EP1929149B1 - Injecteur - Google Patents

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Publication number
EP1929149B1
EP1929149B1 EP06792593A EP06792593A EP1929149B1 EP 1929149 B1 EP1929149 B1 EP 1929149B1 EP 06792593 A EP06792593 A EP 06792593A EP 06792593 A EP06792593 A EP 06792593A EP 1929149 B1 EP1929149 B1 EP 1929149B1
Authority
EP
European Patent Office
Prior art keywords
coupler
piston
driver
face
control
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 - Fee Related
Application number
EP06792593A
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German (de)
English (en)
Other versions
EP1929149A1 (fr
Inventor
Hans-Christoph Magel
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 EP1929149A1 publication Critical patent/EP1929149A1/fr
Application granted granted Critical
Publication of EP1929149B1 publication Critical patent/EP1929149B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the present invention relates to an injection nozzle for an internal combustion engine, in particular of a motor vehicle, having the features of the preamble of claim 1.
  • an injection nozzle of this type which has a nozzle needle which is mounted in a nozzle body adjustable in stroke and for controlling the injection of standing under injection pressure fuel through at least one pinhole.
  • the injector also includes a coupler piston drivingly connected to an actuator and having a coupler surface while the nozzle needle is provided with a control surface.
  • the nozzle needle is arranged adjustable in height relative to the coupler piston and coupled in a closed position of the nozzle needle via a driver coupling for tensile force transmission to the coupler piston.
  • the control surface is hydraulically coupled to the coupler face.
  • the known injection nozzle realizes a two-phase opening kinematic for the nozzle needle.
  • the actuator is operated inversely and is energized or tensioned for the closed position of the nozzle needle.
  • the actuator is de-energized or expanded, whereby it pulls the thus drive-connected coupler piston from at least one injection hole.
  • the driver coupling thereby inevitably the nozzle needle is pulled out of its seat.
  • this first phase of the opening kinematics of the coupler piston is mechanically connected via the driver coupling mechanically connected to the nozzle needle, whereby the opening stroke of the actuator is transmitted directly, so without translation or reduction to the nozzle needle.
  • the nozzle needle is accelerated in the opening direction relative to the coupler piston.
  • Nozzle needle and coupler piston are then hydraulically coupled to each other, at the same time a determined by the coupler surface and the control surface gear ratio is effective.
  • the nozzle needle can perform a relatively large opening stroke in a short time. Overall, such a two-stage direct needle control is favorable for achieving high injection quantities with short injection times.
  • the opening stroke of the nozzle needle is the same size as the opening stroke of the actuator.
  • the actuator must accordingly build comparatively large in the axial direction. For the installation of injectors is on the internal combustion engine regularly little space available, which complicates the realization of the known construction.
  • This construction ensures that during a first phase of the opening kinematics there is a hydraulic coupling between the coupler piston arrangement and the nozzle needle, which works with a first transmission ratio.
  • This first transmission ratio is in this case by the coupler surface in relation to the control surface Are defined. This first transmission ratio can be selected specifically so that a sufficiently large opening force can be introduced into the nozzle needle.
  • a second phase of the opening kinematics begins.
  • the forced coupling between the coupler piston arrangement and the driver piston achieved with the aid of the driver coupling results in a significant change in the hydraulic ratio between the actuator stroke and the nozzle needle stroke as the actuator continues to open.
  • the driver surface is added to the coupler surface, whereby the new or second gear ratio is defined by the sum of coupler surface and driver surface in relation to the control surface.
  • the nozzle needle can be moved during the second phase of the opening kinematics with a reduced opening force with a significantly increased opening speed.
  • relatively large injection quantities can be realized at relatively short injection times.
  • the Kopplerkolbenan extract comprises a drivingly connected to the actuator first coupler piston and coupled via the driver coupling with the driver piston from the switching stroke for tensile force transmission second coupler piston, wherein the two coupler pistons coaxially arranged one inside the other and stroke-adjustable and hydraulically coupled to each other are drive-coupled.
  • the coupler piston assembly constructed of two coupler pistons allows compensation of thermal expansion and manufacturing tolerances. This results in increased reliability and simplified manufacturability for the injection nozzle.
  • the driver piston can now be mounted to be adjustable in stroke on the second coupler piston and, in particular, can be biased into a starting position by means of a return spring supported on the first coupler piston.
  • the injector receives in the field of driver coupling a particularly simple structure that can be implemented comparatively inexpensive.
  • a control valve configured to provide greater flow resistance for a hydraulic flow oriented from the control face to the coupler face than for one from the coupler face to the control surface oriented hydraulic flow.
  • an injection nozzle 1 comprises a nozzle body 2, in which a nozzle needle 3 is mounted adjustable in stroke.
  • the injection nozzle 1 is used for installation in an internal combustion engine, not shown, which is arranged in particular in a vehicle.
  • the injection nozzle 1 is connected in the assembled state to a high-pressure fuel line 4. If several injectors are connected to the same high-pressure fluid line 4, it is a so-called "common rail system".
  • the nozzle needle 3 is used to control the injection of standing under injection pressure fuel through at least one injection hole 5 in an injection chamber 6.
  • the nozzle needle 3 cooperates with a needle seat 7.
  • the nozzle needle 3 is in its closed position and separates the at least one injection hole 5 from a fuel supply 8.
  • This Kraftstoffzufiihrung 8 is connected via a corresponding connecting line 9 to the fuel high-pressure line 4.
  • the nozzle needle 3 is usually a component of a needle assembly 10 which is stroke-adjustable as a unit.
  • this needle assembly 10 consists of the nozzle needle 3, a control piston 11 and a support plate 12. At least two of the individual components of the needle assembly 10 may be loosely attached to each other or be made of one piece.
  • the needle needle 3 or needle assembly 10 has a control surface 13 which axially delimits a control chamber 14.
  • a control chamber sleeve 15 is provided, which is mounted axially adjustable on the nozzle needle 3 and the needle assembly 10.
  • the control surface 13 and the control chamber sleeve 15 are formed or arranged on the control piston 11.
  • a closing pressure spring 16 is provided, which drives the nozzle needle 3 in its closed position.
  • the closing compression spring 16 is supported in the axial direction on the one hand on the control chamber sleeve 15 and on the other hand on the nozzle needle 3 or on the needle assembly 10, here on the support plate 12.
  • the control chamber sleeve 15 is thereby firmly pressed against an intermediate plate 17, whereby in response to the nozzle needle 3 is driven in the direction of its seat 7.
  • the aforementioned intermediate plate 17 is a part of the nozzle body 2 and separates in this a needle portion 18, in which the nozzle needle 3 and the needle assembly 10 is arranged, of an actuator portion 19, in which an actuator 20 is arranged.
  • the Kraftstoffzufiihrung 8 is passed through the intermediate plate 17 in a suitable manner, for. B. by means of at least one unspecified bore.
  • the aforementioned actuator 20, in particular a piezoactuator, is drive-connected to a coupler piston arrangement 21.
  • This coupler piston assembly 21 is equipped with a coupler face 22 which axially bounds a translator pocket 23.
  • a hydraulic control path 24 for example in the form of a control channel 25 through the intermediate plate 17 is passed, the booster chamber 23 and the control chamber 14 are hydraulically coupled to each other. Accordingly, the coupler surface 22 and the control surface 13 are hydraulically coupled to each other.
  • the injection nozzle 1 comprises a driver piston 26 which is arranged to be adjustable in stroke within the nozzle body 2 and which has a driver surface 27.
  • the driver surface 27 also limits the booster chamber 23 axially and is therefore hydraulically coupled to the control surface 13.
  • a driver coupling 28 is provided. This driver coupling 28 is configured such that it transfers tensile forces from the coupler piston assembly 21 to the driver piston 26 only at a switching stroke 29 during an opening stroke of the actuator 20, in which the coupler piston assembly 21 moves away from the at least one injection hole 5. As a result, takes the coupler piston assembly 21 at a beyond the shift stroke 29 Aktorhub the driver piston 26 with.
  • the coupler piston assembly 21 comprises a first coupler piston 30 and a second coupler piston 31.
  • the two coupler pistons 30, 31 are arranged coaxially with one another and mounted to one another in a stroke-adjustable manner.
  • the first coupler piston 30 is drive-connected to the actuator 20, so that a stroke of the actuator 20 inevitably entrains the first coupler piston 30 to carry out the identical stroke.
  • the second coupler piston 31 can be coupled via the driver coupling 28 to the driver piston 26, such that the second coupler piston 31 inevitably entrains the driver piston 26 from the switching stroke 29.
  • the two coupler pistons 30, 31 are drive-hydraulically coupled with each other, so that a stroke of the first coupler piston 30 leads to a corresponding stroke of the second coupler piston 31.
  • the two coupler pistons 30, 31 enclose a coupler space 32, in which the hydraulic coupling of the two coupler pistons 30, 31 takes place.
  • the first coupler piston 30 is designed as a sleeve into which the second coupler piston 31 is inserted in the manner of a plunger.
  • the hydraulic volume trapped in the coupler space 32 forces the hydraulic coupling of the two coupler pistons 30, 31.
  • a stop spring 33 is arranged, which absorbs the forces occurring in the event of a collision of the two coupler pistons 30, 31.
  • the driving piston 26 is arranged coaxially with the second coupling piston 31 and mounted on this hubver texts. Furthermore, the driving piston 26 is biased in a starting position shown here.
  • a return spring 34 is provided, which is supported on the one hand on the driving piston 26 and on the other hand on the first coupler piston 30.
  • the aforementioned starting position of the driving piston 26 is defined here by at least one spacer element 35. About the at least one spacer element 35 of the driver piston 26 is axially supported in its initial position on the intermediate plate 17.
  • the translator space 23 is bounded radially by a translator space sleeve 36.
  • emaumhülse is preferably arranged coaxially with the driving piston 26 and mounted on this hubver plausible.
  • a ⁇ fthungs réellefeder 37 is expediently provided, which is axially supported on the one hand to the Kompaktraumhülse 36 and on the other hand on the first coupler piston 30.
  • the opening pressure spring 37 presses the translator space sleeve 36 axially against the intermediate plate 17.
  • the driver coupling 28 operates here with an effective in the pulling direction positive engagement, via which the driver piston 26 and the coupler piston assembly 21 and the second coupler piston 31 are in an opening stroke of the actuator 20 from the shift stroke 29 with each other.
  • the driver coupling 28 is provided with a step 38 which projects radially from the coupler piston assembly 21 and from the second coupler piston 31.
  • This stage 38 is suitably made in one piece together with the second coupler piston 31.
  • this stage 38 by a separate component, for. B. in the form of a disc to attach to the second coupler piston 31.
  • This step 38 engages behind the driver piston 26 on a side facing away from the actuator 20 side.
  • the step 28 thus engages behind the driving piston 26 on its driver surface 27 or in the booster chamber 23.
  • control valve 39 is arranged in the control path 27.
  • This control valve 39 is designed so that it is opposite to a hydraulic flow oriented by the control surface 13 to the coupler surface 22 a greater flow resistance than a hydraulic flow, which is opposite, that is oriented from the coupler surface 22 to the control surface 13.
  • the control valve 39 is designed as a check valve, which has a valve body 40 which cooperates with a valve spring 41 and with a valve seat 42. The valve spring 41 presses the valve body 40 against the valve seat 42.
  • the valve seat 42 is formed on a side facing the control surface 13 of the intermediate plate 17 and arranged so that the control valve 39 controls the control channel 25 of the intermediate plate 17.
  • the valve body 40 and the valve spring 41 are accordingly arranged in the control chamber 14.
  • a bypass 43 is provided which bypasses the valve body 40 seated in the valve seat 42.
  • the bypass 43 is formed in the valve body 40 itself or passed therethrough.
  • the valve spring 41 is supported on the one hand on the valve body 40 and on the other hand on the nozzle needle 3 and the needle assembly 10 from.
  • the injection nozzle 1 operates as follows:
  • the nozzle needle 3 In the initial state shown, the nozzle needle 3 is in its closed position and separates the at least one spray hole 5 from the fuel supply 8, so that no injection takes place.
  • the driver piston 26 is in its initial position in which it is supported by the return spring 34 via the at least one spacer element 35 on the intermediate plate 17.
  • the control chamber 14 In the control chamber 14, in the booster chamber 23 and in the coupler chamber 32 prevails as in the fuel supply 8 of the respective desired injection pressure. This is achieved for example by targeted leaks or by suitable throttled connection paths.
  • the inversely operated actuator 20 is energized or charged, whereby it has its maximum longitudinal extent. Corresponding electrical connections of the actuator 20 are designated by 44 in the figures.
  • the actuator area 19 in which not only the actuator 20 but also the coupler piston arrangement 21, ie the two coupler pistons 30 and 31, and the driver piston 26 and the translator space sleeve 36 are arranged, the injection pressure also prevails, so that said components are arranged quasi "floating" , The same applies to the nozzle needle 3 and the needle assembly 10 and the control chamber sleeve 15, which are arranged floating in the fuel needle area 18
  • the actuator 20 is now de-energized or expanded, as a result of which its length is reduced.
  • the end of the actuator 20 connected to the first coupler piston 30 leads from the at least one injection hole 5 directed opening stroke through.
  • This Aktorhub the first coupler piston 30 inevitably follows.
  • the second coupler piston 31 follows the hydraulic coupling of the first coupler piston 30. This opening movement is thereby supported by the opening pressure of 37.
  • the volume in the booster chamber 23 increases, as a result of which the pressure in the booster chamber 23 drops. This pressure drop propagates into the control chamber 14 and reduces at the control surface 13, the effective pressure in the closing direction.
  • the opening direction prevails effective forces, whereby the nozzle needle 3 is lifted from the needle seat 7.
  • the second coupler piston 31 is not yet engaged with the driver piston 26 via the driver coupling 28. Consequently, the second coupler piston 31 still performs its opening stroke independently of the driving piston 26, which thus remains in its initial position.
  • the driver piston 26 is biased by the return spring 34 in its initial position and accordingly can slide outside on the second coupler piston 31, while this performs its opening stroke.
  • a hydraulic connection with a first hydraulic transmission ratio is effective between the coupler piston assembly 21 and the nozzle needle 3.
  • This first gear ratio is determined by the ratio of the coupler surface 22 to the control surface 13. This first gear ratio is suitably chosen so that the nozzle needle 3 can be pulled out of its needle seat 7 with a sufficiently large force.
  • the actuator 20 is recharged or energized, causing it to expand again.
  • the closing movement of the nozzle needle 3 is supported by the closing pressure spring 16.
  • the second transmission ratio is present during the closing movement.
  • the driver piston 26 reaches its initial position and stops, while the second coupler piston 31 moves further in the closing direction. Consequently, then there is the first gear ratio.
  • the opening process prevails in the control chamber 14 relative to the booster chamber 23 relative to the booster chamber 23, a positive pressure and the valve body 40 is seated in the valve seat 42, so that the flow resistance of the control path 24 is determined by the bypass 43.
  • the bypass 43 is dimensioned so that there is a certain damping effect. That is, the pressure drop caused by the opening stroke of the actuator 20 and the second coupler piston 31 in the booster chamber 23 can propagate only delayed in the control chamber 14. Since this damping depends on the volume flow, it shows its effect mainly in the second phase of the opening kinematics. As a result, the opening speed of the nozzle needle 3 is at least in the second phase of the opening kinematics smaller than it could be 39 in the absence of the control valve.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (10)

  1. Injecteur pour un moteur à combustion interne, en particulier un véhicule automobile,
    - avec une aiguille d'injecteur (3) montée avec une course réglable dans un corps d'injecteur (2), pour la commande de l'injection de carburant à la pression d'injection à travers au moins un orifice de pulvérisation (5),
    - avec un agencement de piston de couplage (21), qui est connecté par entraînement à un actionneur (20) et qui présente une surface de couplage (22),
    - l'aiguille d'injecteur (3) ou un ensemble d'aiguille (10) présentant l'aiguille d'injecteur (3) présentant une surface de commande qui est accouplée hydrauliquement à la surface de couplage (22),
    caractérisé en ce que
    - l'on prévoit un piston d'entraînement (26) qui présente une surface d'entraînement (27) qui est accouplée hydrauliquement à la surface de commande (13),
    - l'on prévoit un accouplement d'entraînement (28) qui, dans le cas d'une course d'ouverture de l'actionneur (20), transmet seulement à partir d'une course de commutation (29), les forces de traction de l'agencement de piston de couplage (21) au piston d'entraînement (26) et entraîne avec lui le piston d'entraînement (26).
  2. Injecteur selon la revendication 1,
    caractérisé en ce que
    l'accouplement d'entraînement (28) accouple l'agencement du piston de couplage (21) au piston d'entraînement (26) par le biais d'un engagement par coopération de forme agissant dans la direction de traction, qui est en prise lors de la course d'ouverture de l'actionneur (20) à partir d'une course de commutation (29).
  3. Injecteur selon la revendication 1 ou 2,
    caractérisé en ce que
    l'accouplement d'entraînement (28) présente un étage (38) qui dépasse radialement de l'agencement de piston de couplage (21) et qui vient en prise avec le piston d'entraînement (26) d'un côté opposé à l'actionneur (20).
  4. Injecteur selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    - l'agencement de piston de couplage (21) présente un premier piston de couplage (30) qui est connecté par entraînement avec l'actionneur (20),
    - l'agencement de piston de couplage (21) présente un deuxième piston de couplage (31) qui est accouplé par le biais de l'accouplement d'entraînement (28) au piston d'entraînement (26) à partir de la course de commutation (29) pour le transfert de force de traction,
    - les deux pistons d'accouplement (30, 31) sont disposés coaxialement l'un dans l'autre et sont montés avec une course réglable l'un dans l'autre,
    - les deux pistons d'accouplement (30, 31) sont accouplés par entraînement hydraulique l'un à l'autre.
  5. Injecteur selon la revendication 4,
    caractérisé en ce que
    - les deux pistons d'accouplement (30, 31) sont accouplés par entraînement hydraulique l'un à l'autre dans un espace de couplage (32) qui est formé par les deux pistons de couplage (30, 31), et/ou
    - l'un des pistons de couplage (30) forme une douille dans laquelle plonge l'autre piston de couplage (31), et/ou
    - un ressort de butée (33) est disposé dans l'espace de couplage (32).
  6. Injecteur selon la revendication 4 ou 5,
    caractérisé en ce que
    - le piston d'entraînement (26) est monté avec une course réglable sur le deuxième piston de couplage (31), et/ou
    - le piston d'entraînement (26) est précontraint au moyen d'un ressort de rappel (34) dans une position de départ, et
    - le ressort de rappel (34) est supporté d'une part au piston d'entraînement (26) et d'autre part au premier piston de couplage (30) ou à l'actionneur (20), et/ou
    - le piston d'entraînement (26) est supporté dans sa position de départ par le biais d'au moins un élément d'espacement (35) sur une plaque intermédiaire (17) limitant axialement un espace de multiplication (23).
  7. Injecteur selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que
    - la surface de couplage (22) et la surface d'entraînement (27) limitent axialement un espace de multiplication (23) qui est limité radialement par une douille d'espace de multiplication (36) qui est montée avec une course réglable sur le piston d'entraînement (26), et
    - en ce que la douille d'espace de multiplication (36) est pressée au moyen d'un ressort de pression d'ouverture (37) contre une plaque intermédiaire (17) limitant axialement l'espace de multiplication (23) du corps de buse (2), et
    - en ce que le ressort de pression d'ouverture (37) est supporté d'une part sur la douille d'espace de multiplication (36) et d'autre part sur le premier piston de couplage (30) ou sur l'actionneur (20).
  8. Injecteur selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce que
    dans une voie de commande (24) reliant hydrauliquement la surface de couplage (22) à la surface de commande (13), on dispose une soupape de commande (39), qui fournit pour un flux hydraulique orienté de la surface de commande (13) vers la surface de couplage (22), une plus grande résistance à l'écoulement que pour un flux hydraulique orienté de la surface de couplage (22) vers la surface de commande (13).
  9. Injecteur selon la revendication 8,
    caractérisé en ce que
    la soupape de commande (39) est réalisée sous forme de soupape de non retour, dont le corps de soupape (40) est pressé avec un ressort de soupape (41) dans la direction de la surface de couplage (22) dans un siège de soupape (42).
  10. Injecteur selon la revendication 9,
    caractérisé en ce que
    - l'on prévoit une dérivation contournant le corps de soupape (40) reposant dans le siège de soupape (42), et
    - la dérivation (43) est guidée à travers le corps de soupape (40), et/ou
    - le siège de soupape (42) est réalisé d'un côté de la plaque intermédiaire (17) tourné vers la surface de commande (13), qui sépare un espace de multiplication (23) limité par la surface de couplage (22), d'un espace de commande (14) limité par la surface de commande (13) et d'un canal de commande (25) reliant l'espace de multiplication (23) à l'espace de commande (14), et commandé par la soupape de commande (39).
EP06792593A 2005-08-30 2006-07-28 Injecteur Expired - Fee Related EP1929149B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510040912 DE102005040912A1 (de) 2005-08-30 2005-08-30 Einspritzdüse
PCT/EP2006/064763 WO2007025815A1 (fr) 2005-08-30 2006-07-28 Injecteur

Publications (2)

Publication Number Publication Date
EP1929149A1 EP1929149A1 (fr) 2008-06-11
EP1929149B1 true EP1929149B1 (fr) 2009-06-17

Family

ID=37072965

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06792593A Expired - Fee Related EP1929149B1 (fr) 2005-08-30 2006-07-28 Injecteur

Country Status (3)

Country Link
EP (1) EP1929149B1 (fr)
DE (2) DE102005040912A1 (fr)
WO (1) WO2007025815A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006049885A1 (de) * 2006-10-23 2008-04-24 Robert Bosch Gmbh Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen
DE102006053287A1 (de) * 2006-11-13 2008-05-15 Robert Bosch Gmbh Kraftstoffinjektor
DE102007018006A1 (de) * 2007-04-17 2008-10-23 Robert Bosch Gmbh Injektor
DE102008002153B4 (de) 2008-06-02 2016-02-18 Robert Bosch Gmbh Kraftstoff-Injektor
DE102008041553A1 (de) 2008-08-26 2010-03-04 Robert Bosch Gmbh Kraftstoff-Injektor
DE102010042251A1 (de) 2010-10-11 2012-04-12 Robert Bosch Gmbh Kraftstoffinjektor für eine Brennkraftmaschine
DE102015219912B3 (de) * 2015-10-14 2017-04-06 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoffeinspritzung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2280318T3 (es) * 2000-07-18 2007-09-16 Delphi Technologies, Inc. Inyector de combustible.
DE10326044A1 (de) * 2003-06-10 2004-12-30 Robert Bosch Gmbh Einspritzdüse für Brennkraftmaschinen
DE102004035280A1 (de) * 2004-07-21 2006-03-16 Robert Bosch Gmbh Kraftstoffinjektor mit direkter mehrstufiger Einspritzventilgliedansteuerung

Also Published As

Publication number Publication date
DE102005040912A1 (de) 2007-03-08
EP1929149A1 (fr) 2008-06-11
DE502006004022D1 (de) 2009-07-30
WO2007025815A1 (fr) 2007-03-08

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