WO2004040125A1 - Soupape de commande d'un fluide - Google Patents

Soupape de commande d'un fluide Download PDF

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Publication number
WO2004040125A1
WO2004040125A1 PCT/DE2003/003275 DE0303275W WO2004040125A1 WO 2004040125 A1 WO2004040125 A1 WO 2004040125A1 DE 0303275 W DE0303275 W DE 0303275W WO 2004040125 A1 WO2004040125 A1 WO 2004040125A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
closing member
nozzles
valve closing
valve according
Prior art date
Application number
PCT/DE2003/003275
Other languages
German (de)
English (en)
Inventor
Udo Hafner
Waldemar Hans
Frank Brenner
Frank Miller
Guenther Bantleon
Thanh-Hung Nguyen-Schaefer
Christof Vogel
Norbert Krapp
Original Assignee
Robert Bosch 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
Priority claimed from DE10319920A external-priority patent/DE10319920A1/de
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to DE50309492T priority Critical patent/DE50309492D1/de
Priority to EP03773481A priority patent/EP1561027B1/fr
Publication of WO2004040125A1 publication Critical patent/WO2004040125A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1853—Orifice plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0667—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature acting as a valve or having a short valve body attached thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1833—Discharge orifices having changing cross sections, e.g. being divergent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1846—Dimensional characteristics of discharge orifices

Definitions

  • the invention is based on a valve for controlling a fluid according to the type defined in more detail in the preamble of claim 1.
  • Such a valve is known from practice and can be used, for example, as an injection valve in an internal combustion engine of a motor vehicle or as a gas control valve in a fuel cell.
  • the known valve comprises a valve housing, in which a valve closing member is axially displaceably guided, which is operatively connected to an electromagnetic actuation unit.
  • the valve closing member serves to control a fluid flow from an inflow side to an outflow side and for this purpose interacts with a valve seat.
  • the zu- the flow side of the valve is connected to a pressure region surrounding the valve closing member.
  • the valve closing member has on its end face a spherical closing body made of a solid material, which cooperates with a conical seat made of a turned part.
  • the conical seat is followed by a valve plate, which represents a so-called spray orifice plate, via which the fuel or the gasoline is sprayed into a combustion chamber of the internal combustion engine.
  • a valve plate which represents a so-called spray orifice plate, via which the fuel or the gasoline is sprayed into a combustion chamber of the internal combustion engine.
  • There is a dead volume between the valve seat and the spray orifice plate which can sometimes counteract good atomization of the fuel.
  • the dead volume between the sealing seat and the spray orifice plate also leads to poor valve dynamics and undesired evaporation of the fuel in an intake manifold in which the valve is generally arranged.
  • large forces are required to open the valve closing member because there is a large difference between the pressure prevailing in the pressure region surrounding the valve closing member and the pressure acting on the end face of
  • a sealing collar is usually formed on the end face of the valve closing member, which, when the valve closing member is closed, rests on a sealing plate and has a cylindrical bore surrounding the sealing plate.
  • the bore leads to a dead volume space of the sealing plate, which is followed by a nozzle which leads to the outflow side.
  • valve lift is limited due to the high dynamics of the valve, with the result that the sealing seat can be changed essentially with regard to its diameter.
  • an enlargement of the sealing seat leads to an increase in the opening force or magnetic force to be applied, which in turn results in increased power consumption.
  • the diameter of the sealing seat can not be chosen arbitrarily large due to a frequently limited installation space. For these reasons, the volume flows or the mass flows of the flowing gas are often not sufficiently large for the requirements prevailing in gas engines and fuel cell drives.
  • valve according to the invention with the features according to the preamble of claim 1, in which nozzles are formed on the valve plate, which lead to the outflow side and which can be closed by means of the valve closing member, has the advantage when configured as a liquid valve, in particular as a fuel injection valve, that there is no dead volume between the valve plate formed, for example, from an injection orifice plate and the sealing seat, which leads to better atomization of the controlled liquid compared to a valve with a spherical closing body. Without dead volume, there is an even drop spectrum throughout the entire injection process.
  • the so-called dynamic flow range can also be kept linear when opening and closing the valve closing member, which also proves to be advantageous with regard to the performance of the valve.
  • the effective stroke of the valve closing element is identical to the actual stroke of the valve closing element due to the design of the valve seat as a flat seat. There is also no so-called squeeze film flow at the valve seat designed as a flat seat. Furthermore, due to the lack of a spherical closing body made of a solid material, a lower weight of the valve closing member can be achieved, so that lower forces have to be applied to open the valve. This increases the dynamics of the valve.
  • the formation of the valve plate with several small diameter nozzles has the advantage of fine atomization of the controlled liquid.
  • the term fluid is to be understood in its broadest meaning in the present case.
  • the fluid can therefore represent both a liquid and a gas.
  • valve according to the invention When the valve according to the invention is designed as a gas valve, there is no need for a nozzle downstream of the valve plate and thus also for a dead volume space arranged downstream of the valve plate.
  • the lack of a dead volume downstream of the sealing plate leads to increased valve dynamics compared to the known gas valve described above.
  • the formation of the nozzles on the sealing plate also has the advantage over a sealing plate with a downstream nozzle that a lower force is required to actuate the valve closing member.
  • the valve according to the invention can be used in particular as a fuel injection valve in an internal combustion engine of a motor vehicle or also for mass flow control of gases such as hydrogen and natural gas, for example in a fuel cell or a gas engine.
  • the nozzles which are preferably arranged along a circular line, are each provided with a rounded inflow edge in order to improve the flow behavior of the gas in the nozzle.
  • the nozzles each have a sharp inflow edge and widen continuously in the outflow direction, the wall of the nozzles preferably having a curved longitudinal section. With such a shape in particular, a high shear rate can be achieved with the liquid to be controlled, which leads to a fine atomization of the liquid in the nozzles.
  • the nozzles each taper in a funnel shape in the direction of flow, the wall of the nozzles also having an arched longitudinal section in this case.
  • the nozzles can be designed with a smaller diameter than when controlling a gas.
  • the diameter of the nozzles is 90 ⁇ m, for example.
  • the diameter is, for example, in the range of approximately 500 ⁇ m.
  • the mass flow in the valve is determined by the nozzle surfaces.
  • the valve according to the invention can be used as an injection valve for different internal combustion engines with different fuel requirements by simply adapting the number of nozzles by installing a valve plate with a corresponding number of nozzles. In the case of a new application, it is therefore only necessary to modify the valve plate designed as an orifice plate (SLS) accordingly.
  • SLS orifice plate
  • the nozzles can open into an annular channel which is arranged on the side of the valve plate facing away from the valve closing element.
  • the width of the ring channel is preferably chosen so that it is approximately two to three times the nozzle diameter.
  • a rounding of the nozzle inflow edge with a radius of curvature of, for example, 0.050 mm can be provided.
  • a preferred embodiment of the valve according to the invention works on the so-called pressure compensation principle. This can be achieved in that the inflow side is connected downstream to an inner and an outer pressure area, which pressure areas are arranged upstream of the valve seat.
  • the inner pressure region comprises an axial pressure channel of the valve closing member, which exits on the free end face of the valve closing member.
  • the outer pressure area surrounds the valve closing member.
  • the valve closing member which has an annular surface on the end face, which can have a sealing surface interacting with the nozzles, can be actuated with little effort, since when it is opened, essentially the same pressure prevails in the inner and outer pressure region and the fluid is out flows in both pressure areas in the direction of the nozzles.
  • Such a valve also permits high mass flows, since the fluid flows into the nozzles both from the inner pressure area and from the outer pressure area.
  • the inner pressure area and the outer pressure area can be connected via at least one outflow channel formed in the valve closing member.
  • the outflow channel can be designed as an essentially radially oriented bore of the valve closing member, but it can also be inclined with a certain angle of attack in the flow direction with respect to the longitudinal axis of the valve closing member and lead from an axial bore serving as a supply channel to the outside of the valve closing member.
  • the feed channel then also opens into an axial bore, possibly of reduced diameter, which represents the inner pressure area or is part of it.
  • the stroke of the valve closing member is preferably in the range between 60 ⁇ m and 90 ⁇ m, with a pressure of, for example, 3 bar to 4 bar in the inner and outer pressure range. able to see. If very small drops are to be generated, ie if the so-called Sauter Mean Diameter (SMD) is very small, the pressure can also be between 10 and 20 bar. The required opening force is much smaller than with previously known valves, since there is a small pressure area.
  • SMD Sauter Mean Diameter
  • the stroke of the valve closing member is preferably approximately 300 ⁇ m, the gas pressure prevailing in the inner pressure region and the outer pressure region being approximately 8 bar.
  • valve plate or spray hole plate of the valve according to the invention can be made of different materials, such as steel, PEEK with carbon fibers, a hard plastic or a ceramic, for example by an etching, an eroding or a laser method.
  • the valve according to the invention can comprise at least one sealing element in order to increase the tightness in the region of the valve seat.
  • This is expediently arranged on the sealing surface on the end face of the valve closing member and can have one or more sealing lips.
  • the sealing element can consist of different materials.
  • the sealing element for controlling a liquid is formed either from a metal, for example from hardened steel, or also from an elastomer, which can be made of fluorocarbon rubber or Viton.
  • the sealing element can have an annular shape and can be embedded in a corresponding annular groove on the end face of the valve closing element. It can be provided with two sealing lips, one of which is arranged on the inner edge of the sealing ring and thus assigned to the inner pressure area and the other is arranged on the outer edge of the sealing ring and thus is assigned to the outer pressure area.
  • the valve according to the invention can have a base serving as a stop for the valve closing member.
  • This is for example formed on the valve plate.
  • the stop represents an impact absorber and limits the deformation of the elastomeric sealing element, for example, and thus its wear, and clearly defines the air gap on a magnet armature that serves to actuate the valve closing element.
  • the valve closing member itself has a protective ring or Baffle catcher forms to protect the sealing ring.
  • aprons can also be formed on the valve plate for supporting the sealing element. These aprons form the edges of the nozzles, for example.
  • FIG. 1 shows a simplified longitudinal section through a fuel injection valve according to the invention
  • Figure 2 is an enlarged view of area II in Figure 1;
  • FIG. 3 shows a detail of a second embodiment of a fuel injection valve according to the invention
  • Figure 4 shows a simplified longitudinal section through a nozzle of a fuel injection valve
  • Figure 5 shows an alternative embodiment of a nozzle in a simplified longitudinal section
  • Figure 6 shows a schematic section through a gas valve according to the invention with a nozzle plate in a fragmentary, perspective view
  • Figure 7 is a plan view of the nozzle plate of the gas valve according to Figure '6;
  • FIG. 8 shows a sectional view of an alternative embodiment of a gas valve with a nozzle plate
  • FIG. 9 shows a simplified longitudinal section through a sealing area of the gas valve according to FIG. 8 in an enlarged illustration
  • Figure 10 is a view corresponding to Figure 9, but with a changed sealing area.
  • FIG. 1 and 2 show a fuel injection valve 10 for use in an internal combustion engine of a motor vehicle, not shown here, which is used to control a fuel flow from an inflow side 11 to an outflow side 12, the fuel emerging in atomized form on the outflow side 12, as indicated by the dotted areas X in the drawing.
  • the injection valve 10 comprises a multi-part housing 13, in which a magnet coil 15 is arranged, which engages around a deep-drawn guide sleeve 17.
  • a substantially tubular plug 19 is fixed in the guide sleeve 17 and is used to receive a spiral spring 21 acting as a preload spring, on the inflow side 11 of which spring is removed.
  • a magnet armature 14 facing side, a magnet armature 14 abuts, which is guided axially displaceably in the guide sleeve 17.
  • the magnet armature 14 is tubular and forms a valve closing member which cooperates at the end with a valve seat 26 which represents a flat seat.
  • the magnet armature 14 or the valve closing member 14 comprises a first axial bore 16 serving as a supply channel, which is connected to the inflow side 11 of the injection valve 10 and forms an interior of the valve closing member 14.
  • From the first axial bore 16 branch off four radial bores distributed over the circumference of the valve closing member 14, of which three bores 18A, 18B and 18C are shown in the drawing and which lead to a so-called outer pressure region 20 which borders on the outside of the valve closing member 14 and is limited by the guide sleeve 17.
  • the first axial bore 16 opens into a second axial bore 22, the diameter of which is smaller than the diameter of the first axial bore 16 and which emerges on the free end face 24 of the valve closing member 14.
  • the second axial bore 22 of smaller diameter which represents an axial outflow bore, forms a so-called inner pressure region or is part of the same.
  • valve closing member 14 When the valve closing member 14 opens, fuel flows from the first axial bore 16 via the four radial outflow bores into the outer pressure region 20 and via the axial outflow bore 22 to the free end face 24 of the valve closing member 14.
  • the inner pressure region 22 and the outer pressure region 20 are arranged upstream of the valve seat 26, which is designed as a flat seat and cooperates with the free end face 24 of the valve closing member 14 and is formed on a nozzle plate 28 which serves as a spray orifice plate and which is in the guide sleeve 17, for example via a welded connection is fixed.
  • the valve plate 28 is made of steel and is flat on the side of the valve closing member 14.
  • nozzle plate 28 for example ten nozzles or metering bores 30 are formed along a circular line, for example ten slightly set with respect to the longitudinal axis of the injection valve 10, which lead to a frustoconical recess 31 in the valve plate 28.
  • the nozzles 30 each have a diameter of approximately 90 ⁇ m.
  • a sealing ring 36 is arranged in a corresponding recess in the valve closing member 14.
  • the sealing ring 36 is made of fluorocarbon rubber and has a diameter which corresponds to the diameter of the circular line, along which the nozzles 30 are arranged such that the sealing ring 36 closes the nozzles 30 when the valve closing member 14 is closed, only the area of the Nozzles 30 is acted upon by external pressure. This area determines the hydraulic closing force of the valve.
  • the valve closing member 14, which has a stroke of approximately 60 ⁇ m to 90 ⁇ m, is guided in the guide sleeve 17 over the entire length of its lateral surface 33.
  • FIG. 3 shows an alternative embodiment of a fuel injection valve 50, which largely corresponds to the injection valve according to FIG. 1, but differs from it in that the magnet armature 14 has two tubular or ring-shaped guide collars 55 and 56, via which the magnet armature 14 is guided in the guide sleeve 17.
  • the first guide collar 55 is arranged in a region of the lateral surface 33 of the valve closing member 14 that is remote from the valve plate 28.
  • the second guide collar 56 is formed by an annular collar which has an end face which is flush with the end face 24 of the valve closing member 14.
  • Axial bores 57 are formed in the annular collar 56, which ensure a fuel flow between the outer pressure region 20 and the nozzles 30 in the valve plate 28. Otherwise, the structure of valve 50 corresponds to that of the valve according to FIG. 1.
  • FIG. 4 shows an embodiment of a nozzle 30 which passes through a valve plate or an injection orifice plate 28 of a fuel injection valve of the type shown in FIGS. 1 to 3.
  • the nozzle 30 has a sharp inflow edge 58 and widens in the direction of flow, the nozzle 30 having a wall 59, the longitudinal section of which is curved. With such a nozzle, a high shear rate of the fuel can be achieved, so that there is good atomization.
  • FIG. 5 shows an alternative embodiment of a nozzle 30 of an orifice plate 28 for installation in a fuel injection valve, which has a rounded inflow edge 61 and which tapers in a funnel shape in the direction of flow, the nozzle 30 having a wall 62 which has a curved longitudinal section. Furthermore, the nozzle 30 has a sharp outflow edge 63.
  • FIG. 6 shows a gas valve 60 for use in a fuel cell or in a gas engine, which is used to regulate a hydrogen flow or a CNG (compressed natural gas) flow and is structurally similar to the valves according to FIGS. 1 to 3. For reasons of clarity, the previous reference numerals are therefore used for functionally identical components.
  • the gas valve 60 comprises a housing 13, in which a valve closing member 14 is axially displaceably guided in a long guide formed by the housing 13, which is operatively connected to an electromagnetic actuating unit (not shown here) and is coated with a sliding varnish.
  • the valve closing member 14 comprises a first axial bore 16 serving as a supply channel, which is connected to an inflow side of the gas valve 60, not shown here. From the first axial bore 16 branch off four radial bores distributed over the circumference of the valve closing member 14, each of which forms a radial outflow bore and of which three bores 18A, 18B, 18C are shown in FIG. 1, which lead to one on the outside of the valve closing link 14 border, so-called outer pressure region 20. In the axial direction, the first axial bore 16 opens into a second axial bore 22, the diameter of which is smaller than the diameter of the first axial bore 16 and which emerges on the free end face 24 of the valve closing member 14. The second axial bore 22 of smaller diameter, which represents an axial outflow bore, forms a so-called inner pressure region or is part of the same.
  • gas flows from the first axial bore 16 via the radial outflow bores 18A, 18B, 18C into the outer pressure region 20 which represents a gas space and via the axial outflow bore 22 to the free end face 24 of the valve closing member 14.
  • Both the inner pressure region 22 and the outer pressure region 20 are arranged upstream of a valve seat 26 which cooperates with the free end face 24 of the valve closing member 14 and is formed on a nozzle plate 28 which serves as a sealing plate or sealing seat disk and which cooperates with the valve closing member 14.
  • the nozzle plate 28 of the valve 10 intended for gas applications has an effective thickness that is greater than the effective thickness of a nozzle plate intended for liquid applications.
  • fourteen axially aligned nozzles 30 serving as throughflow openings are formed in the nozzle plate 28 along a circular line in the present exemplary embodiment, which nozzles 30 are closed via an annular groove 32 lead an outflow side 12 of the gas valve 60 and are provided with a rounded inflow edge.
  • the nozzles 30 are each designed so that the ratio of their length to their diameter is approximately 0.7. Such a design results in an optimal flow behavior of the gas flowing through the nozzles 30. Alternatively, a different number of nozzles can also be provided.
  • the end face 24 of the valve closing member 14 is designed as an annular surface on which an annular seal 36 made of an elastomeric material is embedded.
  • the ring seal 36 closes the nozzles 32 in the closed position of the valve closing member 14, so that a gas flow from the pressure areas 20 and 22 to the outflow side 12 is blocked.
  • FIG. 8 shows a gas valve 80 which essentially corresponds to that according to FIG. 1.
  • the gas valve 80 differs from the gas valve according to FIG. 6, however, in the design of the valve closing member 14, namely in that it is not provided with radially aligned outflow bores, but in addition to the axial outflow bore 22 has outflow bores 42 aligned at an angle with respect to the longitudinal axis of the valve closing member 14 which lead to the outer pressure region 20, which causes an optimized flow behavior of the gas in question.
  • the sealing area of the gas valve 80 is shown in detail in FIG. 9. It is characterized in that the nozzle plate 28 has an optionally annular base 44 has, which serves as a stop for the valve closing member 14 and is arranged in the edge region of the latter.
  • the nozzle plate 28 has, on the nozzles 30, aprons 46, each serving as a sealing lip, which, when the valve closing member 14 is closed, engage in the annular elastomer seal 36, which is embedded in an annular groove of the valve closing member 14.
  • aprons 46 serving as a sealing lip, which, when the valve closing member 14 is closed, engage in the annular elastomer seal 36, which is embedded in an annular groove of the valve closing member 14.
  • the edges of the elastomer seal 36 are chamfered and the inflow edges of the nozzles 30 are rounded off with a radius of curvature of approximately 0.05 mm.
  • the flow of the gas in question in the gas valve 80 can also be seen in FIG. 9.
  • the gas flows from the inflow side according to an arrow A through the first axial bore 16 of the valve closing member 14 and from there through the outflow channels 42 according to an arrow B into the outer pressure region 20 and on the other hand according to an arrow C through the second axial bore 22 Is part of the inner pressure area.
  • gas flows from the outer pressure region 20 according to an arrow D and from the inner pressure region according to an arrow E to the nozzles 30 and via these to the downstream side of the gas valve 80 according to an arrow F.
  • These flow paths essentially correspond to the flow paths of the fuel in the fuel injection valves shown in FIGS. 1 to 3.
  • FIG. 10 shows an alternative embodiment of a sealing area in a gas valve of the type shown in FIG. 8.
  • the sealing area according to FIG. differs from that according to FIG. 9 in that it has a sealing ring 52 which is provided with two sealing lips 54A and 54B which are arranged on the inner and outer edges of the sealing ring 52.
  • the sealing lips 54A and 54B act on the sealing plate 28, which is designed here without a stop base and without aprons.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Lift Valve (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une soupape de commande d'un fluide, en particulier à actionnement électromagnétique, comprenant un élément de fermeture de soupape (14) qui commande un flux de fluide entre un côté admission et un côté échappement et coopère avec un siège de soupape (26) conçu sous la forme d'un siège plat sur une plaque porte-soupape (28). Selon la présente invention, des buses (30), conçues sur cette plaque porte-soupape (28), mènent au côté échappement et peuvent être obturées au moyen de l'élément de fermeture de soupape (14).
PCT/DE2003/003275 2002-10-26 2003-10-02 Soupape de commande d'un fluide WO2004040125A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE50309492T DE50309492D1 (de) 2002-10-26 2003-10-02 Ventil zum steuern eines fluids
EP03773481A EP1561027B1 (fr) 2002-10-26 2003-10-02 Soupape de commande d'un fluide

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10249963.2 2002-10-26
DE10249963 2002-10-26
DE10319920.9 2003-05-05
DE10319920A DE10319920A1 (de) 2002-10-26 2003-05-05 Ventil zum Steuern eines Fluids

Publications (1)

Publication Number Publication Date
WO2004040125A1 true WO2004040125A1 (fr) 2004-05-13

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PCT/DE2003/003275 WO2004040125A1 (fr) 2002-10-26 2003-10-02 Soupape de commande d'un fluide

Country Status (3)

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EP (1) EP1561027B1 (fr)
DE (1) DE50309492D1 (fr)
WO (1) WO2004040125A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1816342A1 (fr) * 2006-02-03 2007-08-08 Siemens Aktiengesellschaft Ensemble soupape pour soupape d'injection et soupape d'injection
EP2187043A1 (fr) * 2008-11-14 2010-05-19 Delphi Technologies Holding S.à.r.l. Buse d'injection
CN103322217A (zh) * 2012-03-22 2013-09-25 罗伯特·博世有限公司 具有改进的密封配合的比例阀
WO2014139706A1 (fr) * 2013-03-11 2014-09-18 Robert Bosch Gmbh Soupape de commande de fluide à étanchéité renforcée
DE102017210362A1 (de) * 2017-06-21 2018-12-27 Robert Bosch Gmbh Proportionalventil zum Steuern eines gasförmigen Mediums
US10364758B2 (en) 2016-12-20 2019-07-30 Continental Powertrain, USA, LLC High pressure gas phase injector

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10060402B2 (en) 2014-03-10 2018-08-28 G.W. Lisk Company, Inc. Injector valve
EP3290684A1 (fr) 2016-08-31 2018-03-07 Continental Automotive GmbH Injecteur de fluide et aiguille d'injecteur de fluide

Citations (3)

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EP1816342A1 (fr) * 2006-02-03 2007-08-08 Siemens Aktiengesellschaft Ensemble soupape pour soupape d'injection et soupape d'injection
EP2187043A1 (fr) * 2008-11-14 2010-05-19 Delphi Technologies Holding S.à.r.l. Buse d'injection
WO2010055103A1 (fr) * 2008-11-14 2010-05-20 Delphi Technologies, Inc. Buse d'injection
CN102216602A (zh) * 2008-11-14 2011-10-12 德尔福技术控股有限公司 喷嘴
CN102216602B (zh) * 2008-11-14 2016-08-03 德尔福国际运营卢森堡有限公司 喷嘴
CN103322217A (zh) * 2012-03-22 2013-09-25 罗伯特·博世有限公司 具有改进的密封配合的比例阀
CN103322217B (zh) * 2012-03-22 2018-08-14 罗伯特·博世有限公司 具有改进的密封配合的比例阀
WO2014139706A1 (fr) * 2013-03-11 2014-09-18 Robert Bosch Gmbh Soupape de commande de fluide à étanchéité renforcée
US10125735B2 (en) 2013-03-11 2018-11-13 Robert Bosch Gmbh Valve for controlling a fluid with increased sealing action
US10364758B2 (en) 2016-12-20 2019-07-30 Continental Powertrain, USA, LLC High pressure gas phase injector
DE102017210362A1 (de) * 2017-06-21 2018-12-27 Robert Bosch Gmbh Proportionalventil zum Steuern eines gasförmigen Mediums

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EP1561027B1 (fr) 2008-03-26
DE50309492D1 (de) 2008-05-08

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