WO2008049675A1 - Injecteur avec une soupape de commande à compensation de pression axiale - Google Patents

Injecteur avec une soupape de commande à compensation de pression axiale Download PDF

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Publication number
WO2008049675A1
WO2008049675A1 PCT/EP2007/059080 EP2007059080W WO2008049675A1 WO 2008049675 A1 WO2008049675 A1 WO 2008049675A1 EP 2007059080 W EP2007059080 W EP 2007059080W WO 2008049675 A1 WO2008049675 A1 WO 2008049675A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve element
chamber
valve
fuel
pressure
Prior art date
Application number
PCT/EP2007/059080
Other languages
German (de)
English (en)
Inventor
Francois Rossignol
Friedrich Howey
Olivier Charvet
Tony Dumont
Original Assignee
Robert Bosch Gmbh
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
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to EP07803088A priority Critical patent/EP2084390A1/fr
Publication of WO2008049675A1 publication Critical patent/WO2008049675A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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
    • F02M2547/001—Control chambers formed by movable sleeves

Definitions

  • the invention relates to an injector according to the preamble of claim 1.
  • EP 1 612 403 A1 describes a common-rail injector with a pressure-balanced control valve in the axial direction for blocking and opening a fuel discharge path from a control chamber.
  • the control valve By means of the control valve, the fuel pressure can be influenced within the control chamber.
  • the control chamber is supplied via a pressure channel with fuel from a high-pressure fuel storage.
  • a nozzle needle By varying the fuel pressure within the control chamber, a nozzle needle is moved between an open position and a closed position, wherein the nozzle needle in its open position releases the fuel flow into the combustion chamber of an internal combustion engine.
  • the control valve has an adjustable in the axial direction by means of an electromagnetic actuator valve sleeve, which cooperates sealingly with a stationary conical valve seat surface. During its closing movement, the valve sleeve is moved in the axial direction away from the control valve towards the stationary seat element.
  • a bolt is arranged, at the free, the control chamber facing away from the end of the seat member is formed. Through the bolt passes a connecting channel, which is part of the fuel drain path and which connects the control chamber to an annulus within the valve sleeve.
  • valve sleeve valve element
  • a fuel pressure is exerted on the valve sleeve (valve element) only in the radial direction, so that the valve sleeve is pressure-balanced in the axial direction.
  • the construction of the known injector is comparatively expensive due to the intended axially displaceable sleeve.
  • the invention is therefore based on the object to propose an injector with a control valve, which is on the one hand pressure balanced in the axial direction and on the other hand manages without a displaceable in the axial direction of the valve sleeve.
  • the invention is based on the idea to introduce directly into the axially displaceable valve element a Kraftstoffka- channel, which is part of the fuel drainage path from the control chamber to a low pressure chamber.
  • a compensation chamber preferably centrally disposed within the valve element fuel passage of the fuel from the control chamber to a compensation chamber at the Steuerkam- mer remote side of the valve element flow.
  • This compensation chamber is bounded on the one hand by the valve element and on the other hand, with the control valve closed, by the seat element.
  • a compensation surface is provided according to the invention on the valve element, which is acted upon by fuel pressure in the axial direction, ie in the opening direction or in the direction of the needle tip of the nozzle needle.
  • the compensation surface is dimensioned such that an acting on the valve element in the opening direction hydraulic pressure force arises, which compensates for an opposing direction, ie in the closing direction and thus in the direction of the seat member acting on the valve element pressure force or repeals.
  • the pressure force acting in the closing direction is caused by the axial fuel pressure on the valve element in the closing direction.
  • the valve element is moved by an electromagnetic actuator in the opening direction against the force of a biasing spring acting on the valve element.
  • an electromagnetic actuator in the opening direction against the force of a biasing spring acting on the valve element.
  • the arrangement of the electromagnetic actuator axially between the control chamber and the seat member has the advantage that the control amount (fuel) can be dissipated from the low pressure chamber surrounding the seat element in a simple manner, since a corresponding return bore can be drilled directly from above into the low pressure chamber. The placement of this Return bore is not hindered by the advantageous development of the invention by the arrangement of the actuator.
  • a piezoelectric actuator can also be used. Additionally or alternatively, it is conceivable to arrange the actuator such that it applies force to the valve element in the closing direction when energized.
  • the seat element is a ball or a cone.
  • it is a separate component which is arranged supportingly on a component of the injector, preferably on the injector body.
  • the formation of the seat element as a ball has the advantage that it is available as a mass product and thus only the - in particular conical - counter surface must be ground on the valve element.
  • the fuel channel is formed within the valve element as a throttle-free through hole. It is thereby achieved that the fuel pressure in the compensation chamber and immediately adjacent to an opposite end face of the compensating surface of the valve element is at least approximately the same, whereby it is possible, by an equal design of the axial projection surface of the compensation surface and an axial projection surface of the compensation surface opposite end side of the Valve element to create a pressure force compensation in the axial direction.
  • the axial projection surfaces of the compensation surface and the opposite end face form the same size, in a further development of the invention is to match the diameter of the contact surface of the valve element on the valve seat surface of the diameter of the valve element in the region of the end face within the valve element guide.
  • the surfaces which can be acted upon with pressure in the axial direction are the same size on both sides of the valve element, which leads to a pressure force compensation in the axial direction at at least approximately the same pressure on both sides of the valve element.
  • the seat element in particular the ball, can engage in the counter-surface on the valve element by often repeated closing operations in long-term operation, resulting in a change in the valve seat diameter and thus can lead to a change in the compensation area.
  • the valve element has a cylindrical depression in its end region facing the seat element, wherein the seat element adjoins the inner edge, i. abuts the inner diameter of this cylindrical opening. Even if the seat element is incorporated into the valve element during long-term operation, the compensation surface which is effective in the axial direction remains the same size.
  • the bottom of the cylindrical opening within the valve member is tapered toward the mouth of the fuel passage within the valve member.
  • a fuel chamber is provided on the end face of the valve element which is opposite to the compensation chamber, said fuel chamber communicating with the outlet via the connection channel. is connected.
  • This chamber is connected via a fuel channel with outlet throttle with the control chamber.
  • the outlet throttle is matched to the inlet throttle arranged within the pressure chamber which supplies the control chamber with high-pressure fuel, so that when the control valve is open, a net fuel discharge into the low-pressure chamber results.
  • valve element (valve piston) is guided in a bore within a component accommodated in the injector body.
  • the guide bore for the valve element is formed as a through hole, which means that the outlet throttle is not part of this hole.
  • the outlet throttle and possibly also the chamber on the end face of the valve element are for this purpose introduced into a throttle plate arranged adjacent to the component with a through bore.
  • FIG. 1 shows a partially sectioned view of an injector with a pressure-compensated valve element in the axial direction
  • Fig. 2 is an illustration of a possible embodiment of the valve element and the associated seat element and
  • Fig. 3 a partial view of another embodiment of an injector.
  • Figs. 1 and 3 the essential components of a common rail injector 1 are shown.
  • the injector 1 has an injector body 2, a nozzle body 3 and a nozzle clamping nut 4, which is screwed to the injector body 2 and thus clamps the nozzle body 3 against the injector body 2.
  • the nozzle body 3 passes through a through hole 5 of the nozzle lock nut 4 in the axial direction.
  • a guide bore 6 is formed, in which an elongated nozzle needle 7 is guided.
  • the nozzle needle 7 has a closing surface 9 with which it can be brought into tight contact with a needle seat 10 formed inside the nozzle body 3.
  • the nozzle needle 7 is biased by an only partially indicated in Fig. 3 biasing spring 13 in the direction of its closed position.
  • the biasing spring 13 is arranged within a pressure chamber 14 and is supported at one end on a lower end face of a sleeve-shaped component 15 and at its other end on the nozzle needle 7 (not shown).
  • the sleeve-shaped component is braced with the biasing spring, not shown in FIG. 1, against a throttle plate 16 in the axial direction.
  • the sleeve-shaped component 15 is clamped by the pretensioning spring 13 against a (valve) component 17.
  • the sleeve-shaped member 15 defines together with the nozzle needle 7 and the throttle plate 16 and the component 17 a control chamber 18.
  • the control chamber 18 is supplied via a pressure channel 19 with inlet throttle 20 with fuel under high pressure.
  • the pressure channel 19 connects the control chamber 18 via a pocket 54 with a supply line 21, which connects the pressure chamber 14 surrounding the control chamber 18 with a high-pressure fuel storage, not shown.
  • the pressure channel 19 is connected to the supply line 21 via a pocket 22.
  • the pressure chamber 14 (annulus) is supplied with high-pressure fuel from a high-pressure fuel storage also in the embodiment of FIG. 1.
  • the fuel can flow from the pressure chamber in the axial direction as far as the nozzle hole arrangement 11.
  • Fuel can flow from the control chamber 18 to a low-pressure chamber 26 via a drain channel 24 equipped with an outlet throttle 23, which is part of a fuel drainage path 25, and from there flow away via a return line (not shown).
  • a pressure-balanced control valve 28 in the axial direction can block the fuel flow to the low-pressure chamber 26.
  • an axially directed toward the combustion chamber closing force is exerted on the nozzle needle 7.
  • This closing force counteracts an opening force which, as a result of the action of the fuel pressure, is exerted on a step surface (not shown) on the nozzle needle 7. If the control valve 28 is in a closed position and the fuel flow through the fuel drainage path 25 is blocked, the closing force in the stationary state is greater than the opening force, which is why the nozzle needle 7 then assumes its closed position. When the control valve 28 is then opened, the fuel flows from the control chamber 18.
  • the flow cross sections of the inlet throttle 20 and the outlet throttle 23 are matched to one another such that the inflow through the pressure channel 19 is smaller than the outflow through the outlet channel 24 and thus results in a net outflow of fuel when the control valve 28 is open.
  • the resulting pressure drop in the control chamber 18 causes the amount of closing force falls below the amount of the opening force and the nozzle needle 7 lifts from the needle seat 10.
  • the control valve 28 has an axially displaceable valve element 30 which is guided within a component 32 in a guide bore 31 formed as a through-bore.
  • the play between the bolt-shaped valve element 30 and the through-bore 31 is to be selected such that leakage losses from a plane below the component 32 (valve Body) arranged chamber 33 in the low pressure chamber 26 are low.
  • the chamber 33 is hydraulically connected via the outlet channel 24 with the control chamber 18.
  • the control chamber 18 facing end 34 with its end face 35 of the valve member 30 limits the chamber 33 in the plane of the drawing upwards. A pressure force in the closing direction acts on the end face 35 on the valve element 30.
  • a spring force acts on a helical spring 36 which is arranged radially inside a passage opening 37 of the actuator 27 and adjoins one shoulder surface 38 of the valve element 30 and the other end is supported on an adjusting ring 39, which in turn rests on the component 32.
  • the bias of the coil spring 36 and thus the closing force of the control valve 28 can be adjusted.
  • the electromagnetic actuator 27 is arranged in the plane of the drawing below the upper end of the valve element 30 and is pressed against an annular abutment surface 41 of the injector body 2 via a spring 40, which is supported on the component 32. With the electromagnetic actuator 27, an armature plate 42 cooperates, which is positively connected to the valve element 30. It is also conceivable to form the anchor plate 42 in one piece with the valve element 32.
  • the electrical connection of the coil of the actuator 27 is guided via a housing part 43 from the lower side in the drawing plane to the upper end of the injector 1 for electrical contacting (not shown).
  • valve element 30 In the illustrated closed position of the control valve 28, the valve element 30 is supported by a spring-assisted on a sitting as a ball seat member 44, which in axia- Ler direction of the control chamber 18 away directly on the injector body 2 is supported.
  • an inner cone 45 is provided on the plane of the drawing in the upper end of the valve element 30.
  • the diameter D1 of the effective valve seat surface 46 of the seat element 44 corresponds to the outer diameter D1 of the valve element 30 in the guide bore 31.
  • a compensation surface 47 is created within a compensation chamber 48, to which a fuel pressure in the axial direction acts on the valve element 30 in the opening direction.
  • the resulting compressive force counteracts a pressure force in the closing direction, which results from the pressurization of the end face 35 of the valve element 30 from the chamber 33.
  • the embodiment shown in FIG. 1 has the advantage that the outlet channel 24 with outlet throttle 23 are introduced in a separate throttle plate, which rests against the separate component 32, which essentially serves to guide the valve element 30. In this way, the guide bore 31 can be performed as a continuous, easy to be ground through-bore.
  • the throttle plate 16 and the component 32 are united in the component 17, wherein the pressure channel 19 is connected to inlet throttle 20 for connecting the control chamber in a plane other than the cutting plane via a pocket 22 with the supply line 21. Otherwise, the embodiment according to FIG. 3 essentially corresponds to the embodiment according to FIG. 1.
  • the valve element 30 has a cylinder bore 49 at its end facing the seat element 44 (see FIG. 4).
  • the valve element 44 abuts against the upper peripheral edge 50 of this cylinder bore 49.
  • the compensation surface 47 bottom surface of the cylinder bore 49
  • the valve element is conically chamfered. It can be seen that the diameter D1 of the circumferential edge 50, that is to say the diameter of the effective valve seat surface 46, corresponds to the outer diameter D1 of the valve element 30 in the guide section or the approximately identical inner diameter of the guide bore 31.

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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)

Abstract

L'invention concerne un injecteur (1) pour l'injection de carburant dans des chambres de combustion de moteurs à combustion interne. Selon l'invention, un canal de carburant (51) est ménagé dans un obturateur (30) d'une soupape de commande (28) canal par lequel du carburant peut couler d'une chambre de commande (18) vers une chambre de compensation délimitée, lorsque la soupape de commande (28) est fermée, par un élément de siège (44) et par l'obturateur (30). De plus, une surface de compensation (47), pouvant être sollicitée par la pression du carburant dans la direction d'ouverture de l'obturateur (30), est prévue sur l'obturateur (30) à l'intérieur de la chambre de compensation (48). Cette surface permet de compenser une force de pression du carburant agissant dans la direction de fermeture sur l'obturateur (30).
PCT/EP2007/059080 2006-10-27 2007-08-31 Injecteur avec une soupape de commande à compensation de pression axiale WO2008049675A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07803088A EP2084390A1 (fr) 2006-10-27 2007-08-31 Injecteur avec une soupape de commande à compensation de pression axiale

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610050811 DE102006050811A1 (de) 2006-10-27 2006-10-27 Injektor mit axial-druckausgeglichenem Steuerventil
DE102006050811.4 2006-10-27

Publications (1)

Publication Number Publication Date
WO2008049675A1 true WO2008049675A1 (fr) 2008-05-02

Family

ID=38925724

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/059080 WO2008049675A1 (fr) 2006-10-27 2007-08-31 Injecteur avec une soupape de commande à compensation de pression axiale

Country Status (3)

Country Link
EP (1) EP2084390A1 (fr)
DE (1) DE102006050811A1 (fr)
WO (1) WO2008049675A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2778386B1 (fr) * 2013-03-13 2016-03-09 Delphi International Operations Luxembourg S.à r.l. Ensemble soupape de commande et injecteur de carburant comprenant un ensemble soupape de commande

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5094215A (en) * 1990-10-03 1992-03-10 Cummins Engine Company, Inc. Solenoid controlled variable pressure injector
EP0740068A2 (fr) * 1995-04-28 1996-10-30 Lucas Industries public limited company Buse d'injection de combustible
DE19839581A1 (de) * 1997-11-04 1999-05-06 Lucas Ind Plc Treibstoffeinspritzvorrichtung
DE19839572A1 (de) * 1997-11-03 1999-05-06 Caterpillar Inc Treibstoffeinspritzvorrichtung
EP1612403A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Societa' Consortile per Azioni Soupape servo pour controller l'injecteur d'un moteur à combustion interne

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5094215A (en) * 1990-10-03 1992-03-10 Cummins Engine Company, Inc. Solenoid controlled variable pressure injector
EP0740068A2 (fr) * 1995-04-28 1996-10-30 Lucas Industries public limited company Buse d'injection de combustible
DE19839572A1 (de) * 1997-11-03 1999-05-06 Caterpillar Inc Treibstoffeinspritzvorrichtung
DE19839581A1 (de) * 1997-11-04 1999-05-06 Lucas Ind Plc Treibstoffeinspritzvorrichtung
EP1612403A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Societa' Consortile per Azioni Soupape servo pour controller l'injecteur d'un moteur à combustion interne

Also Published As

Publication number Publication date
EP2084390A1 (fr) 2009-08-05
DE102006050811A1 (de) 2008-04-30

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