EP2235356B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2235356B1
EP2235356B1 EP08871452.2A EP08871452A EP2235356B1 EP 2235356 B1 EP2235356 B1 EP 2235356B1 EP 08871452 A EP08871452 A EP 08871452A EP 2235356 B1 EP2235356 B1 EP 2235356B1
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EP
European Patent Office
Prior art keywords
control valve
approximately
angle
sealing line
annular face
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP08871452.2A
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German (de)
English (en)
Other versions
EP2235356A1 (fr
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2235356A1 publication Critical patent/EP2235356A1/fr
Application granted granted Critical
Publication of EP2235356B1 publication Critical patent/EP2235356B1/fr
Active 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
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
  • the fuel pressure can be influenced within a limited by an injection valve element control chamber.
  • the injection valve element is adjusted between an open position and a closed position, wherein the injection valve element releases the fuel flow into the combustion chamber of an internal combustion engine in its open position.
  • this comprises a sleeve-shaped control valve element which can be adjusted by means of an electromagnetic actuator and whose end-face sealing line interacts with a control valve seat.
  • the annular sealing line is formed directly on the inner guide diameter of the control valve sleeve.
  • the guide diameter of the sleeve-shaped control valve element corresponds to the outer diameter of an axially projecting into the control valve element bolt plus a minimum clearance.
  • the sealing line has a minimum width extension. This leads to extremely high surface pressures, which in turn leads to a strong flattening of the sealing edge by the high-momentum forces and by the friction between the control valve element and the control valve seat. This results in a decrease in the surface pressure, which in turn can lead to leaks in the control valve.
  • a switching valve for injectors is known in which the control valve member is in the form of a sleeve.
  • the sleeve-shaped control valve member may have on its inside a conical annular surface which limits the sealing edge of the control valve member.
  • the invention has for its object to propose an improved injector, in the leaks between the control valve element and the control valve seat, at least largely avoided.
  • the invention is based on the idea that the particular annular sealing line (sealing edge) of the injector with an (inner) diameter form, which is greater than the inner guide diameter.
  • the sealing line is not located directly on the inner bore of the control valve element, but is at a radial distance therefrom to the outside staggered.
  • the sealing line is located at the radially outer edge of a seat boundary of the control valve element.
  • the originally very sharp-edged sealing line will widen in the radial direction (plates), but preferably maximally to a radial extent between about 50 ⁇ m and 150 ⁇ m (depending on the actual acting pressures, diameter and forces). It is particularly advantageous that this widening takes place in contrast to the prior art in a trained according to the concept of the invention injector in the radial direction inwardly to the high pressure region, so that in the sequence reduces the pressure level during operation.
  • the sealing line is not directly adjacent to the boundary to the outer diameter of the control valve in the invention, but is relative to this with radial distance, ie radially offset inside, arranged.
  • the radial distance between the inner guide diameter and the sealing line in the new state of the injector is only about 20 microns to 120 microns, preferably about 30 ⁇ m to 100 microns.
  • a sealing line arranged on the inner circumference of the control valve element leads to plastic deformations, in particular at the control valve seat, and thereby reduces the strength values.
  • This is the case, in particular, in the case of control valve seats formed as a flat seat and in the case of conical control valve angles with a flat cone angle of approximately 120 ° and less than 180 °.
  • precisely designed control valve seats have significantly less slippage between the control valve element and the control valve seat, they are characterized by a low Reibverschl constituent. Therefore, the arrangement of the sealing line with radial distance to the inner guide diameter is particularly advantageous in combination with designed as a flat seat or a conical seat with a small cone angle control valve seats.
  • a cone angle is understood to be the angle between two diametrically opposite inclined sections of the cone, that is to say twice the angle between the conical surface and the longitudinal central axis of the control valve element.
  • an inner annular surface adjoins the sealing line radially inward, which is designed to be in the form of an inner cone, that is to say at an angle to the control valve seat, more precisely to the control valve seat surface.
  • a trained inner annular surface forms a seat boundary, whose radially outer boundary is formed by the sealing line.
  • the angle at which the inner annular surface of the control valve seat (Control valve seat surface) extends away between about 0.1 ° and about 50 °.
  • the angle is selected from a range between about 0.5 ° and about 5 °.
  • an advantage is an embodiment in which the inner annular surface, starting from the sealing line, extends radially as far as the inner guide diameter and does not adjoin an additionally innermost annular surface, which would run at an angle to the inner annular surface.
  • the seat boundary is formed radially inward of the edge between the inner annular surface and the guide portion of the control valve element, wherein the inner diameter of the edge corresponds to the guide diameter of the control valve element.
  • the angle which is spanned by the radially inner annular surface and an outer annular surface adjoining radially outside the sealing line is greater as 90 °.
  • the angle is greater than 100 ° selected.
  • Particularly preferred is an embodiment with an angle of about 120 °. It is also inverse cone shapes (inner cone), preferably with a corresponding angle of up to about - 120 °, realized.
  • control valve seat when the control valve seat is designed as a flat seat or as a conical seat with a flat cone angle, an embodiment is preferred in which the radially outside of the sealing line adjacent outer annular surface to the control valve seat, more precisely to the control valve seat surface, is inclined.
  • the angle should be such that on the one hand a sufficient seat limitation is ensured and on the other hand a support function for the sealing line is ensured.
  • the angle is between about 10 ° and about 50 °, in particular between about 20 ° and about 45 °.
  • the angle is about 30 °.
  • the angularly arranged to the control valve seat outer annular surface in the radial direction does not reach to the outer periphery of the control valve member, but in which the outer annular surface merges with radial distance to the sealing line in an outer annular surface.
  • this outer ring surface (outermost ring surface) lies in a plane perpendicular to the longitudinal central axis of the control valve element plane.
  • the radial extent of the outer, immediately adjacent to the sealing line, annular surface is selected so that the sealing line has a greater axial distance to the radially outermost edge of the outer annular surface than the radially innermost edge of the inner annular surface.
  • the outer annular surface is not inclined to the control valve seat (control valve seat surface), but lies in such a plane.
  • the outer annular surface may preferably extend in the radial direction to the outer diameter of the control valve element in this design.
  • the non-oblique arrangement of the outer annular surface is particularly advantageous for designed as a conical seat control valve seats.
  • the angle between the outside of the sealing line adjacent annular surface and the control valve seat is greater than the angle between the radially inner adjacent to the sealing surface annular surface and the control valve seat.
  • the sealing line of the injector especially after a certain period, at most a radial extent of 150 .mu.m, preferably less than 50 .mu.m.
  • the radial extent of the sealing edge immediately after the new production of the injector (substantially) smaller than 50 microns.
  • Fig. 1 a designed as a common rail injector injector 1 for injecting fuel into a combustion chamber of an internal combustion engine (not shown) of a motor vehicle is shown.
  • a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail).
  • this fuel especially diesel or gasoline, is stored under high pressure of about 2000 bar in this embodiment.
  • the injector 1 is connected to other, not shown, injectors via a respective supply line 5.
  • the supply line 5 opens into a pressure chamber 6 of the injector 1.
  • a return line 7 a low-pressure region 8 of the injector 1 is connected to the reservoir 3. Via the return line 7, a later to be explained control amount of fuel from the injector 1 to the reservoir 3 flow.
  • an injection valve element 10 is arranged axially adjustable in this embodiment.
  • the injection valve element 10 is guided with a lower portion in a nozzle body 11, which is clamped by means of a union nut, not shown, against the injector body 9. With its upper section in the plane of the drawing, the injection valve element 10 is guided in an axially facing sleeve section 12 of a throttle plate 13.
  • the injection valve element 10 has at its tip 14 a closing surface 15 with which the injection valve element 10 can be brought into a tight contact with an injection valve element seat 16 formed inside the nozzle body 11.
  • an injection valve element seat 16 formed inside the nozzle body 11.
  • the injection valve member 10 abuts against its injection valve member seat 16, d. H. is in a closed position, the fuel outlet from a nozzle hole arrangement 17 is locked. If, on the other hand, it is lifted off its injection valve element seat 16, fuel can flow directly from the pressure chamber 6 via axial channels 18 formed on the outer circumference of the injection valve element 10 and the annular space 19 between the lower section of the injection valve element 10 and the nozzle body 11 past the injection valve element seat 16 to the nozzle hole arrangement 17 flow and there are essentially injected under high pressure (rail pressure) standing in the combustion chamber, not shown.
  • control chamber 21 is limited, the peripheral wall is bounded radially outwardly from the pressure chamber 6.
  • the control chamber 21 is connected via a radially extending in the sleeve portion 12 inlet throttle 22 with the pressure chamber 6.
  • the control chamber 21 is supplied with high-pressure fuel from the pressure chamber 6.
  • the control chamber 21 is connected via a, arranged in the upper, plate-shaped portion of the throttle plate 13, the drain passage 23 with outlet throttle 24 with a valve chamber 25, which is radially outwardly of a sleeve-shaped control valve element 26 of a control valve 27 (servo-valve) is limited. From the valve chamber 25, fuel can flow into the low-pressure region 8 of the injector when the control valve element 26 which can be actuated by an electromagnetic actuator 28 is lifted from its control valve seat 29, which is formed on the throttle plate 13, ie the control valve 27 is open.
  • the flow cross-sections of the inlet throttle 22 and the outlet throttle 24 are matched to one another such that when the control valve 27 is open, a net outflow of fuel (control amount) from the control chamber 21 via the valve chamber 25 in the low pressure region 8 of the injector 1 and from there via the return line. 7 resulted in the reservoir 3.
  • a pressure pin 30 is received, which receives the pressure forces acting in the axial direction within the valve chamber 25 and the valve chamber 25 seals in the axial direction in the plane of the drawing upwards.
  • the pressure pin 30 is supported on a closure lid 31, to which the pressure pin 30 passes through a holding body 32 for electromagnets 33 of the actuator 28 in the axial direction centric and with radial distance.
  • the pressure pin 30 drops and lies on the top of the throttle plate 13 until the pressure builds up again.
  • the outer diameter of the cylindrical pressure pin 30 corresponds to the inner guide diameter D i of the control valve element 26 less a guide clearance.
  • the control valve element 26 at its outer diameter D a , with which it passes through a plate member 34 with axial distance to the throttle plate 13, out.
  • an anchor plate 35 of the electromagnetic actuator 28 is integrally formed with the control valve element 26 in the illustrated embodiment.
  • the electromagnet 33 of the electromagnetic actuator 28 When the electromagnet 33 of the electromagnetic actuator 28 is energized, the sleeve-shaped control valve member 26 lifts from its control valve seat 29, whereby the pressure within the control chamber 21 drops rapidly and the injection valve member 16 moves in the axial direction in the drawing plane up into the control chamber 21, whereby the nozzle hole assembly 17 is released and fuel can flow into the combustion chamber.
  • a control closing spring 36 which is supported on the closure lid 31, moves the control valve element 26 back to its control valve seat 29.
  • the pressure in the control chamber 21 increases rapidly, whereby the injection valve element 10, supported by the spring force of a closing spring 37, which at one end is supported on a peripheral collar 38 of the control valve element 26 and the other end on the lower end side of the sleeve portion 12, is moved in the direction of the injection valve member seat 16, which in turn the fuel flow from the nozzle hole assembly 17 is interrupted in the combustion chamber.
  • the control valve member 26 In the closed state of the control valve 27, the control valve member 26 is located at an end face, annular contoured sealing line 39 on the control valve seat 29.
  • the sealing line 39 is, as in the following with reference to FIGS. 2 and 3 will be explained, not immediately adjacent to the inner guide diameter D i of the control valve element 26, but arranged at a radial distance to this offset outwards.
  • the very sharp-edged sealing edge after production widens due to the load occurring during operation to a radial extent of between about 50 ⁇ m and about 150 ⁇ m. Due to the compressive forces acting during operation, the sealing line 39 is infiltrated to some extent by fuel under high pressure in the radial direction to the outside.
  • Fig. 2 is a possible education of a detail Fig. 1 shown enlarged.
  • the control valve element 26 with the inner guide diameter D i is shown in its closed position, in which it bears against the control valve seat 29 with its frontal, annular contoured sealing line.
  • the control valve seat 29 is formed in the embodiment shown as a flat seat. It can be seen that the sealing line 39 is not directly adjacent to the inner guide diameter D i , but is arranged at a radial distance a to this.
  • the radial distance a is 100 ⁇ m in the embodiment shown.
  • the angle ⁇ is in the illustrated embodiment about 5 ° (exaggerated), wherein the inner annular surface 40, starting from the sealing line 39, both axially and radially from the control valve seat 29 extends away.
  • the inner annular surface 40 forms a seat boundary and is bounded radially outwardly by the sealing line 39 and radially inwardly by a peripheral edge 41 at the transition to the inner guide diameter D i .
  • the sealing line 39 is adjoined by an outer annular surface 42 which also extends away from the control valve seat 29 in the axial and in the radial direction.
  • the angle ⁇ between the control valve seat 29 and the outer annular surface 42 is in the illustrated embodiment about 30 ° and thus (significantly) greater than the angle ⁇ .
  • an angle ⁇ between the outer ring surface and the inner ring surface 40 of about 145 ° results.
  • the axial distance between the sealing line 39 and the radially outer edge 43 of the outer annular surface 42 is greater than the axial distance between the sealing line 39 and the inner edge 41 of the inner annular surface 40th
  • outer annular surface 44 (outermost annular surface) which lies in a direction perpendicular to the longitudinal central axis L extending plane and extending to the outer diameter D a of the control valve member 26.
  • the radial extension of the outer ring surface 44 (or of its axial projection surface) corresponds to a multiple of the radial extent a (radial distance of the sealing line to the inner guide circumference) of the inner annular surface 40 (or of its axial projection surface).
  • Fig. 3 an alternative embodiment is shown.
  • the control valve seat 29 is not formed as a flat seat, but as a conical conical seat, wherein the cone angle ⁇ in the shown Embodiment is about 160 °.
  • the sealing line 39 (sealing edge), which is arranged with a radial distance a to the inner guide diameter D i , ie the guide bore in the control valve element 26.
  • the angle ⁇ between the lateral surface of the control valve seat 29 and the radially adjacent to the sealing line 39 arranged inner annular surface 40 is in the illustrated embodiment about 4 ° (exaggerated drawn).
  • the outer annular surface 42 which lies in a direction perpendicular to the longitudinal central axis L extending plane and extending to the outer diameter D a of the control valve member 26.
  • the angle ⁇ between the outer annular surface 42 and the control valve seat 29 is in the illustrated embodiment about 22 °, so that in the sequence of the angle ⁇ between the outer annular surface 42 and the inner annular surface 40 is about 154 °.

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

Claims (10)

  1. Injecteur pour injecter du carburant dans une chambre de combustion d'un moteur à combustion interne, en particulier injecteur de rampe commune, avec un élément de soupape d'injection (10) pouvant être déplacé entre une position de fermeture et une position d'ouverture qui peut être piloté au moyen d'une valve de contrôle (27) comportant un élément de valve de contrôle (26) en forme de manchon avec un diamètre de guidage intérieur (Di), pour lequel une ligne d'étanchéité périphérique (39) s'applique lorsque la valve de contrôle (27) est fermée, à un siège de valve de contrôle (29), pour lequel la ligne d'étanchéité (39) est disposée avec une distance radiale (a) par rapport au diamètre de guidage intérieur (Di), pour lequel une surface annulaire (40) intérieure adjacente radialement à l'intérieur à la ligne d'étanchéité (39) est recourbée vers le siège de valve de contrôle (29), caractérisé en ce que le siège de valve de contrôle (29) est constitué comme un siège conique.
  2. Injecteur selon la revendication 1, caractérisé en ce que la ligne d'étanchéité (39) est disposée à une distance radiale (a) par rapport au diamètre extérieur (Da) de l'élément de valve de contrôle (26).
  3. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que la distance radiale (a) entre le diamètre de guidage (Di) et la ligne d'étanchéité (39) est d'environ 20 µm à environ 120 µm.
  4. Injecteur selon la revendication 1, caractérisé en ce que la surface annulaire (40) intérieure adjacente radialement à l'intérieur à la ligne d'étanchéité (39) est recourbée vers le siège de valve de contrôle (29) sous un angle (α) entre environ 0,1° et environ 50°, en particulier entre environ 0,5° et environ 5°.
  5. Injecteur selon la revendication 1, caractérisé en ce que la surface annulaire intérieure (40) s'étend radialement jusqu'au diamètre de guidage intérieur (Di).
  6. Injecteur selon l'une quelconque des revendications 1 ou 5, caractérisé en ce qu'une surface annulaire extérieure (42) adjacente radialement à l'extérieur à la ligne d'étanchéité (39) et la surface annulaire radialement intérieure (40) déploient un angle (γ) supérieur à 90°, de préférence supérieur à 100°, de préférence supérieur à 110°, de façon particulièrement préférée supérieur à 120°, en particulier de préférence supérieur à 140°.
  7. Injecteur selon la revendication 6, caractérisé en ce que la surface annulaire extérieure (42) est inclinée vers le siège de valve de contrôle (29), de préférence sous un angle (β) entre environ 10° et environ 50°, en particulier sous un angle entre environ 20° et environ 45°, en particulier de préférence sous un angle d'environ 30°.
  8. Injecteur selon l'une quelconque des revendications 6 ou 7, caractérisé en ce que la surface annulaire extérieure (42) passe dans une surface annulaire extérieure (44) disposée radialement à l'extérieur de celle-ci, en formant avec la surface annulaire externe (42) un angle qui se situe de préférence dans un plan passant perpendiculairement à l'axe médian longitudinal (L) de l'élément de valve de contrôle (26).
  9. Injecteur selon la revendication 6 ou 7, caractérisé en ce que la surface annulaire extérieure (42) se situe dans un plan passant perpendiculairement à l'axe médian longitudinal (L) de l'élément de valve de contrôle (26) qui s'étend de préférence radialement jusqu'au diamètre extérieur (Da) de l'élément de valve de contrôle (26).
  10. Injecteur selon l'une quelconque des revendications 7 à 9, caractérisé en ce que l'angle (α) entre la surface annulaire intérieure (40) et le siège de valve de contrôle (29) est plus petit que l'angle (β) entre la surface annulaire extérieure (42) et le siège de valve de contrôle (29).
EP08871452.2A 2008-01-22 2008-12-03 Injecteur de carburant Active EP2235356B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810005534 DE102008005534A1 (de) 2008-01-22 2008-01-22 Kraftstoffinjektor
PCT/EP2008/066725 WO2009092484A1 (fr) 2008-01-22 2008-12-03 Injecteur de carburant

Publications (2)

Publication Number Publication Date
EP2235356A1 EP2235356A1 (fr) 2010-10-06
EP2235356B1 true EP2235356B1 (fr) 2015-10-14

Family

ID=40340349

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08871452.2A Active EP2235356B1 (fr) 2008-01-22 2008-12-03 Injecteur de carburant

Country Status (3)

Country Link
EP (1) EP2235356B1 (fr)
DE (1) DE102008005534A1 (fr)
WO (1) WO2009092484A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11746734B2 (en) 2018-08-23 2023-09-05 Progress Rail Services Corporation Electronic unit injector shuttle valve

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008040956A1 (de) * 2008-08-04 2010-02-11 Robert Bosch Gmbh Kraftstoff-Injektor
DE602008005349D1 (de) 2008-12-29 2011-04-14 Fiat Ricerche Brennstoffeinspritzsystem mit hoher Betriebswiederholbarkeit und -stabilität für einen Verbrennungsmotor
DE102009046563A1 (de) * 2009-11-10 2011-05-12 Robert Bosch Gmbh Kraftstoffinjektor
EP2383454A1 (fr) 2010-04-27 2011-11-02 C.R.F. Società Consortile per Azioni Formage du débit d'injection de carburant dans un moteur à combustion interne
EP2405121B1 (fr) 2010-07-07 2013-10-09 C.R.F. Società Consortile per Azioni Système d'injection de carburant pour moteur à combustion interne
US9212639B2 (en) 2012-11-02 2015-12-15 Caterpillar Inc. Debris robust fuel injector with co-axial control valve members and fuel system using same

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009071472A1 (fr) * 2007-12-03 2009-06-11 Robert Bosch Gmbh Soupape de commande pour injecteurs

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2277229T3 (es) 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni Servovalvula para controlar el inyector de combustible de un motor de combustion interna.
EP1795738A1 (fr) * 2005-12-12 2007-06-13 C.R.F. Societa Consortile per Azioni Système d'injection de carburant pour un moteur à combustion interne et méthode correspondante pour commander l'injection de carburant
DE102006027485A1 (de) * 2006-06-14 2007-12-20 Robert Bosch Gmbh Kraftstoffeinspritzventil mit Sicherheitssteuerventil

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009071472A1 (fr) * 2007-12-03 2009-06-11 Robert Bosch Gmbh Soupape de commande pour injecteurs

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11746734B2 (en) 2018-08-23 2023-09-05 Progress Rail Services Corporation Electronic unit injector shuttle valve

Also Published As

Publication number Publication date
WO2009092484A1 (fr) 2009-07-30
DE102008005534A1 (de) 2009-07-23
EP2235356A1 (fr) 2010-10-06

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