EP1561027B1 - Soupape de commande d'un fluide - Google Patents

Soupape de commande d'un fluide Download PDF

Info

Publication number
EP1561027B1
EP1561027B1 EP03773481A EP03773481A EP1561027B1 EP 1561027 B1 EP1561027 B1 EP 1561027B1 EP 03773481 A EP03773481 A EP 03773481A EP 03773481 A EP03773481 A EP 03773481A EP 1561027 B1 EP1561027 B1 EP 1561027B1
Authority
EP
European Patent Office
Prior art keywords
valve
nozzles
valve closing
sealing
closing element
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
EP03773481A
Other languages
German (de)
English (en)
Other versions
EP1561027A1 (fr
Inventor
Udo Hafner
Waldemar Hans
Frank Brenner
Frank Miller
Guenther Bantleon
Thanh-Hung Nguyen-Schaefer
Christof Vogel
Norbert Krapp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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 EP07104186A priority Critical patent/EP1801410B1/fr
Publication of EP1561027A1 publication Critical patent/EP1561027A1/fr
Application granted granted Critical
Publication of EP1561027B1 publication Critical patent/EP1561027B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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 closer defined in the preamble of claim 1. Art.
  • 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 guided axially displaceable, which is in operative connection with an electromagnetic actuator unit.
  • the valve closure member serves to control a fluid flow from an inlet side to an outlet side and cooperates with a valve seat for this purpose.
  • the inflow side the valve is connected to a pressure surrounding the valve closure member.
  • the valve closure member has on its front side a spherical closing body made of a solid material, which cooperates with a conical seat made of a rotating part.
  • the conical seat is followed by a valve plate, which is 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 is 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 dead volume which can sometimes counteract a good atomization of the fuel.
  • the dead volume between the sealing seat and the spray perforated disk further leads to poor valve dynamics and undesirable evaporation of the fuel in a suction pipe, in which the valve is usually arranged.
  • large forces are required to open the valve-closing member because there is a large difference between the pressure existing in the pressure area surrounding the valve-closing member and the pressure acting on the end face of the valve-closing member.
  • 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 Totvolumenraum the sealing plate, which is followed by a nozzle, which leads to the downstream side.
  • gases such as hydrogen or methane have lower density compared to liquid fuels. Therefore, in gases often a much larger volume flow is required, so that in particular a gas valve, a large flow area is desirable at the valve seat.
  • the valve lift is limited because of the high dynamics of the valve, with the result that the sealing seat is variable in terms of its diameter substantially. An enlargement of the sealing seat but leads to an increase in the applied opening force or magnetic force, which in turn has an 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.
  • a fuel injection valve for controlling a fluid is already known.
  • the valve is electromagnetically operated by providing an electromagnetic circuit comprising a magnetic coil, a core serving as an inner pole, a movable magnetic circuit member, and an outer magnetic sheath.
  • the movable magnetic circuit component is a magnetic armature, which is pulled against the inner pole upon energization of the magnetic coil, and at the same time a valve closing member which controls a fluid flow from an inlet side to an outlet side.
  • the designed as a flat plate movable magnetic circuit member or valve closure member cooperates with a formed as a flat seat valve seat member, which is made of a plastic or other non-magnetic material together.
  • the valve seat element has one or more nozzle openings which lead to the downstream side and which can be closed by means of the valve closure member.
  • the actual valve seat forms a formed on the valve seat member, projecting in the direction of the valve closing member ring collar.
  • valve according to the invention having the features according to the preamble of claim 1, in which nozzles are formed on the valve plate, leading to the downstream side and which can be closed by means of the valve closure member has, when designed as a liquid valve, in particular as a fuel injection valve, the advantage that there is no dead volume between the valve plate formed, for example, from a spray perforated disk and the sealing seat, which leads to a better atomization of the controlled liquid compared to a valve with a spherical closing body. Without dead volume, there is a uniform drop spectrum throughout the course of the injection.
  • the so-called dynamic flow range can be kept linear when opening and closing the valve closure member, which also proves to be advantageous in terms of the performance of the valve.
  • the effective stroke of the valve closing member is identical by the formation of the valve seat as a flat seat with the actual stroke of the valve closure member. Also, no so-called squeeze film flow occurs on the valve seat formed as a flat seat. Furthermore, a reduced weight of the valve closure member can be achieved by the absence of a spherical closure member made of a solid material, so that lower forces for opening the valve must be applied. This increases the dynamics of the valve.
  • valve plate with a plurality of small-diameter nozzles has the advantage of fine atomization of the controlled liquid.
  • the term fluid is to be understood in the present case in its broadest meaning.
  • the fluid can thus represent both a liquid and a gas.
  • valve according to the invention as a gas valve, it is possible to dispense with a nozzle connected downstream of the valve plate and thus also with a dead volume space arranged downstream of the valve plate.
  • the absence 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 further has the advantage over a sealing plate with a downstream nozzle that a smaller force for actuating the valve closure member is required.
  • 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 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 an advantageous embodiment of the valve designed as a gas valve for improving the flow behavior of the gas in the nozzle.
  • the nozzles each have a sharp inflow edge and continuously expand in the outflow direction, the wall of the nozzles preferably having a curved longitudinal section.
  • a high shear rate can be achieved in the liquid to be controlled, resulting in a fine atomization of the liquid in the nozzles.
  • the nozzles taper funnel-shaped in each case in the flow direction, wherein the wall of the nozzles can also have a curved longitudinal section in this case.
  • the nozzles may be designed with a smaller diameter than in the control of a gas.
  • the diameter of the nozzles is 90 ⁇ m.
  • the diameter is for example in the range of about 500 microns.
  • the mass flow in the valve is determined by the nozzle areas.
  • the valve can be used according to the invention by simply adjusting the number of nozzles by installing a valve plate with a corresponding number of nozzles as injection valve for different internal combustion engines with a different fuel consumption.
  • SLS spray-orifice plate
  • the nozzles may open into an annular channel, which is arranged on the side facing away from the valve closure member of the valve plate.
  • the width of the annular channel is preferably chosen so that it is approximately two to three times the diameter of the nozzle.
  • a particularly good efficiency with regard to the flow behavior of the gas in the nozzles can be achieved if the height of the annular channel is designed so that in each case the ratio of the length of the nozzle to its diameter is about 0.7 to 1.
  • a rounding off of the nozzle inflow edge with a radius of curvature of, for example, 0.050 mm can be provided, in particular for a valve designed as a gas valve according to the invention.
  • a preferred embodiment of the valve according to the invention operates according to the so-called pressure equalization principle. This can be achieved by connecting the upstream side to an inner and an outer pressure region, which pressure regions are arranged upstream of the valve seat.
  • the inner pressure region comprises an axial pressure channel of the valve closure member, which exits at the free end side of the valve closure member.
  • the outer pressure area surrounds the valve closure member.
  • valve closure member the front side designed as an annular surface, which may have cooperating with the nozzle sealing surface, with little effort operable, since when it opens in the inner and the outer pressure region substantially the same pressure prevails and the fluid both pressure areas flows in the direction of the nozzles.
  • This has the advantage that a particular electromagnetic actuator unit with low power can be interpreted.
  • such a valve allows high mass flows because the fluid flows into the nozzles from both the inner ducking area and the outer pressure area.
  • the inner pressure region and the outer pressure region may be connected via at least one outflow channel formed in the valve closure member.
  • the outflow channel may be formed as a substantially radially aligned bore of the valve closure member, but it may also be inclined at a certain angle in the flow direction relative to the longitudinal axis of the valve closure member and lead from serving as a supply channel, axial bore to the outside of the valve closure member.
  • the supply channel then also opens into an axial bore of possibly reduced diameter, which represents the inner pressure region or is a part thereof.
  • the stroke of the valve closing member is preferably in the range between 60 .mu.m and 90 .mu.m, wherein in the inner and the outer pressure range, a pressure of for example 3 bar to 4 bar prevail can. 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 in this case much smaller than in previously known valves, since a small pressure surface is present.
  • SMD Sauter Mean Diameter
  • the stroke of the valve closing member is preferably about 300 ⁇ m, the gas pressure prevailing in the inner pressure range and the outer pressure range being about 8 bar.
  • the valve plate of the valve according to the invention may be made of different materials, such as steel, PEEK with carbon fibers, a hard plastic or a ceramic, for example after an etching, an erosion or a laser process.
  • the valve according to the invention may comprise at least one sealing element to increase the density 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 may have one or more sealing lips.
  • the sealing element may consist of different materials.
  • the sealing element is formed, for example, for controlling a liquid either of a metal, for example of hardened steel, or also of an elastomer, which may consist of fluorocarbon rubber or Viton.
  • the sealing element In the control of a gas, it is advantageous to form the sealing element of an elastomer.
  • the sealing element made of an elastomer the impact forces which occur, which in turn leads to a reduced noise development, are also reduced.
  • An embodiment of the sealing element made of a suitable metal may be required, in particular, if an excessively high swelling would be expected with an elastomer.
  • the sealing element may be annular and embedded on the valve closure member at its end face in a corresponding annular groove. It may 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 region and the other arranged on the outer edge of the sealing ring and thus associated with the outer pressure region.
  • valve according to the invention may have a base serving as a stop for the valve closure member. This is formed for example on the valve plate.
  • the stopper constitutes a baffle catcher and limits the deformation of, for example, the elastomeric sealing element and thus its wear, and clearly defines the air gap on a magnet armature serving to actuate the valve closure member.
  • the valve closure member itself a guard ring or
  • Impaler to protect the sealing ring forms Impaler to protect the sealing ring forms.
  • aprons for supporting the sealing element may be formed on the valve plate. These skirts, for example, form the edges of the nozzles.
  • FIG. 1 a simplified longitudinal section through a fuel injection valve according to the invention
  • FIG. 2 an enlarged view of the area II in FIG. 1
  • FIG. 3 a partial view of a second embodiment of a fuel injection valve according to the invention
  • FIG. 4 a simplified longitudinal section through a nozzle of a fuel injection valve
  • FIG. 5 an alternative embodiment of a nozzle in a simplified longitudinal section
  • FIG. 6 a schematic section through a gas valve according to the invention with a nozzle plate in a fragmentary perspective view
  • FIG. 7 a top view of the nozzle plate of the gas valve after FIG. 6
  • FIG. 1 a simplified longitudinal section through a fuel injection valve according to the invention
  • FIG. 2 an enlarged view of the area II in FIG. 1
  • FIG. 3 a partial view of a second embodiment of a fuel injection valve according to the invention
  • FIG. 4 a simplified longitudinal section through a nozzle of a fuel injection valve
  • FIG. 5 an alternative embodiment of a nozzle in a simplified longitudinal section
  • FIG. 8 a fragmentary sectional view of an alternative embodiment of a gas valve with a nozzle plate
  • FIG. 9 a simplified longitudinal section through a sealing region of the gas valve after FIG. 8 in an enlarged view
  • FIG. 10 a FIG. 9 corresponding view, but with a modified sealing area.
  • a fuel injection valve 10 is shown for use in an internal combustion engine of a motor vehicle not shown here, which serves to control a fuel flow from an inflow side 11 to a downstream side 12, wherein the fuel exits at the downstream side 12 in atomized form, as indicated by the dotted areas X. indicated in the drawing.
  • the injection valve 10 comprises a multi-part housing 13, in which a magnetic coil 15 is arranged, which engages around a deep-drawn guide sleeve 17.
  • a substantially tubular plug 19 is fixed, which serves to receive a spring acting as a biasing coil spring 21, facing away from the inflow side 11 thereof
  • a magnet armature 14 is applied, which is guided axially displaceably in the guide sleeve 17.
  • the armature 14 is tubular and forms a valve closure member which cooperates with the end face with a flat seat representing valve seat 26.
  • 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 distributed over the circumference of the valve closing member 14 radial bores, of which three holes 18 A, 18 B and 18 C are shown in the drawing and which lead to a so-called outer pressure region 20 which borders on the outside of the valve closure member 14 and is bounded by the guide sleeve 17.
  • the first axial bore 16 opens into a second axial bore 22 whose diameter is smaller than the diameter of the first axial bore 16 and which exits at the free end face 24 of the valve closure member 14.
  • the second axial bore 22 of smaller diameter which is an axial Abströmbohrung forms a so-called inner pressure region or is part of the same.
  • the inner pressure region 22 and the outer pressure region 20 are arranged upstream of the valve seat 26 designed as a flat seat, which cooperates with the free end face 24 of the valve closing member 14 and is formed on a nozzle plate 28 serving as a so-called spray perforated disk, which in the guide sleeve 17, for example via a welded connection is fixed.
  • the valve plate 28 is made of steel and flat on the side of the valve closing member 14.
  • nozzle plate 28 for example, ten nozzles or metering bores 30 which are slightly engaged with respect to the longitudinal axis of the injection valve 10 are formed along a circular line, leading to a frusto-conical recess 31 of the valve plate 28.
  • the nozzles 30 in the present case each have a diameter of about 90 microns.
  • a sealing ring 36 is arranged in a corresponding recess of the valve closing member 14.
  • the sealing ring 36 is made of fluorocarbon rubber and has a diameter corresponding to the diameter of the circular line along which the nozzles 30 are arranged such that the sealing ring 36 closes the nozzle 30 with the valve closure member 14 closed, in which case only the surface of Nozzle 30 is subjected to external pressure. This area determines the hydraulic closing force of the valve.
  • valve closure member 14 which has approximately a stroke of 60 microns to 90 microns, is guided over the entire length of its lateral surface 33 in the guide sleeve 17.
  • FIG. 3 an alternative embodiment of a fuel injection valve 50 is shown, which largely according to the injection valve FIG. 1 corresponds, but differs from this in that the armature 14 has two tubular or annular guide collars 55 and 56 through which the 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 remote from the valve plate 28.
  • the second guide collar 56 is formed by an annular collar, which has an end face, which is aligned with the end face 24 of the valve closing member 14.
  • axial bores 57 are formed, which ensure a flow of fuel between the outer pressure region 20 and the nozzle 30 in the valve plate 28.
  • the structure of the valve 50 corresponds to that of the valve FIG. 1 ,
  • FIG. 4 an embodiment of a nozzle 30 is shown, which is a valve plate or a spray perforated disk 28 of a fuel injection valve in the FIGS. 1 to 3 engages through the type shown.
  • the nozzle 30 has a sharp inflow edge 58 and widens in the flow direction, wherein the nozzle 30 has a wall 59, whose longitudinal section is curved. In such a nozzle, a high shear rate of the fuel can be achieved so that there is good atomization.
  • FIG. 5 an alternative embodiment of a nozzle 30 of a spray orifice plate 28 for installation in a fuel injection valve is shown, which has a rounded inflow edge 61 and the funnel-shaped tapered in the flow direction, wherein the nozzle 30 has a wall 62 which has a curved longitudinal section. Furthermore, the nozzle 30 has a sharp discharge edge 63.
  • a gas valve 60 is shown for use in a fuel cell or in a gas engine, which is used for controlling a stream of hydrogen or a CNG (Compressed Natural Gas) stream and in the construction of the valves according to Figure 1 to 3 like.
  • CNG Compressed Natural Gas
  • 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 actuator not shown here and coated with a lubricating 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 distributed over the circumference of the valve closing member 14 radial bores, each forming a radial outflow bore and of which in FIG. 1 three bores 18A, 18B, 18C are shown, which at one to the outside of the valve closure member 14 adjacent, so-called outer pressure range 20 lead. In the axial direction, the first axial bore 16 opens into a second axial bore 22 whose diameter is smaller than the diameter of the first axial bore 16 and which exits at the free end face 24 of the valve closure member 14. The second axial bore 22 of smaller diameter, which is an axial Abströmbohrung 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 representing a gas chamber and via the axial outflow bore 22 to the free end side 24 of the valve closure 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 serving as a sealing plate or sealing seat disc, which cooperates with the valve closing member 14.
  • the nozzle plate 28 of the gas valve 10 has an effective thickness that is greater than the effective thickness of a nozzle plate intended for liquid applications.
  • nozzle plate 28 In the nozzle plate 28 are as FIG. 7 can be seen along a circular line in the present embodiment, fourteen axially aligned, serving as flow openings nozzles 30 formed, which via an annular groove 32 to lead a downstream 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 about 0.7. Such a design causes optimum flow behavior of the gas flowing through the nozzles 30. Alternatively, another number of nozzles may be provided.
  • the end face 24 of the valve closing member 14 is formed as an annular surface on which an annular seal 36 made of an elastomeric material is embedded.
  • the ring seal 36 closes in the closed position of the valve closing member 14, the nozzle 32, so that a gas flow from the pressure regions 20 and 22 is blocked to the downstream side 12.
  • FIG. 8 a gas valve 80 is shown, which is essentially after that FIG. 1 equivalent.
  • the gas valve 80 differs from the gas valve FIG. 6 However, by the formation of the valve closing member 14, in that it is not provided with radially aligned Abströmbohrept, but next to the axial outflow bore 22 at an angle relative to the longitudinal axis of the valve closure member 14 aligned Abströmbohrept 42 which lead to the outer pressure region 20, what a Optimized flow behavior of the gas in question causes.
  • the sealing area of the gas valve 80 is in FIG. 9 shown in detail. It is characterized in that the nozzle plate 28 has a possibly annular base 44th 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 serving on the nozzle 30 each serving as a sealing lip skirts 46 which engage in the closed valve closure member 14 in the annular elastomeric seal 36 which is embedded in an annular groove of the valve closure member 14.
  • the edges of the elastomeric seal 36 are chamfered and the inflow edges of the nozzles 30 rounded with a radius of curvature of about 0.05 mm.
  • the flow of the gas in question in the gas valve 80 is also FIG. 9 refer to.
  • the gas flows from the inlet 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 in the outer pressure region 20 and the other according to an arrow C through the second axial bore 22, the Part of the inner pressure range is.
  • When opening the valve closing member 14 gas flows from the outer pressure region 20 according to an arrow D and the inner pressure region according to an arrow E to the nozzle 30 and via this according to an arrow F to the downstream side of the gas valve 80.
  • These flow paths correspond substantially to the flow paths of the fuel in the in the FIGS. 1 to 3 illustrated fuel injection valves.
  • FIG. 10 is an alternative embodiment of a sealing region in a gas valve of the FIG. 8 shown type shown.
  • the sealing area after FIG. 10 different depending on the person FIG. 9 in that it comprises a sealing ring 52 which is provided with two sealing lips 54A and 54B, which are arranged at the inner and at the outer edge of the sealing ring 52.
  • the sealing lips 54A and 54B engage with the valve closing member 14 closed to the sealing plate 28, which is formed here without stop base and without aprons.

Landscapes

  • 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)

Claims (11)

  1. Soupape de commande d'un fluide, notamment à actionnement électromagnétique, comprenant un organe d'obturation de soupape (14) commandant la veine de fluide entre le côté d'entrée (11) et le côté de sortie (12) et coopérant avec un siège de soupape (26) réalisé comme siège plat, sur une plaque de soupape (28) qui comporte des buses (30) débouchant du côté de sortie (12) et qui se ferment à l'aide de l'organe d'obturation de soupape (14),
    caractérisée en ce que
    l'organe d'obturation de soupape (14) a au moins un perçage de sortie, radial (18A, B, C) et un perçage axial (22) sortant par sur côté frontal libre (24), et du côté frontal, l'organe d'obturation de soupape (14) comporte au moins un élément d'étanchéité (36, 52) suivi d'un perçage axial formant un orifice de passage avec le perçage axial (22) de l'organe d'obturation de soupape (14),
    l'élément d'étanchéité (36, 52) ayant une surface d'étanchéité en forme de surface annulaire coopérant avec les buses (30) également disposées suivant une répartition annulaire.
  2. Soupape selon la revendication 1,
    caractérisée en ce que
    les buses (30) sont disposées suivant une ligne circulaire.
  3. Soupape selon la revendication 1 ou 2,
    caractérisée en ce que
    les buses (30) comportent une arête d'entrée (61), arrondie ou une arête d'entrée (58), vive.
  4. Soupape selon la revendication 1 ou 2,
    caractérisée en ce que
    les buses (30) ont une arête d'entrée (58), vive et s'élargissant dans la direction de sortie, la paroi (59) des buses (30) ayant une section longitudinale bombée.
  5. Soupape selon l'une des revendications 1 à 4,
    caractérisée en ce que
    les buses (30) débouchent dans un canal annulaire (32) prévu sur le côté de la plaque de soupape (28) non tourné vers l'organe d'obturation de soupape (14).
  6. Soupape selon la revendication 5,
    caractérisée en ce que
    le canal annulaire (32) a une largeur qui correspond sensiblement à deux jusqu'à trois fois le diamètre de buse.
  7. Soupape selon l'une des revendications 1 à 6,
    caractérisée en ce que
    le côté d'entrée est relié en aval à une zone de pression intérieure (22) et une zone de pression extérieure (20), ces zones de pression (20, 22) étant prévues en amont du siège de soupape (26),
    la zone de pression intérieure (22) comprenant un canal de pression axial de l'organe d'obturation de soupape (14) qui débouche sur la face frontale libre (24) de l'organe d'obturation de soupape (14) et l'autre zone de pression (20) entoure l'organe d'obturation de soupape (14).
  8. Soupape selon la revendication 7,
    caractérisée en ce que
    la zone de pression intérieure (22) est reliée à la zone de pression extérieure (20) par au moins un et de préférence quatre canaux de sortie (18A, 18B, 18C ; 42) réalisés dans l'organe d'obturation de soupape (14).
  9. Soupape selon la revendication 1,
    caractérisée en ce que
    l'élément d'étanchéité (52) comporte au moins une lèvre d'étanchéité (54, 55).
  10. Soupape selon l'une des revendications 1 à 9,
    caractérisée par
    un socle (44) servant de butée à l'organe d'obturation de soupape (14).
  11. Soupape selon la revendication 1,
    caractérisée en ce que
    la plaque d'étanchéité (28) comporte des jupes (46) pour pénétrer dans l'élément d'étanchéité (36).
EP03773481A 2002-10-26 2003-10-02 Soupape de commande d'un fluide Expired - Lifetime EP1561027B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07104186A EP1801410B1 (fr) 2002-10-26 2003-10-02 Soupape de commande d'un fluide

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10249963 2002-10-26
DE10249963 2002-10-26
DE10319920A DE10319920A1 (de) 2002-10-26 2003-05-05 Ventil zum Steuern eines Fluids
DE10319920 2003-05-05
PCT/DE2003/003275 WO2004040125A1 (fr) 2002-10-26 2003-10-02 Soupape de commande d'un fluide

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP07104186A Division EP1801410B1 (fr) 2002-10-26 2003-10-02 Soupape de commande d'un fluide

Publications (2)

Publication Number Publication Date
EP1561027A1 EP1561027A1 (fr) 2005-08-10
EP1561027B1 true EP1561027B1 (fr) 2008-03-26

Family

ID=32231861

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03773481A Expired - Lifetime EP1561027B1 (fr) 2002-10-26 2003-10-02 Soupape de commande d'un fluide

Country Status (3)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11346307B2 (en) 2016-08-31 2022-05-31 Vitesco Technologies GmbH Fluid injector and needle for a fluid injector
EP4671575A1 (fr) * 2024-06-25 2025-12-31 SVM Schultz Verwaltungs-GmbH & Co. KG Soupape de régulation de débit et procédé

Families Citing this family (7)

* 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
DE102012204565A1 (de) * 2012-03-22 2013-09-26 Robert Bosch Gmbh Proportionalventil mit verbessertem Dichtsitz
DE102013204152A1 (de) * 2013-03-11 2014-09-11 Robert Bosch Gmbh Ventil zum Steuern eines Fluids mit erhöhter Dichtheit
WO2015138425A2 (fr) 2014-03-10 2015-09-17 G.W. Lisk Company, Inc. Soupape d'injecteur
US10364758B2 (en) 2016-12-20 2019-07-30 Continental Powertrain, USA, LLC High pressure gas phase injector
DE102017210362B4 (de) * 2017-06-21 2024-07-04 Robert Bosch Gmbh Proportionalventil zum Steuern eines gasförmigen Mediums

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19523915A1 (de) * 1995-06-30 1997-01-02 Bosch Gmbh Robert Mikroventil und Verfahren zur Herstellung eines Mikroventils

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8630686D0 (en) * 1986-12-23 1987-02-04 Lucas Ind Plc Fuel injector
DE3943005A1 (de) * 1988-12-28 1990-07-05 Hitachi Ltd Elektromagnetische einspritzventilvorrichtung
US6766969B2 (en) * 2000-09-13 2004-07-27 Delphi Technologies, Inc. Integral valve seat and director for fuel injector

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19523915A1 (de) * 1995-06-30 1997-01-02 Bosch Gmbh Robert Mikroventil und Verfahren zur Herstellung eines Mikroventils

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11346307B2 (en) 2016-08-31 2022-05-31 Vitesco Technologies GmbH Fluid injector and needle for a fluid injector
EP4671575A1 (fr) * 2024-06-25 2025-12-31 SVM Schultz Verwaltungs-GmbH & Co. KG Soupape de régulation de débit et procédé

Also Published As

Publication number Publication date
EP1561027A1 (fr) 2005-08-10
DE50309492D1 (de) 2008-05-08
WO2004040125A1 (fr) 2004-05-13

Similar Documents

Publication Publication Date Title
EP1801410B1 (fr) Soupape de commande d'un fluide
DE602005000662T2 (de) Einspritzventil einer Brennkraftmaschine
EP1579137B1 (fr) Soupape pour la regulation d'un fluide
EP2171255B1 (fr) Étranglement au niveau du pointeau d'une soupape d'injection de carburant pour moteurs à combustion interne
DE69918902T2 (de) Brennstoffinjektor
EP0976013B1 (fr) Soupape de reglage de pression
WO2019016398A1 (fr) Injecteur pour l'injection de carburant
DE10214096B4 (de) Kraftstoffeinspritzvorrichtung
EP1561027B1 (fr) Soupape de commande d'un fluide
EP2470771B1 (fr) Injecteur de carburant
EP1126160B1 (fr) Injecteur pour injecter du carburant dans un moteur à combustion interne
DE10100390A1 (de) Einspritzventil
EP1335128A2 (fr) Soupape hydraulique à haute pression, notamment pour un dispositif d'injection de carburant d'un moteur
EP3446006A1 (fr) Soupape de fermeture et d'ouverture d'un système de conduites
DE102008002153A1 (de) Kraftstoff-Injektor
EP1073836B1 (fr) Ensemble buse pour le dosage de liquides ou de gaz
EP1558865B1 (fr) Vanne a gaz
EP2630361B1 (fr) Injecteur de carburant
EP1574701A1 (fr) Injecteur de common rail
EP4487053B1 (fr) Soupape d'arrêt et système de réservoir d'hydrogène comprenant une soupape d'arrêt
WO2001057394A1 (fr) Soupape d'injection de carburant pour moteurs a combustion interne
DE102013212142A1 (de) Düsenbaugruppe für einen Kraftstoffinjektor sowie Kraftstoffinjektor
DE102004048604A1 (de) Ventil für insbesondere gasförmige Medien
DE10059009A1 (de) Brennstoffeinspritzanlage
DE102007018005A1 (de) Injektor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050527

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB

17Q First examination report despatched

Effective date: 20060209

17Q First examination report despatched

Effective date: 20060209

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50309492

Country of ref document: DE

Date of ref document: 20080508

Kind code of ref document: P

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20081230

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20161025

Year of fee payment: 14

Ref country code: GB

Payment date: 20161025

Year of fee payment: 14

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20171002

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180629

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171002

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171031

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20221215

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 50309492

Country of ref document: DE