WO2005003550A1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs a combustion interne Download PDF

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Publication number
WO2005003550A1
WO2005003550A1 PCT/CH2004/000400 CH2004000400W WO2005003550A1 WO 2005003550 A1 WO2005003550 A1 WO 2005003550A1 CH 2004000400 W CH2004000400 W CH 2004000400W WO 2005003550 A1 WO2005003550 A1 WO 2005003550A1
Authority
WO
WIPO (PCT)
Prior art keywords
injection valve
actuator
fuel injection
fuel
piston
Prior art date
Application number
PCT/CH2004/000400
Other languages
German (de)
English (en)
Inventor
Marco Ganser
Original Assignee
Ganser-Hydromag Ag
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 Ganser-Hydromag Ag filed Critical Ganser-Hydromag Ag
Priority to EP04738041A priority Critical patent/EP1639256A1/fr
Publication of WO2005003550A1 publication Critical patent/WO2005003550A1/fr

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
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • 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
    • 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
    • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
    • F02M47/043—Fluid pressure acting on injection-valve in the period of non-injection to keep it closed
    • 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
    • F02M47/06—Other fuel injectors peculiar thereto

Definitions

  • the present invention relates to a fuel injection valve for intermittent fuel injection into the combustion chamber of an internal combustion engine.
  • Fuel injection valves usually have a pilot valve, which is controlled by means of an electric magnet arrangement, for controlling the injection valve member.
  • Fuel injectors of this type are disclosed, for example, in EP-A-0 603 616, EP-A-0 824 190, EP-A-1 118 765, US-A-5,458,293 and US-A-6, 499, 699.
  • EP-A-0 603 616 EP-A-0 824 190
  • EP-A-1 118 765 US-A-5,458,293
  • US-A-6, 499, 699 At least the fuel losses flowing out of a control chamber into a low-pressure chamber during the injection processes are to be accepted.
  • Pilot-valveless fuel injection valves which operate without fuel loss, are disclosed in the older Swiss patent application No. 2003 1047/03 and in the corresponding international patent application PCT / CH 2004/00266, both not previously published.
  • this is limited on the one hand by means of an injection valve element in the manner of a piston. With its end region facing away from the control chamber, the needle-shaped injection valve member interacts with an injection valve seat.
  • the control chamber is separated from an actuator by means of a sealing element.
  • the actuator which is designed in particular as a piezoelectric or magnetostrictive four actuator, actuates an actuator shaft, which supports a sealing element designed as a membrane over a large area or immerses itself in the control chamber, a membrane-like sealing element ensuring that no fuel can flow out of the control chamber to the actuator.
  • the control chamber is connected by a throttle passage or a sliding fit of the injection valve member to a high-pressure chamber, which in turn is connected to a high-pressure fuel inlet and is delimited by the injection valve seat.
  • the actuator shaft is withdrawn, which leads to the injection valve member being lifted off the injection valve seat.
  • the actuator shaft is moved in the opposite direction against the control chamber, as a result of which the injection valve member is brought back into contact with the injection valve seat. Since strokes of the actuator shaft in the order of magnitude of 0.05-0.08 mm can be achieved with the aforementioned actuators and the injection valve member should be able to carry out a stroke of approximately 0.2-0.3 mm, the diameter of the actuator shaft is or the deflectable part of the diaphragm, chosen to be larger than that of the end region of the injection valve member which acts in the manner of a piston. In addition to the dynamic forces for actuating the injection valve member, the actuator must therefore also absorb the hydraulic force generated by the pressure of the fuel in the control chamber.
  • US-A-4, 579, 283 discloses a piezoelectric actuator actuated
  • Fuel injector actuates a piston which defines the volume of a control space delimited by the piston and a needle-shaped injection valve member changes the other side, the injection valve member interacts with a valve seat molded onto a valve seat element.
  • a needle guide is also formed on this valve seat element, on which the injection valve member is slidably guided with an end region facing the control arm.
  • the piston is also supplied with fuel on its side facing away from the control chamber and the injection valve member moves in dependence on the fuel pressure in the control chamber.
  • EP-A-0 324 905 discloses very similarly constructed fuel injection valves.
  • the forces acting on an actuator piston on the control chamber side are hydraulically largely compensated on the opposite side, which leads to a massive reduction in the forces acting on the actuator shaft.
  • the fuel injector according to the invention can thus be equipped with a lower-power actuator compared to a fuel injector without the force compensation mentioned. Accordingly, according to the invention, it is also possible, for example, to control a fuel injection valve with an actuator of the same power, the injection valve member of which has to perform a larger stroke.
  • the formation of a needle guide on a needle guide part which is independent of a valve seat element having an injection valve seat, offers not only a simple structure but also the possibility of making the injection valve member interacting with the injection valve seat slim in the area of the needle guide.
  • Fig.l in longitudinal section a part of a first embodiment of a fuel injector according to the invention.
  • FIG. 2 in the same representation as FIG. 1, a part of a further embodiment of a fuel injector according to the invention.
  • the fuel injector shown in FIG. 1 has a housing 10, of which only one end region is shown.
  • An actuator shaft 16 is arranged in a central passage 14 running in the direction of the longitudinal axis 12 of the housing and can be moved back and forth in the direction of the longitudinal axis 12 of the housing by means of an actuator 18 fastened to the housing 10.
  • the actuator 18 is preferably an electrically controlled magnetostrictive or piezoelectric actuator, which can move the actuator shaft 16 by a stroke of the order of 0.02-0.08 mm.
  • the actuator shaft 16 protrudes beyond the end face 20 of the housing 10, engages with the protruding part through a sealing element 22 and a compensation chamber 24 which is delimited in the axial direction on the one hand by the sealing element 22 and on the other hand by an actuator piston 26.
  • the actuator piston 26 is firmly connected to the actuator shaft 16; the actuator shaft 16 is preferably formed in one piece together with the actuator piston 26.
  • the compensation space 24 is delimited by a component, which forms a cylinder 30, a sleeve-shaped cylinder element 28, on the inner wall 30 'of which the actuator piston 26 is guided in a sliding fit, preferably in a tight sliding fit (3-10 ⁇ m).
  • the compensation chamber 24 is connected to a high-pressure chamber 34 through the cylinder element 28 by means of a radial passage 32.
  • the cylinder element 28 delimits on the circumference, with respect to the actuator piston 26 on the side opposite the compensation chamber 24, a control chamber 36 which is divided by a partition 38 of the cylinder element 28 into a first sub-chamber 42 assigned to the injection valve member 40 and a second sub-chamber 44 assigned to the actuator piston 26 is.
  • a central connection opening 46 extends through the partition 38.
  • the needle-shaped injection valve member 40 is on the one hand with an end region facing the control chamber 36 in a needle guide 48 formed on a needle guide part 47 of the cylinder element 28 in a sliding fit, preferably in a tight sliding fit (2-10 ⁇ m), displaceably guided in the axial direction and on the other hand acts with a , on a valve seat element 50 trained valve seat 52 together in a known manner.
  • the injection valve member 40 delimits the first partial space 42 and thus the control space 36 in the manner of a piston.
  • the essentially rotationally symmetrical valve seat element 50 is pressed by means of a union nut 54 wound onto the housing 10 to a spacer sleeve 56, which in turn resembles a plate flange Area 58 of the sealing element 22 is pressed in a sealing manner and surrounds the cylinder element 28 at a distance.
  • the recess 60 and the spacer sleeve 56 delimit the high-pressure chamber 34, which is connected to the flow through a fuel supply passage 66 in the plate flange-like region 58 of the sealing element 22 and a fuel supply channel 68 in the housing 10 with a high-pressure fuel inlet 70 arranged thereon.
  • the needle-shaped injection valve member 40 is thus arranged in the high-pressure chamber 34 and extends through it.
  • a circumferential support bead 72 is formed thereon, on which an intermediate disk 74 is supported, on which, on the other hand, one end of a spring 76 - a closing spring designed as a compression spring - bears, the spring of which the other end is supported on the free end face 78 of the cylinder element 28.
  • the spring 76 on the one hand supports the closing movement of the injection valve member 40 and on the other hand presses the cylinder element 28 with its end face facing away from the plate flange-like area 58 of the sealing element 22.
  • a valve plate 78 is arranged in the first sub-space 42, which is held in abutment against the partition 38 by means of a compression spring 80 supported on the injection valve member 40.
  • the valve plate 78 has a throttle passage 82 through which the first sub-space 42 is connected to the connection opening 46 and thus to the second sub-space 44.
  • the outside diameter of the valve plate 78 is smaller than the free cross section of the first sub-space 42, so that a throttling effect is eliminated when the valve plate 78 is lifted off the partition 38 against the force of the compression spring 80.
  • the valve plate 78 thus acts as an asymmetrical throttle valve and as a stop for the injection valve member 40 when the fuel injection valve is in the maximum open position.
  • the intermediate disk 74 for guiding the spring 76 laterally has an inner support collar projecting axially beyond the support surface, and that it can be provided with a U-shaped cut-out in order to make it easy to replace.
  • the force exerted by the spring 76 on the injection valve member 40 can be adjusted by the choice of the thickness of the intermediate disk 74.
  • Sleeve area 58 ' the wall thickness of which is substantially less than that of area 58.
  • the sleeve area 58' lies in the interior of the compensation space 24
  • Actuator shaft 16 and is in a circumferential groove 84 of the
  • Actuator shaft 16 crimped, which is close to
  • Actuator piston 26 is located. The fuel under high pressure in the compensation chamber 24 presses the
  • the actuator piston 26 delimits on the one hand the control chamber 36 with a hydraulically active piston surface 86, and on the other hand the compensation chamber 24 with a hydraulically active compensation surface 88.
  • the compensation surface 88 is smaller than the piston surface 86 by the cross-sectional area of the actuator shaft 66 and the cross-sectional area of the sleeve region 58 ' If the same pressure prevails in the high-pressure chamber 34 and in the control chamber 36, the actuator 18 is thus only loaded in the static state with a force that multiplies the cross-sectional area by the difference between the pressure in the high-pressure chamber 34 and the pressure on the actuator side of the sealing element 22 - for example ambient pressure corresponds to the actuator shaft 16 and the sleeve region 58 '.
  • a throttle inlet 90 through the cylinder element 28 is indicated by dashed lines. It connects the control chamber 36, in particular the second partial chamber 44, to the high-pressure chamber 34.If such a throttle inlet 90 is present, it serves for faster pressure compensation between the high-pressure chamber 34 and the control chamber 36 than it does without the throttle inlet 90 through the needle guide 48 and between the actuator piston 26 and the inner wall 30 'of the cylinder element 28 is possible.
  • the actuator piston 26 is mounted in a sliding fit, preferably in a narrow sliding fit (3-10 ⁇ m), on the inner wall 30 'of a blind hole-like recess 94 in the housing 10.
  • the housing 10 is the component that forms the cylinder 30.
  • the recess 94 extends up to the end face 20 of the housing 10, which thus forms the cylinder 30 for the actuator piston 26.
  • the compensation chamber 24 is connected by a throttle connection 98 to the fuel supply channel 68 and thus to the high-pressure chamber 34. Furthermore, the radial passage 32 is present in parallel with the throttle connection 98, but is now closed by a check valve 100 so that it can be released. This has a ball 102 in the compensation chamber 24 as a valve member, which is pressed by means of an annular spring 104 against the mouth of the radial passage 32 which acts as a valve seat.
  • the needle guide element 106 is held in contact by the spring 76 on the end face 20 of the housing 10. This spring 76 is supported at one end on the free end of the needle guide element 106 and at the other end, via the intermediate disk 74, on the support bead 72 of the injection valve member 40.
  • valve seat element 50 is designed to be correspondingly longer and is pressed directly onto the housing 10 at the end face by means of the union nut 54.
  • the hydraulically effective piston surface interacting with the control chamber 36 is designated 86 and the hydraulically active compensation surface interacting with the compensation chamber 24 on the actuator piston 26 is designated 88.
  • the compensation area 88 corresponds to the piston area 86 minus the cross-sectional area of the actuator shaft 16.
  • the piston area 86 is larger than the hydraulically effective cross-sectional area of the injection valve element 40 that interacts with the control chamber 36. Accordingly, the injection valve element 40 makes a larger stroke than the actuator piston 26 ,
  • the fuel injector shown there functions as follows.
  • the injection valve member 40 is in the closed position, in which it lies sealingly on the injection valve seat 52. Operating pressure prevails in the high-pressure chamber 34, compensation chamber 24 and control chamber 36.
  • the actuator 18 moves the actuator piston 26 by a stroke of the order of magnitude of 0.02-0.08 mm towards the actuator 18 via the actuator shaft 16.
  • the pressure in the second subspace 44 of the control chamber 36 is reduced, As a result, fuel flows from the first sub-space 42 through the throttle passage 82 into the second sub-space 44, which leads to the injection valve member 40 being lifted off the injection valve seat 52 against the force of the spring 76.
  • the throttle passage 82 dampens the movement of the Injection valve member 40. In maximum open position, injection valve member 40 bears against valve plate 78.
  • the static force which the actuator 18 has to absorb corresponds only to the operating pressure of the fuel multiplied by the difference between the piston surface 86 and the compensation surface 88. If there were no compensation surface 88, the actuator 18 would, in the static state, be exposed to a force which corresponds to the operating pressure of the fuel multiplied by the piston area 86.
  • the fuel injector shown in FIG. 2 also functions in the same way. However, the movement of the actuator piston 26 in the direction of the actuator 18 is now additionally damped. In the opposite direction, however, there is practically no damping, since the check valve 100 opens the radial passage 32.
  • the valve plate 78 and thus the compression spring 80 can be dispensed with the valve plate 78 and thus the compression spring 80 in both embodiments shown.
  • the movement of the injection valve member 40 is not damped because the connection opening 46 has practically no throttling effect.
  • the valve plate 78 omitted, to design the connection opening 46 itself as a throttle opening.
  • the movement of the injector member 40 is damped both when the fuel injector is opened and closed. If the actuator 18 is sufficiently strong in the closing direction, such a high pressure will build up in the second partial space 44 that the cylinder element 28, or needle guide element 106, moves away from the system on the surface 22 or the end face 20 (against the force of the Spring 76). In this case, the closing movement of the injection valve member 40 is again faster.
  • the cylinder element 28, or needle guide element 106 in the valve seat element 50 is guided radially, for example with guide ribs, and the coaxiality of the guides 62 and 48 is ensured.
  • the injection valve member 40 and the actuator shaft 16 with actuator pistons 26 can be arranged such that they are disaxed with respect to one another. It is also possible to use actuators of a different type than piezoelectric or magnetostrictive for the movement of the actuator piston 26.
  • the sealing element 22 could be replaced by a bushing 96 with a sliding fit for the actuator shaft 16.
  • the bushing 96 could then be formed on the cylinder element 28 or as a housing bushing.
  • a sealing element 22 shown in FIG. 1 in the embodiment according to FIG. 2 optionally with a plate flange 58 having a smaller outside diameter.

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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)

Abstract

L'invention concerne un piston d'actionneur (26) déplacé en va-et-vient au moyen de l'actionneur (18), qui présente une surface de piston (86) délimitant l'espace de commande (36) et, sur la face opposée, une surface de compensation (88) délimitant l'espace de compensation (24). Ledit espace de compensation (24) est relié à la chambre haute pression (34) et se trouve sous pression de service du carburant. L'espace de commande (36) est par ailleurs délimité par l'élément de soupape d'injection (40), à la manière d'un piston. L'élément de soupape d'injection (52) coopère avec un siège de soupape d'injection (52) et est guidé, en ajustement glissant, par sa zone terminale tournée vers l'espace de commande (36), dans la buse d'injection à aiguille (48) formée sur la partie de buse d'injection à aiguille (48). La partie de buse d'injection d'aiguille (47) est formée sur l'élément de cylindre (28). La pression régnant dans l'espace de commande (36) induit une force exercée dans le sens de l'actionneur (18), sur la surface du piston (86), ladite force étant néanmoins compensée en partie par la surface de compensation (88), ce qui permet d'utiliser des actionneurs (18) de faible puissance.
PCT/CH2004/000400 2003-07-01 2004-06-28 Soupape d'injection de carburant pour moteurs a combustion interne WO2005003550A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP04738041A EP1639256A1 (fr) 2003-07-01 2004-06-28 Soupape d'injection de carburant pour moteurs a combustion interne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH11642003 2003-07-01
CH1164/03 2003-07-01

Publications (1)

Publication Number Publication Date
WO2005003550A1 true WO2005003550A1 (fr) 2005-01-13

Family

ID=33557707

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CH2004/000400 WO2005003550A1 (fr) 2003-07-01 2004-06-28 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (2)

Country Link
EP (1) EP1639256A1 (fr)
WO (1) WO2005003550A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8609065B2 (en) 2007-07-12 2013-12-17 Prosensa Technologies B.V. Molecules for targeting compounds to various selected organs, tissues or tumor cells
EP3141738A1 (fr) * 2015-09-08 2017-03-15 Delphi Technologies, Inc. Rattrapeur de jeu hydraulique disposé dans un servo-injecteur
US9803603B2 (en) 2013-03-01 2017-10-31 Ganser-Hydromag Ag Device for injecting fuel into the combustion chamber of an internal combustion engine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4579283A (en) * 1983-06-16 1986-04-01 Nippon Soken, Inc. Pressure responsive fuel injector actuated by pump
EP0324905A1 (fr) * 1988-01-21 1989-07-26 Toyota Jidosha Kabushiki Kaisha Injecteur de combustible pour un moteur
DE4233273A1 (de) * 1992-01-16 1993-09-02 Diesel Tech Corp Kraftstoffeinspritzanlage mit gemeinsamer druckleitung
DE4306072A1 (de) * 1993-02-26 1994-09-08 Siemens Ag Vorrichtung zum Öffnen und Verschließen einer in einem Gehäuse vorhandenen Durchtrittsöffnung
US5452858A (en) * 1993-03-24 1995-09-26 Nippon Soken Inc. Fuel injector for internal combustion engine having throttle portion
EP1098087A1 (fr) * 1999-10-09 2001-05-09 Delphi Technologies, Inc. Injecteur de combustible

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4579283A (en) * 1983-06-16 1986-04-01 Nippon Soken, Inc. Pressure responsive fuel injector actuated by pump
EP0324905A1 (fr) * 1988-01-21 1989-07-26 Toyota Jidosha Kabushiki Kaisha Injecteur de combustible pour un moteur
DE4233273A1 (de) * 1992-01-16 1993-09-02 Diesel Tech Corp Kraftstoffeinspritzanlage mit gemeinsamer druckleitung
DE4306072A1 (de) * 1993-02-26 1994-09-08 Siemens Ag Vorrichtung zum Öffnen und Verschließen einer in einem Gehäuse vorhandenen Durchtrittsöffnung
US5452858A (en) * 1993-03-24 1995-09-26 Nippon Soken Inc. Fuel injector for internal combustion engine having throttle portion
EP1098087A1 (fr) * 1999-10-09 2001-05-09 Delphi Technologies, Inc. Injecteur de combustible

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8609065B2 (en) 2007-07-12 2013-12-17 Prosensa Technologies B.V. Molecules for targeting compounds to various selected organs, tissues or tumor cells
US9803603B2 (en) 2013-03-01 2017-10-31 Ganser-Hydromag Ag Device for injecting fuel into the combustion chamber of an internal combustion engine
EP3141738A1 (fr) * 2015-09-08 2017-03-15 Delphi Technologies, Inc. Rattrapeur de jeu hydraulique disposé dans un servo-injecteur

Also Published As

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