EP1416152A1 - Soupape pour le contrôle des fluides avec alimentation d'un fluide sous pression - Google Patents

Soupape pour le contrôle des fluides avec alimentation d'un fluide sous pression Download PDF

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Publication number
EP1416152A1
EP1416152A1 EP03021080A EP03021080A EP1416152A1 EP 1416152 A1 EP1416152 A1 EP 1416152A1 EP 03021080 A EP03021080 A EP 03021080A EP 03021080 A EP03021080 A EP 03021080A EP 1416152 A1 EP1416152 A1 EP 1416152A1
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EP
European Patent Office
Prior art keywords
valve
pressure
control chamber
piston
high pressure
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
EP03021080A
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German (de)
English (en)
Other versions
EP1416152B1 (fr
Inventor
Wolfgang Stoecklein
Dietmar Schmieder
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 EP1416152A1 publication Critical patent/EP1416152A1/fr
Application granted granted Critical
Publication of EP1416152B1 publication Critical patent/EP1416152B1/fr
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
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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

Definitions

  • the invention relates to a valve for controlling liquids with a pressure medium supply according to that in the preamble of claim 1 art defined.
  • Valves of the type mentioned in the introduction are from practice known and have a pressure ratio for compressing Fuel from a supply pressure to an injection pressure on.
  • the pressure ratio is with pressure ratio Chambers executed with additional components for pressure translation and injecting fuel into one Combustion chamber of an internal combustion engine are combined.
  • To is a valve from a pressure fluid accumulator or a Pressure medium source, in particular a common rail area, Fuel with a supply pressure or a rail pressure above a pressure medium supply supplied. By means of pressure translation the fuel supplied with the supply pressure is increased compresses a high pressure and with the valve open the high pressure in the combustion chamber of an internal combustion engine injected.
  • the pressure ratio has a piston system, which can be controlled via a control valve and if necessary the high pressure or injection pressure is generated.
  • the High pressure is in the area of an injection nozzle of the valve on.
  • the control valve is preferably actuated via a piezoelectric actuator, which one Part of an actuator system of the valve.
  • the injector and the pressure ratio of the valve are spatially separated from one another and must be drilled and Channels in the valve housing are connected to each other the high pressure fuel from the pressure ratio to be able to lead to the injector.
  • the holes and channels are compressed in phases with the high pressure Fueled so that the valve housing as well as further components having the channels and bores of the valve must be designed high-strength what disadvantageously requires higher component wall thicknesses and in addition, a high sealing effort between individual Components of the valve caused.
  • valve according to the invention for controlling liquids with the features of claim 1 points against it the advantage of that on the holes used in practice and channels for guiding the high pressure or injection pressure compressed fuel from a pressure ratio in an area from which the fuel is in a Combustion chamber of an internal combustion engine through the nozzle body is sprayed out of the valve as far as possible can be dispensed with.
  • valve according to the invention the function of the injection nozzle and the high pressure pressure ratio combined in a structurally compact unit, so that leakage losses, which are negative the injection behavior of a valve for controlling liquids impact are minimized.
  • FIG. 1 is a first embodiment a valve 1 for controlling liquids with a pressure medium supply 2 and a valve element 3 for Controlling a pressure in a high pressure area 4 is shown.
  • the valve element 3 is arranged in a control room 5, the two interacting with the valve element 3 Has valve seats 6, 7.
  • the valve element 3 is in contact the first valve seat 6 is the control chamber 5 from a low pressure area 8 of the valve 1 separately.
  • This position of the valve element 3 is shown in Figure 1, wherein the valve element 3 then abuts the first valve seat 6, when an actuation of the valve element 3 by the Control element designed as a piezoelectric actuator is omitted and the valve element 3 by a spring force a spring 9 is pressed against the first valve seat 6.
  • the control which, for example, is also called a electromagnetic drive system can be executed is on the side facing away from the control room 5 of the first Valve seat 6 arranged.
  • the control element When the control element is energized the valve element 3 becomes from the first valve seat 6 lifted off, creating the control chamber 5 with the low pressure area 8 is connected. Furthermore, the valve element 3 pressed against the second valve seat 7, so that the control room 5 from a valve control room 10 is separated. Since the control room 5 with the pressure medium supply 2 is connected, the valve control chamber 10 when the valve element 3 is in contact with the second valve seat 7 also separated from the pressure medium supply 2.
  • the first valve seat 6 is in the present case a conical seat executed, and interacting with the first valve seat 6 Sealing surface 11 of the valve element 3 is crowned or spherical segment-shaped, so that at plant of the valve element 3 on the first valve seat 6 between the first valve seat 6 and the sealing surface 11 a line contact is present.
  • the second valve seat 7 is a flat surface of one Control chamber 5 delimiting component 42, which with a likewise flat surface or end face 12 of the Valve element 3 cooperates.
  • valve element 3 This configuration of the two valve seats 6, 7 and the sealing surfaces 11, 12 of the valve element 3 is ensured that a production-related axial offset of the first valve seat 6 with respect to a control chamber 5 and the valve control chamber 10 connecting channel 13 the sealing effect of the valve element 3 is not impaired. Furthermore it is guaranteed that at an in the axial direction of valve 1, actuation of valve element 3 an offset of the valve element 3 transverse to the direction of movement of the valve element 3 between the two valve seats 6 and 7 is omitted, so that instantaneous control of the valve 1 is given safely.
  • the valve control chamber 10 is from a valve plate 14 and a piston 15 limits a pressure ratio, the Piston 15 with its end face facing the valve plate 14 16 abuts the valve plate 14.
  • the face 16 of the piston 15 is designed spherical that the channel 13, which is the connection between the valve control chamber 10 and the control room 5, of which Piston 15 is not closed when it contacts valve plate 14 becomes.
  • the piston 15 is designed in two parts and consists from a first with a larger diameter Partial piston 17 and a second with a smaller one Diameter of the partial piston 18.
  • the first partial piston 17 is designed with a central blind hole 19, into which the second partial piston 18 is inserted.
  • the second partial piston 18 is in a spacer sleeve 20, which is inserted between a collar 21 of the second partial piston 18 and the spacer sleeve 20 second spring 22 against a nozzle needle 23 of valve 1 is pressed.
  • the collar 21 is formed at that end of the second piston 18 which by the second spring 22 against the ground the blind hole 19 of the first piston 17 is pressed is. With its end facing away from the collar 21 is the second Partial piston 18 in a guide bore 24 of the nozzle needle 23 guided axially movable.
  • the second sub-piston 18 is with a central through hole 25 which is formed on the end of the collar 21 closed by the first piston 17 and on the one facing away from the first partial piston 17 End of the second partial piston 18 in the guide bore 24 opens.
  • the guide bore 24 is coaxial with it Connection channel 26 formed in the nozzle needle 23 on, via a tap hole 27 with an annular space 28 connected is.
  • the annular space 28 is from a nozzle body 29 and the nozzle needle 23 limited.
  • the nozzle needle 23 is in the nozzle body 29 via a first one Guide area 32 and a second guide area 33 guided axially longitudinally and sealingly, wherein between the first guide area 32 and the second guide area 33 one of the nozzle needle 23 and the nozzle body 29 limited needle control chamber 34 is formed.
  • the needle control room 34 is in the nozzle body 29, one Valve body 35 and the valve plate 14 connecting line 36 connected to the pressure medium supply 2.
  • the needle control space 34 is above the first one Guide area 32 opposite a longitudinal bore 37 of the valve body 35, in which the first piston 17 and the second partial pistons 18 are arranged, sealed. additionally is the needle control space 34 over the second guide area 33 sealed against the annular space 28, wherein in Dependence of the existing pressure conditions in the valve 1 Leakage flows from the needle control chamber 34 in the direction of the annular space 28 or the longitudinal bore 37 or in the opposite Flow towards.
  • the longitudinal bore 37 of the valve body 35 is in a the nozzle body 35, the valve plate 14 and a valve housing 38 extending further connection channel 39 permanent connected to the control room 5.
  • the connection between the pressure medium supply 2 and the Control room 5 has an inlet throttle 40 and an outlet throttle 41 executed, between the inlet throttle 40 and the outlet throttle 41, the connecting line 36 in Branches off in the direction of the needle control chamber 34. So there is the possibility, depending on the throttle effect of the inlet throttle 40 and the throttling action of the outlet throttle 41 an at least approximately constant pressure level of the pressure medium supply 2, which is referred to here as the supply pressure is set to a defined intermediate pressure level. As a result, the intermediate pressure level the connecting line 36 is less than the supply pressure the pressure medium supply 2.
  • a pressure of the control room 5 is dependent the throttling effect of the outlet throttle 41, which in turn is less than the intermediate pressure level. It follows that the pressure in the valve control chamber 10 and the pressure in the Longitudinal bore 37 when the valve element 3 abuts the first Valve seat 6 is the same size, whereas the pressure in the needle control room 34 due to the branching of the connecting line 36 before the flow restrictor 41 larger than that Pressure in the valve control chamber 10 is.
  • valve element 3 For setting an injection start, an injection duration and an injection quantity over force ratios in the Fuel injection valve 1, the valve element 3 over the control element designed as a piezoelectric actuator controlled, which on the valve control room and arranged side of the valve element 3 facing away from the combustion chamber is.
  • the piezoelectric actuator not shown is in a manner known per se from several ceramic Layers built up and points to the valve element 3 facing side an actuator head and on its an actuator foot facing away from the valve element 3 on, which is supported on a wall of the valve housing 38.
  • control room 5 In the position of the valve element shown in FIG. 1 3 is the control room 5 opposite the low pressure area 8, in which preferably a system pressure between 10 prevailing bar and 30 bar, closed.
  • the connection between the control room 5 and the valve control room 10 opened because the valve element 3 by the spring 9 and prevailing pressure in the control room 5 against the first Valve seat 6 is pressed.
  • the piezoelectric actuator In this position of the valve element 3, the piezoelectric actuator is not energized.
  • valve control chamber 10 Since the pressure of the valve control chamber 10 is approximately the pressure in corresponds to the longitudinal bore 37 and the spring force of the second Spring 22 and the pressure and area ratios the needle control chamber 34, the annular chamber 28, the piston 15 and the nozzle needle 23 are coordinated, that is Fuel injection valve 1 closed, and the piston 15 or the first partial piston 17 lies with its end face 16 on the valve plate 14.
  • the fuel injector 1 has the of the annular space 28, the Branch bore 27, the connecting channel 26, the guide bore 24 and the through bore 25 of the second partial piston 18 limited high pressure area 4 its largest volume on.
  • the high pressure area 4 is filled with fuel that has approximately the pressure level of the longitudinal bore 37. This results from the fact that the second partial piston 18th pressed against the first partial piston 17 via the second spring 22 and if there is a pressure gradient between the longitudinal bore 37 and the high pressure area 4 the pressure of the high pressure area 4 to the pressure level of the longitudinal bore 37 is raised. Is the pressure level of the high pressure area 4 greater than the pressure level of the longitudinal bore 37, there is essentially no pressure equalization since the second Sub-piston 18 then bears sealingly on the first sub-piston 17.
  • the piezoelectric actuator or its piezoelectric Ceramic energized, the length of the piezoelectric Ceramic enlarged due to the piezoelectric effect.
  • the valve element 3 from the first Valve seat 6 lifted off and sealing against the second valve seat 7 pressed.
  • the valve element 3 is the pressure medium supply 2, the needle control chamber 34 and the longitudinal bore 37 via the control chamber 5 with the low pressure area 8 connected.
  • the valve control room 10 due to the contact of the valve element 3 on the second valve seat 7 is closed off from the control chamber 5, so that in the valve control chamber 10 is still approximately Pressure level of the control room 5 before opening the first Valve seat 6 is present. This results in a pressure drop between the valve control chamber 10 and the longitudinal bore 37.
  • the piston 15 is lifted off the valve plate 14 to an increasing compression of the second spring 22, whereby a closing force acting on the nozzle needle 23 is increased.
  • the one located in the high pressure area 4 Fuel is compressed to a defined high pressure.
  • the high pressure is due to another effective area 43 of the nozzle needle 23 and leads together with the pressure of the needle control chamber 34, which is also in the opening direction the nozzle needle 23 acts on it to open the valve 1. That means that after reaching the defined high pressure in the high pressure area 4 or in the annular space 28 the nozzle needle 23 is lifted off the sealing seat 30. Then is in the high pressure area 4 or in the annulus 28 under High-pressure fuel through the injection openings 31 into a combustion chamber, not shown Internal combustion engine sprayed and the high pressure in the high pressure range 4 dismantled.
  • the current supply the piezoelectric actuator is interrupted and the Elongation of the piezoelectric ceramic regresses.
  • the valve element 3 lifts off from the second valve seat 7 and is pressed sealingly against the first valve seat 6.
  • the pressure level of the longitudinal bore 37 increases in such a way that the piston 15 is pressed again against the valve plate 14 becomes.
  • the nozzle needle 23 is due to the force relationships pressed against the sealing seat 30.
  • the needle control room 34 is via the inlet throttle 40 and the outlet throttle 41st emptied, which ensures quick needle closing is.
  • nozzle needle 23 If the nozzle needle 23 is to open slowly during an injection, an inlet throttle with a high throttling effect is provided, whereas with the desired high opening speed an inlet throttle with less throttling effect is to be provided.
  • a closing speed of the nozzle needle is essentially due to the throttling effect of both throttles determined, with an increasing throttling effect the Closing speed reduced.
  • the fuel injector points to the Invention the advantages of a fuel injector with pressure translation, namely that a supply pressure is essential can be smaller than that in the valve itself generated injection pressure, whereby a pressure medium supply does not have to be carried out with the same strength as the pressure translation system itself.
  • FIGS. 2, 3 and 4 represent three further embodiments of the valve according to the invention. Differentiate here the exemplary embodiments shown in FIGS. 2, 3 and 4 from the embodiment shown in Figure 1 only in some areas, which is why in the following description and in Figures 2 to 4 for Identical identically and for functionally identical components the same reference numerals be used.
  • the embodiment of the fuel injector shown in Figure 2 1 differs from that in FIG 1 illustrated embodiment of the fuel injector 1 by in the area of the contact surface between the first piston 17 and the second piston 18 arranged filling valve 44, which is a filling ensure the high pressure area 4 with fuel safely should.
  • the filling should be guaranteed even then if there is a theoretically sufficient pressure drop between the high pressure area 4 and the longitudinal bore 37 of the Valve body 35 is not sufficient to fill the Lead high pressure area 4 starting from the longitudinal bore 37 should.
  • the filling valve 44 opens at a certain point Pressure drop between the valve control chamber 10 and the high pressure area 4 and remains open until one Closing pressure in the high pressure area 4 is reached.
  • the embodiment shown in Figure 2 can of fuel injector 1 after Invention be carried out in such a way that the piston 15th is a one-piece stepped piston. That means the first Partial piston 17 and the second partial piston 18 made in one piece are or are firmly connected, whereby a filling of the high pressure area starting from the Longitudinal bore of the valve body is not provided and the High pressure area only starting from the valve control room controlled by opening and closing the filling valve becomes.
  • Fuel injector is based on the description of the Fuel injector according to Figure 1 referenced except for the additional filling of the high pressure area 4 is the same via the filling valve 44.
  • the embodiment of the fuel injector shown in Figure 3 1 differs essentially of the embodiment shown in FIG. 2, that the filling valve 44 is not on the contact area between the first partial piston 17 and the second Partial piston 18 facing end of the first partial piston 17th is arranged, but that the filling valve 44 in the mouth area the through hole 25 into the guide hole 24 is integrated.
  • This measure leads to the fact that Volume of the high pressure area 4 in comparison to the exemplary embodiments 1 and 2 is reduced, which gives the above-described advantages of the fuel injector even stronger after the invention come.
  • a valve closing member 45 designed as a check valve Filling valve 44 and the valve closing member 45 closing spring 47 pressing against a valve sealing seat 46 are arranged in the through hole 25 and through a to the second partial piston 18 after assembly of the valve closing member 45 and the closing spring 47 welded Disc 48 positioned.
  • the disc 48 is with a central Bore 49 for guiding fuel to the high pressure area 4 provided.
  • the through hole 25 of the second Partial piston 18 is in the area of the valve sealing seat 46 with a diameter constriction, which means that Filling valve 44 acting pressure fluctuations in the longitudinal bore 37 and thus also smoothed in the through hole 25 become.
  • the mode of operation of the fuel injection valve 1 corresponds to the embodiment shown in FIG essential to the operation of that shown in Figure 2 Fuel injector, which is why on the description the functioning of the fuel injector Figure 1 and 2 is referred.
  • FIG. 4 shows a further exemplary embodiment of the fuel injection valve 1, its principal constructive execution essentially the embodiment corresponds to Figure 1.
  • the fuel injector 4 is without connection between the Pressure medium supply 2 and the needle control chamber 34 and without the chokes 40 shown in FIGS. 1, 2 and 3 and 41 executed.
  • the fuel injection valve 1 according to FIG. 4 thus compared to the exemplary embodiments according to FIGS. 1, 2 and 3 a simplified embodiment, the injection behavior but not in the differentiated way is adjustable, as in the embodiments of the Figures 1 to 3 is the case, the inlet throttle 40 and have the outlet throttle 41. This results from the fact that the opening behavior of the fuel injector according to Figure 4 only about a throttling effect of an opening 50 can be influenced.
  • the opening 50 is provided in the nozzle needle 23 supplying or discharging fuel into the needle control chamber 34 or out of the needle control chamber 34, and establishes a connection between the needle control room 34 and the high pressure area 4 in the area of Connection channel 26 forth.
  • the valve element 3 is located on the first valve seat 6 and the nozzle needle 23 on the sealing seat 30 on. If the first valve seat 6 is replaced by the valve element 3 released and the second valve seat 7 from the valve element 3 closed, the piston 15 is in the direction of the nozzle needle 23 shifted, the one in the high pressure region 4 existing fuel is compressed to high pressure. At the same time, the pressure in the needle control chamber 34 increases accordingly the throttling effect of the opening 50. Reached the pressure of the high pressure area 4 the opening pressure or the injection pressure, raises the nozzle needle 23 in the direction the valve plate 14 from the sealing seat 30, and in the High pressure area 4 or existing in the annular space 28 Fuel is injected into an injection port 31 Combustion chamber of an internal combustion engine injected.
  • valve element 3 in turn sealingly applied to the first valve seat 6, whereby the piston 15 in the manner described above is moved to the valve plate 14.
  • the nozzle needle 23 is pressed sealingly against the sealing seat 30, the volume of the needle control space 34 reduced.
  • the excess fuel of the needle control room 34 is about the breakthrough 50 in the high pressure area 4 pressed.
  • the closing speed of the nozzle needle 23 is therefore dependent on the throttling effect of the opening 50 and can be varied by changing the throttling effect.
  • the high pressure area 4 is thus after the end of the injection on the one hand via the longitudinal bore 37 and additionally with excess fuel of the needle control chamber 34 filled through the breakthrough 50.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP20030021080 2002-10-31 2003-09-18 Soupape pour le contrôle des fluides avec alimentation d'un fluide sous pression Expired - Lifetime EP1416152B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002150722 DE10250722A1 (de) 2002-10-31 2002-10-31 Ventil zum Steuern von Flüssigkeiten mit einer Druckmittelzuführung
DE10250722 2002-10-31

Publications (2)

Publication Number Publication Date
EP1416152A1 true EP1416152A1 (fr) 2004-05-06
EP1416152B1 EP1416152B1 (fr) 2009-06-17

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EP20030021080 Expired - Lifetime EP1416152B1 (fr) 2002-10-31 2003-09-18 Soupape pour le contrôle des fluides avec alimentation d'un fluide sous pression

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EP (1) EP1416152B1 (fr)
DE (2) DE10250722A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005045233A1 (fr) * 2003-10-06 2005-05-19 Robert Bosch Gmbh Soupape d'injection de carburant pour moteur a combustion interne
EP1793120A1 (fr) * 2005-12-02 2007-06-06 Siemens Aktiengesellschaft Soupape d'un injecteur
WO2008141918A1 (fr) * 2007-05-18 2008-11-27 Robert Bosch Gmbh Injecteur pour un système d'injection de carburant
EP1908952A3 (fr) * 2006-10-05 2009-05-13 Robert Bosch Gmbh Injecteur pour une installation à injection de carburant
EP2083166A3 (fr) * 2008-01-28 2010-11-10 Hitachi Ltd. Injecteur de carburant et moteur à combustion interne
CN112211755A (zh) * 2019-07-10 2021-01-12 罗伯特·博世有限公司 内燃机的水喷射系统以及用于水喷射系统的喷射阀

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2118624A (en) * 1982-04-13 1983-11-02 British Internal Combust Eng >I.C. engine liquid fuel injector
US4509691A (en) * 1982-07-15 1985-04-09 Lucas Industries Public Limited Company Fuel injection nozzles
US5884848A (en) * 1997-05-09 1999-03-23 Cummins Engine Company, Inc. Fuel injector with piezoelectric and hydraulically actuated needle valve
US6454189B1 (en) * 2000-07-03 2002-09-24 Caterpillar Inc. Reverse acting nozzle valve and fuel injector using same

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2118624A (en) * 1982-04-13 1983-11-02 British Internal Combust Eng >I.C. engine liquid fuel injector
US4509691A (en) * 1982-07-15 1985-04-09 Lucas Industries Public Limited Company Fuel injection nozzles
US5884848A (en) * 1997-05-09 1999-03-23 Cummins Engine Company, Inc. Fuel injector with piezoelectric and hydraulically actuated needle valve
US6454189B1 (en) * 2000-07-03 2002-09-24 Caterpillar Inc. Reverse acting nozzle valve and fuel injector using same

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005045233A1 (fr) * 2003-10-06 2005-05-19 Robert Bosch Gmbh Soupape d'injection de carburant pour moteur a combustion interne
EP1793120A1 (fr) * 2005-12-02 2007-06-06 Siemens Aktiengesellschaft Soupape d'un injecteur
EP1908952A3 (fr) * 2006-10-05 2009-05-13 Robert Bosch Gmbh Injecteur pour une installation à injection de carburant
WO2008141918A1 (fr) * 2007-05-18 2008-11-27 Robert Bosch Gmbh Injecteur pour un système d'injection de carburant
US8418941B2 (en) 2007-05-18 2013-04-16 Robert Bosch Gmbh Injector for a fuel injection system
EP2083166A3 (fr) * 2008-01-28 2010-11-10 Hitachi Ltd. Injecteur de carburant et moteur à combustion interne
CN112211755A (zh) * 2019-07-10 2021-01-12 罗伯特·博世有限公司 内燃机的水喷射系统以及用于水喷射系统的喷射阀

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Publication number Publication date
EP1416152B1 (fr) 2009-06-17
DE10250722A1 (de) 2004-05-13
DE50311603D1 (de) 2009-07-30

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