EP1853813B1 - Injecteur - Google Patents

Injecteur Download PDF

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Publication number
EP1853813B1
EP1853813B1 EP05825330A EP05825330A EP1853813B1 EP 1853813 B1 EP1853813 B1 EP 1853813B1 EP 05825330 A EP05825330 A EP 05825330A EP 05825330 A EP05825330 A EP 05825330A EP 1853813 B1 EP1853813 B1 EP 1853813B1
Authority
EP
European Patent Office
Prior art keywords
diverting
plunger
face
space
path
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.)
Not-in-force
Application number
EP05825330A
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German (de)
English (en)
Other versions
EP1853813A1 (fr
Inventor
Wolfgang Stoecklein
Andreas Rau
Michael Bauer
Andreas Gruenberger
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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Publication date
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Publication of EP1853813A1 publication Critical patent/EP1853813A1/fr
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Publication of EP1853813B1 publication Critical patent/EP1853813B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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 present invention relates to an injection nozzle for an internal combustion engine, in particular in a motor vehicle, having the features of the preamble of claim 1.
  • Such injection nozzle is for example from the DE 103 26 046 A1 and comprises a nozzle body having at least one injection hole.
  • a nozzle needle is mounted adjustable in stroke, with which an injection of fuel through the at least one injection hole is controllable.
  • a booster piston is provided, which is drive-coupled with an actuator and having a translator surface.
  • the nozzle needle has a hydraulically coupled to the translator surface control surface.
  • the known injection nozzle works with a direct needle control.
  • the nozzle needle or a needle assembly comprising the nozzle needle has at least one pressure stage, which is hydraulically coupled to a feed path which supplies the fuel under injection pressure to the at least one injection hole.
  • opening forces can be introduced into the nozzle needle or needle assembly via the at least one pressure stage
  • closing forces can be introduced into the nozzle needle or needle assembly via the control surface.
  • the closing forces predominate.
  • To open the nozzle needle of the pressure acting on the control surface pressure is lowered, whereby the closing forces are reduced, so that the opening forces predominate.
  • the nozzle needle lifts and opens at least one Injection port.
  • the pressure reduction at the control surface is achieved by an actuation of the actuator and thus by a stroke of the booster piston.
  • a hydraulic space bounded by both the translator surface and the control surface is increased by the stroke of the intensifier piston, thereby decreasing the pressure therein.
  • a small gear ratio results in the actuation of the actuator to a correspondingly slower opening movement of the nozzle needle and a correspondingly smaller opening stroke.
  • This is advantageous for the realization of precisely dimensioned, small injection quantities with short injection times.
  • Known injection nozzles, with which both small injection quantities and large injection quantities to be realized thus have a mean transmission ratio as a compromise.
  • the actuator in order to still be able to realize a large opening stroke with a comparatively small gear ratio, the actuator must be designed to carry out a correspondingly large stroke on the booster piston. This has the consequence that the actuator builds relatively large volume.
  • the available installation space is limited in internal combustion engines.
  • the injector according to the invention with the features of the independent claim has the advantage over that two different depending on the needle stroke Translation ratios are effective.
  • the gear ratio is constant in known injectors.
  • a bypass piston is provided.
  • the nozzle needle of the bypass piston remains at its stop, so that the stroke of the booster piston moves only the translator surface.
  • the nozzle needle follows the stroke of the booster piston.
  • the forces acting on the escape surface of the bypass piston are greater than the forces acting on the storage surface of the bypass piston.
  • the bypass piston lifts from its stop and thus moves in the same direction as the booster piston.
  • the injector according to the invention can thus control the nozzle needle for carrying out small needle strokes in the region of the first transmission ratio, so as to realize precise and small injection quantities with short injection times.
  • the injection nozzle according to the invention by the second ratio, the nozzle needle so control that in comparatively short times large needle strokes and thus large injection quantities can be realized.
  • the large second gear ratio leads to the fact that the actuator only has to realize a relatively small stroke and accordingly can be built comparatively small.
  • the storage space can be subdivided into a first storage subspace and into a second storage subspace.
  • a throttle piston is provided, which is drive-coupled to the bypass piston at least for the transmission of compressive forces, which is mounted in a manner adjustable in stroke in the booster piston and which contains a throttle path hydraulically coupling the two storage subspaces.
  • the storage area is in a first storage subspace limiting, for example, formed directly on the bypass piston first memory sub-area and in a second Dividing memory space, formed on the throttle piston second memory sub-area divided.
  • the lifting movement of the bypass piston can be damped relative to the booster piston, which is accompanied by a damping of the opening movement of the nozzle needle during the larger, second transmission ratio.
  • the damped needle movement reduces vibration excitation of the system consisting of actuator, booster piston, bypass piston and nozzle needle.
  • the injection process is thus more stable and has a reproducible accuracy. Furthermore, a sudden "popping" of the nozzle needle, so an uncontrolled high speed increase in the transition from the first gear ratio to the second gear ratio is avoided. In this way, the larger needle strokes can still be controlled relatively accurately.
  • an injection nozzle 1 according to the invention comprises a nozzle body 2, which has at least one injection hole 3.
  • the injection nozzle 1 is provided for an internal combustion engine, which can be arranged in particular in a motor vehicle, and serves for injecting fuel into an injection space 4 into which the injection nozzle 1 protrudes in the mounted state at least in the region of the at least one injection hole 3.
  • the injection nozzle 1 contains a nozzle needle 5, which may be part of a needle assembly 6 and with the aid of which an injection of fuel through the at least one injection hole 3 can be controlled.
  • the nozzle needle 5 cooperates with its needle tip 7 with a needle seat 8. If the nozzle needle 5 is seated in its needle seat 8, the at least one injection hole 3 is blocked, that is to say that at least one injection hole 3 is separated from a supply path 9, supplied via the injection-pressure fuel, and supplied to the at least one injection hole 3.
  • the feed path 9 is guided through the interior of the nozzle body 2, so that the components arranged in the nozzle body 2 virtually "float" in the feed path 9 in the fuel. In principle, however, another guidance of the feed path 9 is possible.
  • the nozzle needle 5 or the needle assembly 6 is mounted in the nozzle body 2 in an adjustable stroke.
  • This storage is realized here by a first bearing sleeve 10, in which the needle assembly 6 and the nozzle needle 5 is inserted at a distal end of the needle tip 7.
  • the first bearing sleeve 10 is attached to an intermediate plate 11, which forms a part of the nozzle body 2.
  • the intermediate plate 11 separates the injection nozzle 1 into a needle area containing the nozzle needle 5 and a translator area containing a booster piston 12 and an actuator 13.
  • the feed path 9 is passed through the intermediate plate 11.
  • the needle needle 5 and the needle assembly 6 is biased by a closing pressure spring 15 in the closing direction of the nozzle needle 5.
  • the closing compression spring 15 is supported here on the one hand on a step 16 of the nozzle needle 5 and the needle assembly 6 and on the other hand on the first bearing sleeve 10th
  • the needle needle 5 or its needle assembly 6 has a control surface 17, specifically on a side remote from the at least one spray hole 3.
  • the control surface 17 delimits a control chamber 18 axially, which is also axially limited relative to the control surface 17 of the intermediate plate 11.
  • the control chamber 18 is also enclosed radially by the first bearing sleeve 10.
  • the control chamber 18 may be hydraulically coupled to the feed path 9 via a control space path 19.
  • This control space path 19 can be formed, for example, as here in the region of the bearing between the nozzle needle 5 or needle assembly 6 and the first bearing sleeve 10, e.g. as a clearance or as at least one longitudinal groove which may be formed in the first bearing sleeve 10 and / or in the nozzle needle 5 or in the needle assembly 6. It is also possible to realize the control chamber path 19 by a transverse bore through the first bearing sleeve 10, which connects the control chamber 18 with the supply path 9 hydraulically.
  • the control space path 19 is throttled.
  • the injection nozzle 1 contains the booster piston 12, which is drive-coupled to the actuator 13.
  • the booster piston 12 is mounted adjustable in height in the nozzle body 2.
  • the booster piston 12 is inserted into a second bearing sleeve 20 which is fixedly connected to the intermediate plate 12.
  • the drive coupling between the booster piston 12 and the actuator 13 causes a stroke adjustment of the actuator 13 inevitably produces an identical stroke adjustment of the booster piston 12.
  • the actuator 13 is expediently designed as a piezoelectric actuator, which in the energized state in the stroke direction has a larger dimension than in a de-energized state.
  • the booster piston 12 has a booster surface 21 which axially delimits a coupler space 22.
  • the translator surface 21 is configured annular. Axially opposite the translator surface 21, the coupler space 22 is axially bounded by the intermediate plate 11. Furthermore, the coupler space 22 is bounded radially by the second bearing sleeve 20.
  • the coupler space 22 is hydraulically coupled by a control path 23 with the control chamber 18.
  • the control path 23 is realized here in the form of at least one bore, which penetrates the intermediate plate 11.
  • the coupler space 22 can be hydraulically coupled to the feed path 9 via a coupler space path 24.
  • the coupler space path 24 can be formed radially between the booster piston 12 and the second bearing sleeve 20, for example as a radial play or as at least one longitudinal groove in the second bearing sleeve 20 and / or in the It is also possible in principle to configure the coupler space path 24 by a transverse bore which penetrates the second bearing sleeve 20 and connects the coupler space 22 with the feed path 9.
  • the coupler space path 24 is throttled.
  • the injection nozzle 1 is also equipped with an evasive piston 25, which is mounted in a stroke-adjustable manner in the booster piston 12.
  • the booster piston 12 is designed as a hollow piston open on one side.
  • the bypass piston 25 protrudes into the coupler space 22 and has there an evasion surface 26, which likewise limits the coupler space 22 accordingly.
  • the bypass piston 25 On the side facing away from the escape surface 26, the bypass piston 25 also has a storage surface 27, which defines a storage space 28 which is formed in the booster piston 12.
  • the booster piston 12 can optionally have at least one throttle 29, which hydraulically couples the storage space 28 to the feed path 9.
  • the bypass piston 25 may include a throttle 30 which hydraulically couples the reservoir 28 to the coupler chamber 22.
  • a throttle 30 may also be formed radially between bypass piston 25 and booster piston 12, e.g. in the form of a corresponding radial clearance and / or in the form of at least one longitudinal groove in the booster piston 12 and / or in the bypass piston 25.
  • the bypass piston 25 is axially biased by a return spring 31 against a stop 32.
  • the restoring spring 31 is supported on the one hand on the booster piston 12 and on the other hand on the bypass piston 25, namely on the storage surface 27.
  • the stop 32 is arranged stationary with respect to the nozzle body 2. In the present case, the stop 32 is formed on the intermediate plate 11.
  • the contact between the escape piston 25 and stop 32 is advantageously carried out so that the escape surface 26 is as large as possible.
  • the contacting is quasi punctiform, which is achieved by a convex shaping of the bypass piston 25 in the region of its escape surface 26.
  • the booster piston 12 is biased with an opening compression spring 33 in its opening direction.
  • the opening compression spring 33 is supported on the one hand on the second bearing sleeve 20 and on the other hand on a collar 34 of the booster piston 12 from.
  • the volume of the storage space 28 is expediently greater than the common volume of the coupler space 22 and the control space 18.
  • coupler space 22 and control space 18 form separate spaces which are interconnected by the control path 23, another embodiment is possible in which control space 18 and coupler space 22 coincide in a common space.
  • the actuator 13 In order to carry out an injection of fuel through the at least one spray hole 3 into the injection space 4, the actuator 13 is de-energized, that is, the energization of the actuator 13 is interrupted. The actuator 13 is thus operated inversely. This means that the actuator 13 must be energized to close the at least one injection hole 3.
  • the actuator 13 contracts and performs an actuator stroke 35 indicated by an arrow.
  • This stroke adjustment follows the booster piston 12 inevitably, causing it to move away from the intermediate plate 12.
  • the volume of the coupler space 22 is increased, which is accompanied by a corresponding pressure drop in the coupler space 22.
  • the volume of the storage space 28 is also increased since the escape piston 25 remains biased against its stop 32. With the increase of the storage space volume, a corresponding pressure drop in the storage space 28 is accompanied.
  • the resulting pressure drop in the coupler chamber 22 directly propagates into the control chamber 18. Since the storage space 28 - as explained above - at least in the initial state has a larger volume than the total volume of the coupler chamber 22 and the control chamber 18, the pressure in the storage chamber 28 decreases slower than in the coupler chamber 22 and the control chamber 18. Accordingly, the effective on the storage surface 27 Pressure forces greater than the pressure acting on the alternate surface 26 pressure forces. As a result, the bypass piston 25 initially remains biased against its stop 32.
  • the forces acting in the closing direction on the nozzle needle 5 also decrease. From a predetermined control pressure, the opening forces acting on the nozzle needle 5 or on the needle dressing 6 are then greater than the effective closing forces. Accordingly, the nozzle needle 5 lifts off from the needle seat 8. As a result, the at least one spray hole 3 communicates with the feed path 9. The injection process begins.
  • the nozzle needle 5 and the needle assembly 6 is equipped with at least one pressure stage 36 and 37, which is permanently coupled hydraulically to the feed path 9 /.
  • This first ratio is at least initially defined by the ratio of the control surface 17 to the translator surface 21.
  • This first transmission ratio is comparatively small, so that a small stroke of the booster piston 12 also causes a comparatively small stroke of the nozzle needle 5, which may already be greater than the stroke of the booster piston 12. If only a small injection quantity to be realized can now within this first phase, during which the first ratio is present , the actuator 13 are energized again to stop the initiated opening movement and reverse. While the opening movement of the booster piston 12 is intensively supported by the opening compression spring 33, the closing pressure spring 15 assists the closing movement of the nozzle needle 5.
  • the nozzle needle 5 can continue to stand out from its needle seat 8.
  • the lifting of the nozzle needle 5 from the needle seat 8 can in a space 38, from which the at least one spray hole 3 goes off and is limited by retracted into the needle seat 8 nozzle needle 5 formed by a needle tip 7 seat surface 39, an increasing pressure build up.
  • the forces acting in the opening direction on the needle dressing 6 increase, which additionally accelerates the opening movement of the nozzle needle 5.
  • This has the consequence that the volume of the control chamber 18 decreases faster than the volume of the coupler chamber 22 increases.
  • the bypass piston 25 lifts off from the stop 32 and in particular enters the storage space 28.
  • the new, second transmission ratio is defined by the ratio of the control surface 17 to the total area of translator surface 21 and alternate surface 26.
  • the stroke of the booster piston 12 together with the stroke of the Ausweichkolbens 25 thus produce a relatively large stroke adjustment of the nozzle needle 5.
  • results for the nozzle needle 5 a particularly high opening speed, wherein in addition a comparatively large opening stroke can be realized.
  • due to the large second opening ratio at the same time the required stroke of the actuator 13 remain relatively small, so that the actuator 13 and thus the injector 1 can build comparatively small.
  • the injection nozzle 1 are thus control surface 17, translator 21, alternate surface 26, memory surface 27, the maximum possible Aktorhub and the maximum possible Düsennadelhub coordinated so that when Hubver ein of the actuator 13 to open the nozzle needle 5, the described two-phase or two-stage stroke adjustment for the nozzle needle 5 sets.
  • the bypass piston 25 bears against its stop 32.
  • the gear ratio is relatively small.
  • the bypass piston 25 moves away from its stop 32 during the second phase or second stage.
  • the associated gear ratio is relatively large.
  • the storage space 28 is subdivided into a first storage subspace 40 and into a second storage subspace 41 for this purpose.
  • a throttle piston 42 is provided, which is drive-coupled with the bypass piston 25 at least for the transmission of compressive forces.
  • the throttle piston 42 is also mounted in a stroke-adjustable manner in the booster piston 12 and contains a throttle path 43 which hydraulically couples the two storage subspaces 40 and 41 throttled.
  • the throttling path 43 expediently has a throttle 44 which is arranged between a longitudinal bore 45 which opens into the second storage subspace 41 and a transverse bore 46 which opens into the first storage subspace 40.
  • the throttle piston 42 is fixedly connected to the bypass piston 25.
  • the storage area 27 is divided into a first storage partial area 47 and a second storage partial area 48.
  • the first memory sub-area 47 is at least in the variants of FIGS. 2 and 3 formed directly on the bypass piston 25 and limits the first storage part space 40.
  • the second memory sub-area 28 is formed on the throttle piston 42 and limits the second memory sub-area 41st
  • the embodiment according to Fig. 3 differs from the one according to Fig. 2 in that the throttle path 43 has its path end radially on the throttle piston 42.
  • the throttle 44 forms this path end here.
  • the throttle piston 42 includes a bypass path 49, which is realized here by a connecting bore 50 between the longitudinal bore 45 and the transverse bore 46.
  • the bypass path 49 thus bypasses the throttle path 43 and is here also equipped with a non-return valve 51, which blocks when retracting the throttle piston 42 into the second storage subspace 41.
  • the throttle path 43 is controlled in dependence on the Drosselkolbenhubs.
  • the fuel volume is first displaced from the second storage subspace 41 through the throttle path 43 into the first storage subspace 40.
  • the check valve 51 locks in this movement, the connecting hole 50. From a certain retraction stroke passes over a control edge 52 of the booster piston 12 said path end, so here the throttle 44, whereby the throttle path 43 is locked.
  • the embodiment according to Fig. 4 also has a throttled path 43 controlled by the throttle piston stroke and a bypass path 49 with a check valve 51.
  • the embodiment according to FIG Fig. 4 differs from those according to the FIGS. 2 and 3 in that the throttling piston 42 and the deflecting piston 25 are separate components which lie only loosely against one another.
  • the return spring 31 drives the throttle piston 42 and via this the bypass piston 25 at.
  • the bypass path 49 here has an axial mouth end 53, which is closed at an axial contact between the escape piston 25 and throttle piston 42. When retracting the bypass piston 25 in the storage chamber 28, this is supported on the throttle piston 42 and drives it to retract into the second storage subspace 41.
  • bypass path 49 Because the bypass path 49 is closed, the throttle path 43 is active and the retraction of the bypass piston 25 is throttled. To extend the bypass piston 25 can lift off the throttle piston 42, whereby the bypass path 49 is opened. The bypass piston 25 can thereby extend relatively quickly and relatively undamped and occupy its starting position with abutment against the stop 32.
  • the throttle piston 42 follows, driven by the return spring 31.
  • a further throttle 54 may be arranged.
  • the non-return valve 51 is formed by the interaction of escape piston 25 and throttle piston 42.
  • the first storage subarea 47 is itself designed on the bypass piston 25. Depending on the tightness of a supported on the bypass piston 25 head 55 of the throttle piston 42, this first memory sub-area 47 may also be formed on this head 55.
  • the injection nozzle 1 can also be equipped with an escape path 56 in the region of the bypass piston 25.
  • This escape path 56 is formed in the embodiments shown here by an escape passage 57 which penetrates the bypass piston 25 from the storage surface 27 to the escape surface 26 and is arranged in particular coaxially in this.
  • the escape path 56 and the escape passage 57 may also have any other shape and arrangement.
  • the escape path 56 may be formed by a deflection channel 57 arranged obliquely in the bypass piston 25.
  • the escape path 56 is designed so that it is adjacent to the stop 32 Evasive piston 25 is locked.
  • the blocking effect of the escape path 56 in the initial state of the bypass piston 25, ie in abutment against the abutment 32 bypass piston 25 is achieved in the preferred embodiments shown here, characterized in that the bypass piston 25 has an annular sealing zone 58 on its alternate surface 26.
  • This sealing zone 58 encloses an opening 59 of the escape channel 57, which is associated with the escape surface 26 and lies in this.
  • the bypass piston 25 abuts against the stop 32 with its sealing zone 58.
  • the sealing zone 58 thereby separates the escape path 56 from the coupler space 22 tightly.
  • Deviating from the central arrangement of Dodge channel 57 in the Fig. 5 to 7 may in another embodiment Ausweichkolben 25 and / or intermediate plate 11 be configured such that the sealing surface 58 is on any other diameter, for example, on the outer diameter of the bypass piston 25.
  • the escape path 56 may be throttled.
  • the throttle path 56 contains a throttle 60 for this purpose.
  • the throttle 60 is arranged in the escape passage 57.
  • the escape path 56 may optionally be configured such that it is blocked at a predetermined or a predetermined deviation stroke of the bypass piston 25, in which the bypass piston 25 moves into the storage space 28.
  • a storage space check valve 61 which blocks the escape path 56, here the escape channel 57 when the predetermined deviation stroke is reached.
  • the storage space valve 61 comprises, for example, a valve member 62, which cooperates with a circular valve seat 63.
  • the valve seat 63 is formed on the bypass piston 25, specifically on the storage area 27 thereof.
  • the valve seat 63 encloses an opening 64 of the bypass channel 57, which is assigned to the storage area 27, ie lies in the latter.
  • valve member 62 Upon reaching the predetermined Ausweichhubs the valve member 62 moves into its valve seat 63 and blocks said opening 64 of the escape passage 57 tightly.
  • the valve member 62 is here exemplarily equipped with a flat end face; the valve seat 63 is shaped to be complementary. Alternatively, the valve member 62 may also have any other suitable shape, such as a conical shape or a spherical shape; the valve seat 63 is then formed in each case complementary.
  • the throttle 60 and the throttling of the alternate path 56 serves to ensure that the pressure compensation between the coupler chamber 22 and storage space 28 throttled at the desired switching from the first ratio to the second ratio, that the bypass piston 25 can stand properly from the stop 32 and for the duration the injection process remains lifted.
  • the storage space check valve 61 for the second phase or second stage of the needle opening can ensure that the pressure compensation between the coupler space 22 and the storage space 28 is terminated when the escape stroke of the escape piston 25 is reached. This also makes it possible to avoid premature return of the bypass piston 25 against its stop 32.

Claims (10)

  1. Injecteur pour moteur à combustion interne équipant notamment un véhicule automobile comprenant :
    - un corps de buse (2) muni d'au moins un orifice d'éjection (3),
    - une aiguille d'injecteur (5) montée mobile en translation dans le corps de buse (2) et commandant au moins un orifice d'éjection (3) pour l'injection du carburant,
    - un piston démultiplicateur (12) coopérant dans le sens de l'entraînement avec un actionneur (13) et ayant une surface de démultiplication (21),
    - l'aiguille d'injecteur (5) ou la liaison d'aiguille (6) entourant l'aiguille d'injecteur (5) présente une surface de commande (17) couplée hydrauliquement à la surface de démultiplication (21),
    caractérisé en ce que
    - un piston d'échappement (25) est monté de façon mobile en translation dans le piston démultiplicateur (12),
    - le piston d'échappement (25) présente une surface d'échappement (26) couplée hydrauliquement à la surface de démultiplication (21),
    - le piston d'échappement (25) s'applique contre une butée fixe (32) par rapport au corps de buse (2) dans l'état initial lorsque l'aiguille d'injecteur (5) ferme au moins un orifice d'éjection (3),
    - le piston d'échappement (25) présente une surface d'accumulation (27) qui délimite une chambre d'accumulation (28) réalisée dans le piston démultiplicateur (12).
  2. Injecteur selon la revendication 1,
    caractérisé en ce que
    - la surface de démultiplication (21) délimite une chambre de couplage (22),
    - la surface de commande (17) délimite une chambre de commande (18),
    - la chambre de couplage (22) et la chambre de commande (18) sont soit des chambres séparées reliées hydrauliquement par un chemin de commande (23), soit une chambre commune.
  3. Injecteur selon la revendication 2,
    caractérisé en ce que
    le volume de la chambre d'accumulation (28) est supérieur au volume formé par la réunion de la chambre de couplage (22) et de la chambre de commande (18).
  4. Injecteur selon les revendications 1 à 3,
    caractérisé en ce que
    - la surface d'échappement (26) délimite la chambre de couplage (22) délimitée également par la surface de démultiplication (21) et/ou
    - la surface de commande (17), la surface de démultiplication (21), la surface d'échappement (26), la surface d'accumulation (27), la course d'actionnement maximale possible et la course d'aiguille d'injecteur maximale possible, sont définies entre elles pour qu'un déplacement de l'actionneur (13) pour ouvrir l'aiguille d'injecteur (5), produise un déplacement à deux niveaux de l'aiguille d'injecteur (5),
    - le piston d'échappement (25) s'appliquant contre la butée (32) au cours de la première étape et s'éloignant de la butée (32) pendant la seconde étape.
  5. Injecteur selon les revendications 1 à 4,
    caractérisé en ce que
    - la chambre d'accumulation (28) est subdivisée en une première chambre partielle d'accumulation (40) et en une seconde chambre partielle d'accumulation (41),
    - un piston d'étranglement (42) est prévu, couplé dans le sens de l'entraînement, au piston d'échappement (25) au moins pour transmettre les efforts de poussée, ce piston étant déplacé en translation dans le piston démultiplicateur (12) et il comporte l'une des deux chambres d'accumulation (40, 41) du chemin d'étranglement (43) de couplage hydraulique,
    - la surface d'accumulation (27) est subdivisée en une première surface partielle d'accumulation (47) délimitant la première chambre partielle d'accumulation (40) et en une seconde surface partielle d'accumulation (48) réalisée sur le piston d'étranglement (42) et délimitant la seconde chambre partielle d'accumulation (41).
  6. Injecteur selon la revendication 5,
    caractérisé en ce que
    - le chemin d'étranglement (43) comporte un organe d'étranglement (44),
    - le piston d'étranglement (42) comporte un chemin de dérivation (49) qui contourne l'organe d'étranglement (44) et comporte un clapet antiretour (51) bloquant la seconde chambre partielle d'accumulation (41) lors du mouvement de rentrée du piston d'étranglement (42).
  7. Injecteur selon la revendication 6,
    caractérisé en ce que
    - le piston d'échappement (25) et le piston d'étranglement (42) constituent des composants distincts,
    - le piston d'échappement (25) s'appuie contre le piston d'étranglement (43) lorsqu'il entre dans la première chambre partielle d'accumulation (40), et entraîne celui-ci lors de l'entrée dans la seconde chambre partielle d'accumulation (41),
    - le piston d'échappement (25), lorsque le piston d'étranglement (42) pénètre dans la seconde chambre partielle d'accumulation (41) ferme l'embouchure (53) du chemin de dérivation (49),
    - le piston d'échappement (25) se soulève du piston d'étranglement (42) lorsqu'il sort de la première chambre partielle d'accumulation (40) et ouvre l'embouchure (53) du chemin de dérivation (49).
  8. Injecteur selon les revendications 5 à 7,
    caractérisé en ce que
    - le chemin d'étranglement (43) est commandé en fonction de la course du piston d'étranglement, et/ou
    - le chemin d'étranglement (43) comporte une extrémité de chemin associée radialement au piston d'étranglement (42), et le piston d'étranglement (42) pénètre dans la seconde chambre partielle d'accumulation (41) jusqu'à fermer le chemin d'étranglement (43), jusqu'à ce que l'arête de commande (52) réalisée sur le piston de démultiplication (12) passe sur l'extrémité du chemin.
  9. Injecteur selon les revendications 1 à 8,
    caractérisé en ce que
    lorsque le piston d'échappement (25) est soulevé par rapport à la butée (32), un chemin d'échappement (56) couple hydrauliquement la surface d'accumulation (27) à la surface d'échappement (26) et ferme ce couplage lorsque le piston d'échappement (25) est en appui contre la butée (32).
  10. Injecteur selon la revendication 9,
    caractérisé en ce que
    - le chemin d'échappement (56) est formé par un canal d'échappement (57) traversant le piston d'échappement (25) en partant de la surface d'accumulation (27) jusqu'à la surface d'échappement (26), et/ou
    - le piston d'échappement (25) présente sur sa surface d'échappement (26), une zone d'étanchéité (58), annulaire, par laquelle le piston d'échappement (25) s'appuie contre la butée (32) en position de sortie et qui entoure une ouverture (59) du canal d'échappement (57) associé à la surface d'échappement (26), et/ou
    - le chemin d'échappement (56) et/ou le canal d'échappement (57) sont étranglés ou comportent un organe d'étranglement (60), et/ ou
    - le chemin d'échappement (56) et/ou le canal d'échappement (57) sont fermés pour une certaine course d'échappement du piston d'échappement (25), dirigée dans la chambre d'accumulation (28) ou à partir d'une course d'échappement prédéterminée, et/ ou
    - il est prévu une soupape de fermeture de la chambre d'accumulation (61) qui, lorsqu'on atteint la course d'échappement, ferme le chemin d'échappement (56) et/ou le canal d'échappement (57), et/ou
    - un organe de soupape (62) de la soupape de fermeture de la chambre d'accumulation (61) coopère avec un siège de soupape (63) de forme circulaire réalisé dans la surface d'accumulation (27) et entourant une ouverture (64) du canal d'échappement (57) associé à la surface d'accumulation (27).
EP05825330A 2005-02-18 2005-12-21 Injecteur Not-in-force EP1853813B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005007542 2005-02-18
DE102005026514A DE102005026514B4 (de) 2005-02-18 2005-06-09 Einspritzdüse
PCT/EP2005/057047 WO2006087046A1 (fr) 2005-02-18 2005-12-21 Injecteur

Publications (2)

Publication Number Publication Date
EP1853813A1 EP1853813A1 (fr) 2007-11-14
EP1853813B1 true EP1853813B1 (fr) 2008-11-19

Family

ID=35965968

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05825330A Not-in-force EP1853813B1 (fr) 2005-02-18 2005-12-21 Injecteur

Country Status (6)

Country Link
US (1) US20080093484A1 (fr)
EP (1) EP1853813B1 (fr)
JP (1) JP2008530438A (fr)
AT (1) ATE414848T1 (fr)
DE (2) DE102005026514B4 (fr)
WO (1) WO2006087046A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006004645B4 (de) * 2006-01-31 2012-09-06 Man Diesel & Turbo Se Kraftstoffinjektor
EP2175124B1 (fr) 2006-10-16 2014-09-24 Ganser-Hydromag AG Injecteur de carburant pour moteurs à combustion interne
DE102006053287A1 (de) * 2006-11-13 2008-05-15 Robert Bosch Gmbh Kraftstoffinjektor
JP4618257B2 (ja) * 2007-01-17 2011-01-26 株式会社デンソー 燃料噴射弁
JP4333757B2 (ja) * 2007-03-13 2009-09-16 株式会社デンソー 燃料噴射弁
JP4386928B2 (ja) * 2007-04-04 2009-12-16 株式会社デンソー インジェクタ
DE102007021326A1 (de) * 2007-05-07 2008-11-13 Robert Bosch Gmbh Druckverstärkungssystem für mindestens einen Kraftstoffinjektor
DE102008001330A1 (de) * 2008-04-23 2009-10-29 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102008041561B4 (de) 2008-08-26 2022-05-19 Robert Bosch Gmbh Kraftstoffinjektor sowie Auslegungsverfahren für einen Kraftstoffinjektor
DE102009000181A1 (de) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Kraftstoff-Injektor
EP2602476A1 (fr) * 2011-12-07 2013-06-12 Continental Automotive GmbH Moyen d'ensemble formant soupape pour soupape d'injection et soupape d'injection
DE102015226326A1 (de) * 2015-12-21 2017-06-22 Robert Bosch Gmbh Hydraulische Kopplereinrichtung und Kraftstoffeinspritzventil mit einer solchen

Family Cites Families (7)

* 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
EP0262539B1 (fr) * 1986-09-25 1991-01-09 Ganser-Hydromag Soupape d'injection de combustible
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
US5875764A (en) * 1998-05-13 1999-03-02 Siemens Aktiengesellschaft Apparatus and method for valve control
DE10326046A1 (de) * 2003-06-10 2004-12-30 Robert Bosch Gmbh Einspritzdüse für Brennkraftmaschinen
DE102005008972A1 (de) * 2005-02-28 2006-08-31 Robert Bosch Gmbh Einspritzdüse

Also Published As

Publication number Publication date
DE102005026514A1 (de) 2006-08-24
EP1853813A1 (fr) 2007-11-14
JP2008530438A (ja) 2008-08-07
US20080093484A1 (en) 2008-04-24
WO2006087046A1 (fr) 2006-08-24
ATE414848T1 (de) 2008-12-15
DE502005006031D1 (de) 2009-01-02
DE102005026514B4 (de) 2008-12-24

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