WO2012034748A1 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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Publication number
WO2012034748A1
WO2012034748A1 PCT/EP2011/062513 EP2011062513W WO2012034748A1 WO 2012034748 A1 WO2012034748 A1 WO 2012034748A1 EP 2011062513 W EP2011062513 W EP 2011062513W WO 2012034748 A1 WO2012034748 A1 WO 2012034748A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
fuel injection
pin
spring element
pressure
Prior art date
Application number
PCT/EP2011/062513
Other languages
German (de)
English (en)
Inventor
Andreas Gruenberger
Marco Stieber
Dieter Junger
Jens-Peter Nagel
Michael Kurrle
Udo Schaich
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 WO2012034748A1 publication Critical patent/WO2012034748A1/fr

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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
    • 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
    • F02M63/0014—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
    • 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
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends

Definitions

  • the invention relates to a fuel injection valve, in particular an injector for
  • Fuel injection systems of internal combustion engines Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing,
  • an injector for the injection of fuel into combustion chambers of internal combustion engines is known.
  • the known injector has one in one
  • Injector arranged piezoelectric actuator which actuates a recorded in a valve plate control valve. Furthermore, a nozzle body is provided, at the combustion chamber end of which a nozzle outlet is formed. A nozzle needle is axially movable or actuated in a longitudinal recess of the nozzle body. Further, a rearward, remote from the nozzle outlet end of the longitudinal recess, arranged between the nozzle body and the control valve throttle plate is provided which forms an opening stop for the nozzle needle.
  • the throttle disk acts in this case with the rear side, facing away from the nozzle outlet end face of the nozzle needle and thus limits the opening stroke of the nozzle needle.
  • a control space is formed between the rear nozzle needle end surface and the throttle disk, which is in hydraulic communication with a pressure port serving the fuel supply.
  • a cylindrical holding body is arranged, which accommodates a booster piston and the valve plate containing the control valve.
  • Control valve is arranged a valve pin with a valve body.
  • the valve pin with the valve body has a mushroom-shaped configuration.
  • the valve body is acted upon by a valve spring against a valve seat surface.
  • the valve chamber is on the one hand via a throttle bore, which serves as an inlet and outlet throttle, with the
  • valve chamber of the control valve via a bore serving as a bore with a high-pressure fuel chamber connected.
  • the bypass hole is here by pressing the valve pin
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design of the control valve is made possible.
  • the spring element engages behind the valve body in the region of the valve surface and that the spring element is supported on the one hand on the valve seat surface. In this way, a reliable support of the spring element can be made on the valve seat surface, wherein an optimization of the design of the valve chamber is possible to ensure the smallest possible residual volume. As a result, a rapid closing behavior of a nozzle needle of the fuel injection valve can be achieved by a rapid pressure build-up in the control chamber even without a bypass.
  • the spring element has a plurality of longitudinal slots, which are configured at least in the region of the valve body on the spring element. Through the longitudinal slots, a fuel flow to a sealing seat between the valve body and the valve seat surface is made possible. It is also possible that the spring element has a plurality of circumferential slots, which are provided at least in the region of the valve body. A fuel flow to the sealing seat is then possible via these peripheral slots.
  • a suitable embodiment of the circumferential slots in particular by a bone-shaped configuration of the circumferential slots, an advantageous
  • the Abiaufbohrung opens at a valve seat opposite the inlet side of the valve chamber into the valve chamber, that on an outer side of the sealing sleeve, an annular fuel gap is formed over the fuel from the Abiaufbohrung to the valve seat surface is feasible that the sealing sleeve has a central
  • a radial gap is formed and that at least in the region of the inlet side of the valve chamber, a minimum radial gap
  • Leakage quantity allows.
  • high pressure forces act on the sealing sleeve from the drainage bore in the region of the minimum radial gap.
  • the minimum radial gap is chosen so that the minimum clearance for a required clamping freedom between the
  • the sealing sleeve comprises at the inlet side an end face with a biting edge. This ensures a reliable seal between the radial gap and the Abiaufbohrung or the outside of the sealing sleeve in the region of the inlet side of the valve chamber. It is advantageous that a pressure-relieved space is provided, which is connected to one of
  • Shim is provided which allows adjustment of the opening stroke of the valve body.
  • a spring element arranged in the pressure-relieved space is provided, which acts on the adjusting disk against the valve body.
  • Fig. 1 is a fuel injection valve in an excerpt, schematic
  • Figure 2 is a spring element of the fuel injection valve shown in Figure 1 according to a second embodiment of the invention ..;
  • FIG. 3 shows a spring element of the fuel injection valve shown in FIG. 1 according to a third exemplary embodiment of the invention
  • FIG. 4 shows the detail of IV in FIG. 1 of a fuel injection valve according to a fourth embodiment of the invention
  • FIG. 5 shows the detail of a fuel inlet valve according to a fifth exemplary embodiment of the invention, designated IV in FIG. 1;
  • FIG. 5 shows the detail of a fuel inlet valve according to a fifth exemplary embodiment of the invention, designated IV in FIG. 1;
  • FIG. 6A shows the section of a fuel inlet valve, designated VI in FIG. 1, in accordance with a sixth exemplary embodiment of the invention
  • FIG. 6B is a schematic representation of the detail marked X in FIG. 6A
  • FIG. 6A shows the section of a fuel inlet valve, designated VI in FIG. 1, in accordance with a sixth exemplary embodiment of the invention
  • FIG. 6B is a schematic representation of the detail marked X in FIG. 6A
  • FIG. 7 is a schematic representation of the detail denoted by VII in FIG. 6A;
  • FIG. Fig. 8A in Fig. 1 denoted by VI section of a fuel injection valve in a schematic representation according to the sixth embodiment at a maximum fuel pressure and
  • FIG. 8B in Fig. 8A labeled Y section in a schematic representation.
  • Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the
  • Fuel injection valve 1 is for a fuel injection system with a common rail that leads Diesel fuel under high pressure to a plurality of fuel injection valves 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a housing 2 into which a throttle plate 3 and a valve piece 4 are inserted. Furthermore, the housing 2 is connected to a nozzle body 5. In addition, an injector body 6 is provided, which is connected to the housing 2.
  • a high-pressure bore 7 is configured, which merges into a further high-pressure bore 8 of the valve piece 4.
  • the high-pressure bore 8 On one side 9 of the valve piece 4, the high-pressure bore 8 an enlarged portion 10, from which a connecting hole 1 1 and a throttle bore 12 branch off with an inlet throttle 13, which in the
  • Throttle plate 3 are configured.
  • the connecting hole 1 1 opens into a
  • a nozzle needle 15 is arranged, which is partially surrounded by a sleeve 16. Between the throttle plate 3, the nozzle needle 15 and the sleeve 16, a control chamber 17 is configured.
  • fuel injection valve 1 fuel is passed through the high-pressure bore 8 and the connection bore 11 into the fuel chamber 14.
  • fuel through the inlet throttle 13 from the High-pressure bore 7 branched off and guided into the control chamber 17.
  • the nozzle needle 15 is driven.
  • a closing of the nozzle needle 15 is usually effected, while at a low pressure in the control chamber 17, an opening of the nozzle needle 15 is effected.
  • a throttle bore 18 is configured with an outlet throttle 19.
  • the fuel injection valve 1 also has a control valve 20, via which a fuel flow through the throttle bore 18 can be controlled.
  • the throttle bore 18 is released via the control valve 20 so that fuel over the
  • Throttle bore 18 flows, then the pressure of the fuel in the control chamber 17 drops, resulting in an actuation of the nozzle needle 15. Conversely, if the outflow of fuel through the throttle bore 18 is blocked, then the pressure of the fuel builds up in the
  • the control valve 20 has a valve chamber 21, which is a section
  • valve space 21 is configured in the valve piece 4.
  • the control chamber 17 is connected via the throttle bore 18 with the valve chamber 21.
  • the connection can also be over another
  • Abiaufbohrung 18 made, for example, has a constant diameter.
  • a sealing sleeve 25 of the control valve 20 is arranged in the valve chamber 21, a sealing sleeve 25 of the control valve 20 is arranged. Between the
  • Sealing sleeve 25 and a wall 26 of the valve chamber 21 remains an annular
  • a valve seat surface 27 is configured. Via the fuel gap 26, the fuel passes from the connecting part 23 to the valve seat surface 27.
  • the sealing sleeve 25 has a guide bore 28 in which a valve pin 29 is guided.
  • the valve pin 29 of the control valve 20 has a valve body 30 which is connected to the
  • Valve seat surface 27 to a sealing seat 31 cooperates.
  • the fuel can flow off into a low-pressure space 32 via the open sealing seat 31.
  • a coupler piston 33 is provided which can be actuated via an actuator 34.
  • the actuator 34 may be configured as a piezoelectric actuator 34 or as a magnetic actuator 34.
  • a spring element 35 is also arranged in the valve chamber 21 .
  • the spring element 35 encloses the valve body 30 of the valve pin 29 in sections.
  • Embodiment engages behind the spring element 35, the valve body 30 in the region of Valve seat surface 27.
  • the sealing sleeve 25 has a shoulder 36.
  • the spring element 35 is supported on the one hand on the valve seat surface 27 of the valve member 4 and on the other hand on the shoulder 36 of the sealing sleeve 25 from.
  • the spring element 35 acts on the sealing sleeve 25 in a direction 37.
  • the sealing sleeve 25 is acted upon against an end face 38 of the throttle plate 3.
  • the spring element 35 has a plurality of longitudinal slots 39, of which only the longitudinal slot 39 is marked for the sake of simplicity of illustration.
  • the longitudinal slot 39 extends at least in the region of the valve body 30 by the spring element 35.
  • the longitudinal slot 39 is on the one hand a certain elasticity of the spring element 35 allows.
  • the longitudinal slots 39 serve as feedthroughs for the fuel in order to guide it further from the fuel gap 26 to the sealing seat 31.
  • a pressure-relieved space 45 is configured, which is adjacent to a valve seat surface 27 opposite inlet side 23 of the valve chamber 21.
  • the inlet side 23 is predetermined by the connection part 23.
  • the valve pin 29 guided in the sealing sleeve 25 is pressure-relieved.
  • the valve pin 29 is relieved of pressure with the valve body 30 both from the side of the low-pressure chamber 32 and from the side of the pressure-relieved space 45.
  • the pressure-relieved space 45 is connected via a relief bore 46 with the low pressure.
  • a stop pin 47 is arranged, the one
  • Hub stopper 48 for the valve pin 29 forms.
  • the stop pin 47 is in this case pivotally mounted in the pressure-relieved space 45.
  • a spring element 49 is arranged in the pressure-relieved space 45, which is configured in this embodiment as a valve spring 49.
  • a shim 50 is arranged, which has a through hole 51.
  • a pin 52 of the valve pin 29 engages in the through hole 51 of the dial 50 a.
  • the shim 50 on a collar 53 of
  • Valve pin 29 supported.
  • a distance between the dial 50 and the stroke stop 48 of the stop pin 47 is defined, which defines an opening stroke of the valve body 30.
  • adjustment of the opening stroke of the valve body 30 can be achieved via the dial 50.
  • a parallelism between the dial 50 and the flat stroke stop 48 of the stop pin 47 is ensured in this embodiment, the pivotable mounting of the stop pin 47.
  • a gimbal bearing by a ball segment 54 which is mounted in a spherical cap 55 be realized.
  • Stop bolt 47 is held by the valve spring 49 in the bearing.
  • This embodiment has the advantage that a residual volume of the valve chamber 21 is very small. This allows the control valve 20 to ensure a fast switching behavior without a bypass is required. Thus, a bypass over which fuel under high pressure, for example, from the fuel chamber 14 is guided directly into the valve chamber 21, can be saved. In addition, a reduced by the control valve 20 amount of fuel is thereby reduced, which has a favorable effect on the efficiency.
  • Nozzle needle closing of the nozzle needle 15 can be achieved.
  • the increase in pressure is usually proportional to the volume of the valve chamber 21, the fuel compressibility and the flow rate. Since the fuel compressibility is a constant and an increase in the volume flow, for example via a bypass, has disadvantages, the reduction of the volume of the valve chamber 21 is particularly advantageous. This is achieved by the space-optimized design of the spring element 35. This can also increase the temperature load of the actuator 34 and the rest
  • Fuel return system can be counteracted.
  • High pressure pump can be used.
  • the pump drive power is reduced, so that the efficiency of the internal combustion engine increases.
  • Hubanschlags 48 give more advantages. It is made possible a separate manufacturability of the items, so that a concatenation of length measures deleted. In addition, seat coating tolerances on the dial 50 can be compensated. In addition, setting tolerances with respect to the stroke stop 48 can be reduced.
  • valve body 30 Upon actuation of the valve body 30 thus results in a defined opening cross-section at the sealing seat 31, so that a certain amount of the fuel flows from the valve chamber 21. Due to the pressure drop in the valve chamber 21 flows a corresponding
  • the pressure in the valve chamber 21 increases due to the small valve volume by the inflowing amount from the control chamber 17 again very quickly, so that the pressure in the control chamber 17 by the inflow over the inlet throttle 13 fuel quantity increases rapidly and therefore the nozzle needle 15 quickly closes.
  • the throttle area of the nozzle needle 15 can be traversed quickly, which leads to a better mixture preparation.
  • there is a steep closing edge of the injection rate which is the total amount in the maximum
  • the opening and closing force for actuating the valve body 30 is further reduced by an advantageous guidance of the valve pin 29 in the guide bore 28.
  • the valve pin 29 is guided in the guide bore 28 with a very small clearance and in addition, a reliable seal between the sealing sleeve 25 and the end face 38 of the throttle plate 3 is formed.
  • an advantageous embodiment of a radial gap 56 between the valve pin 29 and the guide bore 28 of the sealing sleeve 25 is provided. This is also described in more detail with reference to FIGS. 6A, 6B, 7, 8A, 8B.
  • Fig. 2 shows the spring element 35 of the fuel injection valve 1 shown in Fig. 1 according to a second embodiment.
  • the sealing force for the sealing sleeve 25 results from a superposition of the hydraulic pressure force and a spring force of the spring element 35, which is tangentially supported on the transition contour of the valve chamber 21.
  • the support is in this embodiment in this case at the
  • the bias of the spring element 35 is in this case transmitted axially to the shoulder 36 of the sealing sleeve 25.
  • the shoulder 36 of the sealing sleeve 25 is designed so that a sufficient radial clearance to the spring element 35 is present in order to center the sealing sleeve 25 through the valve seat of the valve body 30
  • Valve seat surface 27 manufacturing and strength reasons, preferably designed with large radii, so that a head portion 57 of the spring element 35 is preferably designed kelchförmig, so that a smallest possible remaining volume of the valve chamber 21 is formed.
  • the inflow of fuel to the sealing seat 31 is ensured by the longitudinal slots 39, which extend axially.
  • Fig. 3 shows a spring element 35 of the fuel injection valve 1 shown in Fig. 1 according to a third embodiment.
  • the spring element 35 has in this embodiment, a ring 60 with circumferential slots 61, 62, wherein in FIG. 3 for simplicity of illustration, only the circumferential slots 61, 62 are marked.
  • the spring element 35 is designed in the form of a spring sleeve 35.
  • Outer edge 63 of the spring element 35 is configured rounded, so that the
  • Circumferential slots 61, 62 By a sufficient distance of the ring 60 of the valve body 30 in this case a fuel flow between the spring element 35 and the valve body 30 is made possible. As a result, throttling can be avoided.
  • the spring principle can be achieved in this embodiment by a combination of axial bending beams 64, 65, so that between the spring sleeve 35 and the
  • Valve piece 4 only a very small slip occurs.
  • a support ring 66 on which the rounded outer edge 63 is configured, substantially uniformly abut the valve piece 4.
  • the circumferential slots 61, 62 may be configured as bone-shaped peripheral slots 61, 62. As a result, a volume reduction is possible without the rigidity of the spring element 35 is significantly reduced.
  • Fig. 4 shows the designated in Fig. 1 with IV section of the fuel injection valve 1 according to a fourth embodiment.
  • the valve pin 29 at its pin 52 a ball cap 67, which is the flat
  • Hub stop 48 of the stop pin 47 faces. This results in an approximately punctiform contact point 68, with the ball cap 67 on the
  • Stroke stop 48 strikes.
  • the spherical radius of the ball cap 67 is predetermined by the Herz's pressing condition. To avoid an edge support, the squareness between the flat stop surface 48 of the stroke stopper 48 and the valve pin 29 in response to a pin diameter of the pin 25 is limited.
  • Fig. 5 shows the designated in Fig. 1 with IV section of the fuel injection valve 1 according to a fifth embodiment.
  • the valve pin 29 is located on a valve pin 29 facing flat end 69 of the dial 50 at.
  • a side facing away from the end face 69 further end face 70 of the dial 50 faces the stop pin 47.
  • the end face 70, the stroke stop 48 of the stop pin 47 faces, which is formed by a ball cap 71 of the stop pin 47. This is an approximately punctiform
  • Stop bolt 47 formed.
  • a spherical surface contact 68 is formed, which ensures a permanently stable stroke stop 48.
  • FIG. 6A shows the section of the fuel injection valve 1 designated VI in FIG. 1 in accordance with a sixth embodiment. Furthermore, FIG. 6B shows the detail marked X in FIG. 6A in a schematic representation. In Figs. 6A, 6B, a state is illustrated in which a relatively low rail pressure p Rai
  • the fuel pressure across the fuel gap 26 is illustrated by arrows 72 in FIG. 6A.
  • an approximately constant fuel pressure p is applied over the entire fuel gap 26, so that the fuel pressure p exists, in particular in the area of the valve body 30.
  • valve pin guide which is given by the guide bore 28 of the sealing sleeve 25 is, with a very small clearance with a defined distance LR / V to
  • the radial gap 26 has a gap width s in the radial direction, which is selected so that at a gap entrance 74 and a gap outlet 75 is a minimum clearance for a clamping freedom.
  • the manufacturing preferred form for the design of the radial gap 56 is preferably set so that the gap width s is equal to or greater than the minimum gap width at the gap inlet and outlet 74 and 75.
  • the radial gap 56 which is the guide gap 56, executed in the direction 37 with a constant gap width s.
  • the surface of the guide bore 28 and the surface of the outer side 77 are each designed in the form of a cylinder jacket and oriented coaxially with one another.
  • the radial gap 56 is thus configured approximately hollow cylindrical.
  • FIG. 7 shows the section of the fuel injection valve 1 according to the sixth exemplary embodiment, designated VII in FIG. 6A.
  • the sealing sleeve 25 has on her
  • biting edge 78 is a reliable seal between the connection part
  • FIG. 8A shows the section of the fuel injection valve 1 according to the sixth exemplary embodiment, designated VI in FIG. 1, at a maximum rail pressure p Rai
  • FIG. 8B shows a schematic representation of the detail designated Y in FIG. 8A. While at low rail pressure p Rai
  • Radial gap 56 results at high rail pressure p Rai
  • p ra ii_max
  • the leakage quantity dQ can at least approximately disappear.
  • the resulting due to the laminar flow pressure loss along the guide thus has idealized a rectangular course, as illustrated by the arrows 79 in Fig. 8A.

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

Abstract

L'invention concerne une soupape d'injection de combustible (1), qui sert en particulier d'injecteur pour des installations d'injection de combustible de moteurs à combustion interne comprimant de l'air et à auto-allumage. Cette soupape comprend une soupape de commande (20) et un espace de commande (17), l'espace de commande (17) étant relié par un alésage d'étranglement (18) à un espace de soupape (21) de la soupape de commande (20). Dans le cas présent, un boulon de soupape (29) et un élément de ressort (35) sont disposés dans l'espace de soupape (21). Le boulon de soupape (29) présente également un corps de soupape (30), qui coopère avec une surface de siège de soupape (27) pour faire un siège étanche (31). Dans le cas présent, un manchon d'étanchéité (25), dans lequel le boulon de soupape (29) est guidé, est disposé dans l'espace de soupape (21). De plus, l'élément de ressort (35) est guidé sur le côté en passant à côté du corps de soupape (30) du boulon de soupape (29). De plus, l'élément de ressort (35) s'appuie d'une part dans la zone de la surface de siège de soupape (27) et d'autre part sur le manchon d'étanchéité (25). De ce fait, l'espace de soupape (21) peut être réalisé avec un volume restant relativement faible. De ce fait, on peut faire l'économie d'une dérivation et on peut avoir malgré tout un comportement à la fermeture rapide lors de l'actionnement d'un pointeau (15).
PCT/EP2011/062513 2010-09-16 2011-07-21 Soupape d'injection de combustible WO2012034748A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010040874 DE102010040874A1 (de) 2010-09-16 2010-09-16 Brennstoffeinspritzventil
DE102010040874.3 2010-09-16

Publications (1)

Publication Number Publication Date
WO2012034748A1 true WO2012034748A1 (fr) 2012-03-22

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DE (1) DE102010040874A1 (fr)
WO (1) WO2012034748A1 (fr)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
EP2818689A1 (fr) 2013-06-27 2014-12-31 Robert Bosch Gmbh Soupape d'injection de carburant
DE102013212513A1 (de) 2013-06-27 2014-12-31 Robert Bosch Gmbh Kraftstoffeinspritzventil mit mehrteilig ausgeführtem Ventilkörper am Steuerraum

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DE102011078400A1 (de) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Kraftstoffinjektor
DE102012212266B4 (de) * 2012-07-13 2015-01-22 Continental Automotive Gmbh Fluidinjektor
DE102012212264B4 (de) 2012-07-13 2014-02-13 Continental Automotive Gmbh Verfahren zum Herstellen eines Festkörperaktuators

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DE102009003145A1 (de) * 2009-05-15 2010-11-18 Robert Bosch Gmbh Kraftstoffinjektor für Brennkraftmaschinen
DE102009027504A1 (de) * 2009-07-07 2011-01-20 Robert Bosch Gmbh Kraftstoffinjektor für eine Brennkraftmaschine
DE102009045486A1 (de) * 2009-10-08 2011-04-14 Robert Bosch Gmbh Kraftstoff-Injektor

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Publication number Priority date Publication date Assignee Title
DE10353169A1 (de) 2003-11-14 2005-06-16 Robert Bosch Gmbh Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen, insbesondere piezogesteuerter Common-Rail-Injektor
DE102004036367B3 (de) * 2004-07-27 2005-10-13 Siemens Ag Einspritzventil
DE102008001330A1 (de) * 2008-04-23 2009-10-29 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102009001099A1 (de) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Kraftstoffeinspritzventil
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DE102009045486A1 (de) * 2009-10-08 2011-04-14 Robert Bosch Gmbh Kraftstoff-Injektor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2818689A1 (fr) 2013-06-27 2014-12-31 Robert Bosch Gmbh Soupape d'injection de carburant
DE102013212490A1 (de) 2013-06-27 2014-12-31 Robert Bosch Gmbh Kraftstoffeinspritzventil mit einem stoffschlüssig und/oder kraftschlüssig zur Steuerraumhülse verbundenen Ventilkörper
DE102013212513A1 (de) 2013-06-27 2014-12-31 Robert Bosch Gmbh Kraftstoffeinspritzventil mit mehrteilig ausgeführtem Ventilkörper am Steuerraum
EP2818690A1 (fr) 2013-06-27 2014-12-31 Robert Bosch Gmbh Soupape d'injection de carburant dotée d'un corps de soupape conçu en plusieurs parties sur la chambre de commande

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