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EP1671028A1 - Soupape pour commander une liaison dans un systeme de liquide haute pression, notamment un dispositif d'injection de carburant pour un moteur a combustion interne - Google Patents

Soupape pour commander une liaison dans un systeme de liquide haute pression, notamment un dispositif d'injection de carburant pour un moteur a combustion interne

Info

Publication number
EP1671028A1
EP1671028A1 EP04762589A EP04762589A EP1671028A1 EP 1671028 A1 EP1671028 A1 EP 1671028A1 EP 04762589 A EP04762589 A EP 04762589A EP 04762589 A EP04762589 A EP 04762589A EP 1671028 A1 EP1671028 A1 EP 1671028A1
Authority
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.)
Granted
Application number
EP04762589A
Other languages
German (de)
English (en)
Other versions
EP1671028B1 (fr
Inventor
Nestor Rodriguez-Amaya
Christoph Hollmann
Michael Mennicken
Matthias Beck
Hubert Greif
Falk-Alexander Petry
Thilo Rzymann
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1671028A1 publication Critical patent/EP1671028A1/fr
Application granted granted Critical
Publication of EP1671028B1 publication Critical patent/EP1671028B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—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

  • Valve for controlling a connection in a high-pressure liquid system in particular a fuel injection device for an internal combustion engine
  • the invention relates to a valve for controlling a connection in a high-pressure liquid system, in particular a fuel injection device for an internal combustion engine, according to the preamble of claim 1.
  • Such a valve is known from EP 0 840 003 A.
  • This valve is used to control 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, which projects into a valve pressure chamber and which has a sealing surface in the valve pressure chamber on an end face arranged transversely to its longitudinal axis.
  • the valve member cooperates with its sealing surface with a valve seat arranged transversely to its longitudinal axis for closing an opening surrounded by the valve seat with respect to the pressure chamber.
  • valve according to the invention with the features according to claim 1 has the advantage that the functionality of the valve is ensured since at least approximately no or only slight forces are generated on the valve member by the fuel flowing out of the valve pressure chamber.
  • the design according to claim 2 enables a simple design of the pin to achieve the desired effect.
  • the embodiment according to claim 5 enables an at least approximately cavitation-free liquid flow along the valve member and along the valve seat.
  • FIG. 1 Fuel injection device for an internal combustion engine in a longitudinal section in a simplified representation with a Valve
  • Figure 2 shows an enlarged view of the valve in a longitudinal section according to a first embodiment
  • Figure 3 shows an embodiment of the valve modified compared to the first embodiment
  • Figure 4 shows the valve in a longitudinal section according to a second embodiment
  • Figure 5 shows the valve according to the second embodiment a liquid flow
  • FIG. 6 the valve according to an embodiment modified compared to the second embodiment.
  • FIG. 1 shows a fuel injection device for an internal combustion engine of a motor vehicle.
  • 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 a high-pressure fuel pump 10 and a fuel injection valve 12 connected to it, which form a common structural unit.
  • the fuel injection device can also be designed 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 one another and are connected to one another via a line.
  • the fuel injection device can also be designed as an accumulator injection system, in which fuel is conveyed by means of a high-pressure pump into an accumulator, to which at least one injector is connected, on which a control valve is arranged, which is designed like the valve 70 described below.
  • the valve 70 described below can also be used in a storage injection system in which a pressure intensifier is provided, which is preferably integrated close to or in the injector, wherein the Valve 70 for controlling the pressure booster is provided.
  • 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 driven at least indirectly 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 delimits a pump working chamber 22 in the cylinder bore 16, in which fuel is compressed under high pressure during the delivery stroke of the pump piston 18.
  • the pump working chamber 22 is supplied with fuel from a fuel reservoir 24 of the motor vehicle.
  • the fuel injection valve 12 has a valve body 26 which is connected to the pump body 14 and which can be constructed in several parts and in which an injection valve member 28 is guided so as to be longitudinally displaceable in a bore 30.
  • the valve body 26 has at least one, preferably a plurality of injection openings 32 at its end region facing the combustion chamber of the cylinder of the internal combustion engine.
  • the injection valve member 28 has, for example, an approximately conical sealing surface 34 on its end region facing the combustion chamber, 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 lead away.
  • valve body 26 there is an annular space 38 between the injection valve member 28 and the bore 30 towards the valve seat 36, which in its end region facing away from the valve seat 36 passes through a radial expansion of the bore 30 into a pressure chamber 40 surrounding the injection valve member 28.
  • the injection valve member 28 has a pressure shoulder 42 at the level of the pressure chamber 40 by reducing the cross section.
  • a prestressed closing spring 44 engages, through which the injection valve member 28 is pressed towards 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 control piston 50 is tightly connected, which is connected to the injection valve member 28.
  • the bore 48 forms a control pressure chamber 52 which is delimited 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 than this and can be connected to the injection valve member 28.
  • the control piston 50 can be formed in one piece 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 leads from the pump work chamber 22 through the pump body 14 and the valve body 26 to the pressure chamber 40 of the fuel injection valve 12.
  • a channel 62 leads from the pump work chamber 22 or from the channel 60 to the control pressure chamber 52.
  • a channel 64 can also be connected to the control pressure chamber 52 , which forms a connection to a relief chamber, which can serve at least indirectly as the fuel reservoir 24 or another area in which a low pressure prevails.
  • a connection 66 leads from the pump work chamber 22 or from the channel 60 to a relief chamber, which is controlled by a first electrically operated control valve 68.
  • the fuel reservoir 24 or another low-pressure region can serve at least indirectly as a relief space.
  • the control valve 68 can be designed as a 2/2-way valve, as shown in FIG. 1.
  • the control valve 68 is switched between its two switching positions by an actuator 69 which For example, an electromagnet can be against a return spring.
  • a second electrically operated control valve 70 is provided to control the pressure in the control pressure chamber 52.
  • the second control valve 70 is designed as a 3/2-way valve that can be switched between two switching positions. In a first switching position of the control valve 70, the control pressure chamber 52 is connected to the pump working chamber 22 and separated from the relief chamber 24, and in a second switching position of the control valve 70, the control pressure chamber 52 is separated from the pump working chamber 22 and connected to the relief chamber 24.
  • a throttle point 63 is provided in the connection 62 of the control pressure chamber 52 with the pump work chamber 22 and a throttle point 65 is provided in the connection 64 of the control pressure chamber 52 with the relief chamber 24. The throttle point 63 can be arranged in the connection 62 upstream of the control valve 70 or, as shown in FIG.
  • the control valve 70 has an actuator 71, which can be an electromagnet, a piezoelectric actuator or a magnetostrictive actuator, and by means of which the control valve 70 can be switched between its two switching positions against a return spring.
  • the two control valves 68, 70 are controlled by an electronic control device 67.
  • the second control valve 70 is explained in more detail below with reference to FIG. 2.
  • 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 projects into a valve pressure chamber 77 with an end region 75 which is enlarged in diameter compared to the shaft 74.
  • the connection 62 to the pump work chamber opens into the valve pressure chamber 77 22 and on the other hand the connection 64 to the relief chamber 24.
  • the connection 62 runs as an annular gap formed between the shaft 74 and a bore 76 surrounding it. The diameter of the bore 76 is smaller than that of the valve pressure chamber 77.
  • connection 64 which is in the form of a channel or a bore, opens into the opening 78 into the valve pressure chamber 77 and is surrounded by a surface 79 which is transverse, 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 an at least approximately cylindrical extension 80 toward the valve seat 79, the end face of which forms a sealing surface 81 which extends transversely, preferably at least approximately perpendicularly, to the longitudinal axis 73 of the valve member 72.
  • the projection 80 has a smaller diameter than the end region 75 of the valve member 72, but the diameter of the projection 80 is larger than that of the opening 78.
  • the sealing surface 81 extends radially inward from the outer edge of the valve member 72 in such a way that the distance between it and the valve seat 79 increases in the direction of the longitudinal axis 73 of the valve member 72. As a result, a narrow sealing edge is formed on the sealing surface 81 on its outer edge, with which the sealing surface 81 comes to rest on the valve seat 79.
  • a pin 83 projecting into the bore 64 adjoining the opening 78 is arranged on the valve member 72 and is preferably integrally formed on the valve member 72. The diameter of the bore 64 can then be enlarged to the opening 78, as shown in Figure 2.
  • the pin 83 is designed in such a way that 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 essentially no or only a small resulting force in the direction 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 its sealing surface 81. The transition from the inner edge of the sealing surface 81 to the pin 83 is rounded as shown in FIG.
  • the fuel flowing out of the valve pressure chamber 77 and initially flowing approximately radially inward along the sealing surface 81 is thus diverted by the pin 83 such that it subsequently 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 approximately 90 °.
  • the pin 83 has a thickening 84 towards its end protruding into the bore 64, so that the fuel flow is redirected there and runs at an angle ⁇ inclined to the longitudinal axis 73 of the valve member 72 away from the latter.
  • the angle ⁇ can be between greater than 0 ° and approximately 90 ° or also more than 90 °.
  • the pin 83 may have a circumferential annular groove 85 between its thickening 84 and the sealing surface 81, through whose side surfaces pointing in the direction of the longitudinal axis 73 of the valve member 72 the deflection of the fuel flow is effected.
  • the forces caused when the valve member 72 is deflected in the direction of its longitudinal axis 73 are at least approximately equal, so that the valve member 72 as a whole has at least approximately no or only a slight force 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 base of the annular groove 85 and to the circumference of the pin 83 are each rounded in order to keep flow losses low.
  • a conical transition surface 87 is provided, which forms a second valve seat.
  • a conical sealing surface 88 arranged on valve member 72, which cooperates with valve seat 87 to control connection 62.
  • the valve member 72 rests with its second sealing surface 88 on the second valve seat 87, so that the connection 62 to the pump work chamber 22 is separated.
  • 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 to the pump work chamber 22 is opened.
  • the valve member 72 bears with its sealing surface 81 on the valve seat 79.
  • valve member 72 can also be moved by the actuator 71 into a third switching position, in which it is located between its two switching positions explained above. Through the valve member 72, a connection of the valve pressure chamber 77 to the low-pressure region with a small flow cross-section is released, via which fuel can only flow out of the valve pressure chamber 77 in a throttled manner.
  • the valve member 72 is arranged in its third switching position, the pressure build-up in the control pressure chamber 52 is influenced such that a higher pressure prevails in the control pressure chamber 52 than in the valve member 72 arranged in its first switching position, but there is a lower pressure than in the valve member 72 arranged in its second switching position
  • the control valve 70 is designed as a 3/3-way valve.
  • FIG. 3 shows a modified version of the control valve 70, in which the conical valve seat 87 and the conical sealing surface 88 of the valve member 72 are omitted.
  • the valve member 72 for controlling the connection 62 is designed as a slide valve member.
  • the valve member 72 can be closed of the connection 62 with its end region 75 plunge tightly into the bore 76, whereby the connection 62 is closed. If the valve member 72 has its end region 75 swung out of the bore 76 and arranged in the valve pressure chamber 77, the connection 62 is released.
  • FIG. 4 shows the control valve 70 according to a second exemplary embodiment, in which the structure is essentially the same as in the first exemplary embodiment, but the design of the sealing surface 81 is modified.
  • the formation of the pin 83 of the valve member 72 is the same as in the first embodiment.
  • the sealing surface 81 is designed such that it approaches the valve seat 79 radially inward in an outer region 181, starting from its outer edge.
  • the area 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 area 181 of the sealing surface 81 has a radial extension 11, which is preferably approximately 0.3 mm with a diameter d of the valve member 72 of approximately 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 moves away 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 area 281 of the sealing surface 81 has a radial extent 12, which is preferably approximately 0.6 mm.
  • This configuration of the sealing surface 81 forms a flow inlet region 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 a flow outlet region is formed in the second region 281 thereof in which the fuel is out the smallest flow cross-section.
  • the valve seat 79 is at least approximately flat and lies in a radial plane with respect to the longitudinal axis 73 of the valve member 72.
  • the transition from the jacket of the shoulder 80 of the valve member 72 to the first region 181 of the sealing surface 81 is preferably rounded with a radius R, as shown in Figure 4.
  • FIG. 5 shows the improved flow profile at valve member 72 according to the second exemplary embodiment. While in the valve member 72 according to the first exemplary embodiment, flow separations when the flow enters the narrowest
  • FIG. 6 shows the control valve 70 according to an embodiment modified compared to the second exemplary embodiment.
  • the sealing surface 81 on the valve member is at least approximately flat and lies in a radial plane with respect to the longitudinal axis 73 of the valve member 72.
  • the valve seat 79 is designed such that it extends radially inwards from the outer edge 179 of the sealing surface 81 in an outer region 179 approaches.
  • the area 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 extension 11, which is preferably approximately 0.3 mm with a diameter d of the valve member 72 of approximately 2.5 mm.
  • the valve seat 79 is in a second region 279 adjoining its first region 179 formed that this 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 approximately 0.6 mm.
  • Fuel injector explained. During the suction stroke of the pump piston 18, fuel is supplied to it from the fuel reservoir 24. During the delivery stroke of the pump piston 18, the fuel injection begins with a pre-injection, the first control valve 68 being closed by the control device 67, so that the pump work chamber 22 is separated from the relief chamber 24. The control device 67 also brings the second control valve 70 into its second switching position, so that the control pressure chamber 52 is connected to the relief chamber 24 and is separated from the pump work chamber 22. In this case, no high pressure can build up in the control pressure chamber 52.
  • the second device is used by the control device Control valve 70 brought into its first switching position, so that the control pressure chamber 52 is separated from the relief 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 work chamber 22, so that a large pressure force acts on the control piston 50 in the closing direction and the injection valve member 28 is moved into its closed position.
  • the second control valve 70 is brought into its second switching position by the control device 67, so that the control pressure chamber 52 is connected to the relief chamber 24 and is separated from the pump work 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 into its open position.
  • the second control valve 70 is brought into its first switching position by the control device 67, so that the control pressure chamber 52 is separated from the relief chamber 24 and connected to the pump work chamber 22 and builds up in this high pressure and via the force acting on the control piston 50 the fuel injection valve 12 is closed.
  • a post-injection can also take place, for which the second control valve 70 is brought into its second switching position.
  • the second control valve 70 is brought back into its first switching position and / or the first control valve 68 is opened.
  • a control valve 70 configured as described above can also be used in other fuel injectors or High pressure fluid systems are used to control a connection.
  • the control valve 70 can also be designed as a 2/2-way valve, as a 2/3-way valve or as a 3/3-way valve.

Landscapes

  • 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)

Abstract

L'invention concerne une soupape comprenant un élément de soupape (72) qui est déplaçable dans le sens de son axe longitudinal (73), qui fait saillie dans une chambre de pression de soupape (77) et qui présente, dans la chambre de pression de soupape (77), sur une face frontale perpendiculaire à son axe longitudinal (73) une surface d'étanchéité (81) grâce à laquelle l'élément de soupape coopère avec un siège de soupape (79) perpendiculaire à son axe longitudinal (73) pour la fermeture au moins très étendue, par rapport à la chambre de pression de soupape (77), d'un orifice (78) entouré par le siège de soupape (79). Une liaison (64) vers une zone basse pression se rattache à l'orifice (78). L'élément de soupape (72) comprend un tenon (83) qui fait saillie dans la liaison (64) et qui sert à conduire le liquide s'écoulant hors de la chambre de pression de soupape (77) lorsque la surface d'étanchéité (81) de l'élément de soupape (72) est relevée par rapport au siège de soupape (79), de sorte que pratiquement presque aucune force résultante n'est exercée par ce liquide sur l'élément de soupape (72) dans le sens de son axe longitudinal (73).
EP04762589A 2003-09-26 2004-08-04 Soupape pour commander une liaison dans un systeme de liquide haute pression, notamment un dispositif d'injection de carburant pour un moteur a combustion interne Expired - Lifetime EP1671028B1 (fr)

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 (fr) 2003-09-26 2004-08-04 Soupape pour commander une liaison dans un systeme de liquide haute pression, notamment un dispositif d'injection de carburant pour un moteur a combustion interne

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

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

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DE102006061896A1 (de) 2006-12-28 2008-07-03 Robert Bosch Gmbh Kraftstoffinjektor mit einer verbesserten Steuerung der Düsennadel
DE102006061895A1 (de) 2006-12-28 2008-07-03 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung mit einem verbesserten Steuerventil
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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Also Published As

Publication number Publication date
CN100564864C (zh) 2009-12-02
DE10344897A1 (de) 2005-04-21
US7513441B2 (en) 2009-04-07
BRPI0406815A (pt) 2005-12-27
EP1671028B1 (fr) 2012-07-04
CN1856642A (zh) 2006-11-01
JP4253659B2 (ja) 2009-04-15
JP2006510847A (ja) 2006-03-30
US20070063159A1 (en) 2007-03-22
BRPI0406815B1 (pt) 2012-12-11
WO2005040598A1 (fr) 2005-05-06

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