EP2035686B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2035686B1
EP2035686B1 EP07728615A EP07728615A EP2035686B1 EP 2035686 B1 EP2035686 B1 EP 2035686B1 EP 07728615 A EP07728615 A EP 07728615A EP 07728615 A EP07728615 A EP 07728615A EP 2035686 B1 EP2035686 B1 EP 2035686B1
Authority
EP
European Patent Office
Prior art keywords
pressure
diaphragm
shells
fuel injector
diaphragm capsule
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
EP07728615A
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German (de)
English (en)
Other versions
EP2035686A1 (fr
Inventor
Dieter Junger
Nadja Eisenmenger
Christian Faltin
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 EP2035686A1 publication Critical patent/EP2035686A1/fr
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Publication of EP2035686B1 publication Critical patent/EP2035686B1/fr
Not-in-force legal-status Critical Current
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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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from injectors
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the present invention relates to a fuel injector according to the preamble of claim 1.
  • Fuel injectors of the type of interest serve to control the fuel which is injected into the combustion chamber in an internal combustion engine. They are essentially composed of a solenoid valve and a miniservovalve, and actuate a nozzle needle whose opening and closing position is controlled by the solenoid valve, so that injection holes are opened and closed in the injector for injecting the fuel.
  • a fuel injector for injecting fuel into a combustion chamber with a solenoid valve in which upon actuation of the solenoid valve, a control line from a high-pressure fuel to a return pressure in a return line is relieved.
  • a pressure oscillation damping device is provided which dampens pressure fluctuations arising during the termination of the fuel injection by the control of the high-pressure fuel in the low-pressure region.
  • the pressure oscillation damping device is arranged outside of the fuel injector in the return line and has a diaphragm can as a damping element with a balloon-shaped or pillow-shaped elastically compressible membrane.
  • a force injector is disclosed, which is designed with a solenoid valve for controlling the miniservovalve with an armature which can be applied to a valve seat in the lower armature space.
  • the lower armature space is in fluid communication via bores with a control pressure chamber, whereby leakage quantities occurring via at least one return borehole can be returned to a tank above the lower armature space.
  • means for reducing these pressure oscillations in the lower armature space are provided.
  • the means for reducing pressure fluctuations include recesses or internals to be machined in the lower armature space and an enlarged volume of the return bores or of the lower armature space.
  • certain affected by the return of the leakage quantities sections in the solenoid valve and in the injection valve in its volume can be increased.
  • Such an enlargement of the volume, with a defined outflow cross-section, results in a significant reduction of pressure oscillations, but the necessary injector-related volume can not be represented in the available installation space.
  • An essential disadvantage of the known designs of fuel injectors are those pressure oscillations that lead to different opening behavior of the Miniservoventils and thus can lead to volume fluctuations of the injected fuel.
  • Pressure oscillations that propagate through communicating holes in the adjacent solenoid valve space and the magnetic spring space cause a quantity map ripple, which also can not be satisfactorily reduced or avoided by means of the increased fluid volumes.
  • pressure limiting devices for limiting occurring peak pressure values in the fluidic system of a fuel injector. These relate to a fuel injector which has a high-pressure fuel pump with a pump piston driven in a stroke movement, which delimits a pump working chamber which is connected to at least one fuel injector, through which fuel is injected into the combustion chamber of the internal combustion engine. In this case, at least one connection of the pump working space with a discharge region is controlled by an electrically actuated control valve. By the pressure limiting device, a connection of the pump working chamber is opened with a discharge area when a predetermined pressure in the pump working space is exceeded.
  • the pressure limiting device has an elastically deformable membrane which is acted upon by the pressure prevailing in the pump working chamber and which opens the connection of the pump working chamber to the discharge region when the predetermined pressure in the pump working space is exceeded due to its elastic deformation.
  • a disadvantage of the proposed pressure limiting device is the outflow of the fuel into a discharge area, which forms the formation of a closed Systems, ie the integration of the pressure relief device in the closed fluidic system of the return bores without leakage current not possible.
  • the invention includes the technical teaching that the means for reducing pressure oscillations comprise at least one diaphragm can, which is accommodated in a recess which is fluidically connected to the at least one return bore.
  • the integration of a membrane can and the fluidic connection to the return bore have the advantage that the maximum fuel pressure is limited to the level of the maximum diaphragm clamping pressure, whereby the pressure oscillations can be reduced.
  • the flow velocity in the return bore is limited due to the volume taken up or discharged by the membrane can, whereby smaller cross sections of the return bores can be realized. If the pressure in the recess increases, the internal volume decreases due to the deflection of the membrane shells of the diaphragm can. This effect limits the maximum pressure during the pressure oscillations.
  • the diaphragm shells expand again due to the internal pressure within the diaphragm cell and additionally because of the elastic restoring force of the diaphragm shells, so that overall a smoothing of the pressure fluctuations and thus a smoothing of the quantity characteristic waviness can be achieved.
  • the return bores extend from the lower region of the flat seat into the region of the solenoid valve, wherein the portion of the return bore in the direction of the solenoid valve serves as a connecting line into the magnetic spring chamber. Due to the reduced pressure oscillations, the bounce behavior of the armature of the miniservovalve can be reduced or avoided, which enables an improved metering of the amount of fuel injected into the combustion chamber, and the closing behavior of the fuel injector in the final phase of the injection cycle is optimized. Due to the thus achieved improved quantification of the injected fuel quantity due to the minimized or avoided bounce behavior improved combustion of the fuel due to the optimized atomization of the fuel is reachable in the combustion chamber, resulting in a reduction of pollutant emissions.
  • the recess for receiving the diaphragm cell is advantageously designed as a circular depression in the wall of the injector, so that the diaphragm cell can be easily inserted from the outside into the recess formed as a recess.
  • a connecting channel allows fluid communication between the return bore and the recess to provide fluid communication between the recess and the return bore.
  • the closure element seals in the form of a cover, the recess to the outside in the injector body, wherein the closure element may be formed as a circular disc-shaped lid, which is mechanically secured by means of a shaft securing ring in the injector body and fluidly pressure sealed by a ring seal.
  • the biasing member may be made of a thin sheet metal material as an elastic, plate spring-like, circular disk-shaped element, so that the pressure cell is clamped in the region of its circumference by the biasing member against the inside of the closure element.
  • the diaphragm cell is constructed from two circular membrane shells, which are pressure-tight radially circumferentially joined together.
  • the joint connection can advantageously be designed as a welded joint, wherein the membrane box is radially radially positioned and biased in the region of the weld seam of the two membrane shells between the biasing member and the inside of the closure element.
  • a further embodiment of the invention provides that the recess for receiving the diaphragm cell is accommodated in a separate damper housing, wherein the damper housing is arranged on the injector housing and is fluidically connected to the return line.
  • the execution of the means for reducing pressure oscillations in a separate damper housing offers the possibility to arrange the diaphragm can outside the injector body, and the recess in which the diaphragm cell is added to fluidly connect to the system of return bores.
  • the damper housing comprises an interior which is formed by means of a closure element to a closed recess for receiving the diaphragm cell, wherein stops are provided which receive the diaphragm can on the circumference of the weld and radially center. At the closure element and the stop itself stop surfaces are provided which limit the stroke of the membrane shells of the diaphragm cell. Thus, overload, i. a plastic deformation of the membrane shells are avoided.
  • the biasing element is designed to be adjustable in the embodiment of the damper housing, so that the stop, which is integrally formed on the biasing element, is adjustable.
  • the circular membrane shells have a concentric wave structure to increase the compliance. Due to the wave structure, the value of membrane cup deflection may be increased due to the lower compliance and thus the extended elastic range to maximize the maximum volume difference between a maximum pressure and a minimum pressure within the recess.
  • the volume difference relates to the maximum or minimum volume of the interior of the diaphragm cell.
  • the wave structure runs concentrically around the central axis of the circular membrane can and can For example, four wave peaks or troughs include. Concerning the arrangement of the membrane shells to form the membrane can each other on the one hand the opportunity is offered to arrange the two circular membrane shells mirror images of each other, so that the wave structure of the membrane shells against each other and the membrane cell has a symmetrical design.
  • the two circular membrane shells to form the diaphragm cell are arranged parallel, ie in the same direction to each other, so that the wave structure of the membrane shell is rectilinear and the diaphragm cell has an asymmetrical design.
  • the membrane shells can be formed equal to each other, so that a small parts variance can be achieved.
  • the membrane shells can be welded in the mutually facing arrangement, so that the membrane box does not require a preferred installation direction due to their symmetry.
  • a minimum distance results which leads to a minimum thickness of the membrane can and comprises a relatively large volume within the membrane can.
  • the final pressure at a given intake volume ie the volume difference at maximum pressure and minimum pressure within the return bore
  • the limited by the space in their outer diameter diaphragm cell can take under life conditions only a limited intake volume.
  • the swallowing volume requirement decreases with increasing external pressure.
  • the reduction of the initial volume causes a steeper characteristic of the external pressure over the swallowing volume, whereby a higher external pressure can be achieved at the given intake volume.
  • a safe function is achieved even with small absorption volumes.
  • the contour of the membranes in the entire spring region have a small distance, which is made possible by an asymmetrical arrangement of the membrane shells. Due to the low output volume in the diaphragm cell and the resulting steeper pressure volume characteristic, the pressure force which the diaphragm can expands when the external pressure is reduced is reduced bulges, very quickly, whereby a lower load on the membrane shells and the weld in the uninstalled state or outside of the operation of the diaphragm cell is given.
  • a further advantageous embodiment of the present invention provides that the membrane can is filled with helium and has a gas pressure which is greater than the return pressure in the return line or in the recess connected to the return line. If helium is selected as the gas which fills the membrane can, the sealing of the membrane shells is reliably possible and at the same time leads to more favorable properties of the gas state change. Helium has a high adiabatic exponent, with a steeper pressure rise characteristic compared to the isothermal basic design in highly dynamic processes.
  • the diaphragm cell on a stroke limitation which is introduced inside the diaphragm cell.
  • the stroke limiter in this case comprises stirrup elements, which are arranged interlocking, so that this limits both the membrane shells merging membrane shell deflection and the membrane shells divergent Membranschalen vombiegung.
  • the stirrup elements can be welded into the membrane shells on the inside, and have a C-shaped profile structure, which in each case engage one another in opposite directions.
  • the membrane shells bulge outwards, the bending movement of the outer curvature is limited by engagement of the C-shaped profiles of the hoop elements, wherein the hoop elements have a height above the inner side of the membrane shells, which also limit a deflection of the membrane shells inward.
  • the possibility is created by simple means to limit a stroke limitation both as a deflection inward and a bulge of the membrane shells to the outside, without providing external elements to the diaphragm cell.
  • the stirrup elements in the respective membrane shell can be formed equal to one another in order to minimize the parts variance in this case as well, whereby an asymmetrical design of the elements of the stroke limitation within the membrane shells is also possible.
  • the fuel injector 1 comprises an armature 3 and a valve seat 4, wherein the latter separates an armature space 5 from a control chamber of the miniservovalve 2.
  • the armature 3 moves upward in the vertical direction, so that the valve seat 4 in the lower armature space 5 opens.
  • This valve seat 4 is in turn via one or more holes in fluid communication with a control pressure chamber of the miniservovalve 2.
  • the pressure in the control pressure chamber of the miniservoval valve decreases, fluid via the holes in the direction of the valve seat 4 from there into the lower Anchor space 5 flows.
  • the nozzle needle (not shown here) of the fuel injector which is constantly exposed to an acting in the opening direction of high pressure, set in motion, whereby the injection holes are opened and the fuel injector can inject fuel into the combustion chamber.
  • return bores 8 are introduced, wherein the system of the return bores 8 connect to a flat seat 6, and wherein 6 pressure oscillations within the return bore 8 can occur due to the opening or closing movement of the flat seat. Therefore, these are fluidically connected to a recess 10 and act on a diaphragm cell 9, which is incorporated within the recess 10.
  • the recess 10 is arranged on the outside in the injector body 7, and sealed pressure-tight by means of a closure element 12.
  • the injector on the flat seat 6 of the miniservovalve 2 now relieves the control line from rail pressure to return pressure, a high volume flow within the return bore 8 initially arises. This is passed on to the recess 10, so that the diaphragm can 9 is pressurized and the membrane shells are arched inwards , This reduces the inner volume of the diaphragm cell 9, and occurring pressure peaks within return bores 8 are reduced. If, on the other hand, the pressure within the return bore 8 drops, the membrane shells of the membrane can 9 expand again, so that overall the pressure fluctuations are smoothed out.
  • the membrane box 9 is arranged between the closure element 12 and a biasing element 13, which press the membrane shells of the membrane box each on each other to relieve the weld between the membrane shells.
  • FIG. 2 shows an enlarged section of the recess 10 within the injector body 7.
  • the membrane box 9 is arranged, which is formed from a first membrane shell 14 and a second membrane shell 15. If the fuel then flows through the return bore 8 into the recess 10, it first passes into a first space 21, which passes through recesses 29 and 30 within the injector body 7 or the Closure element 12 is possible.
  • a second space 22 is also pressurized with fuel pressure, which is directly connected to the return bore 8. Now increases the pressure within the spaces 21, 22, so the membrane shells 14 and 15 directed towards each other inwardly, so that the volume decreases within the diaphragm cell 9.
  • the deflection of the membrane shells 14 and 15 is limited by a stroke limiter 16, which consists of a first bracket member 17 and a second bracket member 18.
  • the ironing elements have a C-shaped profile, so that they each abut against the inside of the membrane shells 14, 15 and thereby limit the lifting movement.
  • the bracket elements 17 and 18 engage each other when the pressure in the spaces 21, 22 decreases, and the membrane shells 14 and 15 bulge outwards.
  • the membrane box 9 is clamped between a biasing member 13 and the closure member 12, wherein the clamping takes place radially circumferentially at the height of the weld 19 to relieve them due to the bias between the biasing member 13 and the closure member 12.
  • the biasing element 13 is shown in a flying and unbiased condition.
  • the closure element 12 is sealed by means of a sealing element 20 with respect to the outside of the injector body 7, which consists for example of an O-ring.
  • stops 23 and 24 are provided both in the injector body 7 and in the closure element 12, to which the membrane shells 14 and 15 abut outwardly at a curvature of the membrane shells 14, 15.
  • the inner stroke limiter 16 and the outer stroke limiter with the stops 23 and 24 are for simultaneous presentation both in the FIG. 2 shown, for a technical implementation of the arrangement one of the two stroke limits is sufficient.
  • the stops are optionally formed by the housing 7 and the closure element 12 or by the biasing element 13 and the receiving element 28 (see FIG. 3 ).
  • FIG. 2a shows a further embodiment for receiving, limiting and biasing the diaphragm cell 9.
  • the biasing member 13a has at least three exhibitions 32, which relieve the weld seam 19 by elastic bias and simultaneously hold the diaphragm cell 9 in position. Through the exhibitions 32 forms in the enclosure 31 a recess, whereby the space 22 directly and the Room 21 communicates with the return bore 8 via the recess 29a.
  • a latching 33 is formed, which preferably engages in the sealing ring groove of the closure element 12a and produces a positive connection.
  • a stop 24a is formed, which cooperates with the closing element 12a formed on the stop 23a and can be used both for Loslaufdruckvorschreib and to the Hubbegrenzung.
  • the latch 33 is secured by the boundary of the enclosure 31 in the recess 10.
  • the diaphragm mount which is independent of the injector body 7, permits precise pretensioning and idling pressure adjustment and stroke limitation to the outside.
  • the damper assembly 34 provides a high process reliability, since the assembly is not hidden, no collision contours are present in the injector body and a lack of eg the diaphragm cell 9 is reliably detected.
  • the comparatively sensitive diaphragm cell 9 is protected in the damper assembly 34 and independently testable.
  • the damper assembly 34 consists of the closure element 12a, the membrane box 9, the biasing member 13a and the sealing member 20 and is pressure-tight received in the recess 10 of the injector body 7 to the outside, the diaphragm box is on all sides fluidly connected to the return bore 8 in combination.
  • the circular disc-shaped biasing element 13a adopts both the preload to relieve the weld 29 and the function of the Loslauftikvorschreib and stroke limitation.
  • the elastic bias is carried out by at least three flared areas, which lie close to the welding seam on the diaphragm cell.
  • FIG. 3 shows a further embodiment of the means for reducing pressure oscillations, wherein these comprise a diaphragm box 9, which is arranged within a damper housing 11.
  • the damper housing 11 is in turn disposed on the injector body 7, and fluidly and mechanically connected thereto.
  • the mechanical connection comprises a screw connection, wherein the fluidic connection takes place via internal channels into the recess 10 within the damper housing 11 with the system of the return bore 8.
  • the diaphragm cell 9 is received within the damper housing 11 and arranged by means of a closure element 12 in this fixed.
  • a receiving element 28 is provided, which is also formed circular disk-shaped and has a stop 25 in the center.
  • a further biasing element 27 is provided, which end in the direction of the diaphragm cell 9 has an opposite stop 26.
  • the closure element 12 is screwed inside the damper housing 11 and sealed pressure-tight by means of seals.
  • the biasing member 27 is disposed centrally within the closure member 12 and designed as a kind of screw to adjust this by a screwing movement in the direction of the diaphragm cell 9 and removed to this.
  • the centrally arranged stop 25 is formed on the receiving element 28 and acts counter to the abutment 26 of the biasing member 27.
  • FIG. 5 Each different embodiments of the stroke limiter 16 are shown in the diaphragm cell 9.
  • the stroke limiter 16 has C-shaped bracket elements 17 and 18, which engage in one another in such a way that both an inwardly directed membrane deflection and an outwardly directed membrane deflection can be limited.
  • the stroke limitation is in FIG. 5 formed asymmetrically, which is another embodiment of the same. This includes a T-shaped bracket member 17 and each bracket-shaped bracket elements 18, which also engage in such a way and limit an inwardly directed and an outward deflection of the diaphragm shells 14 and 15.
  • the membrane shells 14 and 15 are joined together by a radially circumferential weld 19.
  • FIG. 6a each show a symmetrical and an asymmetric design of the membrane can 9.
  • the membrane shells 14 and 15 are formed equal to each other, so that they are mirror images each rotated by 180 ° to each other and are welded together.
  • the membrane shells 14 and 15 according to FIG. 6b an asymmetrical design, so that the wave structure within the membrane shells are uniform and the overall height in the membrane box 9 is reduced.
  • the membrane shells 14 and 15 each have three shafts, which are formed concentrically around the central axis of the membrane boxes 9, wherein also a different number of waves can be introduced into the membrane shells, which depends on the diameter of the membrane box and the thickness of the sheet material of the membrane shells ,
  • the wave structure enlarges the elastic region for bending the membrane shells 14 and 15, and substantially avoid damage or overloading of the membrane shells (14, 15) and the weld seam 19.
  • the invention is not limited in its execution to the above-mentioned preferred embodiment. Rather, a number of variants is conceivable, which makes use of the illustrated solution even with fundamentally different types of use.

Claims (8)

  1. Injecteur de carburant pour l'injection de carburant dans une chambre de combustion, comprenant une électrovanne (1) prévue pour commander une miniservovalve (2) comprenant un induit mobile (3) qui peut être appliqué de manière hermétique sur un siège de soupape (4) dans l'espace d'induit (5) inférieur, la miniservovalve (2) étant en outre reçue dans un corps d'injecteur (7) et fermant hermétiquement une conduite de commande vis-à-vis d'un siège plat (6) au moyen duquel, lors d'un actionnement de l'électrovanne (1), la conduite de commande peut être détendue par une haute pression de carburant à une pression de retour dans au moins une conduite de retour (8), des moyens étant prévus pour réduire les oscillations de pression dans l'au moins une conduite de retour (8), et les moyens pour réduire les oscillations de pression comprenant au moins une boîte formant membrane (9), qui est reçue dans un évidement (10), caractérisé en ce que l'évidement (10) est amené en liaison fluidiquement avec l'au moins une conduite de retour (8) et est pratiqué dans le corps d'injecteur (7) de sorte que la boîte formant membrane (9) puisse être intégrée dans le corps d'injecteur (7), et en ce que l'évidement (10) est rendu étanche de manière étanche à la pression au moyen d'un élément de fermeture (12), un élément de précontrainte (13) étant disposé dans l'évidement (10) à côté de la boîte formant membrane (9), lequel élément de précontrainte précontraint mécaniquement la boîte formant membrane (9) sur la périphérie du joint des coques de membrane (14, 15) contre l'élément de fermeture (12).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que la boîte formant membrane (9) présente deux coques de membrane (14, 15) en forme de disques circulaires, lesquelles sont assemblées de manière étanche à la pression radialement sur leur périphérie mutuelle.
  3. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que l'évidement (10), en vue de recevoir la boîte formant membrane (9), est reçu dans un boîtier amortisseur séparé (11), le boîtier amortisseur (11) étant disposé sur le boîtier d'injecteur (7) et étant connecté fluidiquement à la conduite de retour (8).
  4. Injecteur de carburant selon la revendication 1, 2 ou 3,
    caractérisé en ce que les coques de membrane (14, 15) en forme de disques circulaires présentent une structure ondulée concentrique, afin d'augmenter la flexibilité des coques de membrane (14, 15).
  5. Injecteur de carburant selon la revendication 4,
    caractérisé en ce que les coques de membrane (14, 15) en forme de disques circulaires sont disposées suivant une symétrie spéculaire pour former la boîte formant membrane (9), de sorte que la structure ondulée des coques de membrane (14, 15) s'étende en sens inverse et que la boîte formant membrane (9) présente une réalisation symétrique.
  6. Injecteur de carburant selon la revendication 4,
    caractérisé en ce que les coques de membrane (14, 15) en forme de disques circulaires, pour former la boîte formant membrane (9), sont disposées parallèlement l'une à l'autre, de sorte que la structure ondulée des coques de membrane (14, 15) s'étende dans le même sens et que la boîte formant membrane (9) présente une réalisation asymétrique.
  7. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que la boîte formant membrane (9) est remplie d'hélium et présente une pression de gaz qui est supérieure à la pression de retour dans la conduite de retour (8) ou dans l'évidement (10) connecté à la conduite de retour (8).
  8. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que la boîte formant membrane (9) comprend une limitation de course (16) qui est introduite du côté intérieur dans la boîte formant membrane (9).
EP07728615A 2006-06-16 2007-04-27 Injecteur de carburant Not-in-force EP2035686B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006027780A DE102006027780A1 (de) 2006-06-16 2006-06-16 Kraftstoffinjektor
PCT/EP2007/054160 WO2007144229A1 (fr) 2006-06-16 2007-04-27 Injecteur de carburant

Publications (2)

Publication Number Publication Date
EP2035686A1 EP2035686A1 (fr) 2009-03-18
EP2035686B1 true EP2035686B1 (fr) 2010-12-15

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07728615A Not-in-force EP2035686B1 (fr) 2006-06-16 2007-04-27 Injecteur de carburant

Country Status (6)

Country Link
US (1) US8038083B2 (fr)
EP (1) EP2035686B1 (fr)
JP (1) JP4878386B2 (fr)
AT (1) ATE491884T1 (fr)
DE (2) DE102006027780A1 (fr)
WO (1) WO2007144229A1 (fr)

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FR2929343A3 (fr) * 2008-03-31 2009-10-02 Renault Sas Circuit de retour de carburant pour dispositif d'injection de carburant et dispositif d'injection de carburant associe
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EP2385241B1 (fr) * 2010-05-04 2013-07-17 Continental Automotive GmbH Amortisseur de pulsation
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DE102010030626A1 (de) * 2010-06-29 2011-12-29 Robert Bosch Gmbh Pulsationsdämpferelement für eine Fluidpumpe und zugehörige Fluidpumpe
US8727752B2 (en) * 2010-10-06 2014-05-20 Stanadyne Corporation Three element diaphragm damper for fuel pump
DE102011008467B4 (de) * 2011-01-13 2014-01-02 Continental Automotive Gmbh Injektor mit Druckausgleichsmitteln
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ATE491884T1 (de) 2011-01-15
US8038083B2 (en) 2011-10-18
EP2035686A1 (fr) 2009-03-18
JP2009540206A (ja) 2009-11-19
US20090127356A1 (en) 2009-05-21
DE102006027780A1 (de) 2007-12-20
JP4878386B2 (ja) 2012-02-15
DE502007005966D1 (de) 2011-01-27
WO2007144229A1 (fr) 2007-12-21

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