EP2466107B1 - Injecteur de carburant comportant une soupape de commande à équilibrage de pression - Google Patents

Injecteur de carburant comportant une soupape de commande à équilibrage de pression Download PDF

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Publication number
EP2466107B1
EP2466107B1 EP20110192957 EP11192957A EP2466107B1 EP 2466107 B1 EP2466107 B1 EP 2466107B1 EP 20110192957 EP20110192957 EP 20110192957 EP 11192957 A EP11192957 A EP 11192957A EP 2466107 B1 EP2466107 B1 EP 2466107B1
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EP
European Patent Office
Prior art keywords
valve
sealing
pressure
chamber
fuel injector
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.)
Not-in-force
Application number
EP20110192957
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German (de)
English (en)
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EP2466107A1 (fr
Inventor
Torsten Leukert
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 EP2466107A1 publication Critical patent/EP2466107A1/fr
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Publication of EP2466107B1 publication Critical patent/EP2466107B1/fr
Not-in-force legal-status Critical Current
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    • 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
    • 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
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced valves

Definitions

  • the invention relates to a fuel injector for an internal combustion engine according to the preamble of claim 1.
  • a fuel injector with a pressure compensated control valve is off DE 10 2008 001 330 known.
  • the control valve actuates a nozzle needle for injecting fuel, wherein the nozzle needle is exposed to a control chamber and the control valve controls the pressure in the control chamber.
  • the control valve has a valve pin and a valve sleeve, wherein the valve sleeve is axially guided on a guide of the valve pin.
  • the valve sleeve is biased by a valve spring urging an annular surface in a high pressure side valve space against a component fixed to the housing, thereby hydraulically separating the high pressure side valve space from a low pressure side valve space.
  • the valve pin is thereby exposed with an end face the low pressure side valve chamber and thus receives a constant low-pressure connection.
  • valve pin is thereby not pressed against the opening of the valve seat against the entire rail pressure in the high-pressure side valve chamber, but has by the low-pressure connection in the low-pressure side valve chamber a pressure equalization with respect to the also exposed to the low pressure counter surface.
  • the guide between valve pin and valve sleeve forms a guide gap, via which a leakage from the high-pressure side valve chamber in the low-pressure side valve chamber can flow out. This leakage must be compensated by a correspondingly higher flow rate in the high-pressure inlet, which in turn is a high-pressure pump providing the high pressure is more heavily loaded or can be used to the leakage lower pressure for injecting the fuel.
  • the invention has for its object to provide a fuel injector in which the control valve no or a greatly reduced leakage occurs, so that the hydraulic losses of the fuel injector can be reduced.
  • the present invention solves the problem in that the opening into the high pressure side valve space guide gap between the valve pin and the valve sleeve is closed by means of a seal to the low pressure side valve chamber out at least when the sealing seat is closed. As a result, hydraulic losses of the fuel injector are reduced, so that a higher efficiency of the entire injection system is achieved.
  • the leakage gap is closed in the closed state of the valve seat.
  • the leakage gap can be opened, because ideally there is no pressure gradient between the high-pressure-side valve chamber and the low-pressure-side valve chamber when the valve seat is open.
  • no leakage occurs at this time.
  • the inner seal on the valve pin is opened, insofar the guide gap is closed only when the valve seat is closed.
  • the seal is effective both when the valve seat is closed and when the valve seat is open.
  • the seal is formed by a sealing disc, which acts on the valve sleeve and the valve pin.
  • the seal on an outer sealing edge and an inner sealing edge, which cooperate in each case with a sealing mating surface.
  • the sealing edges are preferably designed as B sulfurkanten.
  • the outer sealing edge and the inner sealing edge are formed at a radial distance on an end face of the sealing disc, wherein the guide gap is located between the sealing edges.
  • the sealing mating surfaces are formed by an outer sealing surface formed on the valve sleeve and by an inner sealing surface formed on the valve piston. The sealing effect is achieved by the outer sealing edge rests sealingly on the outer sealing surface of the valve sleeve and the inner sealing edge on the inner sealing surface of the valve pin when the sealing seat is closed.
  • the outer sealing edge is arranged on an end face of the valve sleeve and the inner sealing edge on a further annular surface formed on the valve piston, wherein the sealing mating surfaces are executed by an end face formed on the sealing disc.
  • outer sealing edge and outer sealing surface takes place in an outer Dichtben and the interaction of inner sealing edge and inner sealing surface in an inner sealing plane.
  • inner Dichtben in the direction of it opening stroke of the valve pin is slightly below or behind the outer sealing layer.
  • the valve pin has a diameter step.
  • the valve pin is made at least two parts.
  • an annular surface is formed on the diameter graduation, which forms the inner sealing surface or a base surface for forming the inner sealing edge.
  • a montagemese execution is done by a valve pin part and a valve pin sleeve are provided, wherein after insertion of the sealing disc and the valve spring, the two parts of the valve piston connected become.
  • a further assembly-oriented design is carried out by a stepped valve pin member and a separate valve seat body are provided, wherein after insertion of the sealing disc and the valve spring, the two parts of the valve piston are connected.
  • Fig. 1 is a designed as a common rail injector fuel injector for injecting fuel into a combustion chamber, not shown, of a likewise not shown internal combustion engine of a motor vehicle in a schematic representation shown in fragmentary form.
  • the fuel injector comprises a control valve 10 designed as a hydraulic servo valve and an injection valve element 12.
  • the control valve 10 is actuated by an actuator (not shown), for example a piezoactuator, via a hydraulic coupler 14. From the hydraulic coupler 14, only a valve-side piston 15 is shown with an end face 13, which is arranged in a low-pressure space 17.
  • the low-pressure chamber 17 is connected to a low-pressure connection, not shown, which is connected to a fuel return.
  • the control valve 10, the injection valve element 12, the hydraulic coupler and the actuator are housed in an injector housing, which in FIG. 1
  • an injector housing which in FIG. 1
  • individual housing components are hydraulically sealed, such as a holding body 18, a first valve plate 21, a second valve plate 22, a throttle plate 23 and a Nozzle body 24.
  • a high-pressure inlet 16 which is connected at one end to a high-pressure accumulator, not shown (common rail) and the other ends in a pressure chamber 19 within the nozzle body 24 opens.
  • the injector can also be made in one piece.
  • the injection valve element 12 is arranged within the nozzle body 24 and comprises an axially movable nozzle needle 25 and a control chamber sleeve 26.
  • the control chamber sleeve 26 is axially displaceably guided on the nozzle needle 25 and is supported in the axial direction on the housing-fixed throttle plate 23 from.
  • the nozzle needle 25 and the control chamber sleeve 26 are surrounded by the pressure chamber 19, wherein the nozzle needle 25 acts within the pressure chamber 19 in a closed position sealingly on a nozzle needle seat, not shown, in a conventional manner.
  • the injection ports are closed. If, however, the nozzle needle 25 is lifted from the nozzle needle seat, fuel is injected at high pressure within the pressure chamber 19 through the injection openings in the combustion chamber of the internal combustion engine.
  • control chamber sleeve 26 surrounds a control chamber 27, which the nozzle needle 25 is exposed to a pressure surface 28.
  • the control chamber sleeve 26 is supported in the axial direction of the housing-fixed throttle plate 23 and thus separates the control chamber 27 from the pressure chamber 19 hydraulically, the control chamber 27 via the forming sealing gap between Steuerraumhülse 26 and throttle plate 23 from the high pressure region of the pressure chamber 19 with fuel is filled.
  • an inlet throttle may be introduced, for example, in the control chamber sleeve 26 or in the throttle plate 23, which then connect the control chamber 27 with the high-pressure inlet 16.
  • a drain channel 31 is introduced with an outlet throttle 32.
  • About the drain passage 31 of the control chamber 27 is permanently connected to a high-pressure side valve chamber 33 which is radially and axially bounded by the first and second valve plate 21, 22 and by the throttle plate 23.
  • the high-pressure-side valve chamber 33 is part of the control valve 10 and is hydraulically connected via a valve seat 30 to the low-pressure chamber 17.
  • connection channel 34 which is designed with a Mountaindrossel 35, wherein the connecting channel 34 connects the high-pressure side valve chamber 33 with the high-pressure inlet 16.
  • the connecting channel 34 is not absolutely necessary, because the filling of the valve chamber 33 can also take place out of the control chamber 27 via the outlet channel 31.
  • the control valve 10 comprises a valve pin 41, a valve sleeve 42, a sealing disc 43 and a valve spring 44.
  • the valve pin 41 is designed with a mushroom-shaped valve seat body 45 which presses against the housing-fixed valve seat 30 with a sealing seat surface 46.
  • the valve pin 41 has at the end facing the coupler 14 on a counter surface 38 against which the end surface 13 of the valve-side piston 15 of the coupler 14 presses.
  • the valve sleeve 42 and the sealing disc 43 are axially displaceably guided on the valve piston 41, wherein the guide between the valve piston 41 and valve sleeve 42 due to the function, a guide gap 50 is present ( FIG. 2 ).
  • valve pin 41 rests with the sealing seat surface 46 on the housing-tight sealing seat 30.
  • the closing force is applied substantially by the valve spring 44, which is supported on a collar of the mushroom-shaped valve seat body 45 and the sealing discs 43, wherein the sealing disc 43 in turn on the valve sleeve 42 and the valve sleeve 42 with a circumferential annular surface 48 on the Throttle plate 23 is supported.
  • the annular surface 48 forms a sealing surface, so that within the annular surface 48, a low-pressure side valve chamber 49 is formed, which is hydraulically separated by the sealing action of the annular surface 48 from the high-pressure side valve chamber 33.
  • the low-pressure-side valve chamber 49 is exposed to the valve pin 41 with an end face 47.
  • the low-pressure side valve chamber 49 is connected via a formed in the throttle plate 23 hydraulic connection 37 to the mentioned low-pressure connection, which leads into the return line.
  • the valve pin 41 points through the constant low-pressure connection of the low-pressure side Valve chamber 49 a pressure equalization for the end face 47 with respect to the ebenfelle low pressure exposed counter surface 38, wherein the counter surface 38 is determined by the diameter of the valve seat 30.
  • the valve pin 41 for opening the valve seat 30 is not to be pressed against the entire high pressure in the high-pressure-side valve space 33.
  • there is a pressure-compensated control valve 10 in which the valve opening force applied to the end face 47 is essentially determined only by the spring force of the valve spring 44.
  • the diameter of the valve seat 30 determining the mating surface 38 of the valve bolt 41 is selected to be slightly smaller than the pressure surface 47 of the valve bolt 41 exposed to the low-pressure space. As a result, a permanent closing force acts on the valve bolt 41 within the valve space 33.
  • a seal 40 is formed, which closes the guide gap 50 to the high pressure side valve chamber 33 out.
  • the sealing disks 43 are formed on an end face 54 facing the valve sleeve 42 with an outer circumferential sealing edge 51 and an inner circumferential sealing edge 52, wherein the sealing edges 51, 52 extend at a radial distance on the end face 54. Within the radial distance is the guide gap 50.
  • the outer sealing edge 51 acts on the valve sleeve 42 and the inner sealing edge 52 on the valve piston 41 a.
  • respective sealing mating surfaces are provided on the valve sleeve 42 and on the valve piston 41 for the outer and inner sealing edges 51, 52.
  • the sealing edges 51, 52 are expediently designed as B reactkanten.
  • the sealing mating surfaces are formed by an outer sealing surface 56 formed on the valve sleeve 42 and an inner sealing surface 58 formed on the valve piston 41, the outer sealing surface 51 acting on the outer sealing surface 56 and the inner sealing edge 52 on the inner sealing surface 58.
  • the outer sealing surface 56 is of the Sealing disk 43 facing annular surface of the valve sleeve 42 is formed.
  • the valve pin 41 is designed with a diameter graduation, wherein the annular surface lying in the diameter gradation forms the inner sealing surface 58.
  • valve pin 41 of two parts composed, namely according to FIG. 2 from a valve pin part 64 and a valve pin sleeve 65, wherein the valve sleeve 42 is guided on the valve pin sleeve 65.
  • the valve pin sleeve 65 is fastened to the valve pin part 64, for example by means of welding.
  • valve pin 41 it is just as possible to assemble the valve pin 41 from a stepped valve pin part and a separate, separate valve seat body 45.
  • the sealing disc 43 and the valve spring 44 is pushed from the koppler Konen end to the valve pin part and then inserted the koppler Konen end of the valve pin part in a bore of the separate valve seat body 45 and fixed there, for example by welding.
  • the high pressure applied in the high pressure side valve space 33 deforms the sealing disc 43 slightly in the elastic region and presses it with the sealing edges 51, 52 against the sealing surfaces 56, 58 and thus closes the guide gap 50.
  • the stator valve 10 opens the valve seat 30 the valve pin 41 is pressed by the actuator in the direction throttle plate 23.
  • the inner sealing surface 58 on the valve sleeve 42 also dips in the direction of the throttle plate 23. Because at the same time the pressure in the high pressure side valve chamber 33 drops very sharply and thus the contact pressure on the sealing disc 43 decreases, the inner sealing surface 58 is separated from the inner sealing edge 52.
  • the outer sealing edge 51 is arranged on the sealing face 43 facing the end face of the valve sleeve 42 and the inner sealing edge 52 on the annular surface of the valve pin 41 formed by the diameter graduation.
  • the sealing mating surfaces with the outer sealing surface 56 for the outer sealing edge 51 and with the inner sealing surface 58 for the inner sealing edge 52 are then formed by the valve sleeve 42 facing end face 54 of the sealing disc 43.
  • outer sealing edge 51 and outer sealing surface 56 forms an outer sealing edge 61; the interaction of inner sealing edge 52 and inner sealing surface 58 forms an inner sealing plane 62.
  • outer sealing plane 61 and the inner sealing plane 62 are not exactly in the same plane, but that the inner sealing surfaces 62 in the direction of the opening stroke for opening the valve seat 30 is slightly below or behind the outer sealing layer 61. It must be ensured that the control valve 10 in the valve seat 30 closes. Ie.
  • the need for subsequent displacement of the two sealing planes 61, 62 results from the axial tolerances to form a secure valve seat 30, the axial tolerances of the valve sleeve 42 and valve pin sleeve 65 and the vorzuhaltenden wear of the valve seat 30.
  • the maximum offset may be so large that the possible deformation of the Sealing disc 43 does not pass through the high pressure in the plastic deformation range.
  • the high pressure in the control chamber 27 acts on the pressure surface 26 on the nozzle needle 25, whereby the nozzle needle 25 is placed in the nozzle needle seat.
  • the injection openings are closed.
  • the actuator If the actuator is actuated, press the valve-side piston 15 of the coupler 14 with the end face 13 on the counter surface 38 of the valve pin 41.
  • the sealing seat surface 46 is pushed away from the valve seat 30 and a hydraulic connection between the high pressure side valve chamber 33 and the low pressure chamber 17 is formed.
  • the pressure in the high-pressure-side valve chamber 33 and via the drainage channel 31 is also relaxed in the control chamber 27, so that the opening force acting on the nozzle needle 25 in the pressure chamber 19 exceeds the closing force acting on the pressure surface 26 of the nozzle needle 25 in the control chamber 27.
  • the nozzle needle 25 lifts from the nozzle needle seat and releases the injection ports for injecting fuel.

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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 (10)

  1. Injecteur de carburant pour un moteur à combustion interne comprenant une soupape de commande (10) actionnée par un actionneur, qui actionne une aiguille de buse (25) pour l'injection de carburant, l'aiguille de buse (25) étant exposée à un espace de commande (27) et la soupape de commande (10) commandant la pression dans l'espace de commande (27), la soupape de commande (10) ouvrant ou fermant un espace de soupape (33) du côté haute pression connecté hydrauliquement à l'espace de commande (27), par le biais d'un siège de soupape (30) en direction d'un espace basse pression (17), la soupape de commande (10) présentant un boulon de soupape (41) et une douille de soupape (42), la douille de soupape (42) étant guidée axialement sur un guide du boulon de soupape (41), le guide formant entre le boulon de soupape (41) et la douille de soupape (42) un interstice de guidage (50), la douille de soupape (42) étant précontrainte par un ressort de soupape (44) et reposant avec une surface annulaire (48) contre un composant fixé au boîtier (23) et séparant de ce fait hydrauliquement l'espace de soupape du côté haute pression (33) d'un espace de soupape du côté basse pression (49), caractérisé en ce que l'interstice de guidage (50) débouchant dans l'espace de soupape du côté haute pression (33) est fermé entre le boulon de soupape (41) et la douille de soupape (42) au moyen d'un joint d'étanchéité (40) vers l'espace de soupape du côté basse pression (49) au moins lorsque le siège d'étanchéité (30) est fermé.
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce que le joint d'étanchéité (40) est formé par une rondelle d'étanchéité (43) qui agit sur la douille de soupape (42) et le boulon de soupape (41).
  3. Injecteur de carburant selon la revendication 1 ou 2, caractérisé en ce que le joint d'étanchéité (40) présente une arête d'étanchéité extérieure (51) et une arête d'étanchéité intérieure (52), lesquelles coopèrent à chaque fois avec une surface conjuguée d'étanchéité.
  4. Injecteur de carburant selon la revendication 3, caractérisé en ce que l'arête d'étanchéité extérieure (51) et l'arête d'étanchéité intérieure (52) sont réalisées à distance radiale sur une surface frontale (54) de la rondelle d'étanchéité (53), en ce qu'entre les arêtes d'étanchéité (51, 52) se trouve l'interstice de guidage (50), et en ce que les surfaces conjuguées d'étanchéité sont formées par une surface d'étanchéité extérieure (56) réalisée sur la douille de soupape (42) et par une surface d'étanchéité intérieure (58) réalisée sur le piston de soupape (41).
  5. Injecteur de carburant selon l'une quelconque des revendications 2 à 4, caractérisé en ce qu'au moins lorsque le siège d'étanchéité (30) est fermé, l'arête d'étanchéité extérieure (51) repose de manière hermétique sur la surface d'étanchéité extérieure (56) de la douille de soupape (42) et l'arête d'étanchéité intérieure (52) repose de manière hermétique sur la surface d'étanchéité intérieure (58) du boulon de soupape (41).
  6. Injecteur de carburant selon la revendication 3, caractérisé en ce que l'arête d'étanchéité extérieure (51) est disposée sur une surface frontale de la douille de soupape (42) tournée vers la rondelle d'étanchéité (43) et l'arête d'étanchéité intérieure (52) est disposée sur une surface annulaire supplémentaire réalisée au niveau du piston de soupape (41), et en ce que les surfaces conjuguées d'étanchéité sont réalisées par une surface frontale (54) réalisée sur la rondelle d'étanchéité (43).
  7. Injecteur de carburant selon l'une quelconque des revendications 2 à 6, caractérisé en ce que la coopération de l'arête d'étanchéité extérieure (51) et de la surface d'étanchéité extérieure (56) forme un plan d'étanchéité extérieur (61) et la coopération de l'arête d'étanchéité intérieure (52) et de la surface d'étanchéité intérieure (58) forme un plan d'étanchéité intérieur (62) et en ce que le plan d'étanchéité intérieur (62) se situe dans la direction de la course d'ouverture du boulon de soupape (41) derrière le plan d'étanchéité extérieur (61) en vue de l'ouverture du siège de soupape (30).
  8. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que le boulon de soupape (41) est réalisé sous forme étagée et en ce qu'une surface annulaire est réalisée sur la gradation de diamètre, laquelle surface annulaire forme la surface d'étanchéité intérieure (58) ou une surface de base en vue de réaliser l'arête d'étanchéité intérieure (51).
  9. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que le boulon de soupape (41) est réalisé au moins en deux parties et présente une partie de boulon de soupape (64) et une douille de boulon de soupape (65), et en ce qu'après l'insertion de la rondelle d'étanchéité (43) et du ressort de soupape (44), les deux parties (64, 65) du piston de soupape (41) sont reliées l'une à l'autre.
  10. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que le boulon de soupape (41) est réalisé au moins en deux parties et présente une partie de boulon de soupape étagée (64) et un corps de siège de soupape (45), et en ce qu'après l'insertion de la rondelle d'étanchéité (41) et du ressort de soupape (44), les deux parties (64, 45) du piston de soupape (41) sont reliées l'une à l'autre.
EP20110192957 2010-12-16 2011-12-12 Injecteur de carburant comportant une soupape de commande à équilibrage de pression Not-in-force EP2466107B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010063183 DE102010063183A1 (de) 2010-12-16 2010-12-16 Kraftstoffinjektor mit druckausgeglichenem Steuerventil

Publications (2)

Publication Number Publication Date
EP2466107A1 EP2466107A1 (fr) 2012-06-20
EP2466107B1 true EP2466107B1 (fr) 2013-07-17

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EP20110192957 Not-in-force EP2466107B1 (fr) 2010-12-16 2011-12-12 Injecteur de carburant comportant une soupape de commande à équilibrage de pression

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EP (1) EP2466107B1 (fr)
DE (1) DE102010063183A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9016603B2 (en) 2013-01-23 2015-04-28 Caterpillar Inc. Fuel injector
DE102016202945A1 (de) * 2016-02-25 2017-08-31 Robert Bosch Gmbh Elektromagnetisch betätigbares Einlassventil und Hochdruckpumpe mit Einlassventil
CN106704067B (zh) * 2017-01-25 2019-05-14 中国第一汽车股份有限公司 弱泄漏防回油燃料喷射装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008001330A1 (de) 2008-04-23 2009-10-29 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102008041167A1 (de) * 2008-08-12 2010-02-18 Robert Bosch Gmbh Kraftstoffinjektor
DE102009001099A1 (de) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Kraftstoffeinspritzventil
DE102009002742A1 (de) * 2009-04-30 2010-11-04 Robert Bosch Gmbh Kraftstoff-Injektor

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DE102010063183A1 (de) 2012-06-21
EP2466107A1 (fr) 2012-06-20

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