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EP0872636A2 - Soupape d'injection de combustible pour moteurs à combustion interne - Google Patents

Soupape d'injection de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP0872636A2
EP0872636A2 EP98106006A EP98106006A EP0872636A2 EP 0872636 A2 EP0872636 A2 EP 0872636A2 EP 98106006 A EP98106006 A EP 98106006A EP 98106006 A EP98106006 A EP 98106006A EP 0872636 A2 EP0872636 A2 EP 0872636A2
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
pressure
fuel
fuel injection
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.)
Withdrawn
Application number
EP98106006A
Other languages
German (de)
English (en)
Other versions
EP0872636A3 (fr
Inventor
Detlev Dr. Potz
Roger Potschin
Stephan Haas
Thomas Kuegler
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 EP0872636A2 publication Critical patent/EP0872636A2/fr
Publication of EP0872636A3 publication Critical patent/EP0872636A3/fr
Withdrawn legal-status Critical Current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
    • F02M61/04—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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/005—Arrangement of electrical wires and connections, e.g. wire harness, sockets, plugs; Arrangement of electronic control circuits in or on fuel injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive 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
    • F02M61/045—The valves being provided with fuel discharge orifices

Definitions

  • the invention relates to a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out.
  • Outward-opening type fuel injector is an axially displaceable piston-shaped valve member in guided a bore of a valve body.
  • the valve member points to his in the combustion chamber to be supplied Internal combustion engine protruding end from the bore replacing valve member head with an enlarged diameter on, which forms a valve closing member and at whose the Valve body facing side at least indirectly one Sealing surface is arranged.
  • This valve member sealing surface acts with one on the front of the combustion chamber of the valve seat surface provided together, which borders on the bore in the valve body.
  • the known injection valve on the valve head a variety of Injection ports on axially one above the other are arranged and which are now during the outward directed opening stroke movement of the valve member in succession are taxable, so that overall different Have large injection opening cross sections set.
  • the Injection openings are thus in the valve head of the valve member arranged that they are in contact with the valve seat Valve member from the wall of the bore in the valve body are closed and only during the outward facing Opening stroke movement of the valve member by immersion controlled from the hole.
  • the fuel injection valve according to the invention for internal combustion engines with the characterizing features of the claim 1 has the advantage that the operation of the valve member regardless of the high fuel pressure in Pressure chamber is carried out by an additional actuator.
  • This separately actuated actuator is advantageous Formed as a piezo actuator, but can also by other electromechanical actuators are replaced.
  • a hydraulic translation space is provided, through which the relatively small adjustment movement of the piezo actuator in one relatively larger adjustment stroke movement converted on the valve member becomes.
  • valve member one acting in the closing direction of the valve member additional third pressure shoulder on, which is also constant is connected to the high-pressure fuel supply line, so that the closing force on the valve member is more advantageous Always proportional to the pressure in the High pressure fuel supply system rises.
  • the fuel injector can be a so-called Vario register nozzle with a multitude of one above the other arranged spray holes or as a so-called Vario slot nozzle with a rectangular slit-shaped Injection cross section can be formed depending different from the valve member opening stroke Release injection opening cross sections.
  • the Injection cross section or injection course freely selected and be adapted to a corresponding engine map, where both partial strokes, rate shaping and pilot injections possible are.
  • the valve member can now by Actuation by the separate actuator, preferably one Piezo actuator independent of the high fuel pressure in its Opening stroke position can be set. The injection takes place compared to other types of nozzles, even when activated of a partial stroke without throttling, so that the full Pressure energy benefits the jet preparation.
  • FIG. 1 shows a longitudinal section by a first embodiment with only two Pressure application surfaces on the valve member
  • Figure 2 a Enlarged sectional view of Figure 1 in the area the valve member head, the injection opening at first embodiment as a rectangular slot 3
  • Figure 4 is a third Embodiment analogous to the representation of Figure 1, at which an additional third pressure application surface on the valve member is provided
  • Figure 5 shows a fourth embodiment analogous to the representation of Figure 1, in which the valve member via an attached intermediate piston in the hydraulic working space protrudes.
  • the first embodiment shown in Figure 1 of the fuel injection valve according to the invention for internal combustion engines has a valve body 1, which by means of a union nut 3 on a valve holding body axially is clamped.
  • the valve body 1 has an axial Guide bore 7 in which a piston-shaped valve member 9 is guided axially displaceably, as in FIG. 2 shown enlarged, at its in a combustion chamber supplying internal combustion engine projecting lower end has valve head 11 acting as a valve closing member.
  • This protruding from the bore 7 valve head 11 has one the conical sealing surface 13 facing the valve body 1, which in the first embodiment by one on the Valve member head 11 seat ring 15 is formed and which with a corresponding valve seat 17 on the Front side of the valve body on the combustion chamber side 1 cooperates.
  • valve member 9 It is between the wall of the bore 7 and a pressure chamber 19 in part of the shaft of the valve member 9 in the valve body 1 formed axially by one Pressure shoulder on the valve member 9 is limited. It points a first upper pressure shoulder 21 at the end remote from the combustion chamber of the pressure chamber 19 the same pressure application area as a second lower pressure shoulder 23 near the combustion chamber so that Valve member 9 pressure balanced in the first embodiment is.
  • the valve member 9 has, as in FIG. 2 shown enlarged, at least one injection channel 25 in the valve head 11, each by one of the lower Pressure shoulder 23 outgoing axial blind bore 27 and a formed by this radial injection opening 29 is.
  • This radial injection opening 29 points in the first Embodiment a rectangular or slit-shaped Cross-section and opens out from the blind bore 27 so on the peripheral surface of the valve head 11 that the Injection opening 29 when the valve member 17 bears against the valve seat 9 is closed by the wall of the bore 7 and during the outward opening stroke movement of the Valve member 9 only after lifting the sealing surface 13 from Valve seat 17 from overlap with bore 7 emerges.
  • valve member 9 protrudes with a shaft part 31 in a Valve holding body 5 provided spring space 33 and points there a spring plate 35 firmly connected to the valve member 31 on.
  • a valve spring 37 acts on this spring plate 35, on the other hand, with the interposition of spacer rings 39 on the end face 41 facing away from the combustion chamber Valve body 1 supports and so the valve member 9 in contact holds biased on valve seat 17. That sticks out End of the upper shaft part 31 facing away from the combustion chamber Valve member 9 with its end face facing away from the combustion chamber 43 in a hydraulic translation space 45, the preferably in an axially on the valve holding body 5 attached guide body 47 is arranged.
  • a two-part adjusting piston 49 with its combustion chamber side End face 51, the end face 51 being a larger one Cross section has as the end face 43 of Valve element 9.
  • the actuating piston 49 is replaced by one that Actuator biasing return spring 53 via a Ring 55, a sealing washer 57 and a spring plate 59 kept constantly in contact with an electrical actuator, which in the exemplary embodiment is designed as a piezo actuator 61 is.
  • This piezo actuator 61 is designed so that it Applying an electrical voltage to its axial length enlarged and so the actuating piston 49 in the direction of the valve member 9 moves.
  • the high-pressure fuel supply to the fuel injector takes place via a pressure channel 63 in the valve holding body 5, the continues in the valve body 1 and there in the pressure chamber 19 opens.
  • the pressure channel 63 is not one Connection piece shown in more detail to an injection line 65 connected, which in turn from one for all injectors Common high-pressure storage space (common rail) 67 dissipates.
  • This high-pressure storage space 67 is in known manner from a high pressure fuel delivery pump High pressure fuel filled from a storage tank.
  • the fuel injection valve according to the invention for internal combustion engines works in the following way.
  • closed Condition i.e. when the piezo actuator 61 is not energized, this becomes Valve member 9 of the valve spring 37 with its sealing surface 13 held in contact with valve seat 17.
  • Valve member 9 of the valve spring 37 With its sealing surface 13 held in contact with valve seat 17.
  • the Injection openings 29 of the injection channel 25 from the wall the bore 7 in the valve body 1 closed.
  • the one in the high-pressure storage room 67 located high fuel pressure sets itself via the injection line 65 and the pressure channel 63 into the pressure chamber 19 and is therefore also in the Injection channel 25 or at the injection openings 29.
  • There the pressure shoulders 21 and 23 on the valve member 9 have the same pressure application surface, the valve member 9 pressure equalized and is by the valve spring 37 in Closed position maintained.
  • the piezo actuator 61 is energized and injected immediately increases its axial extent. As a result of axial expansion of the piezo actuator 61 becomes the two-part Actuating piston 49 in the direction of the hydraulic working space 45 shifted and displaced a relative in this space large volume of liquid.
  • the valve member 9 against the Restoring force of the valve spring 37 from its valve seat 17th moved so that the sealing surface 13 from the valve seat 17th takes off and the injection openings 29 from the overlap with immerse the wall of the bore 7 of the valve body 1.
  • the injection opening 29 emerging from the Bore 7 of the injection process in the combustion chamber supplying internal combustion engine.
  • the second embodiment shown in Figure 3 differs from that shown in FIGS. 1 and 2 first embodiment only in the training of Valve head 11 and the injection channel provided therein 25.
  • the injector is now not as in the Figures 1 and 2 as a so-called Vario slot nozzle but as Vario register nozzle designed.
  • the function of the seat ring is now taken over by a sleeve 69 with a section 71 facing away from the combustion chamber protrudes into the guide bore 7 in the valve body 1.
  • Of the Injection channel 25 is now through axial recesses 73 formed at the valve head end of the valve member 9, the extend into the area 71 of the sleeve 69.
  • Rows of axially superimposed radial injection bores 75 provided in the sleeve 69 which is analogous to the Injection openings 29 of the first embodiment so in the peripheral wall of the valve member head 11 or the sleeve 69 flow into a valve member lying against the valve seat 17 9 closed by the wall of the bore 7 in the valve body 1 and during the outward opening stroke movement the valve member 9 by emerging from the bore 7 are controllable one after the other.
  • Connect injection bores 75 to the recesses 73 is also an annular groove 77 in the area of Injection bores 75 are provided on valve member 9.
  • the sleeve 69 is firmly attached to the valve member 9, preferably pressed on or shrunk on.
  • the third embodiment shown in Figure 4 differs from the first one shown in FIG Embodiment by providing another additional fuel pressurized Attack surface on the valve member 9, through which the injector pending high fuel pressure in the closing direction the valve member 9 acts.
  • This additional pressure application area is in the third embodiment by a additional third pressure shoulder 79 formed by a lower end face of a pressure sleeve 81 on the combustion chamber side is formed.
  • This pressure sleeve 81 is on the top Shaft part 31 of the valve member 9 pushed on and lies with its upper face away from the combustion chamber at a stop on the valve member 9.
  • This stop of the pressure sleeve 81 in The closing direction of the valve member 9 is determined by a into a corresponding receiving groove on the valve member 9 inserted circlip 83 formed.
  • the third pressure shoulder 79 a closing pressure space 85 is provided, between the end face of the pressure sleeve on the combustion chamber side 81 and the combustion chamber end face 41 of the valve body 1 is limited and that via a connecting channel 87 from the pressure channel 63 filled with high fuel pressure becomes. It has the formation of the third embodiment the advantage that the acting on the valve member 9 Closing force always proportional to the high fuel pressure in the Pressure storage system rises.
  • an intermediate piston 93 projects with its upper end face 95 into the hydraulic working space 45 at the end face 91 of the control piston 49 directly connected to the piezo actuator 61, the end face 95 of the bottom lying intermediate piston 93 is formed smaller than the end face 91 of the actuating piston 49.
  • the intermediate piston 93 With its lower end facing the combustion chamber, the intermediate piston 93 is axially fitted onto the upper shaft part 31 of the valve member 9, which has the advantage that the valve member 9 itself is no longer in the hydraulic Translation space 45 protrudes.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP98106006A 1997-04-18 1998-04-02 Soupape d'injection de combustible pour moteurs à combustion interne Withdrawn EP0872636A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19716226 1997-04-18
DE1997116226 DE19716226C2 (de) 1997-04-18 1997-04-18 Kraftstoffeinspritzventil für Brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0872636A2 true EP0872636A2 (fr) 1998-10-21
EP0872636A3 EP0872636A3 (fr) 2002-01-23

Family

ID=7826893

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98106006A Withdrawn EP0872636A3 (fr) 1997-04-18 1998-04-02 Soupape d'injection de combustible pour moteurs à combustion interne

Country Status (2)

Country Link
EP (1) EP0872636A3 (fr)
DE (1) DE19716226C2 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0977945A1 (fr) * 1997-11-29 2000-02-09 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion interne
FR2782795A1 (fr) * 1998-08-27 2000-03-03 Siemens Ag Dispositif et procede de fourniture dosee d'un fluide, notamment pour injection de carburant
FR2786269A1 (fr) * 1998-11-25 2000-05-26 Siemens Ag Dispositif d'injection de maniere dosee d'un fluide s'accommodant d'une variation de la pression du fluide injecte
DE19943142A1 (de) * 1999-09-09 2001-04-12 Siemens Ag Dosiervorrichtung
WO2001057393A3 (fr) * 2000-02-04 2001-12-20 Bosch Gmbh Robert Systeme hydraulique de demultiplication de course
EP1077326A3 (fr) * 1999-08-18 2003-01-22 Delphi Technologies, Inc. Injecteur à combustible
WO2003085253A1 (fr) * 2002-04-04 2003-10-16 Siemens Aktiengesellschaft Soupape d'injection

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19905152C1 (de) * 1999-02-08 2000-07-27 Univ Dresden Tech Kraftstoffeinspritzdüse für Brennkraftmaschinen
DE19922964C2 (de) * 1999-05-19 2003-03-27 Daimler Chrysler Ag Verfahren zum Einspritzen von Dieselkraftstoff
DE19946603B4 (de) * 1999-09-29 2009-01-15 Robert Bosch Gmbh Brennstoffeinspritzventil mit kompensierenden Dichtelementen
DE10007735A1 (de) * 2000-02-19 2001-09-06 Daimler Chrysler Ag Einspritzventil

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4442764A1 (de) 1994-12-01 1996-06-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01187363A (ja) * 1988-01-21 1989-07-26 Toyota Motor Corp 内燃機関用燃料噴射弁
US5031841A (en) * 1989-02-28 1991-07-16 Volkswagen Ag Metering valve, particularly fuel injection valve
DE4306072C2 (de) * 1993-02-26 1994-12-08 Siemens Ag Vorrichtung zum Öffnen und Verschließen einer in einem Gehäuse vorhandenen Durchtrittsöffnung
DE4325904C2 (de) * 1993-08-02 1995-07-20 Daimler Benz Ag Für eine Dieselbrennkraftmaschine vorgesehene Kraftstoffeinspritzanlage mit einer den Kraftstoff fördernden Hochdruckpumpe in eine gemeinsame Versorgungsleitung (Common-Rail) für alle Einspritzdüsen
DE19500706C2 (de) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen
DE19534445C2 (de) * 1995-09-16 1998-07-30 Man Nutzfahrzeuge Ag Einspritzventil für Brennkraftmaschinen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4442764A1 (de) 1994-12-01 1996-06-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0977945A1 (fr) * 1997-11-29 2000-02-09 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion interne
FR2782795A1 (fr) * 1998-08-27 2000-03-03 Siemens Ag Dispositif et procede de fourniture dosee d'un fluide, notamment pour injection de carburant
FR2786269A1 (fr) * 1998-11-25 2000-05-26 Siemens Ag Dispositif d'injection de maniere dosee d'un fluide s'accommodant d'une variation de la pression du fluide injecte
EP1077326A3 (fr) * 1999-08-18 2003-01-22 Delphi Technologies, Inc. Injecteur à combustible
DE19943142A1 (de) * 1999-09-09 2001-04-12 Siemens Ag Dosiervorrichtung
WO2001057393A3 (fr) * 2000-02-04 2001-12-20 Bosch Gmbh Robert Systeme hydraulique de demultiplication de course
WO2003085253A1 (fr) * 2002-04-04 2003-10-16 Siemens Aktiengesellschaft Soupape d'injection
US7886993B2 (en) 2002-04-04 2011-02-15 Siemens Aktiengesellschaft Injection valve

Also Published As

Publication number Publication date
EP0872636A3 (fr) 2002-01-23
DE19716226A1 (de) 1998-10-29
DE19716226C2 (de) 1999-04-22

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