EP2884088B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2884088B1
EP2884088B1 EP14189616.7A EP14189616A EP2884088B1 EP 2884088 B1 EP2884088 B1 EP 2884088B1 EP 14189616 A EP14189616 A EP 14189616A EP 2884088 B1 EP2884088 B1 EP 2884088B1
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EP
European Patent Office
Prior art keywords
nozzle needle
fuel injector
pressure
low
pressure chamber
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.)
Active
Application number
EP14189616.7A
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German (de)
English (en)
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EP2884088A1 (fr
Inventor
Henning Kreschel
Sebastian Laechele
Holger Rapp
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
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Filing date
Publication date
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Publication of EP2884088A1 publication Critical patent/EP2884088A1/fr
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Publication of EP2884088B1 publication Critical patent/EP2884088B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic 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
    • F02M61/04—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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • 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
    • 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

Definitions

  • the invention relates to a fuel injector for a fuel injection system, in particular a common rail injection system, having the features of the preamble of claim 1.
  • a fuel injector of the type mentioned above is an example of the published patent application DE 10 2008 040 680 A1 out.
  • the known fuel injector comprises for injecting fuel into a combustion chamber of an internal combustion engine an adjustable between an open position and a closed position, multi-part injection valve element, wherein a first part and a second part are coupled via a hydraulic coupler.
  • the hydraulic coupler is limited in the axial direction by a first guide for the first part and by a second guide for the second part.
  • the guides are acted upon radially from the outside by high pressure, while in the hydraulic coupler, a lower pressure is realized.
  • the radially outside applied higher pressure counteracts widening of the guides, so that the fuel injector can be operated comparatively low leakage.
  • the lower pressure in the hydraulic coupler also has the consequence that the parts of the injection valve element coupled thereto are permanently connected to each other during operation of the fuel injector and with considerable forces, so that from a functional point of view they can be regarded as one part. Further, it is proposed in this document that within the hydraulic coupler, a pressure stage is realized which causes a force acting in the closing direction of the injection valve element hydraulic force to accelerate the switching time of the injection valve element. In order to realize the pressure stage, the hydraulically coupled parts of the injection valve element have different diameters, the part lying closer to a nozzle hole arrangement having a smaller diameter than the part remote from the nozzle hole.
  • the fuel injector has a solenoid valve designed as a servo valve, which causes a pressure drop in a control chamber in the open position, which is limited in the axial direction of an end face of the injection valve element.
  • the pressure drop in the control chamber thus causes a relief of the injection valve element until it opens.
  • fuel injectors are for example off DE102008002415A known, which are connected directly via a magnetic or piezoelectric actuator.
  • the required opening force for opening the injection valve element or the nozzle needle must be taken into account when dimensioning the actuator.
  • the force applied by the actuator is transmitted via a switching chain on the end face of the nozzle needle.
  • the switching chain between the actuator and the nozzle needle may have a device for force and / or stroke ratio. Accordingly reduces or increases the required actuator force and increases or decreases in return the required Aktorhub.
  • the present invention seeks to provide a fuel injector for a fuel injection system, in particular a common rail injection system, which allows the use of comparatively small-volume actuators by reducing the required opening force.
  • a small-volume piezoelectric actuator should be possible, via which the fuel injector is directly switchable.
  • the proposed fuel injector comprises a nozzle body and an injector body, each enclosing a high-pressure chamber in which a single- or multi-part nozzle needle for releasing and closing at least one injection opening is received in a liftable manner.
  • the nozzle needle is guided by a low-pressure chamber which is sealed off via at least one guide gap between the nozzle needle and a body limiting the low-pressure space and / or a guide element supported thereon relative to the high-pressure chambers.
  • the nozzle needle has different sized guide diameter d o , d u .
  • the guide diameter d o which is farther away with respect to the injection opening, is smaller than the guide diameter d u , so that the nozzle needle is partially relieved of force in the opening direction.
  • the partial release of force of the nozzle needle causes a reduction in the required opening force, so that - with directly connected injectors - by a small-volume actuator, such as a piezoelectric actuator can be applied.
  • the partial force relief of the nozzle needle causes the switching times can be reduced because the required pressure drop in the control room can be realized faster.
  • the effect of the partial force relief of the nozzle needle can also be represented by the following formulas.
  • the body limiting the low-pressure chamber is a plate-shaped body component which is arranged between the nozzle body and the injector body and which is preferably braced axially with the nozzle body and the injector body via a nozzle retaining nut.
  • the body forms a fixed body component or housing part of the fuel injector.
  • the body limiting the low-pressure space has at least one flow channel for the hydraulic connection of the high pressure spaces formed in the nozzle body and in the injector body. The at least one flow channel ensures the supply of fuel to the at least one injection opening. It is thus part of the flow path of the fuel to be injected.
  • the body limiting the low-pressure space is received in a lift-movable manner in at least one of the high pressure spaces formed in the nozzle body and / or in the injector body.
  • the body limiting the low-pressure space does not necessarily have to be designed as a fixed body component or housing part.
  • the body can also be a coupler body of a hydraulic coupler, which preferably serves to reinforce the force of an actuator and forms a functional unit with it. This is particularly advantageous if the fuel injector is designed as a directly switchable injector.
  • the low-pressure space is connected via at least one connecting channel to a low-pressure region of the fuel injector.
  • the connecting channel is at least partially formed as a radially extending bore.
  • the radially extending Hole in the region of an outer peripheral surface of the low pressure space limiting body, which is preferably formed in this case as a plate-shaped body member, in the low pressure region.
  • the low-pressure region may comprise at least one axially extending connecting channel arranged radially outside with respect to the plate-shaped body component.
  • the low-pressure region is furthermore preferably connectable to a return line of the fuel injection system.
  • the pressure prevailing in the low-pressure chamber preferably corresponds to the return pressure of the fuel injection system.
  • the pressure prevailing in the low-pressure chamber can also be above the return pressure, so that a pressure is possible which lies between the return pressure and the high pressure of a high-pressure accumulator to which the fuel injector is preferably connected.
  • the intermediate pressure level in the low-pressure space can be generated in a manner known per se. For example, equal-pressure valves or pressure divider devices can be used.
  • the pressure in the low-pressure space is preferably at most 20 bar, preferably at most 10 bar, in order to achieve the desired effect of a partially force-loaded nozzle needle.
  • the nozzle needle is preferably in several parts, preferably in two parts, formed.
  • the multi-part design simplifies the realization of different sizes of guide diameter, since a diameter jump can be realized in each case in the region of the connection of two parts, which differ in terms of their diameter.
  • the nozzle needle comprises a first part and a second part having cooperating contact surfaces arranged in the low pressure space. The low pressure in the low pressure chamber and the high pressure applied externally cause a mechanical coupling of the two parts of the nozzle needle.
  • the first part and the second part of the nozzle needle have, in the region of their contact surfaces, a geometry forming a joint.
  • the joint in the contact area can compensate for any axial misalignment between the parts.
  • At least one guide of the nozzle needle is realized by a separate guide element, which is designed as a sleeve and is preferably supported by a biting edge on the body limiting the low-pressure space.
  • the trained as a sleeve separate guide element allows the compensation of any axial offset between the parts of the nozzle needle, since the sleeve relative to the body is radially displaceable.
  • the biting edge of the sleeve increases the sealing force in order to seal the low-pressure space with respect to one of the high-pressure chambers.
  • it is proposed that the sleeve is acted upon by the spring force of a spring in the direction of the body.
  • the sealing force is increased in the contact area of the sleeve with the body. Since the sleeve is surrounded on the outside by high pressure, the high pressure environment causes an additional hydraulic contact pressure. Further preferably, the lifting movement of the nozzle needle via an actuator is directly controlled.
  • the actuator may be, for example, a piezoelectric actuator or a magnetic actuator.
  • a directly controllable or switchable fuel injector has over an indirectly controllable or switchable fuel injector the advantage that no Abêtmenge accumulates, which must be returned and again promoted to high pressure. This can increase the efficiency of the system.
  • a hydraulic coupler is provided for the transmission of the force and / or the stroke of an actuator.
  • the hydraulic coupler has a coupler body with a hollow cylindrical projection for receiving an end portion of the nozzle needle and for forming a control chamber, wherein the control chamber is formed completely in the coupler body.
  • the hydraulic coupler has a coupler body on which a sealing sleeve for receiving an end portion of the nozzle needle and for forming a control chamber is supported.
  • a hollow cylindrical projection on the coupler body is thus unnecessary, which simplifies the production of the hydraulic coupler.
  • the sealing sleeve can also be displaced in the radial direction on Supported coupler body, so that it allows the compensation of any misalignment between the hydraulic coupler and the nozzle needle.
  • sealing sleeve Since the sealing sleeve is surrounded on all sides by high pressure, in the case of a short-term overpressure in the control chamber there is the risk that the sealing sleeve will detach from the coupler body and the control chamber will open. This can be counteracted by the fact that the one-piece solution described above (without separate sealing sleeve) or a sealing sleeve is selected, which has a radially inner biting edge, via which it is supported on the coupler body. In this way, acting on the sealing sleeve opening forces are avoided at a pressure in the control room.
  • the Indian FIG. 1 The nozzle body 1 and the injector body 2 are clamped together axially by means of a nozzle lock nut 26, wherein between the nozzle body 1 and the injector 2 in addition a plate-shaped body member as a Low-pressure chamber 7 limiting body 6 is inserted.
  • the low-pressure chamber 7 is connected via a connecting channel 13 designed as a radial bore to a low-pressure region 14, which is arranged radially outside with respect to the body 6.
  • an obliquely extending flow channel 15 is formed in the body 6, which connects the high-pressure chamber 3 of the nozzle body 1 with the high-pressure chamber 4 of the injector body 2.
  • the fuel injector further comprises a liftable nozzle needle 5 for releasing and closing at least one injection port (not shown).
  • the nozzle needle 5 extends from the high-pressure chamber 3 of the nozzle body 1 into the high-pressure chamber 4 of the injector body 2, being guided in the region of the low-pressure chamber 7 by the plate-shaped body component or body 6.
  • An upper end portion of the nozzle needle 5 is received in a sealing sleeve 23 which is supported on a coupler body 20 of a not shown hydraulic coupler 19 via a radially inner biting edge 24 and acted upon in the direction of the coupler body 20 by the spring force of a spring 17.
  • the coupler body 20, the sealing sleeve 23 and an end face 25 of the end portion of the nozzle needle 5 accommodated in the sealing sleeve 23 thus jointly delimit a control chamber 22 in which a control chamber pressure prevails which causes a pressure force acting on the nozzle needle 5 in the closing direction. If the nozzle needle 5 is raised to release the injection port, the pressure in the control chamber 22nd be lowered. This is done in the present case by actuation of an actuator (not shown), which may be formed for example as a piezoelectric actuator.
  • a reversal of the direction of movement and on the other an amplification of the actuator force or the Aktorhubes be effected via the switched between the piezoelectric actuator and the nozzle needle hydraulic coupler 19, so that the piezoelectric actuator for direct control of the lifting movement of the nozzle needle 5 can be used.
  • the nozzle needle 5 is partially relieved of force.
  • the partial release of force is caused by a diameter jump of the nozzle needle 5 in the region of the low-pressure space 7.
  • the diameter jump leads to the formation of a low pressure surrounded pressure stage 12, wherein the diameter d o of the nozzle needle 5 above the pressure stage 12 is smaller than the diameter d u below the pressure stage 12 is selected.
  • the diameters d o and d u together with the plate-shaped body component or the body 6 form guide gaps 8, 9, via which the low-pressure space 7 is sealed off from the high-pressure spaces 3, 4 by way of the gap seal.
  • the opening can be effected with a comparatively small actuator, in particular when the fuel injector is directly switchable via the actuator.
  • FIG. 2 is a modification of the fuel injector of FIG. 1 shown.
  • the guidance of the nozzle needle 5 is not effected via the plate-shaped body component or the body 6, but via sleeve-shaped guide elements 10, 11 supported thereon.
  • the support is in each case via a biting edge in order to optimize the sealing of the low-pressure chamber 7 with respect to the high-pressure chambers 3, 4.
  • the sleeve-shaped guide elements 10, 11 are acted upon in the direction of the body 6 in each case by the spring force of a spring 17, 18.
  • the sleeve-shaped guide element 10 is acted upon by the spring force of the spring 17, which at the same time holds the sealing sleeve 23 in contact with the coupler body 20.
  • the spring 17 is supported, on the one hand, on the sleeve-shaped guide element 10 and, on the other hand, on the sealing sleeve 23.
  • the sleeve-shaped guide member 11 is pressed by the spring force of the spring 18 to the body 6, which also serves as a closing spring and is supported on the nozzle needle 5.
  • the sleeve-shaped guide elements 10, 11 are radially displaceable relative to the presently formed as a plate-shaped body member body 6 and allow in this way the compensation of any Axis offset.
  • the guide gaps 8, 9 sealing the low-pressure space 7 are formed between the sleeve-shaped guide elements 10, 11 and the guide diameters d 0 , d u of the nozzle needle 5.
  • the low pressure chamber 7 is formed as a simple axial bore within the body 6, which is thus easy to manufacture.
  • FIG. 3 Another preferred embodiment is in FIG. 3 shown. This is different from the one of FIGS. 1 and 2 in that the nozzle needle 5 is designed in several parts, namely in two parts.
  • the two parts 5.1, 5.2 of the nozzle needle 5 each have a different diameter, wherein the diameter d o of the part 5.1 is smaller than the diameter d u of the part 5.2 is selected.
  • the parts 5.1, 5.2 form with the sleeve-shaped guide elements 10, 11 supported on the body 6 guiding gaps 8, 9, via which the low-pressure space 7 formed in the plate-shaped body component 6 is sealed against the high-pressure spaces 3, 4.
  • the contact area of the two parts 5. 1, 5.2 is located in the low-pressure chamber 7 and forms the pressure required to relieve the pressure of the nozzle needle 12 from.
  • a possible axial offset between the two parts 5.1, 5.2 can be effected by a radial displacement of the sleeve-shaped guide elements 10, 11 relative to the body 6.
  • FIG. 4 A modification of the embodiment of the FIG. 3 is in the FIG. 4 shown.
  • the two parts 5.1, 5.2 each have a geometry in the region of their contact surfaces, which cooperate forming a joint 16.
  • the contact surface of the part 5.1 is convex-shaped, while the contact surface of the part 5.2 has a concave-shaped depression, so that the contact region is reduced to a circular line.
  • the geometries also cause a self-centering of the two parts 5.1, 5.2 to each other.
  • FIG. 5 Another modification of the embodiment of the FIG. 3 is in the FIG. 5 shown.
  • FIGS. 6 to 9 Other modifications are in the FIGS. 6 to 9 shown. They are different from those of FIGS. 1 to 5 in particular, that the body 6 is not necessarily designed as a fixed plate-shaped body member which is axially braced between the nozzle body 1 and the injector body 2 by means of a nozzle lock nut 26. Accordingly, the body 6 may have any desired shape and / or be liftably received in the high-pressure space 3.
  • the nozzle needle 5 in one piece and - to form the pressure stage 12 - stepped formed.
  • the nozzle needle 5 has a guide diameter d u and above a guide diameter d o , where also d o ⁇ d u .
  • the guide diameter d u acts together with a sleeve-shaped guide element 11, which is supported on the body 6, forming a guide gap 9.
  • the guide gap 9 seals a trained in the body 6 low-pressure chamber 7, which is formed as an axial bore.
  • the axial bore is stepped, so that adjoining the low-pressure chamber 7 is a guide section which cooperates with the guide diameter d o of the nozzle needle 5 forming a guide gap 8.
  • the guide gap 8 seals the low-pressure chamber 7 against a further pressure chamber formed in the body 6, which may be designed as a control chamber 22 or as a coupler chamber of a hydraulic coupler.
  • the body 6 also serves as a coupler body 20 of the hydraulic coupler (see reference numerals in parentheses).
  • a coupler body 20 As a coupler body 20, the body 6 is received in a liftable manner in the high-pressure chamber 3.
  • the trained in the body 6 control chamber 22 and coupler space is bounded by an end face of the nozzle needle 5, so that prevails at the nozzle needle 5 of the prevailing in the control chamber 22 or coupler hydraulic pressure, via which the lifting movement of the nozzle needle 5 is preferably directly controlled.
  • the embodiment according to the FIG. 7 is different from that of FIG. 6 in that the nozzle needle 5 is formed in two parts and has a first part 5.1 with the guide diameter d o and a second part 5.2 with the guide diameter d u , again d o ⁇ d u . Since in the control chamber 22 or coupler space and in the high pressure chamber 3 prevail significantly higher pressures than in the low pressure chamber 7, the two parts 5.1, 5.2 of the nozzle needle 5 are pressed together with high forces and form a functional unit.
  • the advantage of this embodiment is in particular that the multi-part design of the nozzle needle 5 allows the compensation of an axial and / or angular offset.
  • the two parts 5.1, 5.2 the nozzle needle 5 are ground continuously when the guide diameter is equal to the outer diameter over the entire height of the part. While the first part 5.1 in this case has a convex end for abutment on and for mechanical coupling with the second part of the nozzle needle 5 5. 2, the second part 5. 2 ends in a flat end face. Other face geometries are also conceivable.
  • a modification of the embodiment of the FIG. 7 is in the FIG. 8 shown.
  • the first part 5.1 of the nozzle needle 5 is here performed stepped to make the first part 5.1 receiving bore in the body 6 as a simple axial bore.
  • FIG. 9 refer to. In contrast to the embodiment of FIG. 8 shows the FIG.
  • annular groove 27 connected to the flow channel 15 via a branch 15 'in the region of the guide of the first part 5.1 of the nozzle needle 5.
  • the guide gap 8 is connected in this way to the high-pressure chamber 3.
  • the annular groove 27 In the region of the annular groove 27 is located over the entire circumference of the first part 5.1 of the nozzle needle 5 high pressure. In this way, the annular groove 27 counteracts leakage from the control chamber 22 or coupler space in the direction of the low-pressure space 7.
  • Injektorlochepten that provide a constant coupler volume, for example in direct-switching injectors, causes a leakage from the coupler space in the low-pressure chamber, a permanent reduction of the coupler space pressure. This has the consequence that the injector behavior changes. This must be prevented.
  • the proposed high-pressure connection of the guide gap 8 represents a measure to effectively prevent leakage from the coupler space and thus a reduction of the coupler space pressure.
  • the in connection with the FIGS. 1 to 9 described features can each be used individually or in various combinations. In this way one obtains further modifications and / or alternative embodiments, all of which are part of the invention as defined in the appended claims.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (11)

  1. Injecteur de carburant pour un système d'injection de carburant, en particulier un système d'injection à rampe commune, comprenant un corps de buse (1) et un corps d'injecteur (2), qui entourent respectivement une chambre à haute pression (3, 4), dans lesquelles est disposé un pointeau en une ou plusieurs partie(s) (5) mobile permettant d'ouvrir et de fermer au moins un orifice d'injection, dans lequel le pointeau (5) est conduit à travers une chambre à basse pression (7), qui est étanche par rapport aux chambres à haute pression (3, 4) au moyen d'au moins une fente de guidage (8, 9) entre le pointeau (5) et un élément de guidage (10, 11) qui est réalisé en forme de douille et qui prend appui sur un corps (6) limitant la chambre à basse pression (7), et dans lequel le pointeau (5) présente des diamètres de guidage de grandeur différente (do, du) pour la formation d'un étage de pression (12) disposé dans la chambre à basse pression (7), dans lequel le diamètre de guidage (do) situé plus loin par rapport à l'orifice d'injection est plus petit que le diamètre de guidage (du), de telle manière que le pointeau (5) soit en partie délesté en direction de l'orifice.
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce que le corps (6) limitant la chambre à basse pression (7) est un composant solide en forme de plaque disposé entre le corps de buse (1) et le corps d'injecteur (2), qui est serré axialement de préférence au moyen d'un écrou de serrage de buse (26) avec le corps de buse (1) et le corps d'injecteur (2) et/ou comporte au moins un canal d'écoulement (15) pour le raccordement hydraulique des chambres à haute pression (3, 4).
  3. Injecteur de carburant selon la revendication 1, caractérisé en ce que le corps (6) limitant la chambre à basse pression (7) est disposé de façon mobile dans la chambre à haute pression (3) et/ou dans la chambre à haute pression (4), dans lequel le corps (6) est de préférence un corps de coupleur (20) d'un coupleur hydraulique (19).
  4. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que la chambre à basse pression (7) est raccordée par au moins un canal de raccordement (13) à une région à basse pression (14) de l'injecteur de carburant, dans lequel le canal de raccordement (13) est de préférence réalisé au moins en partie sous la forme d'un alésage s'étendant radialement.
  5. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que le pointeau (5) est réalisé en plusieurs parties, de préférence en deux parties, pour la formation des diamètres de guidage de grandeur différente (do, du), dans lequel une première partie (5.1) et une deuxième partie (5.2) présentent de préférence des faces de contact coopérantes, qui sont disposées dans la chambre à basse pression (7).
  6. Injecteur de carburant selon la revendication 5, caractérisé en ce que la première partie (5.1) et la deuxième partie (5.2) du pointeau (5) présentent dans la région de leurs faces de contact une géométrie formant une articulation (16).
  7. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément de guidage (10, 11) réalisé en forme de douille est appuyé sur le corps (6) par un bord en couteau et/ou est poussé en direction du corps (6) par la force élastique d'un ressort (17, 18).
  8. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que le mouvement de la course du pointeau (5) peut être commandé directement par un actionneur et/ou il est prévu un coupleur hydraulique (19) pour la conversion de la force et/ou de la course d'un actionneur.
  9. Injecteur de carburant selon la revendication 8, caractérisé en ce que le coupleur hydraulique (19) comporte un corps de coupleur (20) avec un épaulement cylindrique creux (21) destiné à recevoir une partie d'extrémité du pointeau (5) et à former une chambre de commande (22).
  10. Injecteur de carburant selon la revendication 8, caractérisé en ce que le coupleur hydraulique (19) comporte un corps de coupleur (20), sur lequel s'appuie une douille d'étanchéité (23) destinée à recevoir une partie d'extrémité du pointeau (5) et à former une chambre de commande (22).
  11. Injecteur de carburant selon la revendication 10, caractérisé en ce que la douille d'étanchéité (23) comporte un bord en couteau (24) situé radialement à l'intérieur, par lequel elle prend appui sur le corps de coupleur (20).
EP14189616.7A 2013-12-10 2014-10-21 Injecteur de carburant Active EP2884088B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013225384.2A DE102013225384A1 (de) 2013-12-10 2013-12-10 Kraftstoffinjektor

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EP2884088B1 true EP2884088B1 (fr) 2016-12-14

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DE3936619A1 (de) * 1989-11-03 1991-05-08 Man Nutzfahrzeuge Ag Verfahren zum einspritzen eines brennstoffes in einen brennraum einer luftverdichtenden, selbstzuendenden brennkraftmaschine, sowie vorrichtungen zur durchfuehrung dieses verfahrens
DE10352736A1 (de) * 2003-11-12 2005-07-07 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadeleinspritzung
JP4297879B2 (ja) * 2005-02-24 2009-07-15 株式会社デンソー インジェクタ
DE102007062702A1 (de) * 2007-12-27 2009-07-02 Robert Bosch Gmbh Kraftstoffinjektor
DE102008002415A1 (de) * 2008-06-13 2009-12-17 Robert Bosch Gmbh Kraftstoffinjektor
DE102008040680A1 (de) 2008-07-24 2010-01-28 Robert Bosch Gmbh Kraftstoff-Injektor
DE102008054421A1 (de) * 2008-12-09 2010-06-10 Robert Bosch Gmbh Kraftstoffinjektor
DE102009002528A1 (de) * 2009-04-21 2010-10-28 Robert Bosch Gmbh Kraftstoffinjektor
DE102010039116A1 (de) * 2010-08-10 2012-02-16 Robert Bosch Gmbh Kraftstoffinjektor
DE102010041109A1 (de) * 2010-09-21 2012-03-22 Robert Bosch Gmbh Kraftstoffinjektor
DE102011076663A1 (de) * 2011-05-30 2012-12-06 Robert Bosch Gmbh Kraftstoffinjektor

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EP2884088A1 (fr) 2015-06-17
DE102013225384A1 (de) 2015-06-11

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