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WO2005026525A1 - Soupape d'injection de carburant pour moteur a combustion interne - Google Patents

Soupape d'injection de carburant pour moteur a combustion interne Download PDF

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Publication number
WO2005026525A1
WO2005026525A1 PCT/DE2004/001331 DE2004001331W WO2005026525A1 WO 2005026525 A1 WO2005026525 A1 WO 2005026525A1 DE 2004001331 W DE2004001331 W DE 2004001331W WO 2005026525 A1 WO2005026525 A1 WO 2005026525A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
control
hollow needle
chamber
needle
Prior art date
Application number
PCT/DE2004/001331
Other languages
German (de)
English (en)
Inventor
Joachim Boltz
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
Publication of WO2005026525A1 publication Critical patent/WO2005026525A1/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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0045—Three-way valves

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known from the document DE 102 05 970 AI.
  • a fuel injection valve has a hollow needle which, with its end on the combustion chamber side, interacts with a valve seat from which at least one injection opening extends.
  • the longitudinal opening of the hollow needle closes or opens the injection opening, the longitudinal movement of the hollow needle taking place through the interplay of a closing force and an opening force.
  • the opening force is generated hydraulically by pressurizing a pressure surface arranged in a pressure chamber.
  • the closing force is preferably also generated hydraulically, in that a corresponding pressure acts on the end of the hollow needle facing away from the valve seat in a control chamber.
  • the hydraulic closing force can also act indirectly on the hollow needle in that a control sleeve delimits the control chamber, which in turn rests on the hollow needle.
  • a control valve is provided through which fuel can be supplied to the control chamber or can be discharged from the control chamber.
  • the hollow needle there is also a longitudinally displaceable valve needle which interacts with the valve seat with its end facing the valve seat and thereby controls the opening of at least one further injection opening.
  • the opening force on the valve needle is also generated hydraulically by the pressure in the pressure chamber, while the closing force is exerted by the pressure in a second control chamber.
  • This second control chamber is formed either in the hollow needle or in the control sleeve interacting with the hollow needle.
  • the known fuel injection valve has the disadvantage that the closing force on the valve needle and thus the pressure in the second control chamber have to be controlled in a complex manner.
  • Either the second control chamber is also connected to the control valve in such a way that its pressure can be adjusted with the aid of the control valve, or a second control valve is to be provided, which causes additional costs and takes up more installation space.
  • Solcl ⁇ e constructions are expensive and have to be sealed in many places.
  • the fuel injection valve according to the invention with the characterizing features of patent claim 1 has the advantage that control of two coaxially guided valve needles is possible in a simple manner and using known and proven control means.
  • the valve needle which is guided in the hollow needle, is acted upon by a closing force by means of a closing spring, the closing spring being supported on the control sleeve.
  • the closing force is therefore generated exclusively by a closing spring, so that the valve needle can be moved in the known manner by appropriately pressurizing a pressure surface.
  • the closing spring is arranged in an inner spring chamber which is formed in the control sleeve and is open towards the valve needle.
  • This configuration is particularly advantageous if this inner spring chamber is connected via an opening in the control sleeve to an outer spring chamber, in which an outer closing spring is arranged and which is connected to a leakage line. In this way, a low fuel pressure is always maintained in both spring chambers, which does not exert any additional, disruptive forces on the valve needles.
  • a control valve is provided in the fuel injection valve, with the aid of which the fuel pressure in the control chamber can be set.
  • the control valve is either a 3/2 or 2/2 Directional valve designed, the 3/2-way valve has the additional ' advantage that the pressure build-up is significantly accelerated after the end of the injection and the valve needle closes accordingly quickly.
  • a 2/2-way valve is generally simpler in design and correspondingly less expensive.
  • FIG. 1 shows a fuel injection valve according to the invention in longitudinal section with schematically illustrated peripheral components and FIG. 2 shows the time course of the needle stroke, injection rate and the force on the valve needle at various injection pressures.
  • FIG. 1 an embodiment of the fuel injection valve according to the invention is shown in longitudinal section.
  • the fuel injection valve has a housing 1, which comprises a valve body 3, a control body 5, a throttle disc 7 and a holding body 9, which abut one another in this order and are pressed against one another by a device not shown in the drawing.
  • a bore 15 is formed in the valve body 3, which is delimited at its combustion chamber end by a conical valve seat 27. From the valve seat 27 go outer injection openings 30 and imiere injection openings
  • a hollow needle 17 is arranged to be longitudinally displaceable and is sealingly guided in a section of the bore 15 facing away from the valve seat.
  • a pressure chamber 24 is formed between the hollow needle 17 and the wall of the bore 15, which extends to the valve seat 27 and which is connected to a high-pressure chamber 11 via an inlet channel 35 running in the housing 1.
  • a predetermined fuel pressure is always maintained in the high-pressure chamber 11, which can be part of a fuel pump or a high-pressure collection chamber, so that this pressure also prevails in the pressure chamber 24 and thus also corresponds to the necessary injection pressure.
  • the hollow needle 17 Starting from the guided section of the hollow needle 17, it tapers towards the valve seat 27 to form a pressure shoulder 22, at the level of which the inlet channel 35 opens into the pressure chamber 24. At its end on the valve seat side, the hollow needle 17 merges into a valve sealing surface 18 with which it connects with the valve seat
  • a through hole 41 is formed in the control body 5, in which a control sleeve 40 is arranged so as to be longitudinally displaceable.
  • the control sleeve 40 rests with its end on the valve seat side against the hollow needle 17, so that it moves in synchronism with it in the through bore 41.
  • Adjacent to the valve body 3, the through bore 41 is expanded to an outer spring space 37, in which an outer closing spring 47 in the form of a helical compression spring is arranged under prestress.
  • the outer closing spring 47 is supported at one end on a stationary support surface 45 and at the other end on an arx of the control sleeve 40 formed shoulder 44.
  • Closing spring 47 results in a force on hollow needle 17 in the direction of valve seat 27, so that it is held in its closed position in the absence of additional forces, that is to say in contact with valve seat 27.
  • a piston-shaped valve needle 20 is arranged so as to be longitudinally displaceable, which has at its end on the valve seat side a valve sealing surface 29 with which the valve needle 20 interacts with the valve seat 27.
  • the valve needle 20 has a pressure surface 23 near the valve sealing surface 29, which is acted upon by the fuel pressure of the pressure chamber 24 when the hollow needle 17 is open and thereby experiences an opening force on the valve needle 20.
  • the valve needle 20 merges into a spring plate 50 which is arranged within an inner spring chamber 38 formed in the control sleeve 40.
  • the spring plate 50 can be designed as a separate part or in one piece with the valve needle 20.
  • an inner closing spring 48 is arranged under pressure, which is supported at one end on the spring plate 50 and at the other end on the control sleeve 40.
  • the inner spring chamber 38 is connected via a connecting bore 42 to the outer spring chamber 37, which is connected via a leakage line 60 to a leak oil chamber, not shown in the drawing.
  • a driving shoulder 52 is formed in the inner spring space 38, which, when the valve needle 20 and the hollow needle 17 are in the closed position, is at a slight axial distance from the spring plate 50.
  • valve needle 20 and the hollow needle 17 in the open position the valve needle 20 is carried during the closing movement of the hollow needle 17 and thus the Steuerl ⁇ ülse 40 by the abutment of the driving shoulder 52 on the spring plate 50 and pressed into its closed position.
  • control chamber 55 The end face 57 of the control sleeve 40 facing away from the hollow needle 17, the through bore 41 and the throttle disk 7 delimit a control chamber 55, the pressure of which exerts a hydraulic force on the control sleeve 40 in the direction of the hollow needle 17.
  • the control chamber 55 is connected to the inlet channel 35 via an inlet throttle 62 and a connecting groove 66 formed in the throttle disk 7, so that fuel always flows into the control chamber 55 via the inlet throttle 62 as long as there is a lower pressure there than in the high-pressure chamber 11 and thus in Inlet channel 35.
  • Control chamber 55 is also connected via an outlet throttle 64 and a control line 69 to a control valve 70, which is also connected to inlet throttle 62 via a further control line 68.
  • control valve 70 is connected to a leakage line 72, which opens into a leakage oil space, not shown in the drawing, in which there is always a low pressure, preferably ambient pressure.
  • the control valve 70 is designed as a 3/2-way valve, which consequently has two switching positions: in the first switching position shown, the Control line 68 and control line 69 connected to each other while the leakage line 72 is closed. In the second switching position, the leakage line is connected to the control line 69 and thus to the flow restrictor 64, while the control line 68 is closed.
  • the fuel injector works as follows:
  • a more or less high pressure is set in the high-pressure chamber 11.
  • a relatively low pressure for example in the order of 30 to 40 MPa, is sufficient for a low power requirement.
  • the injection begins by moving the control valve 70 into its second switching position, so that the control chamber 55 is connected to the leakage line 72.
  • the pressure in the control chamber 55 is reduced below the pressure of the inlet line 35, since the inlet throttle 62 and the outlet throttle 64 are matched to one another in such a way that more fuel flows out of the control chamber 55 than can flow in via the inlet throttle 62.
  • the hydraulic pressure on the pressure shoulder 22 of the hollow needle 17 lifts it off the valve seat 27 and opens the outer injection openings 30.
  • the hydraulic force on the pressure surface 23 is not sufficient to open the valve needle 20 against the force of the inner closing spring 48, so that it remains in its closed position, ie in contact with the valve seat 27.
  • the control valve 70 is brought back into its first switching position, in which it connects the two control lines 68, 69 to one another.
  • the leakage line 72 is closed on the one hand, and on the other hand, fuel flows into the control chamber 55 both via the inlet throttle 62 and via the outlet throttle 64, so that a high fuel pressure is built up again very quickly, which forces the hollow needle 17 into its closed position suppressed.
  • FIG. 2 shows the course of the needle stroke h, the injection rate R and the force F on the valve needle 20 against time, the column denoted by A denoting the low injection pressure, B a medium and C a high injection pressure.
  • the function described above at low injection pressure corresponds to the diagrams in the A column:
  • the needle stroke h a of the hollow needle 17 rises to a maximum and falls again after actuation of the control valve 70. from until the hollow needle 17 is closed.
  • the injection rate R quickly rises to a plateau, since this is limited not only by the stroke of the hollow needle 17, but also by the diameter of the outer injection openings 30.
  • the closing force Fg on the valve needle 20 is reduced by the moving control sleeve 40, since the inner closing spring 48 is extended.
  • the opening force F oe still does not reach this closing force, so that the valve needle 20 remains closed.
  • the hollow needle 17 does not move through its greatest possible stroke: by rapidly actuating the control valve 70, the hollow needle 17 remains in a ballistic state and is braked by the pressure in the control chamber 55 which rises again before it can contact the throttle disk 7.
  • the hollow needle 17 is opened in the manner described above after actuation of the control valve 70.
  • the course of the needle stroke h a of the hollow needle 17 is similar to that in example A, but the increase is due to the higher
  • the hollow needle 17 and the valve needle 20 open practically simultaneously, since immediately after the hollow needle 17 is lifted off the valve seat 27, a very high pressure is applied to the pressure surface 23 and thus a large force acts on the valve needle 20.
  • the injection rate R still shows a slight increase, which is caused by the opening of the hollow needle 17, but very quickly reaches its maximum value, which is higher than the maximum injection rate of example B due to the high pressure.
  • the control valve 70 instead of designing the control valve 70 as a 3/2 way valve, it can also be provided that it is instead designed as a 2/2 way valve which opens or closes the connection of the control line 69 to the leakage line 72.
  • the control line 68 can be omitted in this exemplary embodiment.
  • the opening function remains the same, but the closing of the valve needle 20 takes place more slowly, since the pressure build-up in the control chamber 55 now only takes place via the inlet throttle 62 and thus takes a little more time.
  • the control valve is preferably driven with the aid of a piezo actuator, which allows a very short switching time.
  • a piezo actuator which allows a very short switching time.
  • an electromagnetic control valve 70 it is also possible to use an electromagnetic control valve 70.

Landscapes

  • 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 une soupape d'injection de carburant comprenant un pointeau creux (17) coopérant, par son déplacement longitudinal, avec un siège de soupape (27), de manière à commander l'ouverture d'au moins un orifice d'injection extérieur (30). Il est prévu sur le pointeau creux (17), un épaulement (22) soumis à la pression du carburant, dans un volume à pression (24), et exerçant, de ce fait, sur le pointeau creux (17), une force d'ouverture dans le sens du parcours, à partir du siège de soupape (27). Un manchon de commande (40) s'appliquant au moins indirectement sur le pointeau, est également déplaçable longitudinalement, ledit manchon (40) délimitant, par sa face avant (45) opposée au pointeau (17), un espace de commande (55) dans lequel la pression est réglable. Un pointeau de soupape (20) est disposé, déplaçable longitudinalement, dans le pointeau creux (17), ledit pointeau de soupape commandant, par coopération avec le siège de soupape (27), l'ouverture d'au moins un orifice d'injection intérieur (32). Le pointeau de soupape (20) est sollicité, par un ressort de fermeture intérieur (48), par une force de fermeture, le ressort de fermeture intérieur (48) prenant appui sur le manchon de commande (40).
PCT/DE2004/001331 2003-08-25 2004-06-24 Soupape d'injection de carburant pour moteur a combustion interne WO2005026525A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10338768.4 2003-08-25
DE2003138768 DE10338768A1 (de) 2003-08-25 2003-08-25 Kraftstoffeinspritzventil für Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
WO2005026525A1 true WO2005026525A1 (fr) 2005-03-24

Family

ID=34201908

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2004/001331 WO2005026525A1 (fr) 2003-08-25 2004-06-24 Soupape d'injection de carburant pour moteur a combustion interne

Country Status (2)

Country Link
DE (1) DE10338768A1 (fr)
WO (1) WO2005026525A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004030448A1 (de) * 2004-06-24 2006-01-12 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
TR200402048A1 (tr) * 2004-08-18 2006-03-21 Robert Bosch Gmbh Hidrolik kontrollü değişken kesitli enjektör memesi.

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1270883B (de) * 1966-10-28 1968-06-20 Bosch Gmbh Robert Kraftstoffeinspritzventil
US4382554A (en) * 1980-09-27 1983-05-10 Robert Bosch Gmbh Fuel injection nozzle construction
DE4115457A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE4115477A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE4210563A1 (de) * 1991-04-15 1992-10-22 Volkswagen Ag Kraftstoffeinspritzduese fuer eine mit vor- und haupteinspritzung arbeitende brennkraftmaschine
DE19634105A1 (de) * 1996-08-23 1998-01-15 Daimler Benz Ag Einspritzventil für Verbrennungskraftmaschinen
EP0978649A2 (fr) * 1998-08-06 2000-02-09 Siemens Aktiengesellschaft Buse d'injection de combustible
DE19913286A1 (de) * 1999-03-24 2000-10-12 Man B & W Diesel Ag Einspritzventil
WO2003069151A1 (fr) * 2002-02-14 2003-08-21 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion interne
EP1363015A1 (fr) * 2002-05-14 2003-11-19 Robert Bosch Gmbh Système d'injection de carburant pour un moteur à combustion interne

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1270883B (de) * 1966-10-28 1968-06-20 Bosch Gmbh Robert Kraftstoffeinspritzventil
US4382554A (en) * 1980-09-27 1983-05-10 Robert Bosch Gmbh Fuel injection nozzle construction
DE4115457A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE4115477A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE4210563A1 (de) * 1991-04-15 1992-10-22 Volkswagen Ag Kraftstoffeinspritzduese fuer eine mit vor- und haupteinspritzung arbeitende brennkraftmaschine
DE19634105A1 (de) * 1996-08-23 1998-01-15 Daimler Benz Ag Einspritzventil für Verbrennungskraftmaschinen
EP0978649A2 (fr) * 1998-08-06 2000-02-09 Siemens Aktiengesellschaft Buse d'injection de combustible
DE19913286A1 (de) * 1999-03-24 2000-10-12 Man B & W Diesel Ag Einspritzventil
WO2003069151A1 (fr) * 2002-02-14 2003-08-21 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion interne
EP1363015A1 (fr) * 2002-05-14 2003-11-19 Robert Bosch Gmbh Système d'injection de carburant pour un moteur à combustion interne

Also Published As

Publication number Publication date
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