EP0909891B1 - Vanne de commande de fluide - Google Patents

Vanne de commande de fluide Download PDF

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Publication number
EP0909891B1
EP0909891B1 EP98111325A EP98111325A EP0909891B1 EP 0909891 B1 EP0909891 B1 EP 0909891B1 EP 98111325 A EP98111325 A EP 98111325A EP 98111325 A EP98111325 A EP 98111325A EP 0909891 B1 EP0909891 B1 EP 0909891B1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
valve according
connecting space
space
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
EP98111325A
Other languages
German (de)
English (en)
Other versions
EP0909891A1 (fr
Inventor
Roger Potschin
Friedrich Boecking
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 EP0909891A1 publication Critical patent/EP0909891A1/fr
Application granted granted Critical
Publication of EP0909891B1 publication Critical patent/EP0909891B1/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
    • 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
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • F02M2200/706—Valves for filling or emptying hydraulic chamber
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a valve for controlling Liquids according to the preamble of claim 1.
  • a valve for controlling Liquids according to the preamble of claim 1.
  • a valve is known from EP 0 477 400.
  • a problem with such valves is that on Piezo actuator, on the valve member or on the valve housing and in the hydraulic column of the coupling space changes in length occur that need to be balanced. Because the piezo actuator generates a pressure to open the valve in the coupling space, this pressure also leads to a loss of coupling space fluid. To empty the coupling space prevent refilling is necessary.
  • a Compensated for tolerance due to a specified leak create. This has the disadvantage that one in the two possible directions of flow open connection between the coupling space and z. B. provided a reservoir is, because of the resulting flexibility of the hydraulic space the working behavior of the piezo actuator negatively influenced.
  • the known device is so executed that the hydraulic fluid hermetically in Housing is included. In particular, one leads increased volume to a the transmission stiffness of the hydraulic column formed by the coupling space reducing compressibility.
  • valve according to the invention have the advantage over the other that the coupling space always remains sufficiently filled and via the filling valve coupling fluid only in Direction of coupling space from an existing volume unlimited refill can flow.
  • A is disadvantageous change in length of the entire device avoided and high transmission rigidity achieved. This also applies if the piezo actuator, the valve or the housing its length e.g. change when heated should, because such a change in length in the coupling space is compensated for by licking.
  • the device has a simple structure and works safely and reliably.
  • FIG. 1 shows a fuel injection valve in section
  • Figure 2 shows a first embodiment a filling valve
  • Figure 3 shows a second embodiment a filling valve
  • Figure 4 is a diagram the timing of the filling
  • Figure 5 a third Embodiment of a filling valve
  • Figure 6 a Modification of the design according to Figure 5
  • Figure 7 a Detail of the embodiment according to Figure 6
  • Figure 8 a Modification of the design according to Figure 6 and Figure 9 a another version of the types according to Figures 6 and 8.
  • the valve according to the invention is used in a Fuel injector, which is mainly in the Section is shown in Figure 1.
  • This injector has a valve housing 1, in which in a Longitudinal bore 2 is a valve needle 3, which is also in known way not shown here by a Closing spring can be preloaded in the closing direction.
  • On At one end is the valve needle with a conical shape
  • Provide sealing surface 4 on the protruding into the combustion chamber Tip 5 of the valve housing cooperates with a seat 6, from which lead out injection openings that the inside of the Injection valve, here with the valve needle 3 surrounding filled annular space under fuel under injection pressure 7 connect to the combustion chamber so as to close an injection complete when the valve needle is lifted from its seat Has.
  • the annular space is with a further pressure space 8 connected, constantly in connection with a pressure line 10 stands over which the fuel injection valve from a High-pressure fuel accumulator 9 fuel under Injection pressure is supplied.
  • This high fuel pressure also acts in the pressure chamber 8, and there on one Pressure shoulder 11, via the nozzle needle in a known manner lifted from its valve seat in suitable conditions can be.
  • valve needle At the other end of the valve needle is in a cylinder bore 12 out there and closes with its end face 14 a control pressure chamber 15 which via a throttle connection 16 is permanently connected to an annular space 17 which, like the pressure chamber 8 always with the high-pressure fuel reservoir communicates.
  • Axial leads from control pressure chamber 15 a throttle bore 19 to a valve seat 20 of a control valve 21.
  • the valve seat acts Valve member 22 of the control valve together, which in lifted state a connection between the control pressure chamber 15 and one with hydraulic pressure medium, here preferably diesel fuel, which is the device anyway is available, creates filled low-pressure chamber 18, which in turn is constantly connected to a relief room is.
  • hydraulic pressure medium here preferably diesel fuel
  • valve member 22 In the low pressure chamber 18 is a valve member 22 arranged in the closing direction loading compression spring 24, the acts on the valve member 22 towards the valve seat 20, so that in the normal position of the control valve the connection between low pressure chamber 18 and control pressure chamber 15 is closed.
  • the low pressure space 18 can be considered to the spring arranged there also called the spring chamber become. Since the face of the valve needle in the The area of the control pressure chamber is larger than the area of the Pressure shoulder 11, keeps the same fuel pressure in the Control pressure chamber, which now also prevails in the pressure chamber 8 the valve needle 3 in the closed position. Is this However, valve member 22 is lifted, so the pressure in the the throttle connection 16 from the high-pressure fuel accumulator 9 decoupled control pressure chamber 15 relieved.
  • Valve needle 3 possibly against the force of the closing spring quickly and on the other hand can be in the closed position again brought as soon as the valve member 22 in Closing position comes. From that point on, it builds up quickly via the throttle connection 16 the original high Fuel pressure in the control pressure chamber 15 again.
  • the control valve has one to it Actuation determined piston 25 on the valve member 22 acts and can be actuated by a piezo actuator 32.
  • the Piston 25 is in a in a housing part 26 of the Fuel injection valve arranged guide bore 28 tightly guided and limited, as can be seen in Figure 2, with its end face 29 one with hydraulic pressure medium, here fuel, filled coupling space 30 on its opposite wall from one in one Actuator guide bore 39 guided actuator piston 31 larger Diameter is completed, the part of the piezo actuator 32 is and also by one in the coupling space arranged spring 49, 65 (see Figures 3 and 6) with the Piezo actuator can be non-positively coupled.
  • the Coupling space 30 is used due to the different Piston surfaces of the two pistons 25 and 31 as Translator room by having a small stroke of the Piezo actuator piston 31 in a larger stroke of that Control valve 21 actuating piston 25 translated.
  • Excitation of the piezo actuator with which in principle only small Actuation paths can be achieved with one translated travel of the piston 25 adjusted and that Lifted valve member 22 from its seat 20. That has one Relief of the control pressure chamber, which in turn Opening the valve needle 3 causes.
  • At the work of the Control valve and the pressure ratio occur in the Coupling space 30 very high pressures.
  • this filling valve 33 is in the Embodiment of Figure 2 designed so that the Piston 25 is designed as a stepped piston, the in Diameter of smaller piston part 34 in the guide bore 28 is guided tightly and at the end of the coupling space 30 limited and over a shoulder that a valve seat 35 for the filling valve 33 forms one in diameter larger piston part 78 passes into the spring chamber 18th dips.
  • a closing body 37 of the filling valve 33 is from one in one to the guide hole connecting bore 80 in valve housing 1 tightly guided Piston ring formed, one to the side of the valve 21 as a sealing surface 36 formed end face which is conical is formed and has an annular sealing edge 38 which comes to rest on the valve seat 35. Between the inner Shell surface of the closing body 37 and the piston part 34 is a distance is provided.
  • the actuator guide bore 39 and guide bore 28 of the Pistons 25 can especially when increasing pressure in Coupling space 30 leaks occur.
  • actuator piston 31 and the actuator guide bore 39 is one leadership-related leakage ring gap 79.
  • the Filling of the coupling space 30th from a control room 41, via the filling valve 33 allows.
  • the filling valve 33 as Check valve is formed by the closing body 37 by a spring 42, which is supported on the valve housing the valve seat 35 is loaded.
  • control valve When the control valve is opened, it lifts on the piston 25 attached valve seat 35 and the control chamber 41 is from Leak oil chamber filled. Presses when closing the valve the piston ring 37 on the valve seat 35 and seals the Control room 41 onwards. This creates in the control room Overpressure, which is due to the selectable stiffness of the Control room 41 can be adjusted. The overpressure causes a leak in the leakage connection 40, which leads to Coupling space 30 is directed. That way then the coupling space is filled. Another advantage is that the piston ring 37 when the filling valve closes 33 acts as a vibration damper.
  • FIG. 3 shows a filling valve 43 that immediately is arranged on the coupling space 30.
  • a piston has 25 a head 44 whose underside as the closing body 45 of the Filling valve 43 is formed.
  • One for the closing body 45 certain valve seat 46 is fixed to the housing 26 intended. It serves as a valve stop.
  • Two leadership leaks are with the columns 47 and 48 in the piston 25 and Actuator piston 31 shown.
  • the piston 25 is a shaft 27 of a pilsiform valve member 22, and a Compression spring 24 presses the piston 25 against the coupling space 30, in which a spring 49 is additionally arranged.
  • the devices shown in Figures 5 to 9 they are all alike in that they have one through hole provided piston 25 and that this Through hole on one side of the piston 25 with a Filling valve are provided.
  • Figure 5 one applies the side of the piston 25 facing away from the coupling space 30 arranged filling valve the reference number 54. It will formed by a valve seat 55 on an end face of the Piston 25 and by a closing member 56 on the shaft 27, the only by an appropriately trained end face the shaft 27 is adjusted.
  • the piston is preferably 25 spherical on its end face with a flat radius formed by an angular offset from the piston 25 and Compensate control valve 21 and their plan stop.
  • the piston 25 is along its entire length provided a through hole 57, the mouth 58 for Reduction of wear (lower Hertzian Compression) is enlarged in diameter, and in one Leakage liquid chamber 59 is located.
  • Figure 6 shows a variant in which a filling valve 60 is arranged directly on the coupling space 30. Also here is the piston 25 'along its entire length Through hole 61 provided on their the coupling space 30 facing away into one in a leakage liquid chamber 62 lying cross slot 63 (cf. Figure 7) of the front of the shaft 27 of the Valve member 22 is released.
  • the piston 25 ' has also an outer collar 81, on his in the Leakage chamber diving end of the piston allowed to play a little from the closed position lift off the closing member 22 of the control valve 21, before engaging with this outer waistband on a bulkhead 82 of the case drain chamber.
  • the filling valve 60 has a hollow conical valve seat 66 at the upper mouth of the through hole 61.
  • a ball works as a closing body 67 together, which is subject to the force of a spring 68 Coupling space 30 is arranged and on the actuator piston 31 supported. Is the pressure below the closing body 67 larger than above, the closing body lifts after the Piston 25 'with its outer collar 81 on the end wall 82 for Plant has come off and it takes place with the opening of the Through hole 61 between the coupling space and Leakage chamber 62 a pressure equalization instead. To do that To keep the volume of the coupling space 30 as small as possible, the ball closing body 67 is lowered in the piston.
  • Closing body 69 of a filling valve 70 also only be formed as a spherical section, as in the figure 8 is shown. With a flat valve seat angle is a Small bore diameter of the through bore necessary. Therefore, in the embodiment according to FIG. 8 there is a through hole 71 directly below the closing body 69 provided a constriction 72, below this is the Through hole 71 again.
  • Figure 9 shows that it is also possible to use a filling valve 73 with a ball as a closing body 74 and with a To provide valve seat 75 at the lower end of the piston 25.
  • a through hole bears the reference number 76 here.

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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)
  • Electrically Driven Valve-Operating Means (AREA)

Claims (18)

  1. Vanne (22) pour commander un liquide, comprenant un organe d'obturation (22) sollicité par un ressort de compression (24) dans le sens de la fermeture pour venir en appui contre un siège de soupape (20), un piston (25) destiné à actionner l'organe d'obturation, ce piston fermant comme cloison mobile, une chambre de couplage (30) remplie de liquide hydraulique sous pression, et limitée de l'autre côté par un piston d'actionneur (31) d'un actionneur piézo-électrique (32) dont la course active crée une augmentation de pression dans la chambre de couplage (30), et cette augmentation de pression, le piston (25) l'organe d'obturation (22) contre la force du ressort de compression (24) dans le sens de l'ouverture de la vanne,
    caractérisée en ce que
    le piston (25) est guidé dans un perçage de guidage (28), et
    entre ce perçage et la surface enveloppe du piston (25) on a une liaison de fuite relie la chambre de couplage (30) à une chambre basse pression (18) fournissant et recevant du liquide hydraulique sous pression, et la liaison entre la chambre de couplage (30) et la chambre basse pression (18), comporte une soupape de remplissage (33, 43, 54, 60, 70, 73) prévue sur le piston (25) destiné à actionner l'organe d'obturation (22).
  2. Vanne selon la revendication 1,
    caractérisée par
    une chambre de commande (41) entre la chambre de couplage (30) et la soupape de remplissage (33), et à partir de cette chambre de commande, la chambre de couplage (30) peut être remplie de manière complémentaire par la liaison de fuite (40).
  3. Vanne selon l'une quelconque des revendications 1 et 2,
    caractérisée en ce que
    le piston (25) est un piston étagé (25) avec une partie de piston étagé (34) de grand diamètre et une partie étagée (78) de petit diamètre tournée vers la chambre de couplage (30), et ayant entre les parties étagées, un épaulement qui forme un siège de soupape (35) pour un organe d'obturation (37) de la soupape de remplissage (33), cet organe étant sollicité par un ressort (42) vers le siège de soupape (35).
  4. Vanne selon l'une quelconque des revendications 1 à 3,
    caractérisée en ce que
    l'organe d'obturation de la soupape de remplissage (33) est formé par une surface frontale (36) d'un anneau de piston (37) guidé de manière étanche dans un perçage (80) faisant suite au perçage de guidage (28).
  5. Vanne selon la revendication 4,
    caractérisée en ce que
    la surface frontale (36) est de forme conique et présente une arête d'étanchéité (38), annulaire.
  6. Vanne selon la revendication 1,
    caractérisée en ce que
    le piston (25) est muni d'une tête (44) prévue dans la chambre de couplage (30), cette tête étant réalisée comme organe d'obturation (45) pour la vanne de remplissage (43), cet organe coopérant avec l'embouchure du perçage de guidage (28) dans la chambre de couplage (30).
  7. Vanne selon la revendication 6,
    caractérisée en ce que
    le piston (25) couplé solidairement à l'organe d'obturation (22) est sollicité par le ressort de compression (24) vers la chambre de couplage (30), la soupape de remplissage étant ouverte lorsque l'organe d'obturation (22) est en position de fermeture et cette soupape étant fermée lorsque l'organe d'obturation (22) est ouvert.
  8. Vanne selon la revendication 1,
    caractérisée en ce que
    le piston (25) est muni d'un perçage traversant (57, 61, 71, 76) par le quel la chambre de couplage (30) est reliée à une chambre de liquide de fuite (59, 62), et l'embouchure du perçage traversant sur l'une des faces frontales du piston (25) est commandée par la soupape de remplissage (54, 60, 70, 73).
  9. Vanne selon la revendication 8,
    caractérisée en ce que
    le piston (25) comporte sur l'une de ses faces frontales, une surface d'étanchéité (55, 66, 75) de la soupape de remplissage (54, 60, 70, 73).
  10. Vanne selon la revendication 8,
    caractérisée en ce que
    la face frontale comporte une surface d'étanchéité (66, 75), en forme de cône concave, entourant la sortie du perçage traversant, et contre laquelle un organe d'obturation (67, 69, 74) de la soupape de remplissage (60, 70) est pressé par un ressort (68).
  11. Vanne selon la revendication 10,
    caractérisée en ce que
    l'organe d'obturation (67, 74) est une bille.
  12. Vanne selon la revendication 10,
    caractérisée en ce que
    l'organe d'obturation (69) est un segment de bille.
  13. Vanne selon l'une quelconque des revendications 8 à 12,
    caractérisée en ce que
    la surface d'étanchéité (66) est prévue sur le côté du piston (25) tourné vers la chambre de couplage (30).
  14. Vanne selon la revendication 11,
    caractérisée en ce que
    la surface d'étanchéité est prévue sur le côté du piston (25) non tourné vers la chambre de couplage (30).
  15. Vanne selon l'une quelconque des revendications 13 ou 14,
    caractérisée en ce que
    le ressort s'appuie contre le piston (31) de l'actionneur.
  16. Vanne selon la revendication 9,
    caractérisée en ce qu'
    une embouchure (58) du perçage traversant (57) est entourée dans la chambre de liquide de fuite (59) par la surface d'étanchéité qui coopère comme siège d'étanchéité avec la face frontale de l'organe de soupape (22, 27) pénétrant dans la chambre de liquide de fuite.
  17. Vanne selon la revendication 16,
    caractérisée en ce que
    l'embouchure (58) du perçage traversant (57) a un diamètre agrandi.
  18. Vanne selon l'une quelconque des revendications 16 ou 17,
    caractérisée en ce que
    la surface d'étanchéité (56) est la surface frontale bombée du piston (25).
EP98111325A 1997-10-18 1998-06-19 Vanne de commande de fluide Expired - Lifetime EP0909891B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19746143A DE19746143A1 (de) 1997-10-18 1997-10-18 Ventil zum Steuern von Flüssigkeiten
DE19746143 1997-10-18

Publications (2)

Publication Number Publication Date
EP0909891A1 EP0909891A1 (fr) 1999-04-21
EP0909891B1 true EP0909891B1 (fr) 2002-05-29

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP98111325A Expired - Lifetime EP0909891B1 (fr) 1997-10-18 1998-06-19 Vanne de commande de fluide

Country Status (4)

Country Link
US (1) US6142443A (fr)
EP (1) EP0909891B1 (fr)
JP (1) JPH11241781A (fr)
DE (2) DE19746143A1 (fr)

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* Cited by examiner, † Cited by third party
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DE19859484A1 (de) * 1998-12-22 2000-07-06 Bosch Gmbh Robert Kraftstoff-Einspritzventil für eine Hochdruckeinspritzung
JP4038941B2 (ja) * 1999-08-02 2008-01-30 株式会社デンソー ピエゾインジェクタ
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DE19940300A1 (de) * 1999-08-25 2001-03-01 Bosch Gmbh Robert Steuerventil für einen Injektor
DE19946828C1 (de) * 1999-09-30 2001-07-12 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19946830A1 (de) * 1999-09-30 2001-05-03 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19946831C1 (de) * 1999-09-30 2001-07-12 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19949528A1 (de) * 1999-10-14 2001-04-19 Bosch Gmbh Robert Doppelschaltendes Steuerventil für einen Injektor eines Kraftstoffeinspritzsystems für Brennkraftmaschinen mit hydraulischer Verstärkung des Aktors
DE19951964A1 (de) * 1999-10-28 2001-05-03 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10000575A1 (de) * 2000-01-10 2001-07-19 Bosch Gmbh Robert Einspritzdüse
DE10002270C1 (de) * 2000-01-20 2001-06-28 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
US6570474B2 (en) 2000-02-22 2003-05-27 Siemens Automotive Corporation Magnetostrictive electronic valve timing actuator
DE10019766A1 (de) * 2000-04-20 2001-10-31 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
US6729554B2 (en) 2000-10-05 2004-05-04 Denso Corporation Structure of fuel injector for avoiding injection of excess quantity of fuel
WO2002031346A1 (fr) 2000-10-11 2002-04-18 Siemens Automotive Corporation Ensemble compensateur a membrane souple pour injecteur de carburant et procede correspondant
DE10055644A1 (de) * 2000-11-10 2002-05-23 Siemens Ag Verfahren zum Einstellen eines Leerhubs eines Injektors, wobei der Leerhub durch eine Aktoreinheit mit einem elektrisch ansteuerbaren Aktor und einen vom Aktor betätigten Ventilkolben gebildet wird
EP1381772B1 (fr) * 2000-11-13 2004-08-11 Siemens VDO Automotive Corporation Compensateur magnetique-hydraulique pour injecteur de carburant
JP4280066B2 (ja) * 2000-11-17 2009-06-17 いすゞ自動車株式会社 燃料噴射用インジェクタ、及び燃料噴射用インジェクタのニードルリフトダンピング方法
DE10101796A1 (de) * 2001-01-17 2002-07-18 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10102684A1 (de) * 2001-01-22 2002-08-08 Bosch Gmbh Robert Vorrichtung zur Formung eines flexiblen Einspritzdruckverlaufes mittels eines schaltbaren Aktors
DE10133265A1 (de) * 2001-07-09 2003-01-23 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10140529A1 (de) * 2001-08-17 2003-03-06 Bosch Gmbh Robert Piezoelektrisches Aktormodul
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DE19746143A1 (de) 1999-04-22
DE59804229D1 (de) 2002-07-04
JPH11241781A (ja) 1999-09-07
US6142443A (en) 2000-11-07
EP0909891A1 (fr) 1999-04-21

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