates with the adjoining support ring 80, which is clamped with a radially outwardly extending annular extension 79 between the peripheral ring 77 of the Umströmungs stressess 78 and the projection 62 of the housing 12.
  • the support ring 80 has a radially inner flow guide surface 90, which serves as an inflow surface of the fluid and extends concavely radially inward and with a radially inner portion 92 extending radially and opposite to the end portion 54 of the armature 28 in the version of Figure 2 , or to the end portion 56 of the tube 48, ends in the version of Figure 1.
  • annular projection 94 In the transition region between the concave part and the radially extending part 92 of the flow guide 90, extends from the axially opposite side of the support ring 80, an annular projection 94 in the axial direction to the electromagnet
  • this annular projection 94 is radially surrounded by a step-shaped extension 96 at the end of the sleeve 24 and lies radially inwardly against one end of the core 26 and a sealing ring 98 resting axially against the core 26 and designed as a lip sealing ring is on.
  • this step-shaped widening 96 of the sleeve 24 In the radially outer region, this step-shaped widening 96 of the sleeve 24 is surrounded by a seal 100, which rests against the projection 62 of the housing 12 in the radially outer region.
  • the lip sealing ring 98 abuts against the axial end of the core 26 with its radially extending lip support 102.
  • two sealing lips 104, 106 extend from the radial ends, of which the radially inner sealing lip 104 rests against the tube 48 from radially outside and the radially outer sealing lip 106 rests against the projection 94 of the support ring 80.
  • the lip ends 108 are oriented opposite to the radially inner region 92 of the support ring 80.
  • the inlet port 60 are arranged with the Umströmungsêt 78 and the support ring 80 and the lip seal 98 at the other end of the housing 12. Accordingly, the lip seal 98 abuts with its lip support 102 against an annular, radially extending constriction 110 of the sleeve 24, which limits the displacement of the armature 28 to the inlet port 60.
  • the radially inner sealing lip 104 is correspondingly radially against the thin end 54 of the armature 28 at.
  • the fluid passes only from the outlet port 70 along the gap between the tube 48 and the core 26 in Figure 2, or along the gap between the sleeve 24 and the armature 28 in the space 112, which is correspondingly filled with fluid, while passing through the Seal 100 and a seal 114, which is located on the armature side between the sleeve 24 and the projection 64 of the housing 12, a fluid flow to the electromagnet 10 in the outer region of the sleeve 26 is reliably prevented.
  • this fluid valve can be switched with low electromagnetic forces, since there is a pressure equalization on the moving parts, so that only the restoring force of the compression spring 38 is overcome must be to switch the fluid valve. Thus, the size and the energy consumption of the fluid valve can be reduced. As soon as the valve is opened, the pressure across the gap also spreads into the space 112 in the shortest time, whereby a pressure equalization of the moving parts of the fluid valve is created, so that only the existing friction and the spring force must be overcome for switching.
  • the inlet port 60 including the bypass body 78 and the support ring 80 and the lip seal 98 with the outlet port 70 can be exchanged, with the result that this fluid valve, without having to use other components, run both normally closed and normally open can be.
  • the electromagnet 10 must be energized to close the fluid valve, thus the support surface 57 of the tube 48 rests on the valve seat 58 of the Umströmungs stressess 78, while in the embodiment of Figure 2, the solenoid 10 must be actuated to lift the support surface 57 of the armature 28 from the valve seat 58.
  • the special shape of the anchor unit fulfills several functions.
  • a relatively large inflow cross section is provided for the fluid to be delivered, which in the following can flow through the armature unit with very low pressure loss.
  • the pressure loss at the constriction is partially compensated again by the following extension.
  • the space obtained by this section reduced diameter space to see. This is used on the one hand to accommodate the compression spring and on the other hand to be able to produce the core-facing portion of the armature with a larger volume and thus a larger mass, with the result that the magnetic forces are significantly increased with the same coil size.
  • the fluid valve can be built correspondingly smaller, whereby space is saved.
  • the smooth transition in the area of the constriction ensures a flow rectification in this area and reduces previously existing vortex.
  • the two bearing surfaces do not necessarily have to be the same, but may possibly differ from one another for setting the pressure loss curves.
  • the two bearing surfaces do not necessarily have to be the same, but may possibly differ from one another for setting the pressure loss curves.
  • optionally on the Stop ring are dispensed with, since the maximum stroke of the armature to the core can be adjusted by the distance between the valve seat and the pipe. Also can be dispensed with the valve when the valve is normally closed and the anchor unit can be made only from the anchor itself.

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

Abstract

L'invention concerne des soupapes à fluide pouvant être traversées axialement par un écoulement, en particulier des soupapes d'arrêt de réfrigérant. Lesdites soupapes sont pourvues d'un électroaimant (10), qui présente une bobine (14), un noyau (26) et une unité armature (49) pouvant être traversée par un écoulement ainsi que des éléments culasse magnétique (18, 20, 22), d'un carter (12), dans lequel l'électroaimant (10) est agencé, d'une tubulure d'entrée (60), qui est fixée à une première extrémité axiale du carter (12) et dans laquelle est agencé un corps d'écoulement (78) présentant un siège de soupape (58), d'une tubulure de sortie (70), qui est fixée à une extrémité axiale opposée du carter (12), d'une surface d'appui (57) à une partie d'extrémité axiale (54, 56) de l'unité armature (49), laquelle surface coopère avec le siège (58) de soupape, et d'un ressort de compression (38), par l'intermédiaire duquel l'unité armature (49) est sollicitée en direction du siège (58) de soupape. L'objet de l'invention est de pouvoir obtenir une soupape de ce type de plus petite dimension pour une force magnétique à générer stable. A cet effet, selon l'invention, l'unité armature (49) pouvant être traversée axialement par un écoulement présente sur la périphérie intérieure un étranglement (50), lequel présente un diamètre intérieur se rétrécissant constamment en aval.
PCT/EP2017/065503 2016-07-06 2017-06-23 Soupape à fluide pouvant être traversée axialement par un écoulement WO2018007167A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016112410.9A DE102016112410B4 (de) 2016-07-06 2016-07-06 Axial durchströmbares Fluidventil
DE102016112410.9 2016-07-06

Publications (1)

Publication Number Publication Date
WO2018007167A1 true WO2018007167A1 (fr) 2018-01-11

Family

ID=59239904

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/065503 WO2018007167A1 (fr) 2016-07-06 2017-06-23 Soupape à fluide pouvant être traversée axialement par un écoulement

Country Status (2)

Country Link
DE (1) DE102016112410B4 (fr)
WO (1) WO2018007167A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU3430371A (en) * 1971-10-06 1973-04-12 Matti Vaananen Improvements ina shutoff valve
DE19837694A1 (de) * 1998-08-19 2000-02-24 Aws Apparatebau Arnold Gmbh Coaxialventil mit Gegendruckrückentlastung
EP1235012A2 (fr) * 2001-02-22 2002-08-28 müller co-ax AG Soupape coaxiale
EP1255066A2 (fr) 2001-05-03 2002-11-06 müller co-ax AG Soupape coaxialle
JP2004239283A (ja) * 2003-02-03 2004-08-26 Nippon Steel Corp 水撃現象防止機能に優れたシリンダバルブ
WO2010088108A2 (fr) * 2009-01-27 2010-08-05 Borgwarner Inc. Electrovanne à purge variable (vbs) et à extrémité ouverte présentant un amortissement visqueux inhérent

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH543029A (fr) * 1972-04-04 1973-10-15 Lucifer Sa Valve à trois voies pour fluide
DE3610122A1 (de) 1986-03-26 1987-10-08 Bosch Gmbh Robert Magnetventil
US5529281A (en) 1994-08-24 1996-06-25 The United States Of America As Represented By The Administrator Of National Aeronautics And Space Dual-latching solenoid-actuated valve assembly
FR2740848B1 (fr) 1995-11-08 1998-01-30 Eaton Sa Monaco Electrovanne de regulation et de securite
JP3977066B2 (ja) 2001-12-03 2007-09-19 株式会社テージーケー 電磁比例弁
DE102008051759B3 (de) 2008-10-15 2010-04-29 Karl Dungs Gmbh & Co. Kg Rohrförmige Ventileinrichtung
DE102009060785B4 (de) 2009-12-21 2012-10-18 Ewald Schneider Koaxialventil mit Dichtelement

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU3430371A (en) * 1971-10-06 1973-04-12 Matti Vaananen Improvements ina shutoff valve
DE19837694A1 (de) * 1998-08-19 2000-02-24 Aws Apparatebau Arnold Gmbh Coaxialventil mit Gegendruckrückentlastung
EP1235012A2 (fr) * 2001-02-22 2002-08-28 müller co-ax AG Soupape coaxiale
EP1255066A2 (fr) 2001-05-03 2002-11-06 müller co-ax AG Soupape coaxialle
JP2004239283A (ja) * 2003-02-03 2004-08-26 Nippon Steel Corp 水撃現象防止機能に優れたシリンダバルブ
WO2010088108A2 (fr) * 2009-01-27 2010-08-05 Borgwarner Inc. Electrovanne à purge variable (vbs) et à extrémité ouverte présentant un amortissement visqueux inhérent

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DE102016112410A1 (de) 2018-01-11
DE102016112410B4 (de) 2022-10-20

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