EP1671028B1 - Ventil zur steuerung einer verbindung in einem hochdruckflüssigkeitssystem, insbesondere einer kraftstoffeinspritzeinrichtung für eine brennkraftmaschine - Google Patents

Ventil zur steuerung einer verbindung in einem hochdruckflüssigkeitssystem, insbesondere einer kraftstoffeinspritzeinrichtung für eine brennkraftmaschine Download PDF

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Publication number
EP1671028B1
EP1671028B1 EP04762589A EP04762589A EP1671028B1 EP 1671028 B1 EP1671028 B1 EP 1671028B1 EP 04762589 A EP04762589 A EP 04762589A EP 04762589 A EP04762589 A EP 04762589A EP 1671028 B1 EP1671028 B1 EP 1671028B1
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EP
European Patent Office
Prior art keywords
valve
valve member
longitudinal axis
sealing surface
pressure chamber
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
EP04762589A
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German (de)
English (en)
French (fr)
Other versions
EP1671028A1 (de
Inventor
Nestor Rodriguez-Amaya
Christoph Hollmann
Michael Mennicken
Matthias Beck
Hubert Greif
Falk-Alexander Petry
Thilo Rzymann
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1671028A1 publication Critical patent/EP1671028A1/de
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Publication of EP1671028B1 publication Critical patent/EP1671028B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion

Definitions

  • the invention relates to a valve for controlling a connection in a high-pressure fluid system, in particular a fuel injection device of an internal combustion engine, according to the preamble of claim 1.
  • valve is through the US 6,364,282 B known.
  • This valve is for controlling a connection in a fuel injection device for an internal combustion engine.
  • the valve has a valve member, which is displaceably guided in the direction of its longitudinal axis and which projects into a valve pressure chamber in which at least temporarily high pressure prevails.
  • the valve member has in the valve pressure chamber on a transversely to its longitudinal axis extending end face on a sealing surface, with which it cooperates with a transverse to its longitudinal axis valve seat for at least substantially closing an opening surrounded by the valve seat relative to the valve pressure chamber.
  • a connection to a low-pressure region adjoins the opening, wherein the valve member has a pin projecting into the connection through which liquid flowing out of the valve pressure chamber is conducted in the case of valve member lifted off with its sealing surface from the valve seat, so that at least approximately none or only through this a small resultant force is exerted on the valve member in the direction of its longitudinal axis.
  • the sealing surface of the valve member and the valve seat are each formed conically with different cone angles and at lifted off with its sealing surface from the valve seat valve member results radially inwardly an increasing distance between the sealing surface and the valve seat. Therefore, the flow through the valve is not optimal.
  • a valve having the features of the preamble of claim 1 is also by the US 4 653 455 A known. Also in this valve, the sealing surface of the valve member and the valve seat are conical and at lifted off with its sealing surface from the valve seat valve member results in an approximately constant distance between the sealing surface and the valve seat. Therefore, even with this valve, the flow is not optimal.
  • FIG. 1 a fuel injection device for an internal combustion engine in a longitudinal section in a simplified representation with a
  • valve according to the invention with the features of claim 1 has the advantage that the flow through the valve is improved and an at least approximately cavitation-free liquid flow on the valve member and the valve seat is made possible along.
  • FIG. 2 in an enlarged view the valve in a longitudinal section according to a first embodiment not according to the invention
  • FIG. 3 a comparison with the first embodiment modified non-inventive embodiment of the valve
  • FIG. 4 the valve in a longitudinal section according to a first embodiment of the invention
  • FIG. 5 the valve according to the first embodiment with a liquid flow
  • FIG. 6 the valve according to a modified embodiment of the invention compared to the first embodiment.
  • FIG. 1 a fuel injection device for an internal combustion engine of a motor vehicle is shown.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the fuel injection device is designed for example as a so-called pump-nozzle unit and has for each cylinder of the internal combustion engine in each case a high-pressure fuel pump 10 and a fuel injection valve 12 connected thereto, which form a common structural unit.
  • the fuel injector may be formed as a so-called pump-line-nozzle system in which the high-pressure fuel pump and the fuel injection valve of each cylinder are arranged separately from each other and connected to each other via a line.
  • the fuel injection device can also be designed as a storage injection system, in which by means of a high-pressure pump fuel is conveyed into a memory to which at least one injector is connected, to which a control valve is angeorndet, which is designed as the valve 70 described below.
  • the valve 70 described below can also be used in a storage injection system in which a pressure booster is provided, which is preferably integrated near the injector or in the injector, wherein the Valve 70 is provided for controlling the pressure booster.
  • the high-pressure fuel pump 10 has a pump body 14 with a cylinder bore 16, in which a pump piston 18 is tightly guided, which is at least indirectly driven by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19 in a lifting movement.
  • the pump piston 18 defines in the cylinder bore 16 a pump working chamber 22, in which the delivery stroke of the pump piston 18 compresses fuel under high pressure.
  • the pump working chamber 22 is supplied with fuel from a fuel tank 24 of the motor vehicle.
  • the fuel injection valve 12 has a connected to the pump body 14 valve body 26 which may be formed in several parts, and in which an injection valve member 28 is guided longitudinally displaceably in a bore 30.
  • the valve body 26 At its end region facing the combustion chamber of the cylinder of the internal combustion engine, the valve body 26 has at least one, preferably a plurality of injection openings 32.
  • the injection valve member 28 has, at its end region facing the combustion chamber, an approximately conical sealing surface 34, for example, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the injection openings 32 are discharged.
  • annular space 38 is present between the injection valve member 28 and the bore 30 toward the valve seat 36, which merges in its end region remote from the valve seat 36 by a radial widening of the bore 30 into a pressure chamber 40 surrounding the injection valve member 28.
  • the injection valve member 28 has at the level of the pressure chamber 40 by a cross-sectional reduction on a pressure shoulder 42.
  • a prestressed closing spring 44 At the end remote from the combustion chamber of the injection valve member 28 engages a prestressed closing spring 44, through which the injection valve member 28th is pressed toward the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 of the valve body 26, which adjoins the bore 30.
  • a further bore 48 in which a control piston 50 is guided tightly, which is connected to the injection valve member 28.
  • the bore 48 forms a control pressure chamber 52, which is limited by the control piston 50 as a movable wall.
  • the control piston 50 is supported on the injection valve member 28 via a piston rod 51, which is smaller in diameter, and can be connected to the injection valve member 28.
  • the control piston 50 may be formed integrally with the injection valve member 28, but is preferably connected to the injection valve member 28 as a separate part for reasons of assembly.
  • a channel 60 to the pressure chamber 40 of the fuel injection valve 12.
  • a channel 62 leads to the control pressure chamber 52.
  • the control pressure chamber 52 is also a channel 64 connectable, which connects to a discharge space forms than can serve at least indirectly, the fuel tank 24 or another area in which a low pressure prevails.
  • a connection 66 leads to a discharge space, which is controlled by a first electrically actuated control valve 68.
  • the control valve 68 may, as in FIG. 1 may be formed as a 2/2-way valve.
  • the circuit of the control valve 68 between its two switching positions is effected by an actuator 69 which For example, it may be an electromagnet against a return spring.
  • a second electrically operated control valve 70 is provided for controlling the pressure in the control pressure chamber 52.
  • the second control valve 70 is designed as a 3/2-way valve, which can be switched between two switching positions. In a first switching position of the control valve 70 is connected by this the control pressure chamber 52 to the pump chamber 22 and separated from the discharge chamber 24 and in a second switching position of the control valve 70 is separated by this the control pressure chamber 52 from the pump working chamber 22 and connected to the discharge chamber 24.
  • a throttle point 63 is provided in the connection 64 of the control pressure chamber 52 with the discharge chamber 24, a throttle point 65 is provided.
  • the orifice 63 may be located in the connection 62 upstream of the control valve 70 or as in FIG FIG.
  • the control valve 70 has an actuator 71, which may be an electromagnet, a piezoelectric actuator or a magnetostrictive actuator, and by means of which the control valve 70 can be switched over against a return spring between its two switching positions.
  • the two control valves 68,70 are controlled by an electronic control device 67.
  • the second control valve 70 will be described below with reference to FIG. 2 explained in more detail.
  • the control valve 70 has a valve member 72 which is displaceably guided in the direction of its longitudinal axis 73 via a shaft 74 and which protrudes into a valve pressure chamber 77 with an enlarged end portion 75 in diameter relative to the shaft 74.
  • the connection 62 opens to the pump working space 22 and on the other hand, the connection 64 to the relief space 24.
  • the connection 62 extends as a formed between the shaft 74 and a surrounding hole 76 annular gap.
  • the bore 76 is formed smaller in diameter than the valve pressure chamber 77.
  • the formed in the form of a channel or a bore connection 64 opens into an opening 78 in the valve pressure chamber 77 and is surrounded by a surface 79 which is transversely, preferably at least approximately perpendicular to the longitudinal axis 73 of the valve member 72 extends and forms a valve seat.
  • the valve member 72 has towards the valve seat 79 towards an at least approximately cylindrical projection 80, whose end face forms a sealing surface 81 which extends transversely, preferably at least approximately perpendicular to the longitudinal axis 73 of the valve member 72.
  • the boss 80 has a smaller diameter than the end portion 75 of the valve member 72, but the diameter of the boss 80 is greater than that of the aperture 78.
  • the sealing surface 81 extends as in FIG. 2 represented starting from the outer edge of the valve member 72 radially inwardly inclined so that the distance between the latter and the valve seat 79 in the direction of the longitudinal axis 73 of the valve member 72 increases. On the sealing surface 81, a narrow sealing edge is thereby formed at the outer edge thereof, with which the sealing surface 81 comes into contact with the valve seat 79.
  • bore 64 protruding pin 83 is arranged, which is preferably integrally formed on the valve member 72. The diameter of the bore 64 can then be increased to the opening 78, as in FIG. 2 is shown.
  • the pin 83 is designed in such a way that the fuel flowing out of the valve pressure chamber 77 when the control valve 70 is open is diverted in such a way that at least substantially no or only a small resultant force in the direction thereof is present the longitudinal axis 73 is exerted on the valve member 72.
  • the pin 83 extends in the direction of the longitudinal axis 73 of the valve member 72 to the level of the sealing surface 81. The transition from the inner edge of the sealing surface 81 to the pin 83 extends as in FIG. 2 shown rounded.
  • the pin 83 By means of the pin 83, the fuel flowing out of the valve pressure chamber 77, which initially flows approximately radially inward along the sealing surface 81, is diverted in such a way that it then flows into the bore 64 approximately in the direction of the longitudinal axis 73 of the valve member 72.
  • the fuel flow is thus initially deflected by the pin 83 by about 90 °.
  • the pin 83 has to its projecting into the bore 64 end toward a thickening 84, so that there the fuel flow is deflected again and this at an angle ⁇ inclined to the longitudinal axis 73 of the valve member 72 extends away from this.
  • the angle ⁇ can be between greater than 0 ° and about 90 ° or even more than 90 °.
  • the pin 83 may have between its thickening 84 and the sealing surface 81 has a circumferential annular groove 85 through which in the direction of the longitudinal axis 73 of the valve member 72 facing side surfaces, the deflection of the fuel flow is effected. Due to the multiple deflection of the fuel flow at the side surfaces of the annular groove 85, the forces caused during the deflection on the valve member 72 in the direction of its longitudinal axis 73 at least approximately equal, so that on the valve member 72 a total of at least approximately or only a small force in Direction of the longitudinal axis 73 is generated by the fuel flow.
  • the transitions between the side surfaces of the annular groove 85 to the bottom of the annular groove 85 and the circumference of the pin 83 are each rounded in order to minimize flow losses.
  • a conical transition surface 87 is provided, which forms a second valve seat.
  • a second conical sealing surface 88 which cooperates with the valve seat 87 for controlling the connection 62.
  • the valve member 72 In the second switching position of the control valve 70, the valve member 72 abuts with its second sealing surface 88 on the second valve seat 87, so that the connection 62 is separated to the pump working chamber 22.
  • the valve member 72 In the first switching position of the control valve 70, the valve member 72 is arranged with its second sealing surface 88 at a distance from the second valve seat 87, so that the connection 62 is open to the pump working chamber 22.
  • the valve member 72 abuts with its sealing surface 81 on the valve seat 79.
  • valve member 72 can be moved by the actuator 71 in a third switching position in which it is located between its two above-described switching positions.
  • valve member 72 By the valve member 72 while a connection of the valve pressure chamber 77 is released with the low-pressure region with a low flow cross-section, can flow only throttled on the fuel from the valve pressure chamber 77.
  • valve member 72 When arranged in its third switching position valve member 72 thus the pressure build-up in the control pressure chamber 52 is influenced such that in the control pressure chamber 52, a higher pressure prevails than arranged in its first switching position valve member 72, but a lower pressure prevails than in its second switching position arranged valve member 72nd
  • the control valve 70 is designed as a 3/3-way valve.
  • FIG. 3 is a modified non-inventive embodiment of the control valve 70 shown, in which the conical valve seat 87 and the conical sealing surface 88 of the valve member 72 omitted.
  • the valve member 72 is designed to control the connection 62 as a slide valve member.
  • the valve member 72 can be closed the connection 62 with its end portion 75 dive tight into the bore 76, whereby the connection 62 is closed.
  • the valve member 72 is dipped with its end portion 75 from the bore 76 and disposed in the valve pressure chamber 77, so the connection 62 is released.
  • FIG. 4 the control valve 70 is shown according to a first embodiment of the invention, in which the construction is substantially the same as in the embodiment according to FIG. 2
  • the formation of the sealing surface 81 is modified.
  • the formation of the pin 83 of the valve member 72 is the same as in the embodiment according to Figure 2
  • the sealing surface 81 is formed such that in an outer region 181, starting from its outer edge, it approaches the valve seat 79 radially inwards.
  • the region 181 of the sealing surface 81 is inclined at an angle ⁇ to a radial plane to the longitudinal axis 73 of the valve member 72, which is preferably at least approximately 5 °.
  • the region 181 of the sealing surface 81 has a radial extension 11, which is preferably about 0.3 mm with a diameter d of the valve member 72 of about 2.5 mm.
  • the sealing surface 81 is formed in a second region 281 adjoining its first region 181 in such a way that it is remote from the valve seat 79.
  • the second region 281 of the sealing surface 81 is inclined at an angle ⁇ to the radial plane, which is preferably at least approximately 2 °.
  • the second region 281 of the sealing surface 81 has a radial extent 12, which is preferably about 0.6 mm.
  • a flow inlet region is formed in its first region 181, in which the fuel flowing out of the valve pressure chamber 77 is introduced into the smallest flow cross section between the sealing surface 81 and the valve seat 79, and in its second region 281 a flow outlet region is formed in which the fuel is out the smallest flow cross-section is discharged.
  • the valve seat 79 is at least approximately flat as in the first embodiment and lies in a radial plane with respect to the longitudinal axis 73 of the valve member 72.
  • the transition from the shell of the projection 80 of the valve member 72 to the first region 181 of the sealing surface 81 is preferably rounded with a radius R, like this in FIG. 4 is shown.
  • valve member 72 according to the second embodiment becomes clear. While in the valve member 72 according to the first embodiment flow separations occur at the entrance of the flow in the narrowest flow area between the sealing surface 81 and the valve seat 79, such flow separation in the valve member 72 according to the second embodiment, or at least only to a lesser extent. As a result, the flow losses are reduced and it is achieved a cavitation-free flow.
  • the control valve 70 is shown in accordance with a modified embodiment compared to the first embodiment.
  • the sealing surface 81 on the valve member is at least approximately planar and lies in a radial plane with respect to the longitudinal axis 73 of the valve member 72.
  • the valve seat 79 is formed such that it in an outer region 179, starting from its outer edge radially inwardly of the sealing surface 81st approaches.
  • the region 179 of the valve seat 79 is inclined at an angle ⁇ to a radial plane to the longitudinal axis 73 of the valve member 72, which is preferably at least approximately 5 °.
  • the area 179 of the valve seat 79 has, starting from the outer edge of the sealing surface 81 of the valve member, a radial extent 11, which is preferably about 0.3 mm with a diameter d of the valve member 72 of about 2.5 mm.
  • the valve seat 79 is in a subsequent to the first region 179 second region 279 such formed so that it moves away from the sealing surface 81.
  • the second region 279 of the valve seat 279 is inclined at an angle ⁇ to the radial plane, which is preferably at least approximately 2 °.
  • the second region 279 of the valve seat 79 has a radial extension 12, which is preferably about 0.6 mm.
  • the fuel injector During the suction stroke of the pump piston 18, this fuel is supplied from the fuel tank 24.
  • the fuel injection begins with a pilot injection, wherein the first control valve 68 is closed by the control device 67, so that the pump working chamber 22 is separated from the discharge chamber 24.
  • the control device 67 also the second control valve 70 is brought into its second switching position, so that the control pressure chamber 52 is connected to the discharge chamber 24 and separated from the pump working chamber 22. In this case, no high pressure can build up in the control pressure chamber 52.
  • control unit makes the second Control valve 70 brought into its first switching position, so that the control pressure chamber 52 is separated from the discharge chamber 24 and connected to the pump working chamber 22.
  • the first control valve 68 remains in its closed position. High pressure builds up in the control pressure chamber 52 as in the pump working chamber 22, so that a large pressure force in the closing direction acts on the control piston 50 and the injection valve member 28 is moved into its closed position.
  • the second control valve 70 is brought by the control device 67 in its second switching position, so that the control pressure chamber 52 is connected to the discharge chamber 24 and separated from the pump working chamber 22.
  • the fuel injection valve 12 then opens due to the reduced pressure force on the control piston 50 and the injection valve member 28 moves to its open position.
  • the second control valve 70 is brought by the control device 67 in its first switching position, so that the control pressure chamber 52 is separated from the discharge chamber 24 and connected to the pump working chamber 22 and builds up in this high pressure and acting on the control piston 50 force the fuel injection valve 12 is closed.
  • a post-injection can still take place, to which the second control valve 70 is brought into its second switching position.
  • the second control valve 70 is returned to its first switching position and / or the first control valve 68 is opened.
  • control valve 70 may also in other fuel injectors or High pressure fluid systems are used to control a connection.
  • the control valve 70 may also be designed as a 2/2-way valve, a 2/3-way valve or a 3/3-way valve.

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP04762589A 2003-09-26 2004-08-04 Ventil zur steuerung einer verbindung in einem hochdruckflüssigkeitssystem, insbesondere einer kraftstoffeinspritzeinrichtung für eine brennkraftmaschine Expired - Lifetime EP1671028B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10344897A DE10344897A1 (de) 2003-09-26 2003-09-26 Ventil zur Steuerung einer Verbindung in einem Hochdruckflüssigkeitssystem, insbesondere einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
PCT/DE2004/001744 WO2005040598A1 (de) 2003-09-26 2004-08-04 Ventil zur steuerung einer verbindung in einem hochdruckflüssigkeitssystem, insbesondere einer kraftstoffeinspritzeinrichtung für eine brennkraftmaschine

Publications (2)

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EP1671028A1 EP1671028A1 (de) 2006-06-21
EP1671028B1 true EP1671028B1 (de) 2012-07-04

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US (1) US7513441B2 (zh)
EP (1) EP1671028B1 (zh)
JP (1) JP4253659B2 (zh)
CN (1) CN100564864C (zh)
BR (1) BRPI0406815B1 (zh)
DE (1) DE10344897A1 (zh)
WO (1) WO2005040598A1 (zh)

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DE102006061895A1 (de) 2006-12-28 2008-07-03 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung mit einem verbesserten Steuerventil
DE102006061896A1 (de) 2006-12-28 2008-07-03 Robert Bosch Gmbh Kraftstoffinjektor mit einer verbesserten Steuerung der Düsennadel
DE102011004993A1 (de) * 2011-03-02 2012-09-06 Robert Bosch Gmbh Ventileinrichtung zum Schalten oder Zumessen eines Fluids
CN105298688A (zh) * 2014-06-02 2016-02-03 上海长辛实业有限公司 压力式喷液装置，喷液增压系统及一种增强功率的方法
US12072719B2 (en) * 2018-12-21 2024-08-27 Illinois Tool Works Inc. Valve assembly having flow streamlining elements to prevent oscillating flow effects
CN112065627A (zh) * 2020-09-04 2020-12-11 温州弘腾科技有限公司 一种压力平衡喷油嘴的面积补偿制造方法以及由该方法制得的压力平衡喷油
CN112177824B (zh) * 2020-09-30 2021-11-02 重庆红江机械有限责任公司 一种液驱电控甲醇陶瓷柱塞泵

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US7513441B2 (en) 2009-04-07
CN1856642A (zh) 2006-11-01
CN100564864C (zh) 2009-12-02
BRPI0406815A (pt) 2005-12-27
DE10344897A1 (de) 2005-04-21
WO2005040598A1 (de) 2005-05-06
BRPI0406815B1 (pt) 2012-12-11
JP4253659B2 (ja) 2009-04-15
JP2006510847A (ja) 2006-03-30
EP1671028A1 (de) 2006-06-21
US20070063159A1 (en) 2007-03-22

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