WO2008138800A1 - Injecteur à actionneur piézoélectrique - Google Patents

Injecteur à actionneur piézoélectrique Download PDF

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Publication number
WO2008138800A1
WO2008138800A1 PCT/EP2008/055512 EP2008055512W WO2008138800A1 WO 2008138800 A1 WO2008138800 A1 WO 2008138800A1 EP 2008055512 W EP2008055512 W EP 2008055512W WO 2008138800 A1 WO2008138800 A1 WO 2008138800A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
valve piston
injector according
injector
chamber
Prior art date
Application number
PCT/EP2008/055512
Other languages
German (de)
English (en)
Inventor
Stefan Schuerg
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 WO2008138800A1 publication Critical patent/WO2008138800A1/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
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • 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

Definitions

  • the invention relates to an injector for injecting fuel into the combustion chamber of an internal combustion engine, in particular a common rail injector according to the preamble of claim 1.
  • DE 103 53 169 A1 shows a piezo-controlled common-rail injector with a control valve actuated by means of a piezoactuator and designed as a 3/2-way valve.
  • a control valve When the control valve is open, a control chamber bounded by an end face of a valve element is hydraulically connected to a low-pressure region of the injector, so that a net discharge into the low-pressure region results from the control chamber, which is supplied with high-pressure fuel via an inlet throttle.
  • the pressure in the control chamber decreases, which in turn has an opening movement of the valve element and thus the release of a nozzle hole arrangement result.
  • the piezoelectric actuator does not act directly on a valve piston of the control valve, but only indirectly via a coupler piston of a hydraulic coupler, in particular to compensate for temperature-induced length fluctuations of the piezoelectric actuator.
  • the valve piston is adjustably arranged in the axial direction in a valve chamber which is delimited by a throttle plate in an axial direction. To adjust the valve piston must be expended by the piezoelectric actuator large adjustment forces, since the valve piston from under high pressure standing fuel is pressurized in the direction of its upper valve seat. Due to the large opening force to be applied, the demands on the performance and the stability of the piezoelectric actuator and the entire switching chain are high.
  • the invention is therefore based on the object to propose a piezo-controlled injector, in which the applied by the piezoelectric actuator opening force is reduced.
  • the invention is based on the idea not to arrange the valve piston axially displaceable in a valve chamber, but to form the valve chamber on the valve piston, in particular such that the valve chamber, at least partially, is mitver Surprise in adjusting the valve piston in the axial direction.
  • the valve chamber is arranged at least partially on the outer circumference of the valve piston, such that the valve piston delimits the valve chamber at any time in two opposite axial directions, that is to say from the valve piston two pressure application surfaces acting in opposite axial directions to be provided.
  • the magnitude of the resultant compressive force acting in an axial direction can be determined, which is due to the pressurization of the pressure surfaces of the valve piston acting in the opposite axial directions by the high pressure fuel in the valve chamber .
  • the opening force to be applied by the piezoactuator can be reduced, as a result of which piezoactuators with lower power and thus with a smaller overall volume and lower power consumption can be used.
  • the stability requirements are reduced to the entire switching chain.
  • the acting in opposite axial directions effective pressure application surfaces are at least approximately, preferably exactly the same size.
  • the compressive force components cancel in the opposite axial directions, as a result of which no closing force which is to be overcome by the piezoactuator acts on the valve piston from the fuel located in the valve chamber.
  • the control valve is a pressure-balanced valve in the axial direction.
  • valve piston diameter ie the diameter of the valve piston, with which the valve piston rests against its valve piston seat
  • valve piston guide diameter ie the diameter of the valve piston in its adjacent to the valve chamber guide portion
  • valve piston is formed by a coupler piston of a hydraulic coupler.
  • the coupler piston preferably acts in a force-transmitting manner directly or with another coupler piston, in particular permanently connected to the piezoactuator, in a coupler body.
  • the simultaneous at least partially, preferably complete limitation of the valve chamber by the valve piston in the opposite axial directions and the concomitant minimization of the opening force applied by the piezo actuator allows an embodiment of the hydraulic coupler with a transmission ratio of 1.
  • Such a coupler is relatively easy to implement ,
  • the coupling piston fixedly connected to the piezoelectric actuator is formed as a sleeve closed on one side, is guided in the other coupler piston, in particular the valve piston.
  • valve chamber is limited by a diameter-reduced portion of the valve piston.
  • valve piston sealing diameter is formed by a radially inwardly tapering conical surface (conical surface), which cooperates sealingly with a valve piston seat on a guide member accommodating the valve piston.
  • the control valve it is conceivable to design the control valve as a slide valve, in which case the valve piston diameter is formed by a guide section of the valve piston.
  • valve chamber When the control valve is open, the valve chamber is preferably connected to a discharge chamber, in which a free end of the valve piston protrudes.
  • discharge chamber is in turn connected to the injector return, in particular via a low pressure piezoelectric actuator space which receives the piezoelectric actuator.
  • At least one closing spring is provided with which the valve piston is spring-loaded in the direction of its valve piston seat.
  • the closing spring engages in an end blind bore of the valve piston.
  • an axial stop, which is opposite the valve piston seat, for the valve pistons is formed by a throttle plate, in which Preferably, the outlet throttle of the control chamber and / or the inlet throttle is integrated to the control chamber.
  • an embodiment is advantageous in which the closing spring acting on the valve piston is not (completely) arranged at axial distance from the spring element which acts on the piezoactuator and / or the coupler, but instead in which the spring element and the closing spring (at least in sections) nested in the radial direction, ie is arranged radially in one another.
  • Preferred is an arrangement of the spring element and the closing spring, wherein the closing spring does not project beyond the spring element in the axial direction. This can be realized, for example, in that the spring element and the closing spring are supported on a common support plane in the axial direction.
  • an embodiment can be realized in which the closing spring projects beyond the spring element in the axial direction, in particular when the support surface for the closing spring is axially spaced from the support surface for the spring element.
  • an embodiment can be realized in which the spring element projects beyond the closing spring in two axial directions.
  • an embodiment is advantageous in which the closing spring either on a is integrally formed with the valve piston formed circumferential collar or on a fixed to the valve piston retaining ring in the axial direction.
  • the closing spring either on a is integrally formed with the valve piston formed circumferential collar or on a fixed to the valve piston retaining ring in the axial direction.
  • a circumferential groove is preferably introduced into the valve piston.
  • the closing spring is arranged completely radially within the spring element for the piezoelectric actuator and / or the hydraulic coupler, ie the closing spring does not project beyond the spring element in the axial direction.
  • the closing spring and the spring element are jointly supported on a valve member receiving the guide member in the axial direction.
  • an outer boundary of the coupler space accommodating a coupler volume is not made in one piece, but rather in several parts, preferably in two parts.
  • the boundary of the coupler space as a radially outer circumferential boundary preferably comprises a sleeve part, which cooperates in a sealing manner with a separate cover part from the sleeve part.
  • the sleeve part is spring-loaded against the cover part.
  • the spring element biasing the piezoactuator in the axial direction is preferably provided, which is advantageously supported on a (lower) side facing away from the cover part, annular end face of the sleeve part.
  • a biasing force must be realized with the spring element, which is greater than the product of the maximum fuel pressure within the coupler space and the inner cross-sectional area of the sleeve part.
  • the sleeve part serves as an external guide for guiding the coupler piston, in particular the valve piston.
  • the inner diameter of the sleeve part which corresponds to the Kopplerkolben pressmesser plus a minimum clearance, due to the formation of a separate component can be made particularly accurate and easy.
  • an embodiment is advantageous in which the sleeve part has on its cover part facing the end face a biting edge, preferably with a flat surface on the cover part cooperates sealingly.
  • the provision of a biting edge ensures a sufficient, the tightness of the coupler space ensuring surface pressure.
  • cover part there are various possibilities for forming the cover part. Preferred is an embodiment in which the cover part on the actual piezoelectric actuator, in particular positive fit, is fixed. It is also a one-piece design of the cover part and piezoelectric actuator feasible. Furthermore, it is conceivable that, due to the spring loading of the sleeve part in the mounted state, the cover part bears only on one end face of the piezoactuator and is pressed against the sleeve part against it.
  • an embodiment of the injector in which the cover part is designed as adjusting piece can be compensated with the manufacturing tolerances of the hydraulic actuator and / or a housing part of the injector. It is also conceivable to provide a separate adjusting piece between the actuator and the hydraulic coupler.
  • an embodiment is advantageous in which the control chamber, which can be connected via the control valve to the low-pressure region, not only via an inlet throttle, which opens directly into the control chamber, with high pressure stagnant fuel is refillable, but in addition to the inlet throttle a Flightdrossel is provided, can flow through the high-pressure fuel with the control valve closed in the control chamber, resulting in a faster refilling of the control chamber and thus in a faster pressure increase within the control chamber and thus in turn results in a faster closing behavior of the valve element.
  • the filling throttle which is permanently hydraulically connected to the high-pressure region of the injector, is preferably arranged in such a way that it first flows via this fuel to an outflow throttle, via which the control chamber communicates with the valve chamber of the Control valve is connected and then flows through the outlet throttle into the control chamber.
  • the filling throttle and the outlet throttle are thus connected in series. It is conceivable to arrange the filling throttle such that the fuel can flow directly to the outlet throttle.
  • an embodiment can be realized in which the filling throttle or a filling channel having these opens into the valve chamber and flows out of this outflowing fuel from the valve chamber to the outlet throttle and via this into the control chamber.
  • the filling throttle is arranged in a filling channel, which is branched off from a fuel supply line for supplying the injector with fuel under high pressure.
  • a flow channel discharging out of the control chamber opens into this filling channel with an outlet throttle, so that both the valve chamber of the control valve and the control chamber are directly refilled when the control valve is closed via the filling throttle.
  • the filling channel opens out of a pressure chamber of the injector.
  • 1 is a schematic partial view of a piezo-controlled injector
  • 2 shows a schematic partial view of an alternative embodiment of a piezo-controlled injector, in which a spring element for the piezoelectric actuator and a closing spring for the valve piston, which are arranged nested in the radial direction,
  • Fig. 3 is a schematic representation of an alternately formed coupler space
  • FIG. 4 shows a schematic partial view of a piezo-controlled injector, in which a
  • Fig. 1 a section of a common rail injector designed as an injector 1 for injecting fuel into the combustion chamber of an internal combustion engine is shown.
  • the injector 1 comprises a one-piece or multi-part valve element 2, which is adjustable between an open position and a closed position. In its open position, the valve element 2 releases the fuel flow from a nozzle hole arrangement (not shown) into the combustion chamber of an internal combustion engine.
  • valve element 2 With an upper end face 3, the valve element 2 defines a control chamber 4.
  • the control chamber 4 is arranged radially inside a sleeve 5, which by means of a helical spring 6, which held on a valve element 2 Circlip 7 is supported, spring-loaded in the axial direction on a throttle plate 8.
  • control chamber 4 opens an introduced into the throttle plate 8 inlet throttle 9, which is hydraulically connected to a fuel supply line 10.
  • the fuel supply line 10 connects a pressure chamber 11 which surrounds the control chamber 4 radially on the outside with fuel under high pressure from a fuel high-pressure accumulator (rail) (not shown).
  • a fuel high-pressure accumulator (rail) (not shown).
  • the valve element 2 When the valve element 2 is open, the fuel flows from the pressure chamber 11 through the nozzle hole arrangement (not shown) into the combustion chamber of the internal combustion engine.
  • the control chamber 4 is hydraulically connected to a valve chamber 13 of a control valve 14 (servo valve) via an outlet throttle 12, which is also introduced into the throttle plate 8.
  • the control valve 14 comprises a valve piston 15, which is guided in an axially displaceable manner in a guide bore 16 of a guide part 17.
  • the valve piston 15 of the control valve 14 is formed by a coupler piston of a hydraulic coupler 18, via which an adjusting movement of a piezoelectric actuator 19 is transmitted. This is the piezoelectric actuator
  • the further coupler piston 20 of the coupler 18 is designed as a closed end sleeve, in which the valve piston 15 is guided axially displaceable.
  • valve chamber 13 is bounded radially on the outside by a peripheral wall 24 of the guide bore 16. In both axial directions, the valve chamber 13 is limited exclusively by the valve piston 15.
  • a valve piston sealing diameter D 1 with which the valve piston 15 in its closed position rests against a valve piston seat 25, which is formed by the guide part 17, is just as large as a valve piston guide diameter D 2 in a guide region 26 of the valve piston 15, so that two effective in opposite axial directions pressure application surfaces 27, 28 (projection surfaces) of the valve piston 15 are equal.
  • the actual effective pressure application surfaces (projection surfaces) are drawn with dashed lines.
  • Radially inside, the valve chamber 15 is bounded by a diameter-reduced portion 29 of the valve piston 15.
  • valve chamber 13 By thus constructed valve chamber 13, the force acting in opposite directions Axialkraftkomponenten, which are due to the located within the valve chamber 13, pressurized fuel cancel each other, so that no resultant axial force acts on the valve piston 15.
  • the control valve 14 is thus a pressure balanced in the axial direction valve.
  • the closing spring 30 is disposed within a Ab tenuraums 31 which is bounded radially outwardly of the guide member 17. More specifically, the Ab tenuraum 31 is limited by a bore in the guide member 17 whose diameter is greater than the diameter the guide bore 16.
  • the closing spring 30 is based on one nenenden on the throttle plate 8, which forms an axial stop 32 for the valve piston 15 and the other end at the bottom of an end blind hole 33 in the valve piston 15th
  • the Abschraum 31 is hydraulically connected via a connecting line 34 with a piezoelectric actuator space 35, which in turn is connected to the injector return, not shown.
  • the piezoelectric actuator chamber 35 and the exhaust chamber 31 form a low-pressure region 36 of the injector 1.
  • the piezoelectric actuator 19 is energized in a conventional manner, causing the other coupler piston 21 moves in the drawing plane down. Via the coupler volume 22, an axial force is transmitted to the valve piston 15, which thus likewise moves downwards into the discharge chamber 31 in the plane of the drawing, whereby fuel from the valve chamber 13 and thus via the outlet throttle 12 from the control chamber 4 into the exhaust chamber 31 and can flow to the Injektor Weglauf via the connecting line 34 and the piezoelectric actuator space 35.
  • the flow cross sections of the inlet throttle 9 and the outlet throttle 12 are matched to one another such that when the control valve 14 is open, a net outflow from the control chamber 4 results, which in turn reduces the pressure in the control chamber 4.
  • valve element 2 preferably control rod plus nozzle needle
  • the energization of the piezoelectric actuator 19 is interrupted, whereby the coupler piston 21, in particular due to the spring force of the spring element 23 moves in the drawing plane upwards.
  • the valve piston 15 moves upwards in the drawing plane in the axial direction, whereby the valve piston 15 with a conical surface 37 (valve piston diameter Di) rests against the valve piston seat 25 and the valve piston 15 thus abuts the valve chamber 13 closes.
  • the pressure in the control chamber 4 increases, as a result of which the valve element 2 in the drawing plane is moved downwards onto its valve seat, which in turn terminates the injection process.
  • FIG. 2 corresponds essentially to the exemplary embodiment according to FIG. 1, so that essentially only the differences from the exemplary embodiment according to FIG. 1 are discussed in order to avoid repetition.
  • the closing spring 30 is not arranged within the discharge chamber 31, but within the piezoelectric actuator chamber 35.
  • the closing spring 30 is located radially between the valve piston 15 of the control valve 14 and the spring element 23, which is supported in the axial direction on the hydraulic coupler 18.
  • Both the spring element 23 and the closing spring 30 are supported in the axial direction on an upper plane 38, which is flat in the plane of the drawing, of the guide part 17.
  • the closing spring 30 lies at the other end with its front side facing away from the guide part 17 at a securing point.
  • ring 39 shaft lock ring
  • the closing spring 30 urges the valve piston 15 in the closing direction, in the drawing plane upwards. It is the task of the closing spring 30, the valve piston 15 to move in the direction of the valve piston seat 15 when the energization of the piezoelectric actuator 19 is interrupted.
  • the closing spring 30 By the arrangement of the closing spring 30 shown radially in FIG. 2 radially inside the spring element 23, the installation space of the injector 1 can be minimized compared with the exemplary embodiment according to FIG. 1, in particular in the event that larger valve piston seat diameters are to be realized and consequently in comparison to FIG the embodiment of FIG. 1 larger closing springs must be used with a larger clamping force. As is apparent from Fig. 2, the closing spring 30 does not project beyond the spring element 23 in the axial direction.
  • FIG. 3 only a section of another embodiment of an injector 1 is shown.
  • the illustrated hydraulic coupler 18 can be realized both in the embodiment of FIG. 1 and in the embodiment of FIG. 2.
  • the coupler space 41 surrounding the coupler volume 22 is not realized as a blind hole within the coupler piston 20.
  • the coupler space 41 is bounded radially on the outside by a sleeve part 42.
  • the coupler space 41 is bounded by a cover part 43 which is fixed to the piezoactuator 19.
  • the coupler space 41 bounded by a plane in the drawing upper end face 44 of the valve piston 15, which serves as a coupler piston in the embodiment shown.
  • the sleeve part 42 is spring-loaded in the axial direction in the plane of the drawing upwards by the spring element 23, wherein the spring element 23 on the one hand on a lower, annular end face of the sleeve part 42 in the drawing plane and at the end face 38 of the guide part 17th for the valve piston 15 is supported.
  • the coupler body 21 shown there is formed in two parts in the embodiment of FIG. consists of the lid part 43 and the sleeve part 42.
  • the sleeve part 42 has a circumferential biting edge 45, which is formed directly on the inner circumference of the sleeve part 42 to avoid a pressure step.
  • the biting edge 45 is realized by a slightly conical bevel at the upper end face of the sleeve part 42 in the drawing plane.
  • the spring force (biasing force) with which the spring element 23 biases the sleeve part 42 and thus the piezoelectric actuator 19 is dimensioned so that the sleeve part 42 is not in the axial direction down from the cover part even with a maximum pressurization of the coupler volume 22 during operation of the injector 1 43 can be moved away.
  • the fixed to the piezoelectric actuator 19 cover part 43 has in addition to the sealing of the coupler space 41 in the axial direction in the drawing plane up the task of Einstell Swisss.
  • Axialerstre- cover (thickness) of the cover part 43 manufacturing tolerances of the piezoelectric actuator 19 and other components of the injector 1 are compensated.
  • FIG. 4 The embodiment of an injector 1 shown in FIG. 4 essentially corresponds to the embodiment according to FIG.
  • a Playrossel 46 is provided in the embodiment of an injector 1 shown in FIG. 4 in addition to the inlet throttle 9.
  • the Gredrossel 46 is disposed in a filling channel 47 within the guide member 17, wherein the filling channel 47 is permanently connected to the fuel supply line 10.
  • the fuel supply line 10 and the pressure chamber 11 belong to the high pressure region of the injector 1. In this prevails substantially rail pressure.
  • the filling channel 47 with the filling throttle 46 opens directly into the valve chamber 13.
  • a drain channel 48 which opens out of the control chamber 4 and is integrated into the outlet throttle 12. Since the filling throttle 46 and the outlet throttle 48 are connected in series, with the control valve 14 closed, not only does fuel flow via the inlet throttle from the high-pressure region of the injector into the control chamber 4, but also via the filling throttle 46 and the outlet throttle 12 Fuel over the Golfdrossel 46 into the valve chamber 13 of the control valve 14. Overall, a faster refilling of the valve chamber 13 and the control chamber 4 is achieved hereby, resulting in an increased closing speed of the valve element 2.

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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

La présente invention concerne un injecteur (1) destiné à injecter du carburant dans la chambre de combustion d'un moteur à combustion interne, en particulier un injecteur à rampe commune, comprenant : un élément de soupape (2) qui peut se déplacer en direction axiale entre une position de fermeture et une position d'ouverture dans laquelle le flux de carburant peut s'effectuer librement d'un dispositif d'orifice de buse vers l'intérieur de la chambre de combustion; et un actionneur piézoélectrique (19) qui permet l'actionnement d'un piston de soupape (15) d'une soupape de commande (14), le carburant, lorsque la soupape de commande (14) est ouverte, pouvant sortir d'une chambre de soupape (13) de la soupape de commande (14) pour pénétrer dans une zone basse pression de l'injecteur. Selon l'invention, le piston de soupape (15) délimite la chambre de soupape (13) simultanément dans deux directions axiales opposées.
PCT/EP2008/055512 2007-05-15 2008-05-06 Injecteur à actionneur piézoélectrique WO2008138800A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007022856 2007-05-15
DE102007022856.4 2007-05-15
DE102007047426.3 2007-10-04
DE102007047426A DE102007047426A1 (de) 2007-05-15 2007-10-04 Injektor mit Piezoaktor

Publications (1)

Publication Number Publication Date
WO2008138800A1 true WO2008138800A1 (fr) 2008-11-20

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PCT/EP2008/055512 WO2008138800A1 (fr) 2007-05-15 2008-05-06 Injecteur à actionneur piézoélectrique

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DE (1) DE102007047426A1 (fr)
WO (1) WO2008138800A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010076645A1 (fr) 2008-12-29 2010-07-08 C.R.F. Società Consortile Per Azioni Système d'injection de carburant à haute stabilité et répétabilité de fonctionnement pour un moteur à combustion interne
EP2383454A1 (fr) 2010-04-27 2011-11-02 C.R.F. Società Consortile per Azioni Formage du débit d'injection de carburant dans un moteur à combustion interne
EP2405121A1 (fr) 2010-07-07 2012-01-11 C.R.F. Società Consortile per Azioni Système d'injection de carburant pour moteur à combustion interne

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CH700396A1 (de) * 2009-02-09 2010-08-13 Ganser Hydromag Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
DE102009001104A1 (de) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Kraftstoffinjektor
DE102009001322A1 (de) * 2009-03-04 2010-09-09 Robert Bosch Gmbh Kraftstoffinjektor
DE102009002835A1 (de) 2009-05-06 2010-11-11 Robert Bosch Gmbh Piezokeramik für einen Piezoaktor oder ein Piezoaktormodul
DE102009026533A1 (de) 2009-05-28 2010-12-02 Robert Bosch Gmbh Piezoaktormodul und Piezoinjektor
DE102009027096A1 (de) 2009-06-23 2010-12-30 Robert Bosch Gmbh Kraftstoffinjektor mit Schaltventil
DE102009027494A1 (de) * 2009-07-07 2011-01-13 Robert Bosch Gmbh Kraftstoff-Injektor mit druckausgeglichenem Steuerventil
DE102009029380A1 (de) 2009-09-11 2011-03-24 Robert Bosch Gmbh Verfahren und Vorrichtung zur Herstellung eines piezokeramischen Bauelemets
DE102009029489A1 (de) 2009-09-16 2011-03-24 Robert Bosch Gmbh Piezoaktormodul und ein Verfahren zu dessen Herstellung
DE102009055267A1 (de) * 2009-12-23 2011-06-30 Robert Bosch GmbH, 70469 Druckausgeglichener Kraftstoffinjektor mit Bypass und minimiertem Ventilraumvolumen
DE102010001246A1 (de) 2010-01-27 2011-07-28 Robert Bosch GmbH, 70469 Verfahren und Stoffe zur Herstellung einer Piezokeramik für einen Piezoaktor oder ein Piezoaktormodul

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EP1612398A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Società Consortile per Azioni Injecteur de carburant a soupape de commande a equilibrage des forces
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DE19939452A1 (de) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Vorrichtung zur Einspritzung von Kraftstoff
DE10309885A1 (de) * 2002-03-07 2003-10-16 Nippon Soken Kraftstoffeinspritzvorrichtung
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
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WO2010076645A1 (fr) 2008-12-29 2010-07-08 C.R.F. Società Consortile Per Azioni Système d'injection de carburant à haute stabilité et répétabilité de fonctionnement pour un moteur à combustion interne
EP2383454A1 (fr) 2010-04-27 2011-11-02 C.R.F. Società Consortile per Azioni Formage du débit d'injection de carburant dans un moteur à combustion interne
WO2011135442A1 (fr) 2010-04-27 2011-11-03 C.R.F. Società Consortile Per Azioni Conformation du débit d'injection de carburant dans un moteur à combustion interne
EP2405121A1 (fr) 2010-07-07 2012-01-11 C.R.F. Società Consortile per Azioni Système d'injection de carburant pour moteur à combustion interne
WO2012004368A1 (fr) 2010-07-07 2012-01-12 C.R.F. Società Consortile Per Azioni Système d'injection de carburant pour un moteur à combustion interne
US9068544B2 (en) 2010-07-07 2015-06-30 C.R.F. Società Consortile Per Azioni Fuel-injection system for an internal-combustion engine

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