EP1856403A1 - Injecteur de carburant comprenant un element de soupape d'injection a commande directe qui presente un double siege - Google Patents

Injecteur de carburant comprenant un element de soupape d'injection a commande directe qui presente un double siege

Info

Publication number
EP1856403A1
EP1856403A1 EP06700750A EP06700750A EP1856403A1 EP 1856403 A1 EP1856403 A1 EP 1856403A1 EP 06700750 A EP06700750 A EP 06700750A EP 06700750 A EP06700750 A EP 06700750A EP 1856403 A1 EP1856403 A1 EP 1856403A1
Authority
EP
European Patent Office
Prior art keywords
valve member
injection valve
fuel injector
sealing sleeve
coupling
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.)
Granted
Application number
EP06700750A
Other languages
German (de)
English (en)
Other versions
EP1856403B1 (fr
Inventor
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1856403A1 publication Critical patent/EP1856403A1/fr
Application granted granted Critical
Publication of EP1856403B1 publication Critical patent/EP1856403B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to a fuel injector for injecting fuel supplied to the fuel injector via a high-pressure source into a combustion chamber of a combustion engine.
  • the invention relates to a fuel injector with direct-control injection valve member with double seat.
  • both pressure-controlled and stroke-controlled injection systems can be used.
  • fuel injection systems come next pump-injector units, pump line-nozzle units and storage injection systems are used.
  • Storage injection systems (common rail) advantageously make it possible to adapt the injection pressure to the load and speed of the internal combustion engine.
  • hydraulic translators can be used.
  • Aktorhub and Düsennadelhub required and a use of long mechanical connecting parts. Therefore, these injectors usually have a poor, indirect transfer behavior of the switching force of the actuator on the nozzle needle.
  • an injection valve member is required, which must go through to fully open the injection openings only a small stroke.
  • the essence of the invention is to combine such a double seat of the injection valve member with fuel supply of the injection openings via both sealing seats with a direct control of the injection valve member by a piezo actuator, thereby achieving an optimized injector design.
  • a fuel injector for injecting fuel supplied via a high-pressure source under pressure to the fuel injector into a combustion chamber of an internal combustion engine is proposed.
  • This fuel injector has an injector housing, a high-pressure chamber, a pressure chamber, a nozzle chamber, an electrically actuatable linear actuator mounted in the high-pressure chamber and an injection valve member coupled to the linear actuator via a coupling.
  • the pressure chamber and the high pressure chamber and the nozzle chamber and the pressure chamber fluidly communicate with each other.
  • the injection valve member is linearly guided in at least one guide section, so that the injection valve member can execute an opening and a closing movement parallel or antiparallel to a closing direction.
  • the injection valve member has at least two sealing seats, such that in a closed position the sealing seats abut against at least one wall of the nozzle chamber.
  • the nozzle chamber is subdivided into at least three subspaces, wherein a first subspace in the closing direction and a third subspace in the closing direction are each fluidically connected to the pressure chamber.
  • a closing direction between the first subspace and the third subsection spatially arranged second subspace is fluidly decoupled from the first subspace and the third subspace and is fluidly connected to at least one Einspritzöffhung for injecting fuel into the combustion chamber in combination.
  • the actuator may, for example, be a piezoelectric actuator, although other actuator designs, for example magnetic actuators, may also be used.
  • the coupling may be, for example, a hydraulic coupling.
  • This hydraulic coupling may additionally include, for example, a hydraulic translator, in particular for translating a stroke of the actuator into a stroke of the injection valve member. In the context of the present invention, this is also to be understood as a "direct needle control.” It has proved to be particularly advantageous if this translator has a transmission ratio in the range from 0.5 to 2, preferably in the range from 1.0 to 1, 5 and particularly preferably of 1.0.
  • a gear ratio is to be understood as the ratio of an injection valve member stroke to the stroke of the actuator.
  • the hydraulic coupling can take place, for example, via a coupling space, which is filled in particular with a hydraulic fluid (preferably fuel) and which can be delimited, for example, by a first coupler piston connected to the actuator and a second coupler piston connected to the injection valve member and at least one sealing sleeve.
  • the sealing sleeve can be connected via at least one spring to the first and / or the second coupling piston.
  • the at least one coupling space has a first coupling space and a second coupling space, which are fluidically connected to one another via at least one connecting channel. It is particularly advantageous if this at least one connecting channel has at least one throttle element, on which the at least one connecting channel is narrowed in its cross section.
  • the coupling chambers can be separated, for example, via a partition connected to the injector housing, wherein both a rigid connection and a flexible connection can be used.
  • the at least one sealing sleeve also have two individual sealing sleeves, wherein the first sealing sleeve is connected via a first spring to the first coupler piston and the second sealing sleeve via a second spring to the second coupler piston and wherein the first sealing sleeve and the second sealing sleeve in each case with the Partition are connected.
  • the first sealing sleeve could be connected to the first coupler piston and the second sealing sleeve to the second coupler piston, wherein both sealing sleeves are each supported by a spring on the partition wall.
  • each sealing sleeve is supported in each case with a spring on the respective coupler piston and with a second spring on the partition.
  • the fluidic connection between the pressure chamber and the nozzle chamber or the pressure chamber and the first subspace and / or the second subspace can be effected, for example, via at least one flow channel embedded in the injection valve member.
  • the required actuator length for direct needle control is greatly reduced.
  • no or only a small path ratio is necessary between the actuator and the injection valve member in order to achieve the required injection valve member stroke.
  • a design of the hydraulic coupler with a Hubüber GmbHsdorf by one is possible. This results in a very stiff transmission behavior of Aktorstell member on the injection valve member, whereby an optimal positioning accuracy of the injection valve member is achieved.
  • Such injector design allows accurate metering of small amounts of fuel. Due to the high transfer rigidity and the fast needle movement, a robust design with low influences of manufacturing tolerances is achieved.
  • FIG. 1 shows a first embodiment of a fuel injector with an injection valve member with double seat and a direct control of the injection valve member via an actuator and a hydraulic booster;
  • Figure 2 shows a second embodiment of a fuel injector with an injection valve member with double seat and direct control of the injection valve member with a simple coupling space.
  • Figure 3 shows a third, to Figure 2 alternative embodiment with a simple coupling space and a run on a single coupler piston sealing sleeve.
  • FIG. 1 shows a first, preferred exemplary embodiment of a fuel injector 110 for injecting fuel into a combustion chamber of an internal combustion engine.
  • the fuel injector 110 is connected via a high pressure line 112 to a pressure accumulator (common rail) 114.
  • the fuel injector 110 has an injector housing 116.
  • the injector housing 116 has a high-pressure chamber 118, which communicates with the pressure accumulator 114 via the high-pressure line 112 and is supplied with pressurized fuel.
  • the injector housing 116 has a pressure chamber 120 and a nozzle chamber 122.
  • the pressure chamber 120 communicates with the high-pressure chamber 118 via fuel channels 124, which are embedded in a partition wall 126 which separates the pressure chamber 120 from the high-pressure chamber 118.
  • the fuel channels 124 are designed in this embodiment as cylindrical bores, which are introduced into the partition 126. Other embodiments of the fuel channels are conceivable.
  • an injection valve member 128 is introduced, which is guided along a guide portion 130 in the nozzle chamber 122.
  • the injection valve member 128 may move parallel or anti-parallel to a closing direction 132 of the fuel injector 110.
  • flow channels 134 are provided in the form of embedded in the injection valve member 128 flats. Other configurations of the flow channels 134 are conceivable, for example, bores, etc. These flow channels 134 extend vertically and are evenly distributed along the circumference of the injection valve member in this embodiment.
  • the flow channels 134 cause, despite the guidance of the injection valve member 128 in the guide portion 130, the nozzle chamber 122 is in fluid communication with the pressure chamber 120 of the fuel injector 110. In this way, fuel can flow from the high-pressure chamber 118 through the pressure chamber 120 in the closing direction 132 to one or a plurality of injection openings 136, which are embedded in the lower region of the fuel injector 110 in the wall of a tapered region 138 of the nozzle chamber 122.
  • the configuration of these injection openings 136 is known from the prior art and may, depending on the internal combustion engine, for example, vary in their shape, number and arrangement.
  • a piezoelectric actuator 140 is introduced in this embodiment, which can expand or contract in the closing direction 132 of the injection valve member 128.
  • the piezo actuator 140 is sealed on its surface by a suitable seal against the surrounding medium (fuel), so that the functionality of the piezoactuator 140 is not impaired by the fuel.
  • the piezoelectric actuator 140 is on its upper side via a sealing element 142 against a top wall 144th the injector 116 supported.
  • an opening 146 is introduced, via which electrical contacts 148 for driving the piezoelectric actuator 140 are led out of the injector housing 116.
  • the opening 146 can be tightly closed after the electrical contacts 148 have been removed by a suitable sealing compound, for example a plastic.
  • the piezoactuator 140 is connected to a first coupler piston 150.
  • This first coupler piston 150 is surrounded at its lower edge by a first sealing sleeve 152, which is supported by a first spiral spring 154 against a projection 156 of the first coupler piston 150 and thus pressed against the partition wall 126.
  • the first sealing sleeve 152 has an annular shape and is tight against the first coupler piston 150.
  • a first coupling space 158 is formed between the first coupler piston 150 and the partition wall 126, which is bounded by the partition wall 126, the first coupler piston 150 and the sealing sleeve 152.
  • the first sealing sleeve 152 is formed tapering at its lower end, so that a sealing edge is formed.
  • the first coupling space 158 can be filled, for example by a corresponding gap flow in the guide or by other throttle elements with fuel.
  • the upper end of the injection valve member 128 has a second coupler piston 160.
  • the second coupler piston 160 is surrounded by a second, annular sealing sleeve 162, the edge of which tapers pointedly upwards in this embodiment.
  • Other embodiments of the sealing sleeves 152, 162 are conceivable.
  • the second sealing sleeve 162 is supported by a second spiral spring 164 on a projection 166 of the second coupling piston 160 and is thereby pressed against the partition wall 126.
  • the sealing sleeve 162, the upper surface of the second coupler piston 160 and the partition wall 126 define a second coupling space 168. Again, this second coupling space 168 may be filled with fuel, for example via a gap flow or other throttling elements.
  • a connecting channel 170 is further admitted, via which fuel from the first coupling chamber 158 can flow into the second coupling chamber 168 and vice versa.
  • the connecting channel 170 has substantially the shape of a cylindrical bore. Other embodiments are conceivable, for example, a plurality of holes or non-linear course of the connecting channel 170.
  • a throttle element 172 in the form of a spatially limited compared to the length of the connecting channel 170 narrowing. Other configurations of the throttle element 172 are conceivable.
  • the two coupling spaces 158 and 168 realize a hydraulic force transmission between the first coupler piston 150 (and thus the piezo actuator 140) and the injection valve member 128. This hydraulic force transmission in particular compensates for thermal expansions and manufacturing tolerances of the components.
  • a path-force transmission between the piezo actuator 140 and the injection valve member 128 can be realized by this hydraulic coupler.
  • the device shown in Figure 1 with the two coupling spaces 158 and 168 not only acts as a hydraulic power transmission, but can also act as a hydraulic booster 174 for translating a stroke of the piezo actuator 140 in a stroke of the injection valve member 128.
  • this hydraulic booster 174 is composed of the first coupler piston 150, the first coupling space 158, the connecting channel 170, the second coupling space 168 and the second coupler piston 160.
  • the transmission ratio of the hydraulic booster 174 results from the ratio of the hydraulic surfaces of the coupler pistons 150 and 160, ie the end face of the first coupler piston 150 facing the first coupling space 158 and the end face of the second coupler piston 160 facing the second coupling space 168 Manner can, for example, by a reduced compared to the hydraulic surface of the first coupler piston 150 hydraulic surface of the second coupler piston 160 a stroke ratio with a gear ratio greater than one are brought about, whereby a larger stroke of the injection valve member 128 can be effected even with a small stroke of the piezo actuator 140. As a result, the length of the piezo actuator 140 can be shortened. Even with an area ratio of one, so a 1: 1 -Hubüber acid, the illustrated fuel injector 110 can be operated, the hydraulic translator 174 in this case, for example, as described above, can be advantageously used to compensate for thermal expansion and manufacturing tolerances.
  • the injection valve member 128 has a guide section 130 which adjoins the coupler piston 160 in the closing direction 132, followed by a conical section 176 and a cylindrical front section 178.
  • the cylindrical front portion 178 of the injection valve member 128 has a smaller diameter than the nozzle chamber 122, so that between the front portion 178 and the wall of the nozzle chamber 122, an annular gap 180 is formed.
  • Fuel which flows from the pressure chamber 120 via the flow channels 134 in the guide section 130 of the injection valve member 128, can flow through this annular gap 180 in the closing direction 132 of the injection valve member 128 in the direction of the injection openings 136.
  • the injection valve member 128 in its front portion 178 at its lower end two sealing seats 182, 184 on. These sealing seats 182, 184 are formed as circumferential, circular edges of a constriction 186 in the region of the tip of the injection valve member 128.
  • the sealing seats 182, 184 are firmly against the inner wall of the tapered portion 138 of the nozzle chamber 122.
  • the sealing seats 182, 184 are designed so that they form an annular cavity (second subspace 190, see below) in the region of the annular constriction 186 when the tip of the injection valve member 128 abuts against the inner wall of the conically tapering region 138 of the nozzle chamber 122.
  • the injection openings 136 are arranged in the region of this annular cavity in the wall of the tapered region 138.
  • the sealing seats 182, 184 thus subdivide the nozzle chamber 122 into three subspaces 188, 190, 192:
  • a first subspace 188 which is arranged in the closing direction 132 above the sealing seat 182, has a second subspace 190, which is arranged between the two sealing seats 182 and 184 and a third sub-space 192 disposed below the sealing seat 184 in a region which is not completely filled by the front portion 178 of the injection valve member 128.
  • flow channels 194 are inserted into the injection valve member 128, for example in the form of central bores In the injection valve member 128. Via these flow channels 194, fuel can flow from the first subspace 188 into the third subspace 192, so that both subspaces 188, 192 are fluidically connected to one another and the same fuel pressure prevails in these subspaces 188, 192.
  • the injection openings 136 are sealed by the two sealing seats 182, 184 of the injection valve member 128.
  • two sealing seats 182, 184 are thus opened substantially simultaneously.
  • These sealing seats 182, 184 also advantageously have a large diameter, that is to say a diameter which is as close as possible to the diameter of the first partial space 188.
  • Such a small stroke can already be provided by very short piezo actuators 140, as they are currently manageable in mass production.
  • Typical piezo actuators 140 have actuator lengths of about 35 mm and a stroke of about 45 microns.
  • the structure described causes the hydraulic booster 174 can already be designed with a very low hydraulic ratio, in particular with a transmission ratio between 0.5 and 2, advantageously in the range of one.
  • a stiff transmission behavior between the piezoactuator 140 and the injection valve member 128 is achieved, as a result of which the switching characteristics of the fuel injector 110 are greatly improved.
  • the exact metering of very small pilot injection quantities is made possible.
  • the described embodiment is very robust compared to manufacturing tolerances.
  • the ⁇ ffhungs characterizing the injection valve member 128 can be further optimized.
  • an optimized minimum quantity capability and a favorable injection rate profile can be achieved.
  • FIG. 2 a corresponding embodiment with a modified structure of the hydraulic translator 174 is shown schematically.
  • the fuel injector 110 according to the embodiment of Figure 2, an injector housing 116 having a high-pressure chamber 118, a pressure chamber 120 and a nozzle chamber 122.
  • the design of the injection valve member 128 is analogous to the configuration of the injection valve member 128 according to the exemplary embodiment in FIG. 1.
  • the function of the fuel supply to the injection openings 136, in particular the design of the injection valve member 128 with two sealing seats 182 and 184 and the subspaces 188, 190, 192, is identical or identical in function to FIG. 1.
  • the exemplary embodiment according to FIG. 2 differs from the exemplary embodiment according to FIG. 1 only in the design of the hydraulic booster 174.
  • the piezoactuator 140 is connected at its lower end in the closing direction 132 to a first coupler piston 150, which in turn has a projection 156.
  • the injection valve member 128 in turn has a second coupler piston 160 at its upper end.
  • the first coupler piston 150 and the second coupler piston 160 are both enclosed by a single sealing sleeve 210, which is supported at its upper end on the projection 156 of the first coupler piston 150.
  • the sealing sleeve 210 is supported by a coil spring 212 on the projection 166 of the second coupling piston 160.
  • a coupling space 214 is in this embodiment not in communication with the coupling chamber 214, but has a cylindrical bore 216 through which the sealing sleeve 210 is guided.
  • an annular gap 218 is formed between the sealing sleeve 210 and the partition wall 126, via which fuel can flow from the high-pressure chamber 118 into the pressure chamber 120.
  • the exemplary embodiment illustrated in FIG. 2 has the particular advantage that the number of components is considerably reduced compared to the exemplary embodiment in FIG.
  • the sealing sleeve 210 can also be designed as an integral part of the first coupler piston 150.
  • the sealing sleeve 210 can also be designed as an integral part of the second coupler piston 160, in which case the sealing sleeve 210 would be supported at its upper end by means of the spring 212 against the projection 156 of the first coupler piston 150.
  • two coil springs 210 may alternatively be used, wherein the sealing sleeve 210 would be supported both with respect to the projection 166 of the second coupler piston 160 and with respect to the projection 156 of the first coupler piston 150.
  • a two-part design with separate sealing sleeve 210, as shown in FIG. 2 is advantageous. A minimal volume in the coupling space improves power transmission and minimizes losses.
  • FIG. 3 shows a third exemplary embodiment of a fuel injector 110 that is alternative to the embodiment according to FIG.
  • the injection valve member 128 and the functionality of the sealing seats 182, 184 are analogous to the embodiment according to. Figure 2 configured.
  • This embodiment in turn, has a coupling space 310 for force transmission between the piezoactuator 140 and the injection valve member 128.
  • the coupling space 310 is in turn surrounded by a sealing sleeve 312.
  • the embodiment according to FIG. 3 differs from the embodiment according to FIG. 2 substantially in the guidance of the sealing sleeve 312:
  • the coupling according to FIG. 3 has only one coupler piston 150, on which the sealing sleeve 312 is guided.
  • a guide of the sealing sleeve 312 by a second coupler piston (analogous to the coupler piston 160 according to FIG.
  • the sealing sleeve 312 is provided with a sealing edge 314 at its end pointing downwards (ie toward the injection valve member 128) and is supported directly on the projection 166 of the injection valve member 128.
  • a spring element 316 which is supported at its upper end on the projection 156 of the coupler piston 150 connected to the piezoactuator 140, acts on the sealing sleeve 312 with a force in the closing direction 132.
  • the second coupling piston 160 connected to the injection valve member 128 has been dispensed with, and the sealing sleeve 312 is guided only on the first coupler piston 150 connected to the piezoactuator 140.
  • These embodiments, in which the sealing sleeve 312 takes place only on a coupler piston (150 or 160), are particularly advantageous since in this case distortions between piezoactuator 140 and injection valve member 128, which can occur, for example, due to manufacturing inaccuracies in a multipart injector body, are avoided become.
  • the coupler space 214, 310 merely compensates for manufacturing tolerances. Due to the simple structure with only one coupler space 214, 310, there is generally always a direct force transmission between the piezoactuator 140 and the injection valve member 128 with a transmission ratio of 1. Bezues Schweizerliste
  • Nozzle space 210 Sealing sleeve

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

Abstract

La présente invention concerne un injecteur de carburant (110) qui est conçu pour alimenter en carburant des chambres de combustion de moteurs à combustion interne à allumage automatique. Une source de haute pression (114) permet d'alimenter cet injecteur de carburant en carburant sous pression. Ledit injecteur de carburant (110) présente une commande directe d'un élément de soupape d'injection (128) au moyen d'un actionneur piézo-électrique (140) par l'intermédiaire d'un intensificateur de pression hydraulique (174). L'élément de soupape d'injection (128) de l'injecteur de carburant (110) présente également un double siège. A cette fin, l'élément de soupape d'injection (128) présente deux sièges d'étanchéité (182, 184) qui divisent une chambre de gicleur (122) de l'injecteur de carburant (110) en trois chambres partielles (188, 190, 192). Lorsque l'élément de soupape d'injection (128) est fermé, une première chambre partielle (188) et une troisième chambre partielle (192) sont en liaison fluidique l'une avec l'autre et sont alimentées en carburant. D'un autre côté, la deuxième chambre partielle (190), qui est en liaison avec des orifices d'injection (136), est découplée de manière fluidique des chambres partielles (188, 192) par les sièges d'étanchéité (182, 184). L'ensemble comprenant la combinaison d'une commande directe de pointeau et d'un double siège de l'élément de soupape d'injection (128) présente l'avantage qu'un désétranglement de l'injecteur de carburant (110) a lieu lorsque la levée de l'élément de soupape d'injection est très faible. Il est alors également possible d'utiliser en particulier des actionneurs piézo-électriques courts (140).
EP06700750.0A 2005-03-01 2006-01-17 Injecteur de carburant comprenant un element de soupape d'injection a commande directe qui presente un double siege Not-in-force EP1856403B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005009148A DE102005009148A1 (de) 2005-03-01 2005-03-01 Kraftstoffinjektor mit direktgesteuertem Einspritzventilglied mit Doppelsitz
PCT/EP2006/050237 WO2006092344A1 (fr) 2005-03-01 2006-01-17 Injecteur de carburant comprenant un element de soupape d'injection a commande directe qui presente un double siege

Publications (2)

Publication Number Publication Date
EP1856403A1 true EP1856403A1 (fr) 2007-11-21
EP1856403B1 EP1856403B1 (fr) 2014-05-28

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06700750.0A Not-in-force EP1856403B1 (fr) 2005-03-01 2006-01-17 Injecteur de carburant comprenant un element de soupape d'injection a commande directe qui presente un double siege

Country Status (6)

Country Link
US (1) US20080099583A1 (fr)
EP (1) EP1856403B1 (fr)
JP (1) JP2008531917A (fr)
CN (1) CN101133242A (fr)
DE (1) DE102005009148A1 (fr)
WO (1) WO2006092344A1 (fr)

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FR2988140B1 (fr) * 2012-03-15 2016-02-05 Bosch Gmbh Robert Soupape de regulation de pression d'accumulateur haute pression de carburant de moteur a combustion interne
KR101340888B1 (ko) 2012-10-30 2013-12-13 숭실대학교산학협력단 직접 구동방식 피에조 인젝터
DE102013219225A1 (de) * 2013-09-25 2015-03-26 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoff-Direkteinspritzung
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CN101133242A (zh) 2008-02-27
US20080099583A1 (en) 2008-05-01
EP1856403B1 (fr) 2014-05-28
JP2008531917A (ja) 2008-08-14
DE102005009148A1 (de) 2006-09-07
WO2006092344A1 (fr) 2006-09-08

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