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EP1620645B1 - Soupape d'injection de carburant sans perte - Google Patents

Soupape d'injection de carburant sans perte Download PDF

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Publication number
EP1620645B1
EP1620645B1 EP04730814A EP04730814A EP1620645B1 EP 1620645 B1 EP1620645 B1 EP 1620645B1 EP 04730814 A EP04730814 A EP 04730814A EP 04730814 A EP04730814 A EP 04730814A EP 1620645 B1 EP1620645 B1 EP 1620645B1
Authority
EP
European Patent Office
Prior art keywords
injection valve
actuator
fuel
fuel injection
valve member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04730814A
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German (de)
English (en)
Other versions
EP1620645A1 (fr
Inventor
Marco Ganser
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.)
Ganser Hydromag AG
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
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Publication of EP1620645A1 publication Critical patent/EP1620645A1/fr
Application granted granted Critical
Publication of EP1620645B1 publication Critical patent/EP1620645B1/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
    • 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
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/707—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for avoiding fuel contact with actuators, e.g. isolating actuators by using bellows or diaphragms

Definitions

  • the present invention relates to a fuel injection valve for intermittent fuel injection in the combustion chamber of an internal combustion engine according to the preamble of patent claim 1.
  • An injection valve for internal combustion engines of this kind is made DE 199 42 816 A1 known and has a valve body in which an injection valve member is slidably disposed. In an open position, the injection valve member for injecting fuel into a combustion chamber of the internal combustion engine releases an opening to the combustion chamber.
  • the injection valve member can be brought into the open position by means of an actuator of an actuator arrangement.
  • a hydraulic transmission element is disposed between the actuator and the injection valve member.
  • the hydraulic transmission element has a base body forming a peripheral wall and two membrane-like elements fixedly connected to the base body at the respective end faces.
  • the main body forms with the two membrane-like elements a cavity which is filled with a hydraulic fluid.
  • the one membrane-like element is assigned to the actuator and the other membrane-like element to the injection valve member.
  • the cross-sectional area of the membrane-like element assigned to the actuator is greater than the cross-sectional area of the membrane-like element assigned to the injection valve member.
  • a needle-shaped injection valve member is disposed in a high-pressure chamber, which is connected to a high-pressure fuel inlet, and which cooperates with its one end with an injection valve seat. If the injection valve member lifted from the injector seat, fuel is injected from the high-pressure chamber under very high pressure in a combustion chamber of an internal combustion engine. With its other end, the injection valve member defines a control chamber, which is connected via a connection having a throttle passage with the high-pressure fuel inlet and thus the high-pressure chamber.
  • the high-pressure chamber can be connected to the side opposite the injection valve member by means of an electromagnetically operated pilot valve with a low-pressure chamber and separated from this.
  • the injection valve member is guided in two axially spaced apart areas in a close sliding fit. Between these areas, the injection valve member passes through an annular space which is connected to the low-pressure space.
  • the close sliding fit serves to seal the Control room and the other of the sealing of the high-pressure chamber.
  • fuel flows into the annulus, causing leakage losses.
  • fuel flows out of the control chamber into the low-pressure space during each injection process through the pilot valve, which likewise causes losses.
  • the actuator arrangement has a piezoelectric actuator, which cooperates with a piston element which limits the control chamber with its side facing away from the actuator. The leakage fuel flowing out of the control chamber along the piston element is led away through a low-pressure drain line.
  • an actuator which controls the movement of an injection valve member is sealed off from the spaces of the fuel injection valve filled with fuel by means of a sealing element.
  • the control of the injection valve member is effected by the deflection of the example formed as a diaphragm sealing element by means of the actuator assembly.
  • a fuel injection valve according to the invention requires neither a low-pressure chamber nor a line for the return of fuel into a fuel storage tank. No fuel can escape from the fuel injection valve, except during an injection process through the injection openings into the combustion chamber. Since inventive fuel injection valves operate without a pilot valve, there occur no signs of wear, caused for example by cavitation in the discharge of the fuel on.
  • the fuel injection valve according to the invention opens up a new field of application in addition to the diesel area. It is also suitable for the Injection of gasoline (or other fuels with low viscosity), which is supplied, for example, by means of common rail technology, under a very high pressure to about 1000 bar or more, the injection valve is supplied. As a result, an extremely good atomization during injection is achieved, which can not be achieved satisfactorily at conventional pressures of 80 to 120 bar of known direct gasoline injection systems. Gasoline tends at discharge to vapor bubble formation, which is prevented by a novel fuel injection valve without pilot valve, since no gas flows out into a low-pressure space.
  • fuel injector has a housing 10 through which extends along a housing axis 12 extending recess 14.
  • the recess 14 is formed to the housing axis 12 substantially rotationally symmetrical and stepwise tapered or widening.
  • a tubular valve seat member 16 is inserted with an end portion; on the valve seat member 16 is an injection nozzle 18 at the opposite free end educated.
  • the injector 18 On the inboard side, the injector 18 has an injector seat 20 in the shape of the skirt of a truncated cone. With this injector seat 20, a needle-shaped injection valve member 22 cooperates, the istjoner end portion is formed correspondingly tapered, to abut sealingly in the closed position on the injection valve seat 20.
  • the injection valve seat 20 defines a high-pressure space 24, which is connected by means of a fuel supply channel 26 formed in the housing 10 to a high-pressure fuel inlet 28 - high-pressure fuel connection.
  • the high-pressure fuel inlet 28 is connected in a known manner with a common rail injection system which supplies fuel to the fuel injection valve at a pressure of up to 1000 bar or higher (in the case of diesel application also over 2000 bar).
  • the valve seat element 16 is held in the housing 10, for example by means of an interference fit, and has nozzle openings 30 downstream of the injection valve seat 20 in order to inject fuel at very high pressure into the combustion chamber of an internal combustion engine when the injection valve is open.
  • the injection valve member 22 has in the radial direction projecting guide ribs 32, by means of which it is guided displaceably on the valve seat member 16 in the axial direction.
  • the needle-shaped, the high-pressure chamber by cross-injection valve member 22 is guided with its the injection valve seat 20 remote end portion 34 in a needle guide 36 in sliding fit.
  • the needle guide 36 is formed on a needle guide element 38, which is inserted from the valve seat member 16 side facing away into the housing 10 and is sealingly supported in this by means of a radially projecting circumferential flange on a shoulder 40.
  • the pressed-on by means of a ring screw 42 to the shoulder 40 flange seals the high-pressure chamber 24 so that no fuel between the housing 10 and the needle guide member 38 from the high-pressure chamber 24 in a Akutatoran extract 44 receiving portion of the housing 10 can flow.
  • a sealing element 45 in the form of a membrane 46, which spans the hollow rotationally symmetrical needle guide element 38 and preferably made of metal, in particular steel.
  • the diaphragm 46 seals off the actuator arrangement 44 from a control chamber 48 which is peripherally delimited by the needle guide element 38 and on the side opposite the diaphragm 46 from an end face 50 of the injection valve member 22.
  • the control chamber 48 is connected by the needle guide 36 with the high-pressure chamber 24.
  • the flow cross section between the needle guide element 38 and the injection valve member 22 unfolds such a throttling effect that when deflecting the diaphragm 46 by means of the actuator arrangement 44 substantially more volume is displaced than in the same time fuel from the high-pressure chamber 24 into the control chamber flow in or can flow out vice versa ,
  • the sliding fit in the needle guide 36 for example, a game of a few micrometers.
  • the exposed end face of the sleeve-like needle guide element 38 forms a counter-stop 52, which with a on the injection valve member 22 in the form a circumferential bead formed stop 54 cooperates.
  • the stop 54 and counter stop 52 define the maximum open position of the injection valve member 22.
  • the maximum stroke of the injection valve member 22 is indicated by H.
  • annular disc 56 is inserted between the eyebolt 42 and the diaphragm 46.
  • the annular disc 56 and eyebolt 42 are spaced apart by an actuator shaft 58, which abuts with its convex end face 60 to the corresponding concave shaped exposed portion of the diaphragm 46.
  • actuator shaft 58 which abuts with its convex end face 60 to the corresponding concave shaped exposed portion of the diaphragm 46.
  • the actuator shaft 58 is reciprocated in the axial direction by means of an actuator, which is preferably an electrically driven piezoelectric or magnetostrictive actuator 62.
  • the electrical connection conductors for the actuator 62 are designated 64.
  • the actuator 62 is in an actuator housing 66 taken, which with its diaphragm 46 facing the housing side abuts against a further shoulder 40 'of the housing 10 and is held by means of a threaded into the housing further eyebolt 42' on the further shoulder 40 'in abutment.
  • fuel injector operates as follows.
  • the actuator 62 is driven such that the actuator shaft 58 is in its end position, in which the diaphragm 46 in the direction of the control chamber 48 maximum is distracted.
  • the pressure between the high pressure chamber 24 and the control chamber 48 is balanced. Since the sum of the pressure of the fuel in the direction of the injection valve seat 20 surfaces of the injection valve member 22 is greater than the sum of the counteracted with fuel pressure surfaces, the injection valve member 22 is held on the injection valve seat 20 in abutment.
  • the actuator 62 is driven such that the actuator shaft 58 is withdrawn.
  • the diaphragm 46 moves with the actuator shaft 58 in the direction away from the injection valve seat 20. Since in this short time of movement little or no fuel can flow via the needle guide 36 into the control chamber 48, the volume of the control chamber 48 is slightly increased and displaced by this movement of the diaphragm 46, resulting in the injection valve member 22 being lifted off the injection valve seat 20 towards the inside leads.
  • the pressure in the control chamber 48 is reduced by the movement of the diaphragm 46, which is compensated by the movement of the injection valve member 22 immediately practically completely again.
  • the stop 54 abuts the counter-stop 52.
  • the injection process is terminated by actuating the actuator 62 such that the actuator shaft 58 moves in the direction of the valve seat element 16, so that the injection valve member 22 seals against the injection valve seat 22.
  • the fuel injector is now for the next one Injection process ready.
  • the fuel injection valve is thus also particularly well for pre- or multiple injections, as well as for a course of injection by deliberate choice of the course of movement of the actuator 62 and consequently of the injection valve member 22 both when opening and, where appropriate, when closing.
  • the actuator assembly 44 Since the actuator assembly 44 is completely sealed against the fuel-filled spaces of the fuel injection valve and the control of the injection valve member 22 is carried out without a pilot valve, no fuel losses occur.
  • the fact that the space 63 is not hydraulically connected or connectable to the high-pressure space 24 nor to the control space 48 does not mean that this space is empty (i.e., under vacuum) or must be filled exclusively with air. It may be advantageous to fill this space partially or completely with a hydraulic fluid, e.g. with hydraulic oil to ensure lubrication and durability of the actuator assembly 44.
  • Fig. 2 shown embodiment of the inventive fuel injection valve is that according to Fig. 1 very similar.
  • the same reference numerals are used for the same or equivalent parts as in Fig. 1 and only the differences are explained below.
  • the actuator shaft 58 passes through the actuator 62 and is connected to it on the side facing away from the membrane 46 side 62 '.
  • the direction of movement of the Aktuatorschafts 58 compared to that in the Embodiment according to Fig. 1 vice versa for the same control of the actuator 62.
  • positioning pins 70 penetrate annular disc 56, diaphragm 46 forming sealing element 45, and flange of needle guide element 38. Since these positioning pins 70 engage corresponding positioning holes 72 in housing 10, the position of said parts relative to housing 10 is in the radial direction as well set in the rotational position.
  • bead 54 of the injection valve member 22 forming the stop 54 is encompassed with clearance by a support sleeve 74, which is supported on the one hand at the free end of the needle guide element 38 and on the other hand against a compression spring 76, which in turn is supported on the injection valve member 22 by means of a support disk 78.
  • the compression spring 76 holds the injection valve member 22 at the injection valve seat 20 in abutment when the high-pressure chamber 24 is not under high pressure or the actuator 62 should fail. Moreover, the functioning of the in the Fig. 2 shown fuel injection valve that of in Fig. 1 shown embodiment, but the actuator 62 is to be controlled accordingly reverse.
  • the training according to Fig. 3 is that according to Fig. 1
  • the longitudinal axes 80, 82 of the actuator assembly 44 and the injection valve member 22 are relatively parallel but parallel to each other.
  • This embodiment allows according to the embodiment according to Fig. 1 a more compact design of the housing 10th
  • the axis 80 could also be in an (acute) angle to the longitudinal axis 82.
  • the needle guide element 38 is no longer designed purely rotationally symmetrical.
  • the section forming the needle guide 36 is rotationally symmetrical with respect to the longitudinal axis 82, whereas the part adjoining the membrane 46 forming the sealing element 45 is at least approximately rotationally symmetrical to the longitudinal axis 80.
  • no eyebolt 42 is present; the actuator housing 66 rests directly on the annular disk 56.
  • the actuator housing 66 is pressed by means of the further eyebolt 42 'against the annular disc 56 and thus the membrane 46.
  • Fig. 4 shows a portion of another embodiment of a fuel injection valve according to the invention.
  • the valve seat member 16 is frontally mounted on the housing 10 in this embodiment and secured by a coupling nut 84 thereto. Between the housing 10 and the injection valve member 22, the sealing element 45 forming membrane 46 and the flange of the needle guide member 38 is clamped.
  • the fuel supply passage 26 runs from the housing 10 through these two parts to the valve seat member 16
  • the high pressure chamber 24 is thus exclusively - with the exception of the not shown fuel high pressure inlet and the Brennstoffzu Switzerlandkanal 26 - arranged in the valve seat member 16.
  • the diaphragm 46 is cup-shaped and of the actuator assembly 44 is shown only a part of the Aktuatorschafts 58, which engages in the diaphragm 46 and at the end face 60 corresponding to the diaphragm 46 is flat and formed along the edge with a suitable radius.
  • Dashed on the needle guide element 38 are each a rib-like, radially outwardly projecting guide element of two guides 38a and 38b shown, of which only one is necessary to center the needle guide element 38 in the valve seat member 16 with respect to the housing axis 12 and align.
  • the guides 38a, 38b have in the circumferential direction evenly distributed preferably three guide elements.
  • the diameter D1 of the actuator shaft 58 is, for example, 5 mm.
  • the cup-shaped part of the diaphragm 46 abuts on the actuator shaft 58 and is thin-walled, so that the effective area of the diaphragm 46 corresponds approximately to a diameter of 5.5 to 6 mm.
  • the diameter D2 of the needle guide 36 or the injection valve member 22 in the needle guide 36 selected between 2.5 to 3 mm there is a ratio of about 4.
  • the outer diameter D3 of the cooperating with the injection valve seat 20 part the injection valve member 22 is selected at about 2 mm.
  • a throttle passage 86 can furthermore be formed on the needle guide element 38 in a variant. It is also conceivable, seen in the radial direction, from the fuel supply 26 against the inside of the needle guide member 38 facing side of the diaphragm 46 form with a defined roughness to produce a desired leak between the control chamber 48 and the high-pressure chamber 24 similar to the throttle passage 86. Instead of the throttle passage 86 and / or this leak, a defined greater clearance between the needle guide element 38 and the injection valve member 22 can be selected to increase the reliability in the event that the actuator 62 should fail.
  • the injection valve member 22 could be formed with a stop 54 as in the embodiments described above.
  • a compression spring 76 as in the embodiment according to Fig. 2 , together with the throttle opening 86 and the defined leak between the high-pressure chamber 24 and the control chamber 48, in the embodiment according to Fig. 4 , the reliability in the failure of the actuator 62 can also increase.
  • the embodiment of the cup-shaped membrane 46 of Fig. 4 is quite favorable for the function at high fuel pressure, since the relatively thin diaphragm 46 is fully supported on the front end of the Aktuatorschafts 58 and thus, compared with the embodiments of Fig. 1 to 3 , Has no free area that can oppose the pressure force of the fuel no counter force.
  • the critical transition region 46c of the diaphragm 46 with gradually increasing wall thickness of the thin-walled cylinder jacket-shaped part 46a in the perpendicular sufficientsteehen, thicker area 46b, which forms a flange, can still be supported on the actuator shaft 58.
  • the flat front portion 46d of the diaphragm 46 could also be made thicker than with Fig. 4 shown.
  • the membrane 46 is in one piece, it is preferably produced as a deep-drawn part.
  • the membrane 46 may also consist of several joined parts. For example, in the transition region 46c or in the vicinity thereof, the thin membrane head may be welded to the thicker region 46b. Likewise, the connection of the (possibly thicker) front part 46d to the thinner part of the diaphragm 46 can be realized. Other types of connection of a multi-part membrane 46 are also conceivable.
  • the other membranes 46 may be made of several parts.
  • the thinner cylindrical portion 46a of the diaphragm 46 shortens or expands in accordance with the movement of the actuator shaft 58 in the elastic region of the membrane material.
  • strains 20 to 30 microns per 10 mm membrane length are quite feasible. If other materials are used, e.g. Titanium, titanium alloys or other special alloys, are much larger, elastic strains, up to or over two times, feasible.
  • the actuator shaft 58 must at the same time be as rigid as possible. This can be strongly influenced by suitable choice of material. For example, instead of steel, an actuator shaft 58 made of ceramic material may be well suited.
  • a micro-relative motion results between the inner wall of the cylindrical portion 46a of the diaphragm 46 and the peripheral surface of the actuator shaft 58.
  • friction and wear must be minimized. This can be done, for example, by suitable Feeds, material pairings or lubrication by means of the hydraulic fluid in the space 63 (FIG. Fig. 1 ), coupled with corresponding small lubrication grooves, grooves, micro-lubrication pockets and the like on the peripheral surface of the actuator shaft 58.
  • the longitudinal axes 80, 82 of the actuator assembly 44 and the injection valve member 22 are depressed relative to one another.
  • the valve seat member 16 is placed on the front side of the housing 10 and held by the coupling nut 84 at this.
  • a thick washer 88 is inserted with a passage.
  • the thick annular disc 56 which clamps the sealing element 45 forming diaphragm 46 between itself and the this side end face of the valve seat member 16 circumferentially.
  • the annular disc 56 is supported with its side facing away from the diaphragm 46, such as the washer 88, on the housing 10 from.
  • the membrane 46 in turn seals the control chamber 48 and thus the high pressure chamber 24 from the actuator assembly 44 from.
  • the needle guide 36 is formed on the valve seat member 16 and the needle guide 36 closes on the injection valve seat 20 side facing with a annular enlargement of the recess in the valve seat member 16 of the high-pressure chamber 24, which in turn extends to the injection valve seat 20.
  • the high-pressure chamber 24 is by means of the fuel supply channel 26 which extends in the valve seat member 16 from the extension to the intermediate disc 88 and from there parallel to the longitudinal axis 88 through the washer 88 and in the housing 10 to the high-pressure fuel inlet, not shown.
  • the needle guide 36 which in turn may be a tight sliding fit, formed on the valve seat member 16.
  • the functioning of the in the Fig. 5 shown training form equal to that according to the other forms of training described above.
  • Fig. 7 shows one of the embodiment according to Fig. 4 similar variant, but no needle guide element 38 and no control chamber 48 are present.
  • the valve seat element 16 delimiting the high-pressure chamber 24 on the circumference and the injection side lies sealingly on the flange-like, thicker region 46b of the sealing element 45 forming Diaphragm 46 and presses them, under the action of the union nut 84 sealingly against the housing 10 at.
  • the needle-like injection valve member 22 which is displaceably guided in the direction of the housing axis 12 by means of guide ribs 32, in turn passes through the high-pressure space 24 and cooperates with its conical end area with the injection valve seat 20 formed on the valve seat element 16.
  • the membrane 46 has in the region of the front part 46 d an opening 90, which is penetrated by the injection valve member 22.
  • the membrane 46 is welded along this opening 90 with a shoulder surface 92 'of a thickening 92 of the injection valve member 22.
  • the thickening 92 is thus arranged in the interior of the region bounded by the cup-shaped diaphragm 46 and separated from the high-pressure chamber 24 and cooperates with its flat end face 50 with the likewise flat end face 60 of the Aktuatorschafts 58.
  • the diaphragm 46 and the actuator shaft 58 are formed the same and their interaction is identical to that in FIG Fig. 4 shown and related above Fig. 4 described.
  • the diaphragm 46 and the actuator shaft 58 as in Fig. 4 shown, wherein, however, the front part 46d of the diaphragm 46 is thick-walled and has a blind hole-like central recess for receiving this side end portion of the injection valve member 22.
  • the injection valve member 22 is the same as in Fig. 4 shown trained and it is with the front part 46d of the membrane 46 welded.
  • the front part 46d of the diaphragm 46 and the injection valve member 22 are thus, as in the embodiment according to Fig. 7 , firmly connected together and move towards each other in the direction of the housing axis 12. Same as in Fig.
  • the diaphragm 46 delimits the high-pressure space 24 closely relative to the actuator arrangement 44.
  • the actuator shaft 58 and the thickening 92 of the injection valve member 22 have the same diameter and support the cylindrical thin-walled shell portion 46a of the diaphragm 46 from. This is particularly long trained and thus has an extra large Dehnaller.
  • the injection valve member 22 is held on the injection valve seat 20 in sealing engagement.
  • the actuator shaft 58 is moved away from the injector seat 20. This movement follows the injection valve member 22 immediately as a result of the high-pressure fuel in the high-pressure chamber 24 to the diaphragm 46 in the axial direction force exerted.
  • the actuator shaft 58 and the injection valve member 22 are moved toward the injection valve seat 20 by means of the actuator 62 until the injection valve member 22 rests thereon again.
  • Fig. 8 shows a further embodiment, which in terms of construction of those according to Fig. 4 very similar and identical in function.
  • the essential constructive difference is that the sealing element 45 is no longer formed as a continuous pot-shaped membrane 46, but as a membrane-like cup-shaped sealing element 45 without pot bottom.
  • circular-cylindrical part 46 a of the sealing element 45 is flat and non-positively on the actuator shaft 58 at.
  • the sealing and taker-resistant concerns is supported by the large pressure difference, which prevails between the control chamber 48 and the control chamber 48 side facing away from the sealing element 45.
  • This pressure difference presses the cylindrical part 46a of the sealing element 45 with great force against the actuator shaft 58.
  • the actuator 62 is thus tightly separated from the control chamber 48 by means of the sealing element 45 and the actuator shaft 58.
  • the sealing element 45 is, like the membrane 46 in Fig. 4 , held with a thicker, flange forming portion 46 b between the needle guide member 38 and the housing 10 sealingly clamped.
  • a transition region 46c the wall thickness continuously decreases from the region 46b to the cylindrical part 46a; seen in section, the sealing element in the transition region 46c has the shape of a wedge.
  • magnetostrictive and electrostrictive (piezoelectric) actuators can perform a relatively small stroke with great force, they are particularly suitable for interaction with membranes; due to the small stroke these are dynamically low stress, which contributes to a long life, although the Pressure difference between the two sides of the membrane is very large.
  • injection valve member 22 is not controlled pilot valve.
  • actuators 62 are used with a stroke that is greater than the stroke to be executed by the injection valve member 22, in embodiments with a control chamber 48, the effective area ratios of diaphragm 46 and injection valve member 22 can be chosen such that a Hubuntersch occurs. If appropriate, the area ratios can also be selected so that the stroke of the actuator shaft 58 corresponds to that of the injection valve member 22.
  • the inventive fuel injectors shown need not have strong closing springs, as known pilot valve controlled fuel injectors.
  • closing springs can be used to press the needle guiding element 38 delimiting the control space 48 sealingly against the flange-like area 46b of the sealing element 45.
  • the closing spring would be supported at one end on the injection valve member 22 and the other end on the needle guide element 38. This would be sleeve-shaped - without protruding in the radial direction Clamping flange - formed and would be supported with an annular end face on portion 46 b of the sealing element 45.
  • a tubular intermediate piece would be used which has a radial distance to the needle guide element 38 in order to ensure the flow connection between the fuel feed channel 26 and the high-pressure chamber 24.
  • the region 46b would be pressed by means of the intermediate piece sealingly against the end face of the housing 10.

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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)

Claims (14)

  1. Soupape d'injection de carburant pour l'injection de carburant intermittente dans la chambre de combustion d'un moteur à combustion interne, comprenant un boîtier (10), un espace haute pression (24) connecté à une entrée de carburant haute pression (28) et limité par un siège de soupape d'injection (20), un espace de commande (48), qui est prévu pour être rempli de carburant, un organe de soupape d'injection (22) en forme d'aiguille disposé dans l'espace haute pression (24), qui coopère d'une part avec le siège de soupape d'injection (20) et un agencement d'actionneur (44) comprenant un actionneur qui influencé la pression dans la chambre de commande pour commander le mouvement de l'organe de soupape d'injection (22), un élément d'étanchéité, qui maintient l'actionneur (62) exempt de carburant, étant disposé entré l'espace de commande (48) et l'actionneur (62) fixement et hermétiquement avec sa bride annulaire par rapport au boîtier (10) et étant dévié au moyen de l'agencement d'actionneur (44) pour déplacer l'organe de soupape d'injection (22), caractérisée en ce que l'organe de soupape d'injection (22) est monté de manière déplaçable d'autre part à la manière d'un piston en ajustement glissant sur un guide d'aiguille (36) disposé entre l'espace de commande (48) et l'espace haute pression (24) et limite l'espace de pression (48).
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que l'élément d'étanchéité présente une membrane (46) qui sépare l'espace de commande (48) de l'agencement d'actionneur (44).
  3. Soupape d'injection de carburant selon la revendication 2, caractérisée en ce que l'agencement d'actionneur (44) présente une tige d'actionneur (58) actionnée par l'actionneur (62), qui coopère par un côté frontal (60) avec la membrane (46).
  4. Soupape d'injection de carburant selon la revendication 2 ou 3, caractérisée en ce que la membrane (46) est réalisée en forme de pot et la tige de l'actionneur (38) vient en prise dans la membrane (46).
  5. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que l'élément d'étanchéité est réalisé en forme de membrane et en forme de pot, mais toutefois sans fond de pot, et l'agencement d'actionneur (44) présente une tige d'actionneur (58) actionnée par l'actionneur (62), qui vient en prise à travers l'élément d'étanchéité de manière fixée en entraînement et hermétique.
  6. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 5, caractérisée en ce que l'élément d'étanchéité se compose d'au moins deux parties connectées hermétiquement l'une à l'autre, notamment soudées l'une à l'autre.
  7. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le guide d'aiguille (36) est formé sur un élément de siège de soupape (16) sur lequel est également formé le siège de soupape (20) et qui entoure l'espace haute pression (24).
  8. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le guide d'aiguille (36) est réalisé sur un élément de guide d'aiguille (38) limitant l'espace de commande (48).
  9. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 8, caractérisée en ce que l'ajustement glissant est réalisé sous forme d'ajustement glissant étroit et une connexion (86) réalisant un effet d'étranglement est prévue entre l'espace de commande (48) et l'espace haute pression (24), en dehors de l'ajustement glissant.
  10. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 9, caractérisée en ce que l'organe de soupape d'injection (22) est désaxé par rapport à l'agencement d'actionneur (44).
  11. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 10, caractérisée en ce que la surface de l'élément d'étanchéité à effet de déviation, éventuellement incluant la surface en section transversale de la partie de la tige d'actionneur (38) venant en prise à travers l'élément d'étanchéité, est supérieure à la surface en section transversale de l'organe de soupape d'injection (22) coopérant avec l'espace de commande (48).
  12. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 11, caractérisée en ce que l'organe de soupape d'injection (22) présente une butée (54) qui coopère dans une position d'ouverture maximale admissible de l'organe de soupape d'injection (22) avec une contre-butée (52) qui est disposée fixement par rapport à un boîtier (10).
  13. Soupape d'injection de carburant selon la revendication 8, caractérisée en ce que l'élément de guide d'aiguille (38) présente un guide saillant en forme de nervure (38a, 38b) en vue de son centrage.
  14. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 13, caractérisée en ce que l'agencement d'actionneur (44) présente un actionneur commandé électriquement, piézoélectrique ou magnétostrictif (62).
EP04730814A 2003-05-08 2004-05-03 Soupape d'injection de carburant sans perte Expired - Lifetime EP1620645B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH8092003 2003-05-08
CH10472003 2003-06-16
PCT/CH2004/000266 WO2004099603A1 (fr) 2003-05-08 2004-05-03 Soupape d'injection de carburant sans perte

Publications (2)

Publication Number Publication Date
EP1620645A1 EP1620645A1 (fr) 2006-02-01
EP1620645B1 true EP1620645B1 (fr) 2009-10-07

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EP04730814A Expired - Lifetime EP1620645B1 (fr) 2003-05-08 2004-05-03 Soupape d'injection de carburant sans perte

Country Status (4)

Country Link
EP (1) EP1620645B1 (fr)
AT (1) ATE445098T1 (fr)
DE (1) DE502004010199D1 (fr)
WO (1) WO2004099603A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE447104T1 (de) * 2005-04-14 2009-11-15 Ganser Hydromag Brennstoffeinspritzventil
US9803603B2 (en) 2013-03-01 2017-10-31 Ganser-Hydromag Ag Device for injecting fuel into the combustion chamber of an internal combustion engine
DE102017217991A1 (de) * 2017-10-10 2019-04-11 Robert Bosch Gmbh Injektor zum Dosieren eines Fluids unter hohem Druck und Verfahren zum Betreiben eines solchen Injektors

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19500706C2 (de) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen
DE19802495A1 (de) * 1997-06-19 1998-12-24 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE69911670T2 (de) * 1998-02-19 2004-08-12 Delphi Technologies, Inc., Troy Kraftstoffeinspritzventil
DE50010902D1 (de) * 1999-04-20 2005-09-15 Siemens Ag Fluiddosiervorrichtung
DE19942816A1 (de) * 1999-09-08 2001-03-22 Daimler Chrysler Ag Einspritzventil

Also Published As

Publication number Publication date
EP1620645A1 (fr) 2006-02-01
DE502004010199D1 (de) 2009-11-19
WO2004099603A1 (fr) 2004-11-18
ATE445098T1 (de) 2009-10-15

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