WO2019011973A1 - Injection de carburant et système d'injection conçu pour un moteur à combustion interne - Google Patents

Injection de carburant et système d'injection conçu pour un moteur à combustion interne Download PDF

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Publication number
WO2019011973A1
WO2019011973A1 PCT/EP2018/068762 EP2018068762W WO2019011973A1 WO 2019011973 A1 WO2019011973 A1 WO 2019011973A1 EP 2018068762 W EP2018068762 W EP 2018068762W WO 2019011973 A1 WO2019011973 A1 WO 2019011973A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve member
fuel
chamber
fuel injector
swirling means
Prior art date
Application number
PCT/EP2018/068762
Other languages
German (de)
English (en)
Inventor
Enrico Bärow
Ingmar Berger
Original Assignee
L'orange 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 L'orange Gmbh filed Critical L'orange Gmbh
Publication of WO2019011973A1 publication Critical patent/WO2019011973A1/fr

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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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • F02M21/0257—Details of the valve closing elements, e.g. valve seats, stems or arrangement of flow passages
    • F02M21/026—Lift valves, i.e. stem operated valves
    • F02M21/0263—Inwardly opening single or multi nozzle valves, e.g. needle valves
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • F02M21/0275—Injectors for in-cylinder direct injection, e.g. injector combined with spark plug
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

Definitions

  • the invention relates to a fuel injector with an axially displaceably mounted valve member and a housing body, which has a valve member guide, in which the valve member is at least partially received. Moreover, the invention relates to an injection system for an internal combustion engine which has such a fuel injector.
  • sealing fluid also called barrier fluid
  • barrier fluid By means of a sealing fluid (also called barrier fluid), which is introduced under high pressure into the housing body of such a fuel injector, the valve member guide of the fuel injector can be sealed.
  • sealing the valve member guide by means of the sealing fluid can be prevented, for example, that fuel from a connected to the valve member guide fuel chamber of the fuel injector Uber the Ventilgliedschreibung can penetrate into other areas of the fuel injector, in which presence of the fuel could affect the operability of the fuel injector , For this, however, the sealing fluid pressure must be above the fuel pressure.
  • leakage flow Between the valve member and a wall of the Ventilgliedschreibung can form an unwanted sealing fluid flow (hereinafter referred to as leakage flow). Due to the high pressure of the sealing fluid in comparison to the fuel pressure, as a result of such a leakage flow, an undesired entry of the sealing fluid into the fuel chamber may occur, so that the fuel is mixed with the sealing fluid in the fuel chamber. If no injection of the fuel into an injection volume, such as a combustion chamber of an internal combustion engine, occurs for a long time, the fuel chamber may fill with the sealing fluid so much that mainly or exclusively the sealing fluid is ejected from the fuel chamber in the next injection process.
  • an injection volume such as a combustion chamber of an internal combustion engine
  • the sealing fluid may optionally penetrate into other areas of the fuel injector in which the presence of the sealing fluid may adversely affect the operability of the fuel injector.
  • An object of the invention is to avoid or at least reduce adverse effects of using a sealing fluid on fuel injection.
  • the fuel injector according to the invention has an axially displaceably mounted valve member as well as a housing body.
  • the housing body includes a valve member guide in which the valve member is at least partially received.
  • the fuel injector according to the invention comprises at least one swirling means for swirling a leakage flow of a sealing fluid through the valve member guide for sealing the valve member guide.
  • the invention is based on the recognition that by a turbulence of the flowing through the valve member guide leakage flow whose mass flow can be reduced. In this way, the amount of sealing fluid can be reduced, which flows as a result of the leakage flow within a predetermined period of time in a region of the fuel injector, in which the sealing fluid may possibly affect the functioning of the fuel injector.
  • the reduction of the mass flow of the leakage flow flowing through the valve member guide as a result of the swirling of the leakage flow is due to the fact that the swirl increases the flow resistance for the leakage flow.
  • the fuel injector may in particular be a fuel gas injector. Accordingly, the fuel to be injected by the fuel injector into an injection volume may be a gaseous fuel (fuel gas).
  • the fuel may be natural gas, hydrogen, or other combustible gas or contain at least one of these gases.
  • the fuel injector may be a liquid fuel injector.
  • the fuel to be injected from the fuel injector into the injection volume may be a liquid fuel.
  • the liquid fuel for example, methanol or a mixture containing methanol may be used.
  • the fuel injector can be designed as a so-called single-fuel injector.
  • the fuel injector may be an element of a so-called dual-fuel injector unit.
  • the swirling means is preferably configured to reduce an effective flow cross section of the leakage flow. By reducing the effective flow area of the leakage flow, the swirling means can cause an increase in the flow resistance for the leakage flow.
  • the swirling means may be further configured to transform a portion of the leakage flow into a sealing fluid vortex having a radial flow component.
  • a sealing fluid vortex can cause a reduction in the effective flow cross section of the leakage flow, in particular by a superposition of the sealing fluid vortex with a subsequent part of the leakage flow.
  • the valve member is a fluid-operated valve member.
  • the housing body of the fuel injector may include a control chamber for receiving a control fluid for controlling a position of the valve member.
  • the control fluid used to control the position of the valve member may be, for example, a liquid fuel, particularly diesel fuel, or may contain a liquid fuel.
  • the sealing fluid used to seal the valve member guide may be, for example, oil or contain oil.
  • a liquid fuel or a mixture containing a liquid fuel can be used.
  • the control fluid and the sealing fluid may be the same fluid.
  • the valve member is designed as a nozzle needle. Furthermore, it can be provided that the valve member has a piston portion.
  • the piston portion of the valve member is preferably disposed in the control chamber and divides the control chamber volume variable into two control chambers.
  • the fuel injector may have a sealing chamber for receiving the sealing fluid.
  • the sealing chamber is connected to the valve member guide.
  • the sealing chamber can open into the valve member guide.
  • the sealing chamber is preferably a component of the housing body. Alternatively, the sealing chamber may be a part of the valve member.
  • the housing body may have a fuel chamber for receiving a fuel to be ejected from the housing body.
  • the fuel chamber is connected to the valve member guide.
  • the fuel chamber can in particular open into the valve member guide.
  • the housing body may have one or more nozzle openings, via which the fuel chamber is connected to the surroundings of the fuel injector. It is preferred if the sealing chamber is arranged between the fuel chamber and the control chamber. Further, it is preferable if the swirling means is arranged between the fuel chamber and the control chamber.
  • the swirling means may for example be arranged between the sealing chamber and the control chamber. In this way, the amount of sealing fluid flowing into the control chamber within a predetermined period of time can be reduced.
  • the swirling means is arranged between the sealing chamber and the fuel chamber.
  • valve member need not necessarily be a fluid operated valve member.
  • valve member may be an electromagnetically actuated valve member.
  • valve member has the swirling agent.
  • valve member guide may comprise the swirling means.
  • the swirling means is formed as a recess, in particular as an annular recess.
  • a recess is to be realized in terms of production technology and allows effective swirling of the leakage flow.
  • the recess has an axial symmetry with respect to the longitudinal axis of the valve member.
  • a longitudinal axis of the valve member can be understood to be an axis extending in the longitudinal direction of the valve member through its center of mass.
  • the recess may have an angular cross-sectional area, in particular a triangular cross-sectional area or a rectangular cross-sectional area.
  • the recess may have a rounded cross-sectional area.
  • the fuel injector comprises a plurality of swirling means of the type described above, which each serve to swirl the flowing through the valve member guide leakage flow of the sealing fluid.
  • the fuel injector may, for example, comprise at least three swirling agents, preferably at least five swirling agents, more preferably at least eight swirling agents.
  • the swirling means are arranged one behind the other in the axial direction of the valve member guide.
  • the swirling means can be arranged equidistantly or at different distances from each other.
  • the plurality of swirling means may be elements of the valve member guide or the valve member.
  • the valve member guide of the housing body or the valve member may include the plurality of swirling means.
  • both the valve member and the valve member guide each have at least one of the swirling means.
  • each of the swirling means is formed as a recess.
  • the swirling means may be of similar shape and / or size. That is, the swirling means may have the same shape and / or the same size.
  • adjacent swirling means are at such a distance from one another that a partial flow of the leakage flow, which is deflected at an edge of one of the swirling means in a direction oriented obliquely to the axial direction of the valve member guide, overlaps with one of the next swirling means generated sealing fluid vortex is still oriented obliquely to the axial direction of the valve member guide.
  • the distance between adjacent swirling means is preferably selected such that a partial flow of the leakage flow, which is deflected at an edge of one of the swirling means and oriented by this deflection obliquely to the axial direction, is still oriented obliquely to the axial direction, if a From the next following turbulence generated sealing fluid vortex meets the deflected partial flow.
  • a greater reduction in the effective flow cross-sectional leakage flow can be effected by the swirling means compared to the case where adjacent swirling means have such a large distance to each other that the diverted partial flow is able to assume an axial alignment before them the sealing fluid vortex generated next to the following turbulence means.
  • the distance that adjacent turbulence means have relative to one another is less than half, in particular less than a quarter, of the maximum axial extent of the respective turbulence means.
  • the maximum axial extent of a swirling means is understood to mean its maximum extent in the axial direction of the valve member guide.
  • the spacing of adjacent swirling means may be less than 0.5 mm.
  • the fuel injector has at least one swirling means of the type described above between the control chamber and the sealing chamber, in particular a plurality of swirling means arranged one behind the other in the axial direction of the valve member guide, and at least one swirling means between the fuel chamber and the sealing chamber described type, in particular a plurality of in the axial direction of the valve member guide successively arranged swirling means of the type described above, having.
  • the invention also relates to an injection system for an internal combustion engine.
  • the injection system according to the invention comprises at least one fuel injector according to the invention.
  • the injection system comprises a plurality of fuel injectors, in particular a plurality of fuel injectors according to the invention. These may in particular be connected to a common fuel distribution line of the injection system.
  • the injection system may have one or more further elements, such as a control device for controlling the fuel injector or the fuel injectors.
  • a control device for controlling the fuel injector or the fuel injectors.
  • FIG. 1 shows a schematic representation of an injection system comprising several fuel injectors for an internal combustion engine
  • Fig. 2 is a longitudinal sectional view of one of the fuel injectors of Fig. 1;
  • 3a-3e are sectional views of various embodiments of Verwirbe- means of the fuel injector of Fig. 2;
  • FIGS. 4a-4e representations of the mode of operation of the swirling means from FIGS. 3a-3e
  • Fig. 5 is an illustration of the operation of two adjacent swirling means, which have a large distance from each other;
  • Fig. 6 is an illustration of the operation of two adjacent Verwirbelungsstoff having a small distance from each other.
  • Fig. 1 shows a schematic representation of an injection system 2, which comprises a plurality of identical fuel injectors 4, which are each used to inject a fuel in the same combustion chamber or in different combustion chambers of an internal combustion engine.
  • the injection system 2 comprises a fuel delivery pump 6 and a fuel accumulator 8, in which the fuel to be injected by the fuel injectors 4 into the combustion chamber or into the combustion chambers is stored.
  • the fuel is a gaseous fuel.
  • the injection system 2 comprises a fuel distribution line 10, to which the fuel injectors 4 are connected each Weil by means of a fuel supply line 12.
  • the fuel distribution line 10 is in particular a so-called common rail.
  • Said fuel delivery pump 6 is connected on the output side via a first connecting line 14 to the fuel distribution line 10. On the input side, the fuel delivery pump 6 is connected via a second connecting line 16 to the fuel reservoir 8.
  • the injection system 2 comprises a control unit 18 for controlling the fuel injectors 4 and for controlling the fuel delivery pump 6.
  • a control unit 18 for controlling the fuel injectors 4 and for controlling the fuel delivery pump 6.
  • Each of the fuel injectors 4 and the fuel delivery pump 6 are each connected via an electrical control line 20 to the control unit 18.
  • the fuel delivery pump 6 conveys the fuel from the fuel reservoir 8 to the fuel distribution line 10.
  • the control unit 18 controls the fuel injectors 4 such that the fuel injectors 4 at predetermined injection times the fuel into the combustion chamber or into the combustion chambers inject.
  • FIG. 2 shows by way of example a longitudinal sectional illustration of one of the fuel injectors 4 from FIG. 1.
  • the fuel injector 4 comprises a valve member 22 (also called shut-off body) designed as a nozzle needle and a housing body 24.
  • the housing body 24 is designed in two parts and comprises a first housing element 24a and a second housing element 24b.
  • the housing body 24, more particularly its first housing element 24a, comprises a valve member guide 26.
  • the valve member 22 is received in the valve member guide 26 with radial play.
  • the valve member 22 is mounted axially displaceably in the valve member guide 26. That is, the valve member 22 is slidably disposed in the Ventilgliedmay- tion 26 along its longitudinal axis 28. In the present case, the valve member 22 is thus displaceable in and opposite to the axial direction 30 of the valve member guide 26.
  • the valve member 22 is operable with a control fluid. That is, the position of the valve member 22 is controllable by means of a control fluid.
  • a control fluid diesel fuel is used in the present example.
  • the first housing member 24a of the housing body 24 further includes a control chamber 32 for receiving a control fluid provided for controlling the position of the valve member 22 and a fuel chamber 34 for receiving the fuel. Furthermore, the first housing element 24a comprises a first sealing chamber 36 arranged between the fuel chamber 34 and the control chamber 32 for receiving a sealing fluid.
  • the control chamber 32, the fuel chamber 34 and the first seal chamber 36 are connected to each other through the valve member guide 26.
  • the first housing element 24a of the housing body 24 has a plurality of nozzle openings 38 (also called injection openings) through which the fuel from the fuel chamber 34 can be injected into a combustion chamber.
  • valve member 22 has a shaft portion 40 and a piston portion 42 integrally formed with the shaft portion 40.
  • the piston section 42 of the valve member 22 is arranged in the control chamber 32 and subdivides these variable in volume into a first control chamber 44 closer to the nozzle openings 38 and a second control chamber 46 farther from the nozzle openings 38, the two control chambers 44, 46 being replaced by a sealing element 48 is inserted into a groove of the piston portion 42, are sealed from each other.
  • the second housing element 24b partially covers the control chamber 32 and has a second sealing chamber 52 for receiving a sealing fluid.
  • the fuel injector 4 comprises a biasing means 54 which is formed in the present embodiment as a compression spring, and a stilt 56 with a collar 58.
  • the biasing means 54 abuts the collar 58 of the stilt 56 and pushes the stilt 56 against the valve member 22nd
  • the fuel injector 4 comprises a stop element 60 for limiting movement of the stilt 56.
  • the fuel injector 4 is equipped with an electrically controllable control valve 62, which can be controlled by the control unit 18 of the injection system 2 (see FIG. 1), the control valve 62 being connected via its electrical connection 64 to one of the electrical control circuits 20 of FIG. 1 is connectable.
  • the two control chambers 44, 46, into which the control chamber 32 is divided by the piston section 42 of the valve member 22, are each connected via a control flow line 66 to the control valve 62.
  • the control valve 62 also has Uber a high-pressure side control fluid port 68 and a low-pressure side control fluid port 70, the control valve 62 is connected via its high-pressure side control fluid port 68 to a high pressure side of a figured not shown Steuerfluid Vietnameselaufs the injection system 2 and hisipposeiti- gene control fluid port 70 with a low pressure side of the Control fluid circuit of the injection system 2 is connectable.
  • the fuel injector 4 has a fuel port 72, by means of which the fuel chamber 34 can be connected to one of the fuel supply lines 12 from FIG. 1, and a sealing fluid port 74, through which the two sealing chambers 36, 52 with a sealing fluid source of the injection system 2, not shown in FIG can be connected, wherein the two sealing chambers 36, 52 are each connected by means of a sealing fluid line 76 with the sealing fluid port 74.
  • the fuel is introduced into the fuel chamber 34 via the fuel connection 72.
  • a sealing fluid is introduced into the first sealing chamber 36 via the sealing fluid port 74 and the sealing fluid pressure in the first sealing chamber 36 is maintained above the fuel pressure in the fuel chamber 34.
  • the higher sealing fluid pressure compared to the fuel pressure causes an unintentional entry of sealing fluid into the fuel chamber 34.
  • the respective control chamber 44, 46 is supplied depending on the position of the control valve 62 with a high pressure control fluid or relieved to the low pressure side of the control fluid circuit.
  • the control valve 62 which is actuated by the control unit 18 of the injection system 2, the position of the valve member 22 is influenced. via a control of the control fluid pressure in the respective control chamber 44, 46.
  • the force exerted by the control fluid in total on the piston portion 42 of the valve member 22 is opposite to the force exerted by the biasing means 54 on the valve member 22 by means of the stalk 56, but less in magnitude than that of the biasing means 54 by means of the stalk 56 on the valve member 22 applied force, the valve member 22 is pressed against a sealing surface 78 of the first housing member 24 a. This prevents the fuel from the fuel chamber 34 from reaching the nozzle openings 38 of the first housing element 24a.
  • the control fluid 62 increases the control fluid pressure in the first control chamber 44 and at the same time increases the control fluid pressure in the second control chamber 46 reduced until the force exerted by the control fluid in total on the piston portion 42 of the valve member 22 magnitude exceeds the force exerted by the biasing means 54 by means of the stilt 56 on the valve member 22 force.
  • the first control chamber 44 is supplied from the high pressure side of the control fluid circuit with high pressure control fluid, while the second control chamber 46 is relieved to the low pressure side of the control fluid circuit. In this way, the valve member 22 is removed from the sealing surface 78 of the first housing member 24 a, so that the fuel from the fuel chamber 34 can flow to the nozzle openings 38.
  • control fluid 62 reduces the control fluid pressure in the first control chamber 44 and at the same time increases the control fluid pressure in the second control chamber 46 so that the valve member 22 bears against the sealing surface 78 of the first housing member 24a is pressed.
  • the second control chamber 46 is supplied from the high-pressure side of the control fluid circuit with high-pressure control fluid, while the first control chamber 44 is relieved to the low-pressure side of the control fluid circuit.
  • FIG. 3a shows a sectional representation of a possible embodiment variant of the fuel injector 4 from FIG. 2.
  • the sectional representation shown in FIG. 3a is an enlarged representation of the section 80 of the fuel injector 4 indicated by a dotted rectangle in FIG ,
  • the valve member 22 between the first sealing chamber 36 and the fuel chamber 34 a plurality of swirling means 82 which are arranged in the axial direction 30 of the valve member guide 26 equidistant behind the other.
  • the Verwirbe- means 82 are each formed as an annular circumferential recess and all have the same shape and the same size.
  • the swirling means 82 have an axial symmetry with respect to the longitudinal axis 28 of the valve member 22.
  • the swirling means 82 each serve to swirl a leakage flow of the sealing fluid flowing through the valve member guide 26 from the first seal chamber 36 to the fuel chamber 34 to increase the flow resistance for the leakage flow and thus reduce the mass flow of the leakage flow.
  • the recesses forming the swirling means 82 each have a triangular cross-sectional area. More specifically, the cross-sectional area of each swirler 82 corresponds to an isosceles triangle.
  • FIGS. 3 b to 3 e show sectional views of other possible embodiments of the swirling means 82 of the fuel injector 4.
  • the swirling means 82 each have a rectangular cross-sectional area instead of a triangular cross-sectional area. whereas in the design variant from FIG. 3c, the swirling means 82 each have a rounded cross-sectional area instead of a triangular cross-sectional area.
  • the swirling means 82 each have a triangular cross-sectional area as in the embodiment variant from FIG. 3a.
  • the respective cross-sectional area of the swirling means 82 of FIG. 3d does not correspond to an isosceles triangle, but to an irregular triangle.
  • the swirling means 82 of the valve member guide 26 each have, by way of example, the same cross-sectional area as in the embodiment variant from Fig. 3a.
  • the cross-sectional area of the respective swirling means 82 of the valve member guide 26 may have another of the aforementioned shapes.
  • the shapes of the cross-sectional areas of the swirling means 82 are not limited to those described or illustrated in FIGS. 3a to 3e. That is, the cross-sectional areas of the swirling means 82 may each have other shapes than those described or illustrated.
  • FIG. 4 a exemplarily illustrates one of the swirling means 82 from FIG. 3 a of its mode of action.
  • the leakage flow 84 of the sealing fluid which flows in a gap between the valve member 22 and a wall of the valve member guide 26 from the first sealing chamber 36 to the fuel chamber 34, is shown symbolically in the form of an arrow indicating the flow direction of the leakage flow 84 , Furthermore, the axial direction 30 of the valve member guide 26 is shown in FIG. 4 a.
  • the leakage flow 84 flows in the direction of the fuel chamber 34 as an axial flow, that is, in the axial direction 30 of the valve member guide 26.
  • the effective flow cross section of the leakage flow 84 is defined by the distance 86 between the valve member 22 and the valve member guide 26 specified.
  • the effective flow cross-section of the leakage flow 84 corresponds to the geometric flow cross-section defined by the distance 86 between the valve member 22 and the valve member guide 26.
  • part of the leakage flow 84 flows into the swirling means 82 and is transformed by the swirling means 82 into a sealing fluid swirl 88 with a radial flow component.
  • the sealing fluid vortex 88 strikes with radially outwardly directed alignment on a subsequent part of the leakage flow 84 and overlaps with the subsequent part of the leakage flow 84.
  • This causes a reduction of the effective flow cross section of the leakage flow 84, which leads to an increase of the flow resistance for the Leakage flow 84 leads.
  • the reduction of the effective flow cross section is shown in Fig. 4a by the illustration
  • the radial width 90 of the effective flow cross section in the region of the swirling agent 82 illustrated.
  • FIGS. 5 and 6 each illustrate the operation of two adjacent swirling means 82 of the fuel injector 4 at different distances 92 between the adjacent swirling means 82.
  • the cross-sectional area of the respective swirling means 82 is merely illustrative of a triangular shape. The following
  • Embodiments also apply to other cross-sectional shapes of the swirling means 82.
  • Swirling means 82 which is closest to this sealing chamber 36 is referred to as the first swirling means 82, while the next swirling means 82 is referred to as the second swirling means 82.
  • a partial flow 94 of the leakage flow 84 is deflected at an edge 96 of the first swirling means 82 in an obliquely oriented to the axial direction 30 of the VentilgliedfUhrung 26 direction.
  • the distance 92 of the adjacent swirling means 82 is so great that the partial flow 94 diverted at the edge of the first swirling means 82 still remains
  • the adjacent swirling means 82 have such a distance 92 from each other. that the partial flow 94 deflected at the edge 96 of the first swirling means 82 fails to assume an axial orientation upstream of the second swirling means 82, so that the partial flow 94 is oriented obliquely to the axial direction 30 of the valve member guide 26, if one generated in the second swirling means 82 Seal fluid vortex 88 meets the partial flow 94.
  • the second swirling means 38 (and the subsequent swirling means 82) causes a greater reduction in the effective flow area than by the first swirling means 82. This is illustrated in FIG.
  • the radial width 90 of the effective flow area of the leakage flow 84 is in the range of the second swirling agent 82 is smaller than the radial width 90 of the effective flow cross section of the leakage flow 84 in the region of the first swirling agent 82.
  • the greater flow cross-section reduction in the region of the second swirling agent 82 (and in the region of the subsequent swirling means 82) results in the region of the second swirling agent 82 (FIG. and the subsequent swirling means 82) to a larger flow resistance for the leakage flow 84th
  • the spacing 92 of adjacent swirling means 82 in the embodiment of FIG. 6 corresponds to approximately 10% of the maximum axial extent 98 of the respective swirling means 82.
  • valve member guide 26 or the valve member 22 of the fuel injector 4 of Fig. 2 between the control chamber 32 and the first sealing chamber 36 a plurality of axially disposed in the axial direction 30 of the valve member guide 26 successively Verwirbelungsstoff 82 have.
  • These swirling means 82 serve to swirl a leakage flow passing through the valve member guide 26 from the first seal chamber 36 to the control chamber 32 to increase the flow resistance for this leakage flow and thus reduce the mass flow of this leakage flow.
  • These swirling means 82 may be, for example, as in any of the embodiments described in connection with FIGS. 3a to 6. be trained.
  • the sectional views depicted in FIGS. 3 a to 3 e can thus also be regarded as enlarged representations of possible design variants of the section 100 of the fuel injector 4 indicated by a dotted rectangle in FIG. 2.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un injecteur de carburant (4), comprenant un obturateur (22) monté coulissant axialement ainsi qu'un corps (24) de carter pourvu d'un guidage (26) d'obturateur dans lequel l'obturateur (22) est logé au moins en partie. Selon l'invention, l'injecteur de carburant (4) comporte au moins un moyen de tourbillonnement (82) destiné à faire tourbillonner un écoulement de fuite (84) d'un fluide d'étanchéité destiné à étanchéifier le guidage (26) d'obturateur, lequel écoulement circule à travers le guidage (26) d'obturateur. L'invention concerne en outre un système d'injection (2) pour un moteur à combustion interne, lequel système présente ledit injecteur de carburant (4).
PCT/EP2018/068762 2017-07-12 2018-07-11 Injection de carburant et système d'injection conçu pour un moteur à combustion interne WO2019011973A1 (fr)

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EP1156209A2 (fr) * 2000-05-19 2001-11-21 Siemens Aktiengesellschaft Dispositif de guidage pour systèmes hydrauliques à haute pression
DE102007004252A1 (de) * 2006-01-24 2007-07-26 General Electric Co. Kraftstoffinjectionsvorrichtung
DE102011051904A1 (de) * 2011-07-18 2012-06-21 L'orange Gmbh Vorrichtung mit in einer Führungsbahn längsverschieblicher Hubstange
EP2824311A1 (fr) * 2013-07-10 2015-01-14 EFI Hightech AG Agencement d'un élément de piston et injecteur doté d'un agencement d'élément de piston
DE102015016034B3 (de) * 2015-12-11 2017-03-02 L'orange Gmbh Kraftstoffinjektoranordnung

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DE4139907A1 (de) * 1991-12-04 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De Hochdruckkraftstoffeinspritzeinrichtung
DE10102234A1 (de) * 2001-01-19 2002-07-25 Bosch Gmbh Robert Vorrichtung zur Kraftstoff-Hochdruckversorgung einer Brennkraftmaschine

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EP1156209A2 (fr) * 2000-05-19 2001-11-21 Siemens Aktiengesellschaft Dispositif de guidage pour systèmes hydrauliques à haute pression
DE102007004252A1 (de) * 2006-01-24 2007-07-26 General Electric Co. Kraftstoffinjectionsvorrichtung
DE102011051904A1 (de) * 2011-07-18 2012-06-21 L'orange Gmbh Vorrichtung mit in einer Führungsbahn längsverschieblicher Hubstange
EP2824311A1 (fr) * 2013-07-10 2015-01-14 EFI Hightech AG Agencement d'un élément de piston et injecteur doté d'un agencement d'élément de piston
DE102015016034B3 (de) * 2015-12-11 2017-03-02 L'orange Gmbh Kraftstoffinjektoranordnung

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