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EP3365548B1 - Fuel injector - Google Patents

Fuel injector Download PDF

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Publication number
EP3365548B1
EP3365548B1 EP16787766.1A EP16787766A EP3365548B1 EP 3365548 B1 EP3365548 B1 EP 3365548B1 EP 16787766 A EP16787766 A EP 16787766A EP 3365548 B1 EP3365548 B1 EP 3365548B1
Authority
EP
European Patent Office
Prior art keywords
mobile
piston
flange
effective diameter
nozzle body
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
EP16787766.1A
Other languages
German (de)
French (fr)
Other versions
EP3365548A1 (en
Inventor
Thierry Thibault
Nicolas Rodier
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.)
Delphi Technologies IP Ltd
Original Assignee
Delphi Technologies IP Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
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Publication of EP3365548A1 publication Critical patent/EP3365548A1/en
Application granted granted Critical
Publication of EP3365548B1 publication Critical patent/EP3365548B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10Other injectors with elongated valve bodies, i.e. of needle-valve type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0635Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • F02M51/066Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature and the valve being allowed to move relatively to each other or not being attached to each other
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002Arrangement of leakage or drain conduits in or from injectors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1873Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46Valves, e.g. injectors, with concentric valve bodies
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/502Springs biasing the valve member to the open position

Definitions

  • the present invention relates to a fuel injector more particularly suitable for injection equipment of the "common rail" type, the injector itself being provided with a nozzle, the needle of which is directly opened or closed by an electromagnetic actuator. coil.
  • a prior art fuel injector see for example document DE 198 15 892 A1 , comprises a coil and magnetic armature actuator acting directly on a valve member to open or close fuel injection holes.
  • Such an injector requires a hydraulically balanced, or nearly balanced, valve member so that the relatively small force exerted by the solenoid actuator is sufficient to move said valve member.
  • the present invention aims to remedy the drawbacks mentioned above by proposing a simple and economical solution.
  • the invention provides a movable valve member adapted to be arranged in the nozzle body of a fuel injector, the movable member extending along a main axis between a top end and a bottom end provided with a movable valve seat provided to cooperate along a circular line of effective diameter with a fixed seat arranged on the internal face of the nozzle body.
  • the movable member is designed to slide between a closed position in which the two valve seats are in sealed contact along said circular line preventing fuel injection and an open position in which the two valve seats are distant. each other allowing said injection .;
  • the movable member comprises a piston formed of a first male cylinder of effective diameter forming the upper end of the movable member and, a second cylinder of larger outer diameter provided with an internal cylindrical bore of effective diameter extending axially in the second cylinder to a bottom and, a shutter member formed of a cylindrical body comprising a male cylindrical shaft of fitted effective diameter sliding with clearance in the internal bore of the piston and, of a male pointed cylindrical member of larger diameter than the effective diameter, the pointed cylindrical member extending to an end in tip provided with the movable valve seat and forming the lower end of the movable member.
  • the movable valve member is hydraulically balanced and has a variable length between its upper end and its lower end due to the sliding of the cylindrical shaft in the internal bore of the piston.
  • the movable member further comprises a first spring compressed between the piston and the shutter member and continuously biasing the piston and the shutter member towards an extension of the movable member.
  • the obturator member further comprises a disc collar substantially arranged between the cylindrical shaft and the pointed cylinder, said collar extending radially from the cylindrical body of the obturator member to a peripheral edge intended to fit slidably against the internal face. of the injector nozzle body.
  • the flange has an upper face facing the piston and an opposite underside facing the valve seat. Said flange further defines a first restricted orifice and a second restricted orifice both extending between opposing faces of the flange and allowing pressurized fuel to pass at reduced speed from one side of the flange to the other in creating a pressure difference between the faces of the collar.
  • the piston is further provided with a return channel extending from the bottom of the internal bore and opening out at the top end of the first cylinder.
  • the bore comprises a first section of diameter larger than the effective diameter and, a second section of effective diameter so that the piston comprises a circular end forming a sealing lip cooperating with a circular annular surface of the upper face of the collar.
  • the first restricted orifice being arranged outside said circular annular surface and, the second restricted orifice being arranged inside said circular annular surface.
  • the movable member is limited in extension by a mooring means preventing the shutter member from disengaging from the piston and, in compression, by the sealing lip in sealed abutment on the upper face of the collar.
  • the invention also relates to an injection nozzle of a high pressure fuel injector, the nozzle comprising a movable valve member produced according to the preceding paragraphs.
  • the nozzle also includes a nozzle body elongated along the major axis, the body having a tapered cylindrical peripheral side wall at one end and a top wall at the other end.
  • the upper wall is provided with a pressurized fuel inlet and an axial bore opening forming an annular guide of effective diameter and, the tapered end is provided on the inner face of the wall of the nozzle body of the seat.
  • fixed valve arranged near injection holes extending through the peripheral wall.
  • the movable member is arranged axially to slide in the interior space of the nozzle body, the first cylinder of the piston being slidably fitted in the opening annular guide, so that the movable valve seat cooperates with the fixed valve seat and that the 'movable assembly is able to slide along the main axis between the closed position and the open position in which the movable seat is at a distance from the fixed seat.
  • the invention also extends to a fuel injector comprising an actuator and a nozzle produced as described above, the actuator being an electromagnet comprising a fixed coil and a movable magnetic armature directly attached to the piston.
  • a fuel injector 10 shown in figure 1 is briefly described so as to identify the main components.
  • the injector 10 extends along a main axis X1, and comprises an actuator assembly 12, drawn at the top of the figure, and a nozzle assembly 14, drawn below.
  • the actuator assembly 12 comprises a substantially cylindrical body 16 extending from an injector head 18 to the lower transverse face 20 and, in a bore 22 provided for this purpose, the body 16 contains an electromagnet 24 comprising a coil 26 fixed in the body 16 and a movable magnetic armature 28 along the main axis X1.
  • the nozzle assembly 14 also comprises a body 30 arranged as an axial extension of the actuator body 16 and whose peripheral wall 32 defines an interior space V.
  • the nozzle body 30 extends axially in a cylindrical part from an upper face. 34 transverse in sealed surface contact with the lower face 20 of the injector body, up to a part of smaller section ending in a pointed end 36 provided with injection holes 38 extending through the peripheral wall 32 from an inlet located on the inner face 40 to an outlet located on the outer face 42.
  • the nozzle body 30 comprises a fuel inlet port 44, said port 44 being arranged in the upper face 34 and , at the other end of the body 30, the internal face 40 of the peripheral wall is provided, just above the inlets of the injection holes 38, with a fixed valve seat 46.
  • a movable valve member 48 also referred to as a needle by professionals, is arranged to slide along the main axis X1.
  • the movable member 48 is telescopic mainly comprising a cylindrical piston 50 and a shutter member 52 arranged to slide with respect to each other.
  • the piston 50 emerges through a bore 54 from the upper face 34 of the nozzle body, this part emerging from the nozzle body being integral with the magnetic armature 28 and, on the other hand, on the opposite side, on the side of the nozzle.
  • the pointed end 36, the shutter member is provided with a movable seat of valve 56 cooperating with the fixed seat 46.
  • the movable valve member 48 moves axially between a closed position PF in which the movable valve seat 56 is in sealed contact against the fixed valve seat 46 along a circular line of effective diameter DE and, an open position PO in which the two seats are distant from each other.
  • PF closed position
  • PO open position
  • the nozzle body 30 forms a small volume known to those skilled in the art under the name S-bag. which open the injection holes 38.
  • the actuator assembly 12 and the nozzle assembly 14 are secured to each other by an injector nut 58 which, threaded around the nozzle body 30 and resting thereon on an outer shoulder is screwed tightly to the body actuator 16.
  • the injector 10 further comprises a high pressure channel 60 extending into the actuator body 16 from an inlet mouth to the underside 20 where it communicates with the inlet port 44 for fuel in the body. nozzle.
  • the fuel F enters the interior space V of the nozzle body and occupies the entire available volume of said space V.
  • the nozzle assembly 14 is now described in more detail with reference to figures 2 and following.
  • the piston 50 of the movable valve member 48 is a cylindrical part comprising a first thin cylinder 62 of outside diameter equal to the effective diameter DE and, below in the arbitrary direction of the figure, a second cylinder 64 of larger outside diameter, the first and second cylinder 62, 64 joining at a transverse shoulder 66.
  • the second cylinder 64 of the piston is provided with a bore 68 opening into the lower face limiting the lower end to a bevelled annular surface forming a sealing lip 70. From this lip 70, the bore 68 extends axially in the second cylinder 64 in a first section 72 of diameter D72 greater than the effective diameter DE then in a second section 74 of diameter equal to the effective diameter DE.
  • the two sections of the bore 72, 74 connect according to an internal shoulder from which the second section 74 extends to a bottom face 76 from which a return channel 78 starts which extends axially in the first cylinder 72 until it emerges from it in the emerging part outside the body nozzle.
  • the obturator member 52 of the movable valve member 48 comprises for its part three coaxial cylindrical parts, the central part of which is a transverse disc collar 80, sometimes referred to by its English name "boost flange", the outside diameter of which is adjusted to slide to the face. 40 of the body 30. From the center of the upper face 82 of the flange 80 extends a cylindrical shaft 84 of diameter equal to the effective diameter DE, said cylindrical shaft 84 extending firstly through the first section 72 of the piston bore and then slidably engaging the second section 74 of the piston bore.
  • a pointed cylindrical shaft 88 of diameter D88 greater than the effective diameter DE From the center of the lower face 86 of the flange 80 extends a pointed cylindrical shaft 88 of diameter D88 greater than the effective diameter DE, said pointed cylindrical shaft 88 being provided at its pointed end with the movable valve seat 56 cooperating with the fixed seat 46 of nozzle body valve 30.
  • the collar 80 is provided on its upper face 82 with an annular sealing surface 90 cooperating with the sealing lip 70 of the piston as well as with two restricted orifices passing through the collar 80 between its upper face 82 and its lower face 86.
  • the first restricted orifice 94 is arranged outside the annular sealing surface 90, that is to say between the annular surface 86 and the peripheral edge of the flange, while the second restricted orifice 96 is on the outside. inside the annular sealing surface 90.
  • the flange 80 Due to the sliding fit of the flange 80 in the inner face of the wall of the nozzle body, the flange 80 separates the inner space V of the nozzle body into an upstream space V1 located above the flange 80, on the side of the upper face 82 and the inlet 44 for fuel in the nozzle body and, a downstream space V2 located below the flange 80, on the side of the lower face 86 and the holes of injection 38 opening into the bag S.
  • the restricted orifices 94, 96 therefore create fluid communications between the upstream V1 and downstream V2 spaces.
  • the cylindrical shaft 88 of diameter DE passes through the first section 72 which defines a annular chamber C1 into which the second restricted orifice 94 opens, establishing fluid communication with the downstream space V2.
  • bottom face 76 of the second bore of the piston and the end of the cylindrical shaft 84 define a return chamber C2 in which a spring 92 is compressed which tends to move the two parts 50, 52 away, one on the other and extend the movable valve member 48.
  • a securing means 98 shown schematically in the figure by two annular protuberances engaging complementarily and limiting said extension of the movable valve member 48.
  • the first cylinder 62 of the piston is axially guided in the bore 54 of the upper face of the nozzle body.
  • the bore 54 has a diameter D54 slightly greater than the effective diameter DE of the piston and an independent annular guide 100 fitted around the first cylinder 62 guarantees sealing.
  • the annular guide 100 has an internal diameter equal to the effective diameter DE and is held pressed against the nozzle body 30 by a second spring 102 compressed between the annular guide 100 and the shoulder 66 of the piston.
  • the second spring 102 therefore permanently urges the piston towards the bottom of the figure and presses the annular guide 100 against the top of the nozzle body.
  • the face of the guide 100 in contact with the nozzle body 30 is bevelled and forms another sealing lip.
  • the diameters and the clearances are shown to be exaggeratedly different.
  • the annular guide 100 is integrated into a top guide 104 comprising the upper transverse face 34 of the nozzle body, face provided with the fuel inlet orifice 44, from the center of which the annular guide 100 extends.
  • Said guide top 104 is held in place compressed between the nozzle body 30 and the actuator body 16 by the injector nut 58.
  • Said other spring 102 is then compressed between the top guide 104 and the shoulder 66 of the piston.
  • the first cylinder 62 of the piston is caused to slide in the annular guide 100 and, the cylindrical shaft 84 is caused to slide in the second section 74 of the bore in the piston.
  • these sliding adjustments of male cylinders and female requires an operating clearance J of a few microns, which does not prevent writing that all of the male and female cylinders have a diameter equal to the effective diameter DE, said diameter being the nominal diameter.
  • the injector 10 is arranged within a common rail type of fuel injection equipment supplying pressurized fuel to several injectors. Pressurized fuel F therefore enters through the inlet of the injector and, in contemporary diesel injection equipment, the pressurization of the diesel fuel can reach 2000 or 3000 bars. To illustrate this operation, it is arbitrarily chosen that the fuel pressure at the inlet of the injector is 2500 bars.
  • the fuel F enters the nozzle body 30 and occupies all the internal space V available.
  • a first phase according to figures 2 or 3 , the electromagnet 24 is not supplied, the second spring 102 pushes the piston 50 towards the shutter member 52 and, the shutter member 52 is itself pushed back by the first spring 92 in the closed position PF, that is to say say that the sealing lip 70 of the piston is in sealed contact against the annular surface 90 arranged on the upper face of the flange and the movable valve seat 56 is in sealed contact against the fixed seat 46 along the line circular of effective diameter DE. Bag S is isolated from volume V2. Thus, the annular chamber C1 is only in communication with the downstream space V2 via the second restricted orifice 96.
  • the fuel F entered into the upstream space V1 via the inlet port 44 passes into the downstream space V2 via the first restricted orifice 94 then rises in the annular chamber C1 via the second restricted orifice 96.
  • the passage of fuel F through the restricted orifices allows the three spaces V1, V2, C1 to be filled with fuel F at high pressure. A slight difference in pressure may exist between these three spaces.
  • the pressure in the downstream space V2 may be only 2200 bars and the pressure in the bag S of 2100 bars.
  • the pressure in the annular chamber C1 is substantially equal to that in the space downstream V2 and, the return chamber C2 being permanently in communication with the low pressure, no particular pressure prevails there.
  • the piston 50 is hydraulically balanced. Indeed the cumulative area of the faces generating a downward force on the piston is equal to the cumulative area of the faces generating an upward force on the piston.
  • the forces generated by the pressure applying to the faces of the piston 50 faces distributed between the first cylinder of effective diameter DE and the second bore also of effective diameter DE, whatever the shape or profile of said faces, s' balance.
  • shutter member 52 the pressurized faces of which extend between the cylindrical shaft of effective diameter DE and the valve seat also of effective diameter DE.
  • the electromagnet 24 begins to be supplied, the magnetic armature 28 is attracted by the magnetic field M generated by the coil 26 and, driven by the magnetic armature, the piston 50 has started to rise.
  • the second spring 102 is compressed while the first spring 92 expands, the forces of the two springs partially compensating for each other, the electromagnet 24 then only having to overcome the difference between the forces of the springs.
  • the first spring 92 maintains the shutter member 52 in the closed position PF while the means 98 for anchoring the piston 50 and the shutter member 52 is just actuated so that the movable member 48 cannot extend further.
  • the sealing lip 70 being raised and away from the annular sealing surface 90, the annular chamber C1 is in fluid communication with the upstream space V1 and pressurized fuel F can pass from the upstream space V1. to the downstream space V2 via the two restricted orifices 94, 96, which helps to balance the pressures in the upstream V1 and downstream V2 spaces.
  • a third phase illustrated by the figure 5 the power supply to the electromagnet 24 is maintained and the piston 50 continues to rise.
  • the piston 50 drives the shutter member 52 so that the valve seat 46, 56 opens and allows pressurized fuel F to be injected through the injection holes 38
  • the pressure in the bag S then increases and contributes to the force for opening the shutter member 52.
  • the flow of fuel F passing through the first and second restricted orifices 94, 96 creates a slight pressure differential, the pressure in l. 'the upstream space V1 being slightly greater than the pressure in the downstream space V2 so as to generate a force which opposes the opening force of the pressure in the bag S.
  • the shutter member 52 therefore remains hydraulically balanced and , the electromagnet has only a small effort to provide to continue opening the obturator member.
  • the pressure in the downstream space V2 is approximately 2400 bars and the pressure in the bag S is approximately 2300 bars.
  • the pressure in the annular chamber C1 is equal to that which is in the upstream space V1 and, the return chamber C2 still being in communication with the low pressure, no particular pressure prevails there.
  • the length of the first spring 92 does not vary since from the second phase detailed above, the anchoring means 98 is actuated and the electromagnet 24 only has to overcome the compressive force of the second spring 102.
  • a fourth closing phase the supply to the electromagnet is interrupted and the piston 50, under the influence of the second spring 102, descends to a sealed stop against the upper face of the collar.
  • the pressurized fuel F can no longer pass from the upstream space V1 to the downstream space V2 except through the first restricted orifice 94.
  • the pressure in the downstream space V2 may be only 2200 bars and the pressure in the bag S of 2100 bars.
  • the pressure in the annular chamber C1 is substantially equal to that which is in the downstream space V2 and, the return chamber C2 being permanently in communication with the low pressure, no particular pressure prevails there.

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

Description

DOMAINE TECHNIQUETECHNICAL AREA

La présente invention concerne un injecteur de carburant plus particulièrement adapté à un équipement d'injection de type « à rampe commune », l'injecteur lui-même étant pourvu d'une buse dont l'aiguille est directement ouverte ou fermée par un actionneur électromagnétique à bobine.The present invention relates to a fuel injector more particularly suitable for injection equipment of the "common rail" type, the injector itself being provided with a nozzle, the needle of which is directly opened or closed by an electromagnetic actuator. coil.

ARRIERE-PLAN TECHNOLOGIQUE DE L'INVENTIONTECHNOLOGICAL BACKGROUND OF THE INVENTION

Un injecteur de carburant de l'art antérieur, voir par exemple le document DE 198 15 892 A1 , comprend un actionneur à bobine et armature magnétique agissant directement sur un membre de vanne de sorte à ouvrir ou fermer des trous d'injections de carburant.A prior art fuel injector, see for example document DE 198 15 892 A1 , comprises a coil and magnetic armature actuator acting directly on a valve member to open or close fuel injection holes.

Un tel injecteur impose un membre de vanne hydrauliquement équilibré, ou quasiment équilibré, de sorte que la force relativement faible exercée par l'actionneur à solénoïde soit suffisante pour mouvoir ledit membre de vanne.Such an injector requires a hydraulically balanced, or nearly balanced, valve member so that the relatively small force exerted by the solenoid actuator is sufficient to move said valve member.

RESUME DE L'INVENTIONSUMMARY OF THE INVENTION

La présente invention vise à remédier aux inconvénients mentionnés précédemment en proposant une solution simple et économique.The present invention aims to remedy the drawbacks mentioned above by proposing a simple and economical solution.

Dans ce but, l'invention propose un membre mobile de vanne adapté à être agencé dans le corps de buse d'un injecteur de carburant, le membre mobile s'étendant selon un axe principal entre une extrémité haute et une extrémité basse pourvue d'un siège mobile de vanne prévu pour coopérer le long d'une ligne circulaire de diamètre effectif avec un siège fixe agencé sur la face interne du corps de buse. Le membre mobile est prévu pour coulisser entre une position fermée dans laquelle les deux sièges, de vanne sont en contact étanche le long de ladite ligne circulaire interdisant l'injection de carburant et, une position ouverte dans laquelle les deux sièges de vanne sont distant l'un de l'autre permettant ladite injection.;For this purpose, the invention provides a movable valve member adapted to be arranged in the nozzle body of a fuel injector, the movable member extending along a main axis between a top end and a bottom end provided with a movable valve seat provided to cooperate along a circular line of effective diameter with a fixed seat arranged on the internal face of the nozzle body. The movable member is designed to slide between a closed position in which the two valve seats are in sealed contact along said circular line preventing fuel injection and an open position in which the two valve seats are distant. each other allowing said injection .;

De plus, le membre mobile comprend un piston formé d'un premier cylindre mâle de diamètre effectif formant l'extrémité haute du membre mobile et, d'un second cylindre de plus large diamètre extérieur pourvu d'un alésage cylindrique interne de diamètre effectif s'étendant axialement dans le second cylindre jusqu'à un fond et, d'un membre obturateur formé d'un corps cylindrique comprenant un arbre cylindrique mâle de diamètre effectif ajusté coulissant avec jeu dans l'alésage interne du piston et, d'un membre cylindrique pointu mâle de plus large diamètre que le diamètre effectif, le membre cylindrique pointu s'étendant jusqu'à une extrémité en pointe pourvue du siège mobile de vanne et formant l'extrémité basse du membre mobile.In addition, the movable member comprises a piston formed of a first male cylinder of effective diameter forming the upper end of the movable member and, a second cylinder of larger outer diameter provided with an internal cylindrical bore of effective diameter extending axially in the second cylinder to a bottom and, a shutter member formed of a cylindrical body comprising a male cylindrical shaft of fitted effective diameter sliding with clearance in the internal bore of the piston and, of a male pointed cylindrical member of larger diameter than the effective diameter, the pointed cylindrical member extending to an end in tip provided with the movable valve seat and forming the lower end of the movable member.

Ainsi, le membre mobile de vanne est hydrauliquement équilibré et a une longueur variable entre son extrémité haute et son extrémité basse due au coulissement de l'arbre cylindrique dans l'alésage interne du piston.Thus, the movable valve member is hydraulically balanced and has a variable length between its upper end and its lower end due to the sliding of the cylindrical shaft in the internal bore of the piston.

Le membre mobile comprend de plus un premier ressort comprimé entre le piston et le membre obturateur et sollicitant en permanence le piston et le membre obturateur vers une extension du membre mobile.The movable member further comprises a first spring compressed between the piston and the shutter member and continuously biasing the piston and the shutter member towards an extension of the movable member.

Le membre obturateur comprend de plus une collerette discale sensiblement agencée entre l'arbre cylindrique et le cylindre pointu, ladite collerette s'étendant radialement depuis le corps cylindrique du membre obturateur jusqu'à un bord périphérique prévu pour s'ajuster coulissant contre la face interne du corps de buse d'injecteur. La collerette a une face supérieure en regard du piston et une face inférieure opposée en regard du siège de vanne. Ladite collerette définit de plus un premier orifice restreint et un second orifice restreint s'étendant tous deux entre les faces opposées de la collerette et permettant à du carburant sous pression de passer à vitesse réduite d'un côté à l'autre de la collerette en créant une différence de pression entre les faces de la collerette.The obturator member further comprises a disc collar substantially arranged between the cylindrical shaft and the pointed cylinder, said collar extending radially from the cylindrical body of the obturator member to a peripheral edge intended to fit slidably against the internal face. of the injector nozzle body. The flange has an upper face facing the piston and an opposite underside facing the valve seat. Said flange further defines a first restricted orifice and a second restricted orifice both extending between opposing faces of the flange and allowing pressurized fuel to pass at reduced speed from one side of the flange to the other in creating a pressure difference between the faces of the collar.

Le piston est de plus pourvu d'un canal de retour s'étendant depuis le fond de l'alésage interne et débouchant en extrémité haute du premier cylindre.The piston is further provided with a return channel extending from the bottom of the internal bore and opening out at the top end of the first cylinder.

L'alésage comprend un premier tronçon de diamètre plus large que le diamètre effectif et, un second tronçon de diamètre effectif de sorte que le piston comprend une extrémité circulaire formant une lèvre d'étanchéité coopérant avec une surface annulaire circulaire de la face supérieure de la collerette. Le premier orifice restreint étant agencé à l'extérieur de ladite surface annulaire circulaire et, le second orifice restreint étant agencé à l'intérieur de ladite surface annulaire circulaire.The bore comprises a first section of diameter larger than the effective diameter and, a second section of effective diameter so that the piston comprises a circular end forming a sealing lip cooperating with a circular annular surface of the upper face of the collar. The first restricted orifice being arranged outside said circular annular surface and, the second restricted orifice being arranged inside said circular annular surface.

Le membre mobile est limité en extension par un moyen d'amarrage empêchant au membre obturateur de se dégager du piston et, en compression par la lèvre d'étanchéité en butée étanche sur la face supérieure de la collerette.The movable member is limited in extension by a mooring means preventing the shutter member from disengaging from the piston and, in compression, by the sealing lip in sealed abutment on the upper face of the collar.

L'invention est également relative à une buse d'injection d'un injecteur de carburant à haute pression, la buse comprenant un membre mobile de vanne réalisé selon les paragraphes précédents.The invention also relates to an injection nozzle of a high pressure fuel injector, the nozzle comprising a movable valve member produced according to the preceding paragraphs.

La buse comprend également un corps de buse allongé selon l'axe principal, le corps ayant une paroi périphérique latérale cylindrique fuselée à une extrémité et, une paroi supérieure à l'autre extrémité. La paroi supérieure est pourvue d'un orifice d'entrée de carburant sous pression et d'un alésage axial débouchant formant guide annulaire de diamètre effectif et, l'extrémité fuselée est pourvue sur la face interne de la paroi du corps de buse du siège fixe de vanne agencé à proximité de trous d'injections s'étendant au travers de la paroi périphérique.The nozzle also includes a nozzle body elongated along the major axis, the body having a tapered cylindrical peripheral side wall at one end and a top wall at the other end. The upper wall is provided with a pressurized fuel inlet and an axial bore opening forming an annular guide of effective diameter and, the tapered end is provided on the inner face of the wall of the nozzle body of the seat. fixed valve arranged near injection holes extending through the peripheral wall.

Le membre mobile est agencé axialement coulissant dans l'espace intérieur du corps de buse, le premier cylindre du piston étant ajusté coulissant avec jeu dans le guide annulaire débouchant, de sorte que le siège mobile de vanne coopère avec le siège fixe vanne et que l'ensemble mobile soit apte à coulisser selon l'axe principal entre la position fermée et, la position ouverte dans laquelle le siège mobile est à distance du siège fixe.The movable member is arranged axially to slide in the interior space of the nozzle body, the first cylinder of the piston being slidably fitted in the opening annular guide, so that the movable valve seat cooperates with the fixed valve seat and that the 'movable assembly is able to slide along the main axis between the closed position and the open position in which the movable seat is at a distance from the fixed seat.

L'invention s'étend également à un injecteur de carburant comprenant un actionneur et une buse réalisée comme précédemment décrit, l'actionneur étant un électroaimant comprenant une bobine fixe et une armature magnétique mobile directement fixée au piston.The invention also extends to a fuel injector comprising an actuator and a nozzle produced as described above, the actuator being an electromagnet comprising a fixed coil and a movable magnetic armature directly attached to the piston.

BREVE DESCRIPTION DES DESSINSBRIEF DESCRIPTION OF THE DRAWINGS

D'autres caractéristiques, buts et avantages de l'invention apparaîtront à la lecture de la description détaillée qui va suivre, et en regard des dessins annexés, donnés à titre d'exemple non limitatif et sur lesquels:

  • la figure 1 est vue d'ensemble d'un injecteur selon l'invention.
  • la figure 2 est un schéma de la buse de l'injecteur de la figure 1.
  • les figures 3, 4 et 5 sont identiques à la figure 2 et illustrent différentes phase de fonctionnement de la buse d'injecteur.
Other characteristics, aims and advantages of the invention will become apparent on reading the detailed description which follows, and with reference to the appended drawings, given by way of non-limiting example and in which:
  • the figure 1 is an overall view of an injector according to the invention.
  • the figure 2 is a diagram of the injector nozzle of the figure 1 .
  • the figures 3, 4 and 5 are identical to the figure 2 and illustrate different phases of operation of the injector nozzle.

DESCRIPTION DES MODES DE REALISATION PREFERESDESCRIPTION OF THE PREFERRED EMBODIMENTS

Un injecteur 10 de carburant représenté en figure 1 est décrit succinctement de sorte à identifier les principaux composants. L'injecteur 10 s'étend selon un axe principal X1, et comprend un ensemble actionneur 12, dessiné en haut de la figure, et un ensemble de buse 14, dessiné en-dessous.A fuel injector 10 shown in figure 1 is briefly described so as to identify the main components. The injector 10 extends along a main axis X1, and comprises an actuator assembly 12, drawn at the top of the figure, and a nozzle assembly 14, drawn below.

L'ensemble actionneur 12 comprend un corps 16 substantiellement cylindrique s'étendant depuis une tête d'injecteur 18 jusqu'à face transverse inférieure 20 et, dans un alésage 22 prévu à cet effet, le corps 16 renferme un électroaimant 24 comprenant une bobine 26 fixe dans le corps 16 et une armature magnétique mobile 28 selon l'axe principal X1.The actuator assembly 12 comprises a substantially cylindrical body 16 extending from an injector head 18 to the lower transverse face 20 and, in a bore 22 provided for this purpose, the body 16 contains an electromagnet 24 comprising a coil 26 fixed in the body 16 and a movable magnetic armature 28 along the main axis X1.

L'ensemble de buse 14 comprend également un corps 30 agencé en prolongement axial du corps 16 d'actionneur et dont la paroi périphérique 32 définit un espace intérieur V. Le corps de buse 30 s'étend axialement en une partie cylindrique depuis une face supérieure 34 transverse en contact surfacique étanche avec la face inférieure 20 du corps d'injecteur, jusqu'à une partie de plus faible section se terminant en une extrémité pointue 36 pourvue de trous d'injections 38 s'étendant au travers de la paroi périphérique 32 depuis une entrée située sur la face interne 40 jusqu'à une sortie située sur la face externe 42. De plus, le corps de buse 30 comprend un orifice d'entrée 44 de carburant, ledit orifice 44 étant agencée dans la face supérieure 34 et, à l'autre extrémité du corps 30, la face interne 40 de la paroi périphérique est pourvue, juste au-dessus des entrées des trous d'injection 38, d'un siège fixe de vanne 46.The nozzle assembly 14 also comprises a body 30 arranged as an axial extension of the actuator body 16 and whose peripheral wall 32 defines an interior space V. The nozzle body 30 extends axially in a cylindrical part from an upper face. 34 transverse in sealed surface contact with the lower face 20 of the injector body, up to a part of smaller section ending in a pointed end 36 provided with injection holes 38 extending through the peripheral wall 32 from an inlet located on the inner face 40 to an outlet located on the outer face 42. In addition, the nozzle body 30 comprises a fuel inlet port 44, said port 44 being arranged in the upper face 34 and , at the other end of the body 30, the internal face 40 of the peripheral wall is provided, just above the inlets of the injection holes 38, with a fixed valve seat 46.

Dans l'espace intérieur V un membre mobile de vanne 48, également dénommé aiguille par les professionnels, est agencé coulissant selon l'axe principal X1. Le membre mobile 48 est télescopique comprenant principalement un piston 50 cylindrique et un membre obturateur 52 agencés coulissant l'un par rapport à l'autre. D'une part le piston 50 émerge par un alésage 54 de la face supérieure 34 du corps de buse, cette partie émergeante hors du corps de buse étant solidaire du armature magnétique 28 et, d'autre part à l'opposé, du côté de l'extrémité pointue 36, le membre obturateur est pourvu d'un siège mobile de vanne 56 coopérant avec le siège fixe 46. En fonctionnement, le membre mobile de vanne 48 se déplace axialement entre une position fermée PF dans laquelle le siège mobile de vanne 56 est en contact étanche contre le siège fixe de vanne 46 le long d'une ligne circulaire de diamètre effectif DE et, une position ouverte PO dans laquelle les deux sièges sont éloignés l'un de l'autre. Dans l'extrême pointe du corps de buse 30, sous cette ligne circulaire, « sous » pris dans le sens de la figure, le corps de buse 30 forme un petit volume connu de l'homme du métier sous le nom de sac S dans lequel débouchent les trous d'injections 38.In the interior space V a movable valve member 48, also referred to as a needle by professionals, is arranged to slide along the main axis X1. The movable member 48 is telescopic mainly comprising a cylindrical piston 50 and a shutter member 52 arranged to slide with respect to each other. On the one hand, the piston 50 emerges through a bore 54 from the upper face 34 of the nozzle body, this part emerging from the nozzle body being integral with the magnetic armature 28 and, on the other hand, on the opposite side, on the side of the nozzle. the pointed end 36, the shutter member is provided with a movable seat of valve 56 cooperating with the fixed seat 46. In operation, the movable valve member 48 moves axially between a closed position PF in which the movable valve seat 56 is in sealed contact against the fixed valve seat 46 along a circular line of effective diameter DE and, an open position PO in which the two seats are distant from each other. In the extreme tip of the nozzle body 30, under this circular line, "under" taken in the direction of the figure, the nozzle body 30 forms a small volume known to those skilled in the art under the name S-bag. which open the injection holes 38.

L'ensemble actionneur 12 et l'ensemble buse 14 sont solidarisés l'un à l'autre par un écrou d'injecteur 58 qui, enfilé autour du corps de buse 30 et y prenant appui sur un épaulement extérieur est vissé serré sur le corps d'actionneur 16.The actuator assembly 12 and the nozzle assembly 14 are secured to each other by an injector nut 58 which, threaded around the nozzle body 30 and resting thereon on an outer shoulder is screwed tightly to the body actuator 16.

L'injecteur 10 comprend de plus un canal haute pression 60 s'étendant dans le corps d'actionneur 16 depuis une bouche d'entrée jusque dans la face inférieure 20 où il communique avec l'orifice d'entrée 44 de carburant dans le corps de buse. Le carburant F entre dans l'espace intérieur V le corps de buse et occupe tout le volume disponible dudit espace V.The injector 10 further comprises a high pressure channel 60 extending into the actuator body 16 from an inlet mouth to the underside 20 where it communicates with the inlet port 44 for fuel in the body. nozzle. The fuel F enters the interior space V of the nozzle body and occupies the entire available volume of said space V.

L'ensemble de buse 14 est maintenant décrit plus en détail en référence aux figures 2 et suivantes.The nozzle assembly 14 is now described in more detail with reference to figures 2 and following.

Le piston 50 du membre mobile de vanne 48 est une pièce cylindrique comprenant un premier cylindre mince 62 de diamètre extérieur égale au diamètre effectif DE et, en dessous dans le sens arbitraire de la figure, un second cylindre 64 de plus large diamètre extérieur, le premier et le second cylindre 62, 64 se joignant selon un épaulement transverse 66. L'homme du métier comprendra aisément que les dimensions et diamètres décrits comme étant égaux le sont en tenant compte des tolérances normales de fabrication et autres jeux de fonctionnement.The piston 50 of the movable valve member 48 is a cylindrical part comprising a first thin cylinder 62 of outside diameter equal to the effective diameter DE and, below in the arbitrary direction of the figure, a second cylinder 64 of larger outside diameter, the first and second cylinder 62, 64 joining at a transverse shoulder 66. Those skilled in the art will easily understand that the dimensions and diameters described as being equal are so taking into account normal manufacturing tolerances and other operating clearances.

Le second cylindre 64 du piston est pourvu d'un alésage 68 débouchant dans la face inférieure limitant l'extrémité basse à une surface annulaire biseautée formant lèvre d'étanchéité 70. Depuis cette lèvre 70, l'alésage 68 s'étend axialement dans le second cylindre 64 en un premier tronçon 72 de diamètre D72 supérieur au diamètre effectif DE puis, en un second tronçon 74 de diamètre égal au diamètre effectif DE. Les deux tronçons de l'alésage 72, 74, se raccordent selon un épaulement intérieur duquel le second tronçon 74 s'étend jusqu'à une face de fond 76 de laquelle part un canal de retour 78 qui s'étend axialement dans le premier cylindre 72 jusqu'à en déboucher dans la partie émergeante hors du corps de buse.The second cylinder 64 of the piston is provided with a bore 68 opening into the lower face limiting the lower end to a bevelled annular surface forming a sealing lip 70. From this lip 70, the bore 68 extends axially in the second cylinder 64 in a first section 72 of diameter D72 greater than the effective diameter DE then in a second section 74 of diameter equal to the effective diameter DE. The two sections of the bore 72, 74, connect according to an internal shoulder from which the second section 74 extends to a bottom face 76 from which a return channel 78 starts which extends axially in the first cylinder 72 until it emerges from it in the emerging part outside the body nozzle.

Le membre obturateur 52 du membre mobile de vanne 48 comprend quant à lui trois parties cylindrique coaxiales dont la partie centrale est une collerette discale 80 transverse, parfois dénommée de son nom anglais « boost flange », dont le diamètre extérieur est ajusté coulissant à la face interne 40 du corps 30. Du centre de la face supérieure 82 de la collerette 80 s'étend un arbre cylindrique 84 de diamètre égal au diamètre effectif DE, ledit arbre cylindrique 84 s'étendant d'abord au travers du premier tronçon 72 de l'alésage du piston et s'engageant ensuite ajusté coulissant dans le second tronçon 74 de l'alésage du piston. Du centre de la face inférieure 86 de la collerette 80 s'étend un arbre cylindrique pointu 88 de diamètre D88 supérieur au diamètre effectif DE, ledit arbre cylindrique pointu 88 étant pourvu en son extrémité pointue du siège mobile 56 de vanne coopérant avec le siège fixe 46 de vanne du corps de buse 30.The obturator member 52 of the movable valve member 48 comprises for its part three coaxial cylindrical parts, the central part of which is a transverse disc collar 80, sometimes referred to by its English name "boost flange", the outside diameter of which is adjusted to slide to the face. 40 of the body 30. From the center of the upper face 82 of the flange 80 extends a cylindrical shaft 84 of diameter equal to the effective diameter DE, said cylindrical shaft 84 extending firstly through the first section 72 of the piston bore and then slidably engaging the second section 74 of the piston bore. From the center of the lower face 86 of the flange 80 extends a pointed cylindrical shaft 88 of diameter D88 greater than the effective diameter DE, said pointed cylindrical shaft 88 being provided at its pointed end with the movable valve seat 56 cooperating with the fixed seat 46 of nozzle body valve 30.

La collerette 80 est pourvue sur sa face supérieure 82 d'une surface annulaire d'étanchéité 90 coopérant avec la lèvre d'étanchéité 70 du piston ainsi que de deux orifices restreint traversant la collerette 80 entre sa face supérieure 82 et sa face inférieure 86. Le premier orifice restreint 94 est agencé à l'extérieur de la surface annulaire d'étanchéité 90, c'est-à-dire entre la surface annulaire 86 et le bord périphérique de la collerette, alors que le second orifice restreint 96 est à l'intérieur de la surface annulaire d'étanchéité 90.The collar 80 is provided on its upper face 82 with an annular sealing surface 90 cooperating with the sealing lip 70 of the piston as well as with two restricted orifices passing through the collar 80 between its upper face 82 and its lower face 86. The first restricted orifice 94 is arranged outside the annular sealing surface 90, that is to say between the annular surface 86 and the peripheral edge of the flange, while the second restricted orifice 96 is on the outside. inside the annular sealing surface 90.

Du fait de l'ajustement glissant de la collerette 80 dans la face interne de la paroi du corps de buse, le collerette 80 sépare l'espace intérieur V du corps de buse en un espace amont V1 situé au-dessus de la collerette 80, du côté de la face supérieure 82 et de l'orifice d'entrée 44 de carburant dans le corps de buse et, un espace aval V2 situé en-dessous de la collerette 80, du côté de la face inférieure 86 et des trous d'injection 38 s'ouvrant dans le sac S. Les orifices restreints 94, 96, créent donc des communications de fluide entre les espaces amont V1 et aval V2.Due to the sliding fit of the flange 80 in the inner face of the wall of the nozzle body, the flange 80 separates the inner space V of the nozzle body into an upstream space V1 located above the flange 80, on the side of the upper face 82 and the inlet 44 for fuel in the nozzle body and, a downstream space V2 located below the flange 80, on the side of the lower face 86 and the holes of injection 38 opening into the bag S. The restricted orifices 94, 96 therefore create fluid communications between the upstream V1 and downstream V2 spaces.

En s'engageant dans le second tronçon 74 de l'alésage, l'arbre cylindrique 88 de diamètre DE traverse le premier tronçon 72 qui définit, une chambre annulaire C1 dans laquelle débouche le second orifice restreint 94 établissant une communication de fluide avec l'espace aval V2.By engaging in the second section 74 of the bore, the cylindrical shaft 88 of diameter DE passes through the first section 72 which defines a annular chamber C1 into which the second restricted orifice 94 opens, establishing fluid communication with the downstream space V2.

De plus, la face du fond 76 du second alésage du piston et l'extrémité de l'arbre cylindrique 84 définissent une chambre de retour C2 dans laquelle est comprimé un ressort 92 qui tend à éloigner les deux pièces 50, 52, l'une de l'autre et à allonger le membre mobile de vanne 48.In addition, the bottom face 76 of the second bore of the piston and the end of the cylindrical shaft 84 define a return chamber C2 in which a spring 92 is compressed which tends to move the two parts 50, 52 away, one on the other and extend the movable valve member 48.

Dans la chambre annulaire C1 est agencé un moyen d'amarrage 98, schématisé sur la figure par deux protubérances annulaires s'engageant complémentairement et limitant ledit allongement du membre mobile de vanne 48.In the annular chamber C1 is arranged a securing means 98, shown schematically in the figure by two annular protuberances engaging complementarily and limiting said extension of the movable valve member 48.

Le premier cylindre 62 du piston est axialement guidé dans l'alésage 54 de la face supérieure du corps de buse. Selon l'alternative de la figure 2, l'alésage 54 a un diamètre D54 légèrement supérieur au diamètre effectif DE du piston et, un guide annulaire 100 indépendant ajusté autour du premier cylindre 62 garantie l'étanchéité. Le guide annulaire 100 a un diamètre intérieur égal au diamètre effectif DE et est maintenu plaqué contre le corps de buse 30 par un second ressort 102 comprimé entre le guide annulaire 100 et l'épaulement 66 du piston. Le second ressort 102 sollicite donc en permanence le piston vers le bas de la figure et plaque le guide annulaire 100 contre le haut du corps de buse. La face du guide 100 en contact avec le corps de buse 30 est biseautée et forme une autre lèvre d'étanchéité. Sur les figures les diamètres et les jeux sont représentés exagérément différents.The first cylinder 62 of the piston is axially guided in the bore 54 of the upper face of the nozzle body. According to the alternative of figure 2 , the bore 54 has a diameter D54 slightly greater than the effective diameter DE of the piston and an independent annular guide 100 fitted around the first cylinder 62 guarantees sealing. The annular guide 100 has an internal diameter equal to the effective diameter DE and is held pressed against the nozzle body 30 by a second spring 102 compressed between the annular guide 100 and the shoulder 66 of the piston. The second spring 102 therefore permanently urges the piston towards the bottom of the figure and presses the annular guide 100 against the top of the nozzle body. The face of the guide 100 in contact with the nozzle body 30 is bevelled and forms another sealing lip. In the figures the diameters and the clearances are shown to be exaggeratedly different.

Selon l'alternative de la figure 4, le guide annulaire 100 est intégré à un guide haut 104 comprenant la face transverse supérieure 34 du corps de buse, face pourvue de l'orifice d'entrée 44 de carburant, du centre de laquelle s'étend le guide annulaire 100. Ledit guide haut 104 est maintenu en place comprimé entre le corps de buse 30 et le corps d'actionneur 16 par l'écrou d'injecteur 58. Ledit autre ressort 102 est alors comprimé entre le guide haut 104 et l'épaulement 66 du piston.According to the alternative of figure 4 , the annular guide 100 is integrated into a top guide 104 comprising the upper transverse face 34 of the nozzle body, face provided with the fuel inlet orifice 44, from the center of which the annular guide 100 extends. Said guide top 104 is held in place compressed between the nozzle body 30 and the actuator body 16 by the injector nut 58. Said other spring 102 is then compressed between the top guide 104 and the shoulder 66 of the piston.

En fonctionnement, le premier cylindre 62 du piston est amené à coulisser dans le guide annulaire 100 et, l'arbre cylindrique 84 est amené à coulisser dans le second tronçon 74 de l'alésage dans le piston. L'homme du métier comprendra alors que ces ajustements glissant de cylindres mâles et femelles nécessite un jeu de fonctionnement J de quelques microns, ce qui n'empêche pas d'écrire que tous des cylindres mâles et femelles ont un diamètre égal au diamètre effectif DE ledit diamètre étant le diamètre nominal.In operation, the first cylinder 62 of the piston is caused to slide in the annular guide 100 and, the cylindrical shaft 84 is caused to slide in the second section 74 of the bore in the piston. Those skilled in the art will then understand that these sliding adjustments of male cylinders and female requires an operating clearance J of a few microns, which does not prevent writing that all of the male and female cylinders have a diameter equal to the effective diameter DE, said diameter being the nominal diameter.

Le fonctionnement de l'injecteur 10 est maintenant succinctement présenté en référence aux figures 2 à 5.The operation of the injector 10 is now briefly presented with reference to the figures 2 to 5 .

L'injecteur 10 est agencé au sein d'un équipement d'injection de carburant de type à rampe commune alimentant en carburant sous pression plusieurs injecteurs. Par la bouche d'entrée de l'injecteur entre donc du carburant pressurisé F et, dans un équipement d'injection diesel contemporain la pressurisation du carburant diesel peut atteindre 2000 ou 3000 bars. Pour illustrer ce fonctionnement il est choisi arbitrairement que la pression du fuel en entrée de l'injecteur est de 2500 bars.The injector 10 is arranged within a common rail type of fuel injection equipment supplying pressurized fuel to several injectors. Pressurized fuel F therefore enters through the inlet of the injector and, in contemporary diesel injection equipment, the pressurization of the diesel fuel can reach 2000 or 3000 bars. To illustrate this operation, it is arbitrarily chosen that the fuel pressure at the inlet of the injector is 2500 bars.

Le carburant F entre dans le corps de buse 30 et occupe tout l'espace interne V disponible.The fuel F enters the nozzle body 30 and occupies all the internal space V available.

Dans une première phase, selon les figures 2 ou 3, l'électroaimant 24 n'est pas alimenté, le second ressort 102 repousse le piston 50 vers le membre obturateur 52 et, le membre obturateur 52 est lui-même repoussé par le premier ressort 92 en position fermée PF, c'est-à-dire que la lèvre d'étanchéité 70 du piston est en contact étanche contre la surface annulaire 90 agencée sur la face supérieure de la collerette et, le siège mobile 56 de vanne est en contact étanche contre le siège fixe 46 le long de la ligne circulaire de diamètre effectif DE. Le sac S est isolé du volume V2. Ainsi, la chambre annulaire C1 n'est en communication qu'avec l'espace aval V2 via le second orifice restreint 96.In a first phase, according to figures 2 or 3 , the electromagnet 24 is not supplied, the second spring 102 pushes the piston 50 towards the shutter member 52 and, the shutter member 52 is itself pushed back by the first spring 92 in the closed position PF, that is to say say that the sealing lip 70 of the piston is in sealed contact against the annular surface 90 arranged on the upper face of the flange and the movable valve seat 56 is in sealed contact against the fixed seat 46 along the line circular of effective diameter DE. Bag S is isolated from volume V2. Thus, the annular chamber C1 is only in communication with the downstream space V2 via the second restricted orifice 96.

Le carburant F entré dans l'espace amont V1 via l'orifice d'entrée 44 passe dans l'espace aval V2 via le premier orifice restreint 94 puis remonte dans la chambre annulaire C1 via le second orifice restreint 96. Le passage du carburant F par les orifices restreint permet le remplissage des trois espaces V1, V2, C1 avec du carburant F à haute pression. Une légère différence de pression peut exister entre ces trois espaces. En phase de fermeture, si 2500 bars de pression règnent dans l'espace amont V1, la pression dans l'espace aval V2 peut n'être que de 2200 bars et la pression dans le sac S de 2100 bars. La pression dans la chambre annulaire C1 est sensiblement égale à celle qui se trouve dans l'espace aval V2 et, la chambre de retour C2 étant en permanence en communication avec la basse pression, aucune pression particulière n'y règne.The fuel F entered into the upstream space V1 via the inlet port 44 passes into the downstream space V2 via the first restricted orifice 94 then rises in the annular chamber C1 via the second restricted orifice 96. The passage of fuel F through the restricted orifices allows the three spaces V1, V2, C1 to be filled with fuel F at high pressure. A slight difference in pressure may exist between these three spaces. In the closing phase, if 2500 bars of pressure prevail in the upstream space V1, the pressure in the downstream space V2 may be only 2200 bars and the pressure in the bag S of 2100 bars. The pressure in the annular chamber C1 is substantially equal to that in the space downstream V2 and, the return chamber C2 being permanently in communication with the low pressure, no particular pressure prevails there.

Durant cette phase fermée du siège de vanne, des fuites statiques mineures de carburant F ont lieu via les jeux de fonctionnement J ménagés d'une part entre l'arbre cylindrique 84 et le second tronçon 74 de l'alésage dans le piston, cette fuite s'échappant à basse pression via la chambre de retour C2 et le canal de retour 78 et, d'autre part entre le premier cylindre 62 du piston et le guide annulaire 100, cette fuite s'échappant également à basse pression pour rejoindre un circuit de retour vers un réservoir basse pression non représenté.During this closed phase of the valve seat, minor static fuel leaks F take place via the operating clearances J provided on the one hand between the cylindrical shaft 84 and the second section 74 of the bore in the piston, this leakage escaping at low pressure via the return chamber C2 and the return channel 78 and, on the other hand between the first cylinder 62 of the piston and the annular guide 100, this leak also escaping at low pressure to join a circuit back to a low pressure tank, not shown.

L'homme du métier reconnaitra de plus que le piston 50 est hydrauliquement équilibré. Effectivement la surface cumulée des faces générant sur le piston une force vers le bas est égale à la surface cumulée des faces générant sur le piston une force vers le haut. Ainsi, les forces générées par la pression s'appliquant aux faces du piston 50, faces réparties entre le premier cylindre de diamètre effectif DE et le second alésage également de diamètre effectif DE, quelles que soient la forme ou le profil desdites faces, s'équilibrent.Those skilled in the art will further recognize that the piston 50 is hydraulically balanced. Indeed the cumulative area of the faces generating a downward force on the piston is equal to the cumulative area of the faces generating an upward force on the piston. Thus, the forces generated by the pressure applying to the faces of the piston 50, faces distributed between the first cylinder of effective diameter DE and the second bore also of effective diameter DE, whatever the shape or profile of said faces, s' balance.

Il en va de même pour le membre obturateur 52 dont les faces sous pression s'étendent entre l'arbre cylindrique de diamètre effectif DE et le siège de vanne également de diamètre effectif DE.The same applies to the shutter member 52, the pressurized faces of which extend between the cylindrical shaft of effective diameter DE and the valve seat also of effective diameter DE.

Dans une seconde phase illustrée par la figure 4, l'électroaimant 24 commence à être alimenté, l'armature magnétique 28 est attirée par le champ magnétique M généré par la bobine 26 et, entrainé par l'armature magnétique le piston 50 a commencé à se soulever. Le second ressort 102 se comprime alors que le premier ressort 92 se détend, les forces des deux ressorts se compensant partiellement et, l'électroaimant 24 n'ayant alors à vaincre que la différence entre les forces des ressorts. Le premier ressort 92 maintiens le membre obturateur 52 en position fermée PF tandis que le moyen d'amarrage 98 du piston 50 et du membre obturateur 52 est juste actionné de sorte que le membre mobile 48 ne peut pas s'allonger davantage.In a second phase illustrated by the figure 4 , the electromagnet 24 begins to be supplied, the magnetic armature 28 is attracted by the magnetic field M generated by the coil 26 and, driven by the magnetic armature, the piston 50 has started to rise. The second spring 102 is compressed while the first spring 92 expands, the forces of the two springs partially compensating for each other, the electromagnet 24 then only having to overcome the difference between the forces of the springs. The first spring 92 maintains the shutter member 52 in the closed position PF while the means 98 for anchoring the piston 50 and the shutter member 52 is just actuated so that the movable member 48 cannot extend further.

La lèvre d'étanchéité 70 étant soulevée et éloignée de la surface annulaire d'étanchéité 90, la chambre annulaire C1 est en communication de fluide avec l'espace amont V1 et, du carburant F pressurisé peut passer de l'espace amont V1 à l'espace aval V2 via les deux orifices restreint 94, 96, ce qui contribue à équilibrer les pressions dans les espaces amont V1 et aval V2.The sealing lip 70 being raised and away from the annular sealing surface 90, the annular chamber C1 is in fluid communication with the upstream space V1 and pressurized fuel F can pass from the upstream space V1. to the downstream space V2 via the two restricted orifices 94, 96, which helps to balance the pressures in the upstream V1 and downstream V2 spaces.

Dans une troisième phase illustrée par la figure 5, l'alimentation électrique de l'électroaimant 24 est maintenue et le piston 50 continu de monter. Le moyen d'amarrage 98 étant actionné, le piston 50 entraîne le membre obturateur 52 de sorte que le siège de vanne 46, 56, s'ouvre et permet à du carburant F sous pression d'être injecté via les trous d'injections 38. La pression dans le sac S augmente alors et contribue à l'effort d'ouverture du membre obturateur 52. Le débit de carburant F traversant les premier et second orifices restreints 94, 96, créé un léger différentiel de pression, la pression dans l'espace amont V1 étant légèrement supérieure à la pression dans l'espace aval V2 de sorte à générer une force qui s'oppose à l'effort d'ouverture de la pression dans le sac S. Le membre obturateur 52 reste donc hydrauliquement équilibré et, l'électroaimant n'a qu'un petit effort à fournir pour poursuivre l'ouverture du membre obturateur.In a third phase illustrated by the figure 5 , the power supply to the electromagnet 24 is maintained and the piston 50 continues to rise. With the docking means 98 actuated, the piston 50 drives the shutter member 52 so that the valve seat 46, 56 opens and allows pressurized fuel F to be injected through the injection holes 38 The pressure in the bag S then increases and contributes to the force for opening the shutter member 52. The flow of fuel F passing through the first and second restricted orifices 94, 96, creates a slight pressure differential, the pressure in l. 'the upstream space V1 being slightly greater than the pressure in the downstream space V2 so as to generate a force which opposes the opening force of the pressure in the bag S. The shutter member 52 therefore remains hydraulically balanced and , the electromagnet has only a small effort to provide to continue opening the obturator member.

En phase d'ouverture, si 2500 bars de pression continuent de régner dans l'espace amont V1, la pression dans l'espace aval V2 est d'environ 2400 bars et la pression dans le sac S est de 2300 bars environ. La pression dans la chambre annulaire C1 est égale à celle qui se trouve dans l'espace amont V1 et, la chambre de retour C2 étant toujours en communication avec la basse pression, aucune pression particulière n'y règne.In the opening phase, if 2500 bars of pressure continue to reign in the upstream space V1, the pressure in the downstream space V2 is approximately 2400 bars and the pressure in the bag S is approximately 2300 bars. The pressure in the annular chamber C1 is equal to that which is in the upstream space V1 and, the return chamber C2 still being in communication with the low pressure, no particular pressure prevails there.

La longueur du premier ressort 92 ne varie pas puisque dès la seconde phase ci-dessus détaillée le moyen d'amarrage 98 est actionné et, l'électroaimant 24 n'a à vaincre que la force de compression du second ressort 102.The length of the first spring 92 does not vary since from the second phase detailed above, the anchoring means 98 is actuated and the electromagnet 24 only has to overcome the compressive force of the second spring 102.

Dans une quatrième phase de fermeture, l'alimentation de l'électroaimant est interrompue et le piston 50, sous l'influence du second ressort 102, redescend en butée étanche contre la face supérieure de la collerette. Le carburant F pressurisé ne peut plus passer de l'espace amont V1 vers l'espace aval V2 que par le premier orifice restreint 94.In a fourth closing phase, the supply to the electromagnet is interrupted and the piston 50, under the influence of the second spring 102, descends to a sealed stop against the upper face of the collar. The pressurized fuel F can no longer pass from the upstream space V1 to the downstream space V2 except through the first restricted orifice 94.

L'injection continue et le carburant pressurisé F ne pouvant plus passer de l'espace amont V1 à l'espace aval V2 que par le premier orifice restreint 94, un important différentiel de pression se créé, la pression en amont étant la plus importante. Cette différence de pression entraîne le membre obturateur 52 vers la fermeture PF du siège de vanne et l'arrêt de l'injection.As the injection continues and the pressurized fuel F can no longer pass from the upstream space V1 to the downstream space V2 through the first restricted orifice 94, a large pressure differential is created, the upstream pressure being the most important. This pressure difference drives the shutter member 52 towards closing PF of the valve seat and stopping the injection.

Durant cette phase de fermeture, si 2500 bars de pression règnent dans l'espace amont V1, la pression dans l'espace aval V2 peut n'être que de 2200 bars et la pression dans le sac S de 2100 bars. La pression dans la chambre annulaire C1 est sensiblement égale à celle qui se trouve dans l'espace aval V2 et, la chambre de retour C2 étant en permanence en communication avec la basse pression, aucune pression particulière n'y règne.During this closing phase, if 2500 bars of pressure prevail in the upstream space V1, the pressure in the downstream space V2 may be only 2200 bars and the pressure in the bag S of 2100 bars. The pressure in the annular chamber C1 is substantially equal to that which is in the downstream space V2 and, the return chamber C2 being permanently in communication with the low pressure, no particular pressure prevails there.

Des simulations et des essais concluants ont été réalisés sur des injecteurs dont le diamètre effectif est de 1,5 mm, la somme des efforts des ressorts est un peu supérieure à 40N de sorte que le siège de vanne soit étanche en position fermée sous une pression de 250 bars pour compenser une pression dans la chambre de combustion, notamment en fin de combustion. L'électroaimant doit pouvoir engendrer une force de l'ordre de 65N sur une course d'environ 250 µm.Simulations and conclusive tests have been carried out on injectors with an effective diameter of 1.5 mm, the sum of the forces of the springs is a little greater than 40N so that the valve seat is tight in the closed position under pressure. 250 bars to compensate for a pressure in the combustion chamber, in particular at the end of combustion. The electromagnet must be able to generate a force of the order of 65N over a stroke of approximately 250 µm.

LISTE DES REFERENCES UTILISEESLIST OF REFERENCES USED

X1X1
axe principalmain axis
VV
espace intérieur du corps de buseinterior space of the nozzle body
MM
champ magnétiquemagnetic field
FF
carburantfuel
PFPF
position ferméeclosed position
POPO
position ouverteopen position
DEOF
diamètre effectifeffective diameter
D72D72
diamètre du premier tronçon d'alésagediameter of the first bore section
D88D88
diamètre de l'arbre pointusharp shaft diameter
V1V1
espace amontupstream space
V2V2
espace avaldownstream space
C1C1
chambre annulaireannular chamber
C2C2
chambre de retourreturn chamber
JJ
jeu de fonctionnementrunning game
SS
sacbag
1010
injecteurinjector
1212
ensemble actionneuractuator assembly
1414
ensemble de busenozzle set
1616
corps d'actionneuractuator body
1818
tête d'injecteurinjector head
2020
face transverse inférieure du corps d'actionneurlower transverse face of the actuator body
2222
alésage de bobinecoil bore
2424
électroaimantelectro magnet
2626
bobinecoil
2828
armature magnétiquemagnetic frame
3030
corps de busenozzle body
3232
paroi périphérique de corps de buseperipheral wall of nozzle body
3434
face transverse supérieure du corps de buseupper transverse face of the nozzle body
3636
extrémité pointuepointed end
3838
trous d'injectioninjection holes
4040
face interne de la paroi périphériqueinternal face of the peripheral wall
4242
face externe de la paroi périphériqueexternal face of the peripheral wall
4444
orifice d'entrée de carburant dans le corps de busefuel inlet port in the nozzle body
4646
siège fixe de vannefixed valve seat
4848
membre mobile de vannemovable valve member
5050
pistonpiston
5252
membre obturateurobturator member
5454
alésage de la face supérieure du corps de busebore of the upper face of the nozzle body
5656
siège mobile de vannemovable valve seat
5858
écrou d'injecteurinjector nut
6060
canal à haute pressionhigh pressure channel
6262
premier cylindre du pistonfirst cylinder of the piston
6464
second cylindre du pistonsecond piston cylinder
6666
épaulement extérieur du pistonouter piston shoulder
6868
alésage du pistonpiston bore
7070
lèvre d'étanchéitésealing lip
7272
premier tronçon de l'alésage dans le pistonfirst section of the bore in the piston
7474
second tronçon de l'alésage dans le pistonsecond section of the bore in the piston
7676
face de fond du second tronçonbottom face of the second section
7878
canal de retourreturn channel
8080
collerettecollar
8282
face supérieure de la colleretteupper face of the collar
8484
arbre cylindriquecylindrical shaft
8686
face inférieure de la colleretteunderside of the collar
8888
cylindre pointupointed cylinder
9090
surface annulaire d'étanchéitéannular sealing surface
9292
premier ressortfirst spring
9494
premier orifice restreintfirst orifice restricted
9696
second orifice restreintsecond orifice restricted
9898
moyen d'amarragemooring means
100100
guide annulaireannular guide
102102
second ressortsecond spring
104104
guide hauttop guide

Claims (7)

  1. Mobile valve member (48) that is designed to be arranged in the nozzle body (30) of a fuel (F) injector (10), the mobile member (48) extending along a main axis (X1) between a top end and a bottom end that is provided with a mobile valve seat (56) designed to cooperate with a static seat (46) arranged on the inner face (40) of the nozzle body about a circular line of the effective diameter (DE), the mobile member (48) being designed to slide between a closed position (PF) in which the two valve seats (46, 56) are in sealing contact about said circular line to prevent fuel injection, and an open position (PO) in which the two valve seats are separated from one another to enable said injection;
    characterized in that the mobile member (48) includes:
    - a piston (50) made up of a first male cylinder (62) of effective diameter (DE) forming the top end of the mobile member (48) and a second cylinder (64) with a greater external diameter provided with an internal cylindrical bore (68) of effective diameter (DE) extending axially (X1) in the second cylinder (64) as far as a back (76),
    - a shutoff member (52) made up of a cylindrical body comprising a male cylindrical shaft (84) of effective diameter (DE) that fits slidingly with clearance (J) in the internal bore (68) of the piston, and a male pointed cylindrical member (88) with a greater diameter (D88) than the effective diameter (DE), the pointed cylindrical member (88) extending as far as a pointed end including the mobile valve seat (56) and forming the bottom end of the mobile member (48),
    such that the mobile valve member (48) is hydraulically balanced and the length between the top end and the bottom end thereof is variable as a result of the sliding of the cylindrical shaft (84) in the internal bore (68) of the piston;
    the mobile valve member (48) also including a first compressed spring (92) between the piston (50) and the shutoff member (52) that permanently stresses the piston and the shutoff member to extend the mobile member.
  2. Mobile valve member (48) according to Claim 1, in which the shutoff member (52) also has a disk flange (80) substantially arranged between the cylindrical shaft (84) and the pointed cylinder (88), said flange extending radially from the cylindrical body of the shutoff member to a peripheral edge designed to fit slidingly against the inner face (40) of the injector nozzle body, the flange (80) having an upper face (82) facing the piston and an opposing lower face (86) facing the valve seat, said flange also defining a first restricted orifice (94) and a second restricted orifice (96), both of which extend between the opposing faces of the flange, enabling the pressurized fuel (F) to flow at reduced speed from one side to the other of the flange, creating a pressure difference between the faces of the flange.
  3. Mobile valve member (48) according to any one of the preceding claims, in which the piston (50) also has a return channel (78) extending from the back (76) of the internal bore (68) and opening out at the top end of the first cylinder.
  4. Mobile valve member (48) according to one of Claims 2 or 3, in which the bore (68) has a first section (72) of greater diameter than the effective diameter (DE) and a second section (74) of effective diameter (DE), such that the piston (50) includes a circular end forming a sealing lip (70) cooperating with a circular annular surface (90) of the upper face of the flange, the first restricted orifice (94) being arranged on the outside of said circular annular surface (90) and the second restricted orifice (96) being arranged on the inside of said circular annular surface (90).
  5. Mobile valve member (48) according to Claim 4, in which the mobile member is limited in extension by anchoring means (98) preventing the shutoff member (52) from becoming detached from the piston (50), and in compression by the sealing lip (70) butting sealingly against the upper face of the flange.
  6. Injection nozzle (14) of a high-pressure fuel injector, the nozzle including a mobile valve member (48) made according to any one of the preceding claims, and
    a nozzle body (30) that is elongate along the main axis (X1) and that has a cylindrical lateral peripheral wall (32) that is tapered at one end, and an upper wall at the other end, the upper wall having a pressurized fuel inlet orifice (44) and an axial through-bore forming an annular guide (100) of effective diameter (DE), the tapered end being formed on the inner face of the wall of the nozzle body of the static valve seat (46) arranged close to the injection holes (38) extending across the peripheral wall,
    the mobile member (48) being arranged axially to slide in the internal space (V) of the nozzle body, the first cylinder (62) of the piston fitting slidingly with clearance (J) in the open annular guide (100), such that the mobile valve seat (56) cooperates with the fixed valve seat (46) and that the mobile assembly (48) can slide along the main axis (X1) between the closed position (PF) and the open position (PO) in which the mobile seat is separated from the static seat.
  7. Fuel injector (10) including an actuator (24) and a nozzle (14) made according to Claim 6, characterized in that the actuator (24) is an electromagnet including a static coil (26) and a mobile magnetic armature (28) attached directly to the piston (50).
EP16787766.1A 2015-10-23 2016-10-18 Fuel injector Active EP3365548B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1560122A FR3042822B1 (en) 2015-10-23 2015-10-23 FUEL INJECTOR
PCT/EP2016/074983 WO2017067930A1 (en) 2015-10-23 2016-10-18 Fuel injector

Publications (2)

Publication Number Publication Date
EP3365548A1 EP3365548A1 (en) 2018-08-29
EP3365548B1 true EP3365548B1 (en) 2020-12-09

Family

ID=54848795

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16787766.1A Active EP3365548B1 (en) 2015-10-23 2016-10-18 Fuel injector

Country Status (5)

Country Link
US (1) US10502170B2 (en)
EP (1) EP3365548B1 (en)
CN (1) CN108138717B (en)
FR (1) FR3042822B1 (en)
WO (1) WO2017067930A1 (en)

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Publication number Priority date Publication date Assignee Title
HUE027556T2 (en) * 2012-06-13 2016-10-28 Delphi Int Operations Luxembourg Sarl Fuel injector
GB2567191B (en) * 2017-10-05 2020-04-29 Delphi Tech Ip Ltd Fuel injector
US11035332B2 (en) * 2017-12-19 2021-06-15 Caterpillar Inc. Fuel injector having dual solenoid control valves
GB2574841A (en) * 2018-06-19 2019-12-25 Rklab Ag Injector apparatus
JP7143715B2 (en) * 2018-10-05 2022-09-29 株式会社デンソー fuel injection valve and engine system
CN109720604B (en) * 2019-01-31 2024-05-24 北京星际荣耀空间科技股份有限公司 Medium supply structure, attitude and orbit control power system and rocket
CN112879177B (en) * 2021-02-05 2022-07-08 中国空气动力研究与发展中心空天技术研究所 Hypersonic mechanical transmission type gas-liquid dual-purpose pulse injection device and method

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US4306680A (en) * 1980-05-12 1981-12-22 General Motors Corporation Compression operated injector
DE4142940C2 (en) * 1991-12-24 1994-01-27 Bosch Gmbh Robert Electrically controlled pump nozzle
GB9404260D0 (en) * 1994-03-05 1994-04-20 Lucas Ind Plc Fuel injection nozzles
JP3938970B2 (en) * 1997-04-17 2007-06-27 株式会社日本自動車部品総合研究所 Accumulated fuel injection system
DE19954802A1 (en) 1999-11-13 2001-05-17 Bosch Gmbh Robert Fuel injector
US7051993B2 (en) * 2004-03-10 2006-05-30 Eaton Corporation Solenoid operated valve and method of making same
CN100368679C (en) * 2004-04-30 2008-02-13 株式会社电装 Injector having structure for controlling nozzle needle
JP2011190798A (en) * 2010-02-17 2011-09-29 Denso Corp Fuel injection valve
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Also Published As

Publication number Publication date
CN108138717B (en) 2020-03-13
EP3365548A1 (en) 2018-08-29
CN108138717A (en) 2018-06-08
US20180313316A1 (en) 2018-11-01
FR3042822B1 (en) 2017-12-22
US10502170B2 (en) 2019-12-10
WO2017067930A1 (en) 2017-04-27
FR3042822A1 (en) 2017-04-28

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