EP1636484B1 - Injecteur pour moteurs a combustion interne - Google Patents

Injecteur pour moteurs a combustion interne Download PDF

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Publication number
EP1636484B1
EP1636484B1 EP04729036A EP04729036A EP1636484B1 EP 1636484 B1 EP1636484 B1 EP 1636484B1 EP 04729036 A EP04729036 A EP 04729036A EP 04729036 A EP04729036 A EP 04729036A EP 1636484 B1 EP1636484 B1 EP 1636484B1
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EP
European Patent Office
Prior art keywords
compensator
control
face
nozzle
pressure
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.)
Expired - Lifetime
Application number
EP04729036A
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German (de)
English (en)
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EP1636484A1 (fr
Inventor
Friedrich Boecking
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
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Robert Bosch GmbH
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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
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • 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
    • 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
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • 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
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • F02M2200/706—Valves for filling or emptying hydraulic chamber

Definitions

  • the present invention relates to an injection nozzle for internal combustion engines with the features of the preamble of claim 1.
  • Such an injection nozzle is off US 4,022,166 in which a nozzle body is provided with a nozzle needle guided therein, with which the injection of fuel through at least one injection hole is controllable.
  • a piezoelectric actuator is drive-coupled to a control piston, wherein the control piston has a control surface which is exposed to a control chamber.
  • the nozzle needle is exposed to a Kompensator Structure a Kompensatorraum, the Kompensatorraum and the control chamber are hydraulically coupled by means of a hydraulic path.
  • the nozzle needle is further exposed to a pressure shoulder a nozzle chamber, which is permanently high fuel pressure.
  • Another injector is for example from the DE 100 60 836 C1 known and has a nozzle body having at least one injection hole.
  • the nozzle body also contains a needle guide in which a nozzle needle is guided. With the nozzle needle, the injection of fuel through the at least one spray hole is controllable.
  • a control valve is arranged in a supply line which supplies the at least one spray hole under high pressure fuel, with which the Fuel supply can be controlled by the supply line to the at least one spray hole.
  • This control valve is drive-coupled to its actuation with an actuator.
  • the nozzle needle carries at its end facing away from the at least one injection port end a control piston which is guided in a stroke-adjustable hub.
  • This control room communicates on the one hand with the controllable with the control valve supply line.
  • a suitably throttled drain line from the control room which leads to a leakage oil chamber and which is controllable with a slide.
  • This slide forms a part of the control valve and is thus actuated together with the control valve by the actuator.
  • the nozzle needle has at its end facing the at least one spray hole a pressure stage which acts in a pressurization in the opening direction of the nozzle needle.
  • control valve closes the supply line and the slide opens the drain line.
  • the nozzle needle is then biased by spring force into its closed position; the at least one spray hole is thus closed.
  • the control valve lifts from the associated seat, whereby the supply line is open and can affect the pressure level of the nozzle needle of the high fuel pressure.
  • the high fuel pressure can not build up because the drain line is still open. Accordingly, the opening forces prevail at the nozzle needle, so that the nozzle needle opens and an injection takes place.
  • the injection nozzle according to the invention with the features of the independent claim has the advantage over that the nozzle needle can be controlled directly by the operation of the control piston. This is made possible by the fact that the high fuel pressure is applied both to a compensator surface of the nozzle needle and to a control surface of the control piston, wherein the control surface and the compensator surface are coupled together via a corresponding hydraulic path. This means that a pressure change at the control surface, which is triggered by an actuation of the actuator, so the control piston, is also effective directly on the compensator of the nozzle needle, which changes directly the balance of forces on the nozzle needle to open or close the nozzle needle , The effort to realize such a direct nozzle needle control is considerably reduced.
  • the control piston for opening the nozzle needle can be actuated such that the applied pressure drops at the first compensator surface assigned to the nozzle needle.
  • the actuator drives the control piston in the direction in which the control piston associated with the first control surface is biased anyway by the fuel high pressure applied thereto. That is, by the actuation of the actuator, the first control surface yields in the direction of the compressive forces acting on it. Consequently, the actuator does not have to generate actuating forces, but only a sufficiently fast adjustment of the control piston cause.
  • This embodiment is advantageous since the fuel in modern injection systems is in the meantime supplied at very high pressures, for example 800 bar, via the supply line to the at least one injection hole.
  • control piston is drive-coupled to the actuator via a drive rod, wherein the actuator is designed as a hollow actuator, through which the drive rod is guided centrally.
  • the drive rod carries on a side facing away from the control piston side of the actuator a drive piston driven by the actuator, wherein the actuator is designed and arranged such that it drives the drive piston in an opening stroke direction of the nozzle needle when actuated.
  • the injection nozzle 1 has a nozzle body 2, which is equipped with at least one injection hole 3. It is clear that the nozzle body 2 regularly has more than one injection hole 3. Through the at least one injection hole 3, the injection nozzle 1 can inject fuel into a combustion chamber or mixture formation space 4.
  • the nozzle body 2 contains a single nozzle needle 5, which is guided in a stroke-adjustable manner in the nozzle body 2 in a needle guide 6.
  • the nozzle needle 5 acts on its, the at least one spray hole 3 facing nozzle tip 7 with a sealing seat 8 which is formed in the nozzle body 2 and usually has a circular ring shape.
  • a supply line 9 is formed, which leads in the nozzle body 2 to a nozzle chamber 10 and is supplied with fuel which is at a high pressure.
  • the supply line 9 is connected to a common for several injectors 1 high-pressure line, so-called “common rail principle”.
  • the common high-pressure line is fed by means of a common high-pressure pump.
  • the supply line 9 may be connected directly to a high-pressure pump.
  • the nozzle chamber 10 is connected via an annular space 11 with the at least one injection hole 3, wherein between the annular space 11 and the at least one injection hole 3 of the sealing seat 8 is arranged.
  • the nozzle needle 5 has in the nozzle chamber 10 and in the annular space 11 a pressure stage 12, which faces the at least one injection hole 3.
  • the pressure stage 12 is the difference between a guide surface 13 in cross-section of the needle guide 6 minus a sealing surface 14 in the sealing seat 8.
  • In operation of the injector 1 is at the pressure stage 12 permanently high fuel pressure, so that the nozzle needle 5 with an opening force in their symbolized by an arrow opening direction 15 acts, is loaded.
  • the nozzle needle 5 is assigned a first compensator surface 16.
  • the injection nozzle 1 also includes a control piston 18 which is drive-coupled to an actuator 19.
  • the actuator or actuator 19 is used to adjust the control piston 18 and may be formed, for example, as a piezoelectric actuator.
  • the actuator 19 drives a drive piston 39, which is fixedly connected to a drive rod 40, which in turn is fixedly connected to the control piston 18. In principle, however, other drive couplings between actuator 19 and control piston 18 are feasible.
  • the control piston 18 is mounted in a control piston guide 20 adjustable in stroke in the nozzle body 2 and has a first control surface 21.
  • a first hydraulic path 22 is formed, which hydraulically couples the first control surface 21 with the first compensator 16.
  • a hydraulic coupling in the present case is understood to mean a pressure transmission path which can transmit the pressure applied to the first control surface 21 to the first compensator surface 16 and vice versa.
  • the first control surface 21 is arranged in a first control chamber 23 and can be acted upon by a pressure therein.
  • the first compensator surface 16 is also arranged in a first compensator space 24 and can be acted upon there by a pressure.
  • the first control chamber 21 communicates with the first compensator chamber 24 via a connecting line 25.
  • the first hydraulic path 22 thus passes through the first control chamber 23, the connecting line 25 and the first compensator chamber 24.
  • a second hydraulic path 29 is also formed, via which the first control chamber 23 is hydraulically coupled to the second control chamber 28 and to the supply line 9.
  • the first compensator surface 16 is formed on a compensator piston 32 which is guided in a compensator piston guide 33 in the nozzle body 2 and is drive-coupled to the nozzle needle 5.
  • the Kompensatorkolben 32 is fixedly connected to the nozzle needle 5 and can be made in particular with this one-piece or in one piece.
  • the first compensator surface 16 faces the at least one spray hole 3 and thus acts when the pressure is applied in the opening direction 15.
  • the compensator piston 32 has, on a side facing away from the at least one spray hole 3 side, a second compensator surface 34, which accordingly faces the first compensator surface 16.
  • the second compensator surface 34 is arranged in a second compensator space 35 and can be acted upon there with a pressure.
  • the second compensator chamber 35 communicates with the supply line 9, so that in the second Kompensatorraum 35 the high pressure fuel permanently prevails.
  • the high-pressure fuel effective at the second compensator surface 34 generates a force acting in the closing direction 17 on the unit of the compensator piston 32 and the nozzle needle 5.
  • the first hydraulic path 22 leads from the first compensator surface 16 through the first compensator space 24, through the connecting line 25 and through the first control chamber 23 to the first control surface 21.
  • the second hydraulic path 29 couples the first control surface 21 to the supply line 9, but in this embodiment leads through a feed line 36, in which a feed valve 37 is arranged.
  • the feed valve 37 is formed here as a non-return valve, which blocks to the supply line 9 and opens to the first control chamber 23 out and which is also spring-loaded in its blocking direction.
  • a spring 38 which serves to restore the control piston 18 and on the one hand on the nozzle body 2 and on the other hand on the drive piston 39 is supported.
  • the embodiment of the injection nozzle 1 according to the invention shown in FIG. 1 operates as follows:
  • the nozzle needle 5 is closed, ie the needle tip 7 is seated in the sealing seat 8 and thereby separates the at least one spray hole 3 from the supply line 5.
  • the feed line 36 allows pressure equalization between the supply line 9 and the first Control chamber 23, so that in the first control chamber 23 substantially the high fuel pressure prevails.
  • the fuel high pressure is also applied to the first compensator surface 16 via the first hydraulic path 22.
  • the second compensator chamber 35 the high-pressure fuel permanently prevails, so that it also bears against the second compensator surface 34.
  • the Kompensator vom 16, 34 and the pressure stage 12 are coordinated so that in the initial state at the nozzle needle 5 and on the unit of Kompensatorkolben 32 and nozzle needle 5, a resultant Adjusting force that acts in the closing direction 17. Accordingly, the nozzle needle 5 is pressed with its needle tip 7 against the sealing seat 8.
  • a return spring 26 arranged in the second compensator chamber 35 also acts in the closing direction and exerts an additional closing force on the nozzle needle 5.
  • the actuator 19 For injecting fuel into the combustion chamber 4, the actuator 19 is now actuated, such that the control piston 18 again performs an opening stroke 31.
  • the control piston 18 penetrates with its first control surface 21 deeper into the first control chamber 23, whereby the volume of the first control chamber 23 decreases.
  • the feed valve 37 blocks and thereby prevents escape of the fuel from the first control chamber 23 through the feed line 36 into the supply line 9.
  • the increasing pressure from the first control chamber 23 propagates directly into the first compensator chamber 24. Accordingly, the pressure on the first compensator surface 16 also increases, so that the forces acting in the opening direction 15 on the unit of compensator piston 32 and nozzle needle 5 increase.
  • the pressure in the second compensator space 35 remains constant, so that the forces acting in the closing direction on the unit of Kompensatorkolben 32 and nozzle needle 5 remain constant.
  • the pressure increase caused by the opening stroke 31 is so high that the balance of forces on the unit of compensator pistons 32 and nozzle needle 5 changes to the effect that an effective resultant force in the opening direction 15 now arises. Consequently, the nozzle needle 5 lifts from its sealing seat 8 and the at least one injection hole 3 communicates with the supply line 9. Accordingly, fuel is injected through the at least one injection hole 3 into the combustion chamber 4.
  • the actuator 19 is actuated to reset the control piston 18, wherein the return movement of the control piston 18 is supported by the spring 38.
  • the volume of the first control chamber 23 is increased again, so that the pressure in the first control chamber 23 drops again to a corresponding extent.
  • This pressure drop propagates again via the first hydraulic path 22 to the first compensator chamber 24.
  • the associated pressure drop at the first compensator surface 16 again leads in the following to a change in the balance of forces on the unit of Kompensatorkork 32 and nozzle needle 5, to the effect that again in the closing direction 17 effective resulting force arises.
  • the resulting pressure force thus drives supported by the return spring 26, the unit of Kompensatorkolben 32 and nozzle needle 5 in the closed position of the nozzle needle 5 at.
  • the at least one injection hole 3 is again separated from the supply line 9, so that the injection process is completed.
  • FIG. 1 The embodiment shown in FIG. 1 is characterized by a particularly simple structure and works with a direct control of the nozzle needle 5.
  • the pressure at the first compensator surface 16 is increased to open the nozzle needle 5.
  • the pressure in the first control chamber 23 and thus in the first compensator chamber 24 can not substantially fall below the high fuel pressure when the control piston 18 is reset since the feed line 36 brings about a corresponding pressure equalization through the corresponding operating feed valve 37.
  • Fig. 2 shows a second embodiment of an injection nozzle 1 according to the invention, which referenced because of the matches with the previous embodiments of FIG. 1 in terms of components and functions on the pertaining to Figs. 1 and 2 and subsequently essentially only the differences will be explained.
  • the first compensator surface 16 on the compensator piston 32 is arranged on a side facing away from the at least one injection hole 3 so that it acts in the closing direction 17 when pressure is applied.
  • the opposing second compensator surface 34 acts in the opening direction 15.
  • the return spring 26 is accordingly arranged in the first compensator chamber 24 in this embodiment and is supported on the nozzle body 2 and on the first compensator surface 16.
  • the feed valve 37 is constructed in the embodiment shown here so that it locks in a pressure drop in the first control chamber 23, thereby preventing a subsequent flow of fuel from the supply line 9 into the first control chamber 23.
  • a spring assembly 41 in the feed valve 37 ensures that the feed valve 37 can still open at a less pronounced pressure drop to allow pressure equalization between the first control chamber 23 and feed line 9.
  • the feed line 36 could also contain a throttle point, which virtually blocks the second hydraulic path 29 during dynamic processes and a Pressure equalization is possible when quasi-static conditions exist.
  • the actuator 19 is formed as a hollow actuator, which includes a central passage opening 42 through which the drive rod 40 is passed.
  • the drive piston 39 is then fastened to the drive rod 40 on a side of the actuator 19 facing away from the control piston 18.
  • the actuator 19 in contrast to the embodiments described above, perform an opening stroke 31, which is oriented away from the at least one spray hole 3.
  • the control piston 18 is thus adjusted in its opening stroke 31 in the opening direction 15 of the nozzle needle 5. This has the consequence that within the hydraulic coupling between the control piston 18 and the compensator piston 32, no force direction reversal is required.
  • the embodiment of the injection nozzle 1 according to the invention shown in FIG. 2 operates as follows:
  • the nozzle needle 5 is closed, ie their needle tip 7 blocks the at least one spray hole 3.
  • the second Kompensatorraum 35 of high fuel pressure prevails in the second Kompensatorraum 35 of high fuel pressure.
  • the second hydraulic path 29 is active in the present static state, so that a pressure equalization between the supply line 9 and the first control chamber 23 can take place. Accordingly, the high fuel pressure also prevails in the first control chamber 23.
  • the high-pressure fuel therefore prevails in the first compensator chamber 24 via the first hydraulic path 22.
  • the same pressure namely the high pressure fuel.
  • the closing force prevails, so that the balance of forces on the unit of compensator piston 32 and nozzle needle 5 results in an effective force in the closing direction 17.
  • the return spring 26 acting in the closing direction.
  • the actuator 19 is actuated so that it drives the control piston 18 to perform the opening stroke 31.
  • the opening stroke 31 acting in the opening direction 15 causes an enlargement of the first control chamber 23, with the result that the pressure in the first control chamber 23 drops sharply and rapidly.
  • this dynamic behavior causes the feed valve 37 to block and prevents fuel from flowing from the feed line 9 into the first control chamber 23.
  • the pressure drop forming in the first control chamber 23 propagates into the first compensator chamber 24. Accordingly, the force acting on the first compensator surface 16 in the closing direction 17 is reduced.
  • the high fuel pressure still prevails.
  • the balance of forces on the unit of compensator piston 32 and nozzle needle 5 changes to the effect that a resultant force acting in the opening direction is produced. Accordingly, the nozzle needle 5 lifts off from its sealing seat 8, so that the high-pressure fuel passes unhindered to at least one spray hole 3 and is injected via this into the combustion chamber 4.
  • the actuator 19 is now actuated so that it moves the control piston 18 back again.
  • the volume of the first control chamber 23 decreases, so that there the pressure rises again.
  • the spring arrangement 41 in the feed valve 37 causes the high fuel pressure to prevail again in the first control chamber 23.
  • the caused by the provision of the control piston 18 pressure increase in the first control chamber 23 is transmitted through the first hydraulic path 22 directly into the first Kompensatorraum 24, so that the effective at the first Kompensator Structure 16 closing force again increases substantially to the initial value.
  • the force effect of the return spring 26 is also actuated so that it moves the control piston 18 back again.
  • This embodiment is characterized by a comparatively simple structure, wherein it allows a direct actuation of the nozzle needle 5.
  • a pressure drop is generated on the first compensator surface 16 to open the nozzle needle 5.

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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)

Claims (4)

  1. Injecteur de moteur à combustion interne notamment pour un véhicule automobile comprenant :
    - un corps d'injecteur (2) ayant au moins un orifice d'éjection (3),
    - une aiguille d'injecteur (5) guidée dans un guide d'aiguille (6) du corps d'injecteur (2), pour commander l'injection de carburant à travers au moins un orifice d'éjection (3),
    - une conduite d'alimentation (9) aboutissant dans le corps d'injecteur (2) dans la chambre d'injecteur (10) pour l'alimenter en carburant à haute pression,
    - la conduite d'alimentation (9) fournissant du carburant à haute pression à au moins un orifice d'éjection (3),
    - un piston de commande (18) couplé pour être entraîné, par un actionneur (19), ce piston ayant une première surface de commande (21),
    - l'aiguille d'injecteur (5) est couplée pour être entraînée à un piston compensateur (32) ayant une première surface de compensation (16),
    - la première surface de compensation (16) est couplée hydrauliquement à la première surface de commande (21) par un premier chemin hydraulique (22),
    - le premier chemin hydraulique (22) traverse une première chambre de commande (23) dans laquelle se trouve la première surface de commande (21) pour arriver par une conduite de liaison (25) dans une première chambre de compensation (24) dans laquelle se trouve la première surface de compensation (16), chemin par lequel la première chambre de commande (23) communique avec la première chambre de compensation (24),
    caractérisé en ce que
    la première surface de commande (21) est couplée hydrauliquement à la conduite d'alimentation (9) par un second chemin hydraulique (29) muni d'une soupape d'alimentation (37),
    le piston compensateur (32) présente une seconde surface de compensation (34) dans une seconde chambre de compensation (35) communiquant avec la conduite d'alimentation (9) de façon qu'il règne en permanence une haute pression de carburant dans la seconde chambre de compensation (35) et
    la première et la seconde surface de compensation (16, 34) sont opposées de sorte que la course d'ouverture (31) du piston de commande (18) engendre une force résultante agissant dans le sens de l'ouverture (15).
  2. Injecteur selon la revendication 1,
    caractérisé en ce que
    la première surface de compensation (16) est tournée vers l'orifice d'éjection (3) et agit ainsi dans le sens de l'ouverture (15) et la soupape d'alimentation (37) du second chemin hydraulique (29) ferme la conduite d'alimentation (9) et l'ouvre vers la première chambre de commande (23).
  3. Injecteur selon la revendication 1,
    caractérisé en ce que
    la première surface de compensation (16) est tournée vers l'orifice d'éjection (39) et ainsi, lorsque la pression est appliquée, elle agit dans le sens de la fermeture (17) et la soupape d'alimentation (37) du second chemin hydraulique (29), lors de la course d'ouverture (31) du piston de commande (18), évite que le carburant ne continue de passer de la conduite d'alimentation (9) dans la première chambre de commande (23).
  4. Injecteur selon la revendication 3,
    caractérisé en ce que
    le piston de commande (18) est actionné pour ouvrir l'aiguille d'injecteur (5) de façon à faire chuter la pression appliquée contre la première surface de compensation (16).
EP04729036A 2003-06-10 2004-04-23 Injecteur pour moteurs a combustion interne Expired - Lifetime EP1636484B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10326046A DE10326046A1 (de) 2003-06-10 2003-06-10 Einspritzdüse für Brennkraftmaschinen
PCT/DE2004/000848 WO2004111433A1 (fr) 2003-06-10 2004-04-23 Injecteur pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1636484A1 EP1636484A1 (fr) 2006-03-22
EP1636484B1 true EP1636484B1 (fr) 2007-09-12

Family

ID=33482739

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04729036A Expired - Lifetime EP1636484B1 (fr) 2003-06-10 2004-04-23 Injecteur pour moteurs a combustion interne

Country Status (6)

Country Link
US (1) US20060032940A1 (fr)
EP (1) EP1636484B1 (fr)
JP (1) JP2006514216A (fr)
KR (1) KR20060021356A (fr)
DE (2) DE10326046A1 (fr)
WO (1) WO2004111433A1 (fr)

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10326259A1 (de) * 2003-06-11 2005-01-05 Robert Bosch Gmbh Injektor für Kraftstoff-Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren
DE102004010183A1 (de) * 2004-03-02 2005-09-29 Siemens Ag Einspritzventil
DE102004028522A1 (de) * 2004-06-11 2005-12-29 Robert Bosch Gmbh Kraftstoffinjektor mit variabler Aktorhubübersetzung
DE102004037124A1 (de) * 2004-07-30 2006-03-23 Robert Bosch Gmbh Common-Rail-Injektor
US7568633B2 (en) * 2005-01-13 2009-08-04 Sturman Digital Systems, Llc Digital fuel injector, injection and hydraulic valve actuation module and engine and high pressure pump methods and apparatus
DE102005004738A1 (de) 2005-02-02 2006-08-10 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine
CN100593081C (zh) * 2005-02-18 2010-03-03 罗伯特·博世有限公司 喷嘴
DE102005026514B4 (de) * 2005-02-18 2008-12-24 Robert Bosch Gmbh Einspritzdüse
DE102005008973A1 (de) 2005-02-28 2006-08-31 Robert Bosch Gmbh Einspritzdüse
DE102005042786B4 (de) * 2005-09-08 2009-04-16 Siemens Ag Kraftstoffinjektor mit hermetisch abgedichtetem Hydrauliksystem
US7793638B2 (en) 2006-04-20 2010-09-14 Sturman Digital Systems, Llc Low emission high performance engines, multiple cylinder engines and operating methods
DE102007001363A1 (de) * 2007-01-09 2008-07-10 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff in Brennräume von Brennkraftmaschinen
JP4333757B2 (ja) * 2007-03-13 2009-09-16 株式会社デンソー 燃料噴射弁
EP1970556B1 (fr) 2007-03-15 2009-12-30 Ford Global Technologies, LLC Injecteur
US20080264393A1 (en) * 2007-04-30 2008-10-30 Sturman Digital Systems, Llc Methods of Operating Low Emission High Performance Compression Ignition Engines
CN101680410B (zh) * 2007-05-09 2011-11-16 斯德曼数字系统公司 具有主动针控制器的多级增强型喷射器和喷射方法
JP4633766B2 (ja) * 2007-06-08 2011-02-16 株式会社日本自動車部品総合研究所 燃料噴射弁
US7954472B1 (en) 2007-10-24 2011-06-07 Sturman Digital Systems, Llc High performance, low emission engines, multiple cylinder engines and operating methods
US7958864B2 (en) * 2008-01-18 2011-06-14 Sturman Digital Systems, Llc Compression ignition engines and methods
JP4831131B2 (ja) * 2008-06-06 2011-12-07 株式会社デンソー 燃料噴射弁
DE102008032133B4 (de) * 2008-07-08 2015-08-20 Continental Automotive Gmbh Kraftstoffeinspritzvorrichtung
US20100012745A1 (en) * 2008-07-15 2010-01-21 Sturman Digital Systems, Llc Fuel Injectors with Intensified Fuel Storage and Methods of Operating an Engine Therewith
DE102009002528A1 (de) * 2009-04-21 2010-10-28 Robert Bosch Gmbh Kraftstoffinjektor
US8596230B2 (en) * 2009-10-12 2013-12-03 Sturman Digital Systems, Llc Hydraulic internal combustion engines
US8887690B1 (en) 2010-07-12 2014-11-18 Sturman Digital Systems, Llc Ammonia fueled mobile and stationary systems and methods
US9206738B2 (en) 2011-06-20 2015-12-08 Sturman Digital Systems, Llc Free piston engines with single hydraulic piston actuator and methods
US9464569B2 (en) 2011-07-29 2016-10-11 Sturman Digital Systems, Llc Digital hydraulic opposed free piston engines and methods
DE102012212614A1 (de) * 2012-07-18 2014-01-23 Continental Automotive Gmbh Piezoinjektor mit hydraulisch gekoppelter Düsennadelbewegung
US9181890B2 (en) 2012-11-19 2015-11-10 Sturman Digital Systems, Llc Methods of operation of fuel injectors with intensified fuel storage
DE102012222509A1 (de) 2012-12-07 2014-06-12 Continental Automotive Gmbh Piezoinjektor
DE102012223934B4 (de) 2012-12-20 2015-10-15 Continental Automotive Gmbh Piezoinjektor
EP2806149A1 (fr) * 2013-05-23 2014-11-26 Delphi International Operations Luxembourg S.à r.l. Injecteur de carburant
US20160377040A1 (en) * 2015-06-24 2016-12-29 Great Plains Diesel Technologies, L.C. Fuel injection rate modulation by magnetostrictive actuator and fluidomechanical coupler
GB201515892D0 (en) * 2015-09-08 2015-10-21 Delphi Int Operations Lux Srl Hydraulic lash adjuster arranged in a servo injector
DE102024127635A1 (de) * 2024-09-24 2026-03-26 Atlas Copco Ias Gmbh Antrieb für ein Ventil und Applikationsvorrichtung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022166A (en) * 1975-04-03 1977-05-10 Teledyne Industries, Inc. Piezoelectric fuel injector valve
JPH01187363A (ja) * 1988-01-21 1989-07-26 Toyota Motor Corp 内燃機関用燃料噴射弁
DE19519191C2 (de) * 1995-05-24 1997-04-10 Siemens Ag Einspritzventil
DE19839125C1 (de) * 1998-08-27 2000-04-20 Siemens Ag Vorrichtung und Verfahren zur Dosierung von Fluid

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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US20060032940A1 (en) 2006-02-16
DE502004004964D1 (de) 2007-10-25
EP1636484A1 (fr) 2006-03-22
KR20060021356A (ko) 2006-03-07
JP2006514216A (ja) 2006-04-27
DE10326046A1 (de) 2004-12-30
WO2004111433A1 (fr) 2004-12-23

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