EP2310662B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2310662B1
EP2310662B1 EP09779562A EP09779562A EP2310662B1 EP 2310662 B1 EP2310662 B1 EP 2310662B1 EP 09779562 A EP09779562 A EP 09779562A EP 09779562 A EP09779562 A EP 09779562A EP 2310662 B1 EP2310662 B1 EP 2310662B1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel injector
fuel
injection valve
valve element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP09779562A
Other languages
German (de)
English (en)
Other versions
EP2310662A1 (fr
Inventor
Matthias Burger
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 EP2310662A1 publication Critical patent/EP2310662A1/fr
Application granted granted Critical
Publication of EP2310662B1 publication Critical patent/EP2310662B1/fr
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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

Definitions

  • the invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injector is out of the DE 10 2004 005 452 A1 known.
  • the rail pressure prevails in the hydraulic coupler.
  • a disadvantage of the known fuel injector is that the pressure in the coupler space is the same size as outside the coupler space. This leads to a relatively slow response of the injection valve element in its control.
  • a hydraulic element which acts as a pressure intensifier in the manner of a coupler.
  • the hydraulic coupler there is low pressure and a lower pressure than outside.
  • An outflow in the direction of the low pressure region of the injector is not known from the cited document.
  • the pressure in the coupler space is the same or higher than the system pressure in the drive case.
  • the present invention seeks to further develop a fuel injector according to the preamble of claim 1 such that the injection valve element in a control with responds to the least possible delay.
  • This object is achieved in a fuel injector with the features of claim 1 according to the invention, that in the hydraulic coupler, a lower pressure is realized than outside the guides.
  • the invention is based on the idea to achieve a strong compression of the two separate, coupled by means of the hydraulic coupler (operatively connected), injection valve element parts characterized in that the hydraulic coupler, more precisely a coupler space of the coupler, in particular permanently, with a low pressure source, in particular one with a Injector return associated low pressure region of the injector, is connected. Due to the reduced within the hydraulic coupler compared to the high-pressure region of the fuel injector, the injection valve element parts are permanently and substantially interconnected during operation of the fuel injector, so that they can be considered as one-piece from a functional point of view.
  • a fuel injector designed according to the concept of the invention provides that both guides are surrounded at least in sections radially outwardly with fuel under high pressure.
  • the at least one injector component which delimits the guide gap radially outwardly, is surrounded by high-pressure fuel in an area radially outward of the respective guide gap formed between the at least one injector component and the injection valve element, thereby expanding the guide gaps by penetrating into the guide gaps High pressure fuel is avoided.
  • a low-pressure stage is realized, which causes a force acting in the closing direction of the injection valve element hydraulic force.
  • the injection valve element switching time can be accelerated. Since the closing force generated by the low-pressure stage, hydraulic, acting on the injection valve element, closing force is rail horrin, this closing force acts not only during the injection, as in a closing throttle, but permanently. It is particularly preferred if an additional closing throttle, which reduces the fuel pressure in the region of the injection valve element support in comparison to the fuel pressure in the region of an inlet channel of the fuel injector, is dispensed with. By providing a closing throttle, the effective injection pressure would be reduced by up to about 150 bar.
  • the low-pressure stage is preferably implemented by reducing the diameter of the injection valve element part (nozzle needle) adjacent to the nozzle hole arrangement in comparison with the diameter of the nozzle-hole-remote injection valve element part in a section (something) delimiting the hydraulic coupler.
  • the guide diameter of the guide facing the nozzle hole arrangement is preferably somewhat smaller than the guide diameter of the other, the hydraulic coupler axially limiting (in particular upper) guide.
  • the hydraulic coupler is connected via a connecting channel to a low pressure region of the fuel injector.
  • the connecting channel at least approximately, throttle-free, prevails within the hydraulic coupler, at least approximately, low pressure, preferably in a pressure range between about 0 and 20 bar.
  • the hydraulic coupler limiting guides is formed by a sleeve-shaped extension of a plate member, said sleeve-shaped extension, at least partially, preferably completely, radially outwardly surrounded by under high pressure fuel. It is particularly preferred to provide in the plate member a portion of the connecting channel, in particular as a radial channel, which connects the hydraulic coupler with the low-pressure region of the fuel injector. In the low-pressure region of the fuel injector, not only the named connection channel but also a discharge channel from a control chamber via which fuel flows out of the control chamber in the direction of the injector return when the control valve is open, preferably discharges.
  • At least one, preferably throttle-free, axial channel is provided, can flow through the fuel with the injector element open in the axial direction of the nozzle hole arrangement.
  • the plate element is arranged between an (upper) injector body and a (lower) nozzle nozzle arrangement having a nozzle body, that is clamped between these housing parts.
  • the nozzle body is screwed by means of a union nut with an external thread of the injector body.
  • At least one of the couplers axially delimiting guides is formed by a arranged in a high-pressure chamber, in particular spring-loaded sleeve.
  • the sleeve is pressed by the spring in the axial direction against the previously described plate member.
  • this spring is at the same time an injection valve element part in the direction of the nozzle hole arrangement acted upon closing spring which is at one end on the sleeve and the other end on the injection valve element part, in particular on a peripheral collar or a locking ring of the injection valve element part supported.
  • the hydraulic coupler is placed at the low pressure applied to the injector return.
  • the pressure in the hydraulic coupler is dimensioned so that it is under the high pressure of the fuel outside of the hydraulic coupler limiting guides, but above the low pressure in the range of injector return.
  • at least one throttle is preferably arranged in the connection channel connecting the hydraulic coupler to the low-pressure region. This is adjusted so that the pressure in the hydraulic coupler is higher than in the area of the injector return.
  • the pressure in the hydraulic coupler is now load-dependent, it is preferred, in the case of providing such a throttle, to dispense with a low-pressure stage in the hydraulic coupler, so that the hydraulic coupler no longer has the function of a hydraulic Closing force to produce, but only a coupling function. Due to the somewhat increased pressure in the hydraulic coupler, the already small amount of leakage, which flows through the guides into the hydraulic coupler and thus into the low-pressure region, is further reduced.
  • the throttle is designed so that the pressure in the hydraulic coupler corresponds approximately to half the rail pressure.
  • a closing throttle is preferably provided for generating a hydraulic closing force, which is dimensioned such that the pressure in the region of the tip of the injection valve element is lower, preferably by about 50 to 200 bar, than the rail pressure.
  • Structurally particularly elegant is an embodiment in which such a closing throttle is arranged in an injector component which defines a control chamber radially inwardly.
  • an inlet throttle for the control chamber and an outlet throttle from the control chamber and possibly also a filler throttle are preferred in this injector component introduced for accelerated refilling of the control chamber.
  • Fig. 1 is a designed as a common rail injector fuel injector 1 for injecting fuel into a combustion chamber of an internal combustion engine, not shown Motor vehicle shown.
  • a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel or gasoline, under high pressure, stored in this embodiment about 2000 bar.
  • the fuel injector 1 is connected, among other injectors, not shown, via a supply line 5.
  • the supply line 5 opens into a supply channel 6 of the fuel injector 1, which opens into a high-pressure chamber 7 of the fuel injector 1.
  • the high-pressure chamber 7 forms a mini-rail, due to which pressure oscillations are minimized.
  • a return line 8 a low-pressure region 9 of the fuel injector 1 is connected to the reservoir 3. Via an injector return port 10 and the return line 8, a control amount to be explained later as well as a small leakage quantity of fuel can flow away from the fuel injector 1 to the reservoir 3.
  • the fuel injector 1 has a housing 11, which has an injector body 12 into which the supply channel 6 is introduced and comprises a lower nozzle body 13. Between the injector body 12 and the nozzle body 13, a plate element 14 to be explained later is clamped, wherein the nozzle body 13 is clamped against the plate element 14 by means of a union nut 15 and this in turn against the nozzle body 13. For this purpose, the union nut 15 is screwed to an external thread of the injector body 12.
  • the head part of the housing 11 is formed by a clamping nut 16, which is screwed to the injector body 12, and which clamps a cover element 17, comprising the injector return port 10, against an electromagnet arrangement 18 of an electromagnetic actuator 19, which will be explained later in the axial direction on an inner shoulder 20 of the clamping nut 16 rests.
  • a two-part injection valve element 21 is accommodated in the housing 11, more precisely in the injector body 12 and in the nozzle body 13, a two-part injection valve element 21 is accommodated.
  • This comprises an upper, first part 22 (control rod) and a lower, second part 23 (nozzle needle).
  • the first and the second part 22, 23 of the injection valve element 21 are coupled together via a hydraulic coupler 24 to be explained later and behave like a single component.
  • the second, lower part 23 of the injection valve element 21 is guided in a guide bore 25 in the nozzle body 13.
  • axial channels 26 are formed on the outer circumference of the second part 23 in an area within the guide bore 25, through which fuel can flow from the high-pressure chamber 7 into a lower annular space 67 when the injection valve element 21 is open, in which substantially the same fuel pressure prevails as in the high-pressure space 7.
  • the axial channels 26 designed as bevels and an axial channel 66 in the plate element 14 are (at least approximately) throttle-free.
  • the fuel pressure in a gap formed between the plate member 14 and the guide bore 25 27 corresponds to the fuel pressure within the high-pressure chamber 7.
  • otherwise required in the prior art closing throttle Fig. 1 In contrast to the later to be explained embodiment according to Fig. 2 ) deliberately omitted.
  • the injection valve element 21, more precisely the second part 23, has at its tip 28 a closing surface 29 with which the injection valve element 21 can be brought into tight contact with an injection valve element seat 30 (nozzle needle seat) formed inside the nozzle body 13.
  • an injection valve element seat 30 nozzle needle seat
  • the injection valve member 21 abuts its injection valve member seat 30, i. is in a closed position, the fuel outlet from a nozzle hole arrangement 31 is locked. If, on the other hand, it is lifted off its injection valve element seat 30 and is in a non-ballistic open position, fuel can flow from the high-pressure chamber 7 via the intermediate space 27 and the lower annular space 67 past the injection valve element seat 30 to the nozzle hole arrangement 31 and there substantially under high pressure (Rail pressure) standing in the combustion chamber are injected.
  • a control chamber 35 is limited, via a radially extending in the sleeve-shaped portion 33 inlet throttle 36 with high-pressure fuel is supplied from the high-pressure chamber 7.
  • the control chamber 35 is connected to a valve chamber 39 of a control valve 40 (servo-valve) via a flow restrictor 38 provided in an upper, plate-shaped section 37 of the injector component 34.
  • the valve chamber 39 is bounded radially outwardly by a sleeve-shaped control valve member 41, which is integral with one with the electromagnetic actuator 19 cooperating armature plate 42 is formed.
  • the sleeve-shaped control valve element 41 is pressure balanced in its closed position in the axial direction.
  • the control chamber 35 is bounded axially upward by a guide pin 43 which is axially supported on the cover member 17 and on the one hand has the task to guide the control valve member 41 during its adjustment and on the other hand to seal the valve chamber 39 in the axial direction upwards.
  • fuel can flow into the low-pressure region 9 of the fuel injector 1 when the control valve element 41 actuated by the electromagnetic actuator 19 is lifted off its control valve seat 44, which is designed as a flat seat and arranged on the plate-shaped section 37 of the injector component 34, ie the control valve 40 is open.
  • the injection valve element 21 thus lifts off from its injection valve element seat 30, so that fuel can flow out through the nozzle hole arrangement 31.
  • the energization of the solenoid assembly 18 of the electromagnetic actuator 19 is interrupted.
  • the sleeve-shaped control valve element 41 moves back onto its control valve seat 44.
  • the fuel flowing in through the inlet throttle 36 rapidly increases the pressure in the control chamber 35, as a result of which the injection valve element 21 is supported by the Spring force of a closing spring 47, is moved back to its injection valve element seat 30, which in turn the fuel flow from the nozzle hole assembly 31 is interrupted in the combustion chamber.
  • the filling of the control chamber 35 via the inlet throttle 36 is accelerated via a Ruddrossel 61 which connects the high pressure chamber 7 permanently hydraulically with the valve chamber 39. Possibly. can also be dispensed with this Standdrossel 61.
  • the first and second parts 22, 23 of the injection valve element 21 are hydraulically coupled together in the hydraulic coupler 24, more specifically in a coupler space 48, and behave as a single component. This is due to the fact that the hydraulic coupler 24, or the coupler chamber 48 is permanently connected via a multi-part connecting channel 49 with the arranged in the injector low pressure region 9 of the fuel injector 1, and thus during operation of the fuel injector 1 permanently low pressure lies.
  • the connecting channel 49 is formed by a provided in the plate member 14 radial channel 50, an annular space 51 radially between the plate member 14 and the union nut 15 and a vertically extending channel 52 in the injector 12th
  • the hydraulic coupler 24 is limited in the embodiment shown in the axial direction upward by a first guide 53 for the first part 22 of the injection valve element 21 and in the axial direction down from a second guide 54 for the second, lower part 23 of the injection valve element 21st
  • the first guide 53 comprises a first guide gap 55 (annular gap) radially between a sleeve-shaped extension 56 of the plate member 14 and a lower portion of the first part 22 of the injection valve element 21.
  • the second guide 54 comprises a second guide gap 57 (annular gap) radially between a
  • the closing spring 47 is supported at one end on the lower end face of the sleeve 58 and at the other end on a circumferential collar 59 of the second part 23 of the injection valve element 21 from the closing spring 47 spring-loaded sleeve 58 and an upper portion of the second part 23 of the injection valve element 21.
  • the guide gaps 55, 57 are comparatively fuel-tight. This is primarily attributable to the fact that the first guide 53, more precisely the sleeve-shaped extension 56, is arranged inside the high-pressure chamber 7, that is to say is surrounded radially on the outside by high-pressure fuel. As a result, the first guide gap 55 experiences no expansion radially outward due to the low leakage flowing through the first guide gap 55 into the coupler space 48.
  • the second guide 54 more precisely, the sleeve 58 is disposed within the gap 27, in which approximately the same pressure prevails as in the high-pressure chamber 7, so that the second guide gap 57 is not widened because the sleeve 58 radially outward from under high pressure Fuel is surrounded. As a result, the amount of leakage flowing via the guides 53, 54 into the hydraulic coupler 24 is which continues to flow via the connecting channel 49 into the low-pressure region 9, low.
  • a low-pressure stage 60 realized, which has a force acting in the closing direction of the injection valve element 21 force.
  • the low-pressure stage 60 is realized in that the diameter D I of the first part 21 in the region of the first guide 53 (slightly) is greater than the diameter D II of the second part 23 of the injection valve element 21 in the region of the second guide 54.
  • the injection valve element 21 should open only when the control valve 40 can already be operated non-ballistic. Without the realized low-pressure stage 60, the start of injection can be delayed only for a mechanically soft injection valve element 21 or a small drain / inlet throttle ratio. Both measures lead to disadvantages in the injector behavior: While a soft injection valve element 21 leads to a poorer multiple injection suitability, a small drain / feed throttle ratio reduces the increase in the jet force of the injection jet and generally leads to emission disadvantages.
  • a throttle 62 In contrast to the embodiment according to Fig. 1 is integrated in the connecting channel 49, more precisely in the radial channel 50 between the hydraulic coupler 24 and the low-pressure region 9, a throttle 62. This is designed so that prevails in the hydraulic coupler 24, more precisely in the coupler 48, about half the pressure, as in the high-pressure chamber 7 and in the intermediate space 27. This is achieved in that the pressure drop across the guides 53, 54 in about the pressure drop the throttle 62 corresponds.
  • the over the guide gaps 55, 57 flowing off leakage amount is further reduced.
  • the component load of the plate member 14 and the sleeve 58 is reduced.
  • the fuel injector 1 according to Fig. 2 equipped with an additional closing throttle 63, which is introduced into the sleeve-shaped portion 33 of the Injektorbauteils 34.
  • This connects the high-pressure chamber 7 with one in comparison to Fig. 1 additional, annular inlet chamber 64, which surrounds the sleeve-shaped portion 33 radially on the outside, and which is sealed via an annular sealing element 65 relative to the serving as a minirail high-pressure chamber 7.
  • the closing throttle 63 is designed in the illustrated embodiment so that the pressure in the high pressure chamber 7 is about 50-200 bar less than the rail pressure in the inlet space 64.
  • the embodiment according to Fig. 1 do not open the inlet throttle 36 and the Golfdrossel 61 from the high-pressure chamber 7, but from the inlet chamber 64.
  • the throttle 62 can, as shown, be designed as a simple throttle bore. Due to the necessary small flow cross sections which are necessary in the throttle 62, a conventional throttle bore, however, is relatively difficult to produce for reasons of tolerance. Therefore, it is preferable to perform the throttle 62 as an annular gap throttle. This can be achieved, for example, by positioning an insert part, for example a pin, in the actual throttle bore, on which the Fuel must flow past radially outside. The advantage of such a construction is the easier manufacturability.

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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 de carburant, en particulier injecteur à rampe commune, pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion interne, comprenant un élément de soupape d'injection (21) en plusieurs parties pouvant être déplacé entre une position d'ouverture et une position de fermeture, une première partie (22) et une deuxième partie (23) de l'élément de soupape d'injection (21) étant accouplées l'une à l'autre par le biais d'un coupleur hydraulique (24) qui est limité radialement par un premier guide (53) pour la première partie (22) et par un deuxième guide (54) pour la deuxième partie (23), le premier et le deuxième guide (53, 54) étant entourés au moins en partie radialement à l'extérieur par du carburant haute pression, caractérisé en ce qu'une plus faible pression règne dans le coupleur hydraulique (24) que radialement à l'extérieur des guides (53, 54).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    dans le coupleur hydraulique (24), sur l'élément de soupape d'injection (21) est réalisé un étage basse pression (60) provoquant une force de fermeture.
  3. Injecteur de carburant selon l'une quelconque des revendications 1 ou 2,
    caractérisé en ce que
    le coupleur hydraulique (24) est raccordé par le biais d'un conduit de raccordement (49) à une région basse pression (9) de l'injecteur de carburant (1).
  4. Injecteur de carburant selon la revendication 3,
    caractérisé en ce que
    le premier et/ou le deuxième guide (53, 54) est/sont formés par une saillie (56) en forme de douille d'un élément formant plaque (14), dans lequel est incorporé en partie le conduit de raccordement (49), de préférence sous forme de conduit radial (50).
  5. Injecteur de carburant selon la revendication 4,
    caractérisé en ce
    qu'au moins un conduit axial (66), de préférence sans étranglement, est prévu dans l'élément formant plaque (14).
  6. Injecteur de carburant selon l'une quelconque des revendications 4 ou 5,
    caractérisé en ce que
    l'élément formant plaque (14) est disposé entre un corps d'injecteur (12) et un corps de buse (13) présentant un agencement de trou de buse (31).
  7. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le premier et/ou le deuxième guide (53, 54) est/sont formés par une douille (58) disposée dans un espace haute pression (7), notamment sollicitée par la force d'un ressort.
  8. Injecteur de carburant selon l'une quelconque des revendications 3 à 7,
    caractérisé en ce
    qu'un étranglement (62) est disposé dans le conduit de raccordement (49), lequel est dimensionné de telle sorte que la pression dans le coupleur hydraulique (24) soit inférieure à la haute pression entourant les guides (53, 54) et soit supérieure à la pression dans la région basse pression (9).
  9. Injecteur de carburant selon la revendication 8,
    caractérisé en ce
    qu'un étranglement de fermeture (63) est prévu, lequel est dimensionné et disposé de telle sorte que la pression dans la région d'une pointe (28) de l'élément de soupape d'injection (21) soit inférieure à la pression dans un conduit d'amenée de carburant de l'injecteur de carburant (1).
  10. Injecteur de carburant selon la revendication 9,
    caractérisé en ce que
    l'étranglement de fermeture (63) est disposé dans un composant d'injecteur (34) limitant une chambre de commande (35).
EP09779562A 2008-07-24 2009-05-27 Injecteur de carburant Not-in-force EP2310662B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810040680 DE102008040680A1 (de) 2008-07-24 2008-07-24 Kraftstoff-Injektor
PCT/EP2009/056467 WO2010009932A1 (fr) 2008-07-24 2009-05-27 Injecteur de combustible

Publications (2)

Publication Number Publication Date
EP2310662A1 EP2310662A1 (fr) 2011-04-20
EP2310662B1 true EP2310662B1 (fr) 2013-01-02

Family

ID=41168644

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09779562A Not-in-force EP2310662B1 (fr) 2008-07-24 2009-05-27 Injecteur de carburant

Country Status (4)

Country Link
US (1) US8864054B2 (fr)
EP (1) EP2310662B1 (fr)
DE (1) DE102008040680A1 (fr)
WO (1) WO2010009932A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009000181A1 (de) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Kraftstoff-Injektor
DE102013225384A1 (de) 2013-12-10 2015-06-11 Robert Bosch Gmbh Kraftstoffinjektor
DE102014205093A1 (de) 2014-03-19 2015-09-24 Robert Bosch Gmbh Kraftstoffinjektor
GB201421885D0 (en) * 2014-12-09 2015-01-21 Delphi International Operations Luxembourg S.�.R.L. Fuel injector
US10006429B2 (en) * 2016-03-31 2018-06-26 GM Global Technology Operations LLC Variable-area poppet nozzle actuator
CN114060193A (zh) * 2020-08-04 2022-02-18 温特图尔汽柴油公司 大型柴油机的燃料喷射阀以及大型柴油机

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19500706C2 (de) 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen
EP1131552B1 (fr) * 1998-11-10 2002-11-27 Ganser-Hydromag Ag Soupape d'injection de carburant destinee a des moteurs a combustion interne
DE10229418A1 (de) * 2002-06-29 2004-01-29 Robert Bosch Gmbh Einrichtung zur Dämpfung des Nadelhubes an Kraftstoffinjektoren
DE10248379A1 (de) * 2002-10-17 2004-04-29 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine
DE102004005452B4 (de) 2004-02-04 2014-01-09 Robert Bosch Gmbh Düsenhalterkombination mit direktgesteuertem Einspritzventilglied
DE102004035313A1 (de) * 2004-07-21 2006-02-16 Robert Bosch Gmbh Kraftstoffinjektor mit zweistufigem Übersetzer
DE102005016796A1 (de) * 2005-04-12 2006-10-19 Robert Bosch Gmbh Zweistufig öffnender Kraftstoffinjektor
DE102006008648A1 (de) 2006-02-24 2007-08-30 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine
DE102007001363A1 (de) * 2007-01-09 2008-07-10 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff in Brennräume von Brennkraftmaschinen

Also Published As

Publication number Publication date
EP2310662A1 (fr) 2011-04-20
US8864054B2 (en) 2014-10-21
DE102008040680A1 (de) 2010-01-28
US20110139906A1 (en) 2011-06-16
WO2010009932A1 (fr) 2010-01-28

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