WO2005045227A1 - Systeme d'injection de carburant pour un moteur a combustion interne - Google Patents

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

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Publication number
WO2005045227A1
WO2005045227A1 PCT/DE2004/001769 DE2004001769W WO2005045227A1 WO 2005045227 A1 WO2005045227 A1 WO 2005045227A1 DE 2004001769 W DE2004001769 W DE 2004001769W WO 2005045227 A1 WO2005045227 A1 WO 2005045227A1
Authority
WO
WIPO (PCT)
Prior art keywords
injection valve
valve member
section
fuel injection
fuel
Prior art date
Application number
PCT/DE2004/001769
Other languages
German (de)
English (en)
Inventor
Henning Hermes
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 WO2005045227A1 publication Critical patent/WO2005045227A1/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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • 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
    • 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
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the invention is based on one
  • Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 42 11 651 AI.
  • This fuel injection device has a high-pressure fuel pump and a fuel injection valve connected to it.
  • the fuel injection valve has an injection valve member, through which at least one injection opening is controlled.
  • the fuel injection valve has a pressure chamber connected to the high-pressure fuel pump, the injection valve member being acted upon by the pressure prevailing in the pressure chamber in an opening direction and being movable in the opening direction against a closing force.
  • the fuel injection device also has a control valve, by means of which a connection of the pressure chamber to a relief region is controlled at least indirectly. If the connection to the relief area is opened by the control valve, no high pressure can build up in the pressure chamber, so that the fuel injection valve is closed and no fuel injection takes place.
  • connection to the relief area is closed by the control valve, high pressure can build up in the pressure chamber, which is generated by the high-pressure fuel pump. If the pressure in the pressure chamber is sufficiently high to reach the To overcome the injection valve member acting closing force, the injection valve member opens and fuel is injected through the at least one injection opening.
  • the aim is to only inject a small amount of fuel as a pre-injection during an injection cycle, and to inject a large amount of fuel only during a subsequent main injection.
  • the control valve is closed for a short time, so that sufficiently high pressure builds up in the pressure chamber and the injection valve member opens, and then the control valve is opened again, so that the pressure in the pressure chamber drops so much that the injection valve member due to this on it effective closing force closes again.
  • the high-pressure fuel relaxes when the control valve is opened, and due to the inertia of the fuel, the pressure in the fuel injection valve, especially in the pressure chamber and in connection with the at least one injection opening, not only drops to the low pressure prevailing in the relief region but continues to decrease on
  • Vapor pressure level so that vapor bubbles form in the fuel injector. These vapor bubbles lead to an unstable pressure build-up in a subsequent main injection, so that the amount of fuel injected cannot be metered exactly. This leads to undesirable scattering of the amount of fuel injected during the main injection and thus to poor results
  • the fuel injection device according to the invention with the features according to claim 1 has the advantage that an excessive pressure drop in the fuel injection valve when the control valve is opened by the throttle point controlled by the injection valve member or the slide
  • FIG. 2 shows the section of the fuel injection device designated by II in FIG. 1 according to a second embodiment
  • FIG. 4 shows section II of the fuel injection device according to a fourth exemplary embodiment.
  • FIG. 1 shows a fuel injection device for an internal combustion engine of a motor vehicle.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the fuel injection device is preferably designed as a so-called pump-nozzle unit and has for each cylinder of the internal combustion engine a high-pressure fuel pump 10 and a fuel injection valve 12 connected to it, which form a common structural unit.
  • the fuel injection device is preferably designed as a so-called pump-nozzle unit and has for each cylinder of the internal combustion engine a high-pressure fuel pump 10 and a fuel injection valve 12 connected to it, which form a common structural unit.
  • the fuel injection device is preferably designed as a so-called pump-nozzle unit and has for each cylinder of the internal combustion engine a high-pressure fuel pump 10 and a fuel injection valve 12 connected to it, which form a common structural unit.
  • the fuel injection device is preferably designed as a so-called pump-nozzle unit and has for each cylinder of the internal combustion engine a high-pressure fuel pump 10 and
  • Fuel injection device can also be designed as a so-called pump-line-nozzle system, in which the high-pressure fuel pump and the fuel injection valve of each cylinder are arranged separately from one another and are connected to one another via a line. Furthermore, it can also be provided that only one high-pressure fuel pump 10 is provided, to which a plurality of fuel injection valves 12 are connected.
  • the high-pressure fuel pump 10 has a pump body 14 with a cylinder bore 16, in which a pump piston 18 is tightly guided, which is driven at least indirectly by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19 in a lifting movement.
  • the pump piston 18 is limited in the
  • Cylinder bore 16 a pump work chamber 22, in which fuel is compressed under high pressure during the delivery stroke of the pump piston 18.
  • the pump work chamber 22 is supplied with fuel from a fuel reservoir 24 of the motor vehicle, for example by means of a feed pump 23.
  • the fuel injection valve 12 has a valve body 26 which is connected to the pump body 14 and which can be constructed in several parts and in which at least one injection valve member 28 is guided so as to be longitudinally displaceable in a bore 30.
  • One or more intermediate bodies can be arranged between the pump body 14 and the valve body 26.
  • the valve body 26 has at least one, preferably a plurality of injection openings 32 at its end region facing the combustion chamber of the cylinder of the internal combustion engine.
  • the injection valve member 28 has, for example, an approximately conical sealing surface 34 on its end region facing the combustion chamber, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the injection openings 32 lead away.
  • Valve body 26 has an annular space 38 between injection valve member 28 and bore 30 toward valve seat 36, which in its end region facing away from valve seat 36 merges into a pressure chamber 40 surrounding injection valve member 28 by radial expansion of bore 30.
  • the injection valve member 28 has a pressure shoulder 42 at the level of the pressure chamber 40 by reducing the cross section.
  • a prestressed closing spring 44 engages, by means of which the injection valve member 28 is pressed toward the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 of a part 27 of the valve body 26 which adjoins the bore 30.
  • a further injection valve member is displaceably arranged within the hollow injection valve member 28, through which at least one further injection opening is controlled. It can be provided that either only the outer injection valve member 28 opens and the at least one injection opening 32 opens or both Open the injection valve members and open all injection openings.
  • a channel 50 leads from the pump work chamber 22 through the pump body 14 and the valve body 26 to the pressure chamber 40 of the fuel injection valve 12.
  • a connection 52 leads from the channel 50 to a relief area, which the fuel reservoir 24 can serve, at least indirectly, which is operated by an electrically operated control valve 54 is controlled.
  • the control valve 54 can, as shown in FIG. 1, be designed as a 2/2-way valve.
  • the control valve 54 can have an electromagnetic actuator or a piezo actuator and is controlled by an electronic control device 56.
  • the fuel injection device also has a piston-shaped slide 58 which adjoins the injection valve member 28 and through the spring chamber 46 into a spring chamber 46 on its side
  • Injection valve member 28 extends the bore 60 adjacent side.
  • the slide 58 is supported on the one hand at least indirectly, for example via a spring plate 62, on which the closing spring 44 also acts, on the injection valve member 28.
  • the closing spring 44 also acts, on the injection valve member 28.
  • the bore 60 has a radial widening, through which an annular chamber 66 surrounding the slide 58 is formed. The part of the channel 50 leading from the pump working space 22 opens into the annular space 66 and into the area of the bore 60 between the
  • Annulus 66 and the spring chamber 46 opens to the pressure chamber 40 further part of the channel 50.
  • the slide 58 has a constriction 158 with a smaller diameter than in its remaining sections 258.
  • the slide 58 with its large diameter portion 258 is arranged in the annular space 66 at a short distance from the bore 60, only one between the slide 58 and the bore 60 Small annular gap remains, which forms a throttle point 59 in the connection between the outlet of the channel 50 from the bore 60 to the pressure chamber 40 and the connection of the channel 50 to the pump work chamber 22 and its connection 52 to the relief area.
  • Injection valve member 28 moves in its opening direction 29, the slide 58 with its large diameter section 258 further immerses in the annular space 66, so that between the section 158 of the slide 58 and the bore 60 a larger flow cross-section in the connection between the outlet of the Channel 50 from the bore 60 to the pressure chamber 40 and the connection of the channel 50 to the pump work chamber 22 and its connection 52 to the relief area is released.
  • the slider 58 is thus a control part depending on the stroke of the
  • Injection valve member 28 controls the flow cross-section in the channel 50 between the pressure chamber 40 and the connection of the channel 50 with the connection 52 leading to the relief region 24. With its large diameter 258 compared to the constriction 158, the slide 58 is tightly guided in the bore 60, so that little or no fuel leakage from the annular space 66 into the spring space 46 or into the space of the bore 60 in which the spring 64 is arranged, can drain.
  • High pressure builds up. If the pressure prevailing in the pressure chamber 40 is so high that it generates a greater force on the injection valve member 28 via the pressure shoulder 42 than the force of the closing spring 44, the injection valve member 28 moves in the opening direction 29 and releases the at least one injection opening 32, through which fuel is injected.
  • the slide 58 moves with the injection valve member 28 and releases the large flow cross section, so that fuel can flow unthrottled from the pump working chamber 22 into the pressure chamber 40 and the annular chamber 38 to the injection openings 32.
  • Fuel injection begins with a pre-injection in which only a small amount of fuel is injected.
  • control valve 54 is opened again by the control device 56, so that the high pressure in the pump work chamber 22, in the channel 50 and in the pressure chamber 40 is relieved.
  • the injection valve member 28 closes, so that the slide 58 with its large diameter section 258 is arranged at a short distance from the bore 60 and only releases the small flow cross section forming the throttle point 59.
  • the pressure in the pressure chamber 40 and in the annular chamber 38 of the fuel injection valve 12 then drops only slowly and does not fall below the vapor pressure of the fuel, so that no vapor bubbles can form.
  • Throttle point 59 is in the pressure chamber 40 and in the annular space 38 Maintain the pressure level that prevails before the pre-injection.
  • the volume enclosed in the fuel injection valve 12 by the throttle point 59 formed between the slide 58 and the bore 60 is as large as possible.
  • the control valve 54 is closed by the control device 56, so that the pressure in the pump work chamber 22, in the channel 50 and in the pressure chamber 40 rises again and the injection valve member 28 opens when the opening pressure is reached.
  • the pressure chamber 40 has a somewhat delayed increase in pressure compared to the pump working chamber 22, which is particularly advantageous for the metering of small injection quantities during the pre-injection.
  • FIG. 2 shows a section of the fuel injection device according to a second exemplary embodiment, in which the essential structure is the same as in the first exemplary embodiment and essentially only the differing features are explained below.
  • the part of the channel 50 leading from the pump working space 22 opens into the annular space 66 surrounding the slide 58.
  • the bore 60 leads from the annular space 66 to the spring space 46, and there is another one between the spring space 46 and the annular space 66 by expanding the bore 60 formed, the annular space 70 surrounding the slide 58 is provided.
  • the part of the channel 50 leading to the pressure space 40 opens into the further annular space 70.
  • the slide 58 has the constriction 158 between the two annular spaces 66 and 70.
  • the slide 58 is with its large diameter portions 258 in the area of the bore 60 between the annular space 66 and the space of the bore 60 in which the spring 64 is arranged, and in the area of the bore 60 between the further annular space 70 and Spring chamber 46 guided tightly. If the injection valve member 28 is in its closed position, the slide 58 is arranged with its large diameter section 258 in the annular space 66 at a short distance from the bore 60, with only a small annular gap remaining between the slide 58 and the bore 60, which Restrictor 59 forms in the connection between the outlet of the channel 50 from the bore 60 to the pressure chamber 40 and the connection of the channel 50 to the pump work chamber 22 and its connection 52 to the relief area.
  • connection of the channel 50 to the pump work chamber 22 and its connection 52 to the relief area is released.
  • the function of the fuel injection device according to the second embodiment is the same as that described above in the first embodiment.
  • Annular space 66 opens out from the part of the channel 50 leading from the pump working space 22.
  • the further annular space 70 which is offset axially from the injection valve member 28 and surrounds the slide 58, from which the part of the channel 50 leading to the pressure space 40 leads.
  • the spring chamber 46 is arranged on the side of the slide 58 facing away from the injection valve member 28, following the bore 60.
  • the prestressed closing spring 44 is arranged in the spring chamber 46, which is supported on the one hand on the base of the spring chamber 46 and on the other hand on the slide 58. The closing spring 44 thus generates both the closing force on the injection valve member 28 and the slide 58 in contact with the injection valve member 28, so that no separate spring 64 is required as in the first and second exemplary embodiments. If that
  • Injection valve member 28 is in its closed position, the slide 58 with its large diameter section 258 is arranged in the annular space 66 at a short distance from the bore 60, only a small annular gap remaining between the slide 58 and the bore 60, which is the throttle point 59 in the connection between the outlet of the channel 50 from the bore 60 to the pressure chamber 40 and the connection of the channel 50 to the pump work chamber 22 and its connection 52 to the relief area.
  • the fuel injection valve 12 has the injection valve member 28, which is acted upon by the closing spring 44 arranged in the spring chamber 46 in its closing direction.
  • the injection valve member 28 has in the pressure chamber 40 surrounding it the pressure shoulder 42, via which a force in the opening direction 29 is generated on the injection valve member 28 by the pressure prevailing in the pressure chamber 40.
  • the channel leading from the pump work space 22 50 opens into an annular space 72 which surrounds the injection valve member 28 and is formed by a radial expansion of the bore 30 and which is arranged offset with an axial distance from the pressure space 40 to the spring space 46.
  • the injection valve member 28 has a section 128 adjoining its pressure shoulder 42.
  • a section 228 adjoins the closing spring 44 toward the closing spring 44 and is arranged in the region of the annular space 72.
  • the section 228 of the injection valve member 28 is guided in the bore 30 tightly to the spring chamber 46.
  • the section 128 of the injection valve member 28 passes through the bore 30 between the pressure space 40 and the annular space 72 with great radial play.
  • its section 228 is arranged in the annular space 72 at a short distance from the bore 30, with only a small annular gap remaining between the section 228 and the bore 30, which connects the throttle point 59 in the connection forms between the pressure chamber 40 and the connection of the channel 50 to the pump work chamber 22 and its connection 52 to the relief region.
  • a further bore 74 opening into the pressure chamber 40 can be provided, which opens at an end face of the valve body 26, to which the intermediate body or another valve body part connects, through which the bore 74 is closed when the fuel injection valve 12 is assembled.
  • the additional bore 74 enables a flow measurement for the fuel flowing into the pressure chamber 40 via the throttle point between the injection valve member 28 and the bore 30 when the injection valve member 28 is arranged in its closed position.
  • the throttle point which is determined by the distance of the section 228 of the injection valve member 28 from the bore 30 in the annular space 72, can be set to a certain size with the aid of this flow measurement in order to achieve a predetermined flow of fuel.

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

Abstract

L'invention concerne un système d'injection de carburant comprenant une pompe à carburant haute pression (10) et une soupape d'injection de carburant (12) reliée à la pompe, ladite soupape d'injection de carburant (12) présentant un élément de soupape d'injection (28). Cette soupape d'injection de carburant (12) comprend une chambre de pression (40) reliée à la pompe à carburant haute pression (10), ledit élément de soupape d'injection (28) étant sollicité dans le sens d'ouverture (29) par la pression régnant dans cette chambre de pression (40). Un raccordement (52) entre la chambre de pression (40) et une zone de décharge (24) est au moins indirectement commandé par une soupape de commande (54). Une section d'écoulement est prévue entre la chambre de pression (40) et le raccordement (52) menant à la zone de décharge (24), laquelle section est commandée par un élément de commande (58) en fonction de la course dudit au moins un élément de soupape d'injection (28), de sorte que, lorsque cet élément de soupape d'injection (28) se trouve en position de fermeture, seule une faible section d'écoulement, formant un point d'étranglement (59) est libérée, et, lorsque ledit élément de soupape d'injection (28) se déplace dans le sens d'ouverture (29), une plus grande section d'écoulement est libérée.
PCT/DE2004/001769 2003-10-06 2004-08-06 Systeme d'injection de carburant pour un moteur a combustion interne WO2005045227A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003146210 DE10346210A1 (de) 2003-10-06 2003-10-06 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10346210.4 2003-10-06

Publications (1)

Publication Number Publication Date
WO2005045227A1 true WO2005045227A1 (fr) 2005-05-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2004/001769 WO2005045227A1 (fr) 2003-10-06 2004-08-06 Systeme d'injection de carburant pour un moteur a combustion interne

Country Status (2)

Country Link
DE (1) DE10346210A1 (fr)
WO (1) WO2005045227A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60132065A (ja) * 1983-12-20 1985-07-13 Nissan Motor Co Ltd 燃料噴射ノズル
DE4211651A1 (de) * 1992-04-07 1993-10-14 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung, insbesondere Pumpedüse für Brennkraftmaschinen
US5299919A (en) * 1991-11-01 1994-04-05 Paul Marius A Fuel injector system
EP0844383A2 (fr) * 1996-11-12 1998-05-27 Lucas Industries Public Limited Company Injecteur
US6161773A (en) * 1994-05-31 2000-12-19 Caterpillar Inc. Fuel injector nozzle with guide to check clearance passage providing injection rate shaping

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60132065A (ja) * 1983-12-20 1985-07-13 Nissan Motor Co Ltd 燃料噴射ノズル
US5299919A (en) * 1991-11-01 1994-04-05 Paul Marius A Fuel injector system
DE4211651A1 (de) * 1992-04-07 1993-10-14 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung, insbesondere Pumpedüse für Brennkraftmaschinen
US6161773A (en) * 1994-05-31 2000-12-19 Caterpillar Inc. Fuel injector nozzle with guide to check clearance passage providing injection rate shaping
EP0844383A2 (fr) * 1996-11-12 1998-05-27 Lucas Industries Public Limited Company Injecteur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 0092, no. 94 (M - 431) 20 November 1985 (1985-11-20) *

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Publication number Publication date
DE10346210A1 (de) 2005-04-21

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