EP1357283B1 - Dispositif d'injection de carburant pour un moteur à combustion interne - Google Patents

Dispositif d'injection de carburant pour un moteur à combustion interne Download PDF

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Publication number
EP1357283B1
EP1357283B1 EP03004643.7A EP03004643A EP1357283B1 EP 1357283 B1 EP1357283 B1 EP 1357283B1 EP 03004643 A EP03004643 A EP 03004643A EP 1357283 B1 EP1357283 B1 EP 1357283B1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
fuel
suction valve
valve
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.)
Expired - Lifetime
Application number
EP03004643.7A
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German (de)
English (en)
Other versions
EP1357283A3 (fr
EP1357283A2 (fr
Inventor
Stefan Kieferle
Achim Koehler
Sascha Ambrock
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 EP1357283A2 publication Critical patent/EP1357283A2/fr
Publication of EP1357283A3 publication Critical patent/EP1357283A3/fr
Application granted granted Critical
Publication of EP1357283B1 publication Critical patent/EP1357283B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/464—Inlet valves of the check valve type
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is characterized by the DE 198 48 035 A1 known.
  • This fuel injection device has a high-pressure pump which is provided for a common-rail injection system in which fuel is conveyed under high pressure into a reservoir by the high-pressure pump. With the memory arranged on the cylinders of the internal combustion engine injectors are connected.
  • a feed pump is provided in common rail injection systems, is conveyed by the fuel from a reservoir to the high pressure pump.
  • the high pressure pump has a plurality of pump elements, each with a working space limiting, driven in a stroke pump piston. It is provided in the working space opening a suction valve which opens during the suction stroke of the pump piston and flows through the fuel into the working space.
  • the suction valve has a valve member acted upon by a closing spring in a closing direction, the closing spring being supported on the pump piston. At the beginning of the suction stroke of the piston is compressed by this the closing spring most, so that the pressure at which the suction valve opens is higher than during the suction stroke of the pump piston, during which the closing spring is increasingly relaxed. Under certain operating conditions of the internal combustion engine, in particular in overrun, should be promoted by the high-pressure pump no fuel in the memory. To ensure this, the opening differential pressure of the suction valve is set relatively high, for example to at least 2 bar. However, this leads to the fact that the delivery rate of the high-pressure pump is not optimal.
  • a fuel injection device which comprises a high-pressure pump, in which the closing spring of the suction valve is supported at least indirectly on the pump piston.
  • a fuel injection device with a high-pressure pump which has a suction valve whose opening differential pressure is equal to or less than 0.9 bar.
  • the opening differential pressure of the suction valve is not dependent on the stroke of the pump piston, so that the specified value for the opening differential pressure is not transferable to a suction valve with depending on the stroke of the pump piston changing opening differential pressure, as there is not a single fixed value for the opening differential pressure present is.
  • the information in the DE 199 41 850 A1 thus do not give sufficient teaching for the determination of the opening differential pressure in a suction valve with depending on the stroke of the pump piston changing opening differential pressure.
  • the fuel injection device according to the invention with the features of claim 1 has the advantage that the minimum opening differential pressure of the suction valve is very low and thereby the delivery rate of the high-pressure pump is improved.
  • FIG. 1 a fuel injection device for an internal combustion engine of a motor vehicle in a schematic representation with a high-pressure pump
  • FIG. 2 one in FIG. 1 denoted by II Section of the high pressure pump in an enlarged view with a pump piston in a top dead center
  • FIG. 3 the cutout II with the pump piston in a bottom dead center.
  • FIG. 1 a fuel injection device for an internal combustion engine, for example of a motor vehicle is shown.
  • the internal combustion engine is preferably a self-igniting internal combustion engine and has one or more cylinders.
  • the fuel injection device has a feed pump 10, which is arranged for example in a fuel tank 12 of the motor vehicle, but can also be arranged outside of the container 12.
  • the feed pump 10 may have an electric drive motor and sucks, for example, via a pre-filter 14 fuel from the fuel tank 12 at.
  • the feed pump 10 can also be driven mechanically, for example, by the internal combustion engine.
  • a line 16 leads to a high-pressure pump 18.
  • a fuel filter 20 is arranged in the line 16, which is designed as a fine filter and which is flowed through by the funded by the feed pump 10 fuel.
  • the high-pressure pump 18 has, for example, a plurality of pump elements 22, each of which has a pump piston 26 guided in a cylinder bore 24, which is driven via an eccentric drive 28 in a stroke movement.
  • the high-pressure pump 18 is preferably driven mechanically by the internal combustion engine.
  • the funded by the high pressure pump 18 fuel is over a line 30 is supplied to a memory 32.
  • Each pump element 22 has a work space 34 bounded by the pump piston 26 into which an inlet from the feed pump 10 opens and from which a discharge to the accumulator 32 is discharged.
  • a suction valve 36 opening into the working space 34 is provided, and in the outlet of each pump element 22, a pressure valve 38 opening towards the reservoir 32 is provided.
  • an injector 40 For each cylinder of the internal combustion engine, an injector 40 is provided, is injected through the fuel into the combustion chamber of the cylinder. Each injector 40 is connected to the reservoir 32 via a conduit 42, and the opening of the fuel injector 40 is controlled by an electrically actuated valve 44 which is driven by an electronic controller 46. From the injectors 40, a return 41 to the fuel tank 12 can dissipate uninjected fuel.
  • a pressure valve 48 For controlling and / or limiting the pressure prevailing in the memory 32, a pressure valve 48 may be provided which opens when a predetermined pressure is exceeded and releases a return via a line 50 from the memory 32 into the fuel tank 12.
  • a pressure sensor 52 On the memory 32, a pressure sensor 52 is also arranged, through which the pressure in the memory 32 is detected and electrically connected to the Control device 46 is connected, which is thus supplied with a signal for the pressure prevailing in the memory 32.
  • a return 54 may be provided, via which, for example, a leakage amount of fuel can flow and which can open into the conduit 50.
  • a fuel metering device 60 is arranged, through which a flow area of the connection to the high pressure pump 18 is adjusted.
  • the fuel metering device 60 is actuated by the control device 46.
  • the fuel metering device 60 has a flow control valve 62 and an actuator 64, which is controlled by the control device 46.
  • the flow control valve 62 By means of the flow control valve 62, the flow area of the connection to the high pressure pump 18 can be adjusted continuously between zero and a maximum flow area.
  • actuator 64 an electromagnet or a piezoelectric actuator can be used, which is supplied in each case by the control device 46 with a defined electrical voltage and thereby brings the flow control valve 62 in a defined position in which this releases a defined flow area.
  • the controller 46 sets a desired pressure in the memory 32 specified.
  • the control device 46 receives a signal for the actual pressure in the memory 32.
  • the pressure in the memory 32 is dependent on the amount of fuel delivered by the high-pressure pump 18 into the accumulator 32.
  • the amount of fuel delivered by the high-pressure pump 18 can be changed by changing the flow area of the connection to the feed pump 10 by means of the fuel metering device 60.
  • the fuel metering device 60 is controlled by the control device 46 such that it sets in the connection to the feed pump 10, a flow area which is so large that the high-pressure pump 18 inflowing amount of fuel is so large that funded by the high-pressure pump 18 into the memory 32 Amount of fuel to maintain the predetermined target pressure in the memory 32 is sufficient. If the actual pressure in the accumulator 32 is less than the target pressure, then a too small amount of fuel is conveyed by the high-pressure pump 18 and the fuel metering device 60 is controlled by the control device so that it releases a larger flow area in the connection to the feed pump 10 and thus by the high pressure pump 18 delivered amount of fuel is increased.
  • the suction valve 36 of a pump element 22 is explained in more detail, wherein all pump elements 22 are identical.
  • an inlet channel 72 for the funded by the pump 10 fuel into the working space 34 is formed.
  • the working space 34 facing a valve seat 74 is formed, which is for example at least approximately conical.
  • the suction valve 36 has a valve member 76, which is formed for example in the form of a ball and which cooperates with the valve seat 74 for controlling the connection of the inlet channel 72 with the working space 34.
  • the valve member 76 is received, for example, in a pump member 26 towards the arranged support member 78.
  • the suction valve 36 also has a closing spring 80, which is formed for example as a helical compression spring and which is clamped between the pump piston 26 and the support member 78.
  • a closing spring 80 By the closing spring 80, the valve member 76 is pressed in the closing direction to the valve seat 74.
  • the valve member 76 is also acted upon by the pressure prevailing in the working space 34 in the closing direction.
  • the pump piston 26 has at its end facing the valve member 76 a reduced in diameter extension 82, wherein at the transition from the full diameter of the pump piston 26, where this is tightly guided in the cylinder bore 24 to the extension 82, an annular shoulder 84 is formed on the closing spring 80 is supported.
  • the closing spring 80 surrounds the extension 82 and the carrier part 78 is subsequently arranged on the extension 82.
  • the front end of the extension 82 of the pump piston 26 forms a stop for limiting the opening movement of the valve member 76 by the support member 78 comes to the extension 82 to the plant.
  • the closing spring 80 of the suction valve 36 is highly compressed and accordingly exerts a high force on the valve member 76, with which this is pressed against the valve seat 74.
  • the force generated by the closing spring 80 and by the pressure prevailing in the working space 34 on the valve member 76 counteracts the force generated in the inlet channel 72 pressure on the valve member 76 in the opening direction.
  • the valve member 76 moves against the force of the closing spring 80 in Opening direction and releases the mouth of the inlet channel 72 into the working space 34.
  • the pressure at which the valve member 76 moves in the opening direction is referred to as the opening differential pressure of the suction valve 36.
  • the pump piston 26 moves according to its top dead center FIG. 2 according to its bottom dead center according to FIG. 3 .
  • the closing spring 80 is increasingly relaxed, so that this causes a smaller force in the closing direction on the valve member 76 and corresponding to the opening differential pressure of the suction valve 36 is lower.
  • the opening differential pressure of the suction valve 36 is highest and will be referred to as maximum opening differential pressure hereinafter.
  • the opening differential pressure decreases.
  • a mean opening differential pressure of the suction valve 36 results.
  • the opening differential pressure of the suction valve 36 is the lowest, and is hereinafter referred to as the minimum opening differential pressure. It is envisaged that the minimum opening differential pressure of the suction valve 36 is less than 0.9 bar, preferably at most 0.8 bar.
  • the mean opening differential pressure and the maximum opening differential pressure of the suction valve 36 are then dependent on the spring rate c of the closing spring 80, that is, the change in the force generated by this force relative to the spring travel, and the stroke of the pump piston 26 between the top and bottom dead center.
  • the spring rate c of the closing spring 80 may have a small value, but the force exerted by the closing spring 80 on the valve member 76 substantially changes over the relatively large suction stroke of the pump piston 26.
  • the mean opening differential pressure of the suction valve 36 is greater than 0.9 bar.
  • the ratio between the average opening differential pressure and the minimum opening differential pressure of the suction valve 36 is greater than 1 and is at most about 10.
  • the influence of tolerances of the components of the high-pressure pump 18 can be reduced to the opening pressure and thus also an improvement of the uniform fuel delivery can be achieved by all pump elements 22.
  • the filling of the working space 34 can be improved, since the two filling decisive parameters, namely the filling effective pressure difference before and after the suction valve 36 and the opening duration of the suction valve 36, at low opening differential pressure of the suction valve 36 large are.
  • a delivery pump 10 with a lower delivery rate and a correspondingly smaller dimensioned drive can be used, which is less expensive. Characterized in that by means of the fuel metering device 60 of the Druchflußquerites from the feed pump 10 forth is completely closed, a zero promotion of the high-pressure pump 18 is ensured even at low opening differential pressure of the suction valve 36.

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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)

Claims (4)

  1. Dispositif d'injection de carburant pour un moteur à combustion interne et comprenant une pompe haute pression (18) qui refoule du carburant à haute pression dans un accumulateur (32), avec lequel sont raccordés des injecteurs (40) disposés au niveau des cylindres du moteur à combustion interne, comprenant une pompe de refoulement (10) qui refoule du carburant depuis un réservoir (12) jusqu'à la pompe haute pression (18), la pompe haute pression (18) présentant au moins un élément de pompe (22) avec un piston de pompe (26) limitant un espace de travail (34), entraîné dans un mouvement de course, et l'espace de travail (34) présentant une connexion au côté pression de la pompe de refoulement (10) dans laquelle est disposée une soupape d'admission (36) s'ouvrant vers l'espace de travail (34) à travers laquelle du carburant afflue dans l'espace de travail (34) lors de la course d'admission du piston de pompe (26), la soupape d'admission (36) présentant un organe de soupape (76) sollicité dans une direction de fermeture par un ressort de fermeture (80), le ressort de fermeture (80) s'appuyant au moins indirectement contre le piston de pompe (26) et avec une augmentation de la course d'admission du piston de pompe (26), la force de fermeture exercée par le ressort de fermeture (80) sur l'organe de soupape (76) diminuant, caractérisé en ce qu'une différence de pression d'ouverture minimale de la soupape d'admission (36) est inférieure à 0,9 bar, en ce qu'une différence de pression d'ouverture moyenne de la soupape d'admission (36) dans une position intermédiaire du piston de pompe (26) dans la région de la demi-course d'admission du piston de pompe (26) vaut au moins 0,9 bar et en ce que le rapport de la différence de pression d'ouverture moyenne à la différence de pression d'ouverture minimale de la soupape d'admission (36) est supérieur à 1 et vaut au maximum 10.
  2. Dispositif d'injection de carburant selon la revendication 1, caractérisé en ce que la différence de pression d'ouverture minimale de la soupape d'admission (36) vaut au maximum 0,8 bar.
  3. Dispositif d'injection de carburant selon l'une quelconque des revendications 1 ou 2, caractérisé en ce qu'entre la pompe de refoulement (10) et la soupape d'admission (36) est disposé un dispositif de dosage de carburant (60) qui ajuste une section transversale de passage pour le carburant s'écoulant vers la soupape d'admission (36) et qui permet de fermer complètement la section transversale de passage.
  4. Dispositif d'injection de carburant selon la revendication 3, caractérisé en ce que le dispositif de dosage de carburant (60) ajuste la section transversale de passage de telle sorte qu'une quantité de carburant soit refoulée par la pompe haute pression (18) dans l'accumulateur (32), laquelle quantité de carburant est nécessaire pour maintenir une pression prédéfinie dans l'accumulateur (32).
EP03004643.7A 2002-04-23 2003-03-03 Dispositif d'injection de carburant pour un moteur à combustion interne Expired - Lifetime EP1357283B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10218022 2002-04-23
DE10218022A DE10218022A1 (de) 2002-04-23 2002-04-23 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP1357283A2 EP1357283A2 (fr) 2003-10-29
EP1357283A3 EP1357283A3 (fr) 2004-09-22
EP1357283B1 true EP1357283B1 (fr) 2014-07-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03004643.7A Expired - Lifetime EP1357283B1 (fr) 2002-04-23 2003-03-03 Dispositif d'injection de carburant pour un moteur à combustion interne

Country Status (4)

Country Link
US (1) US6959694B2 (fr)
EP (1) EP1357283B1 (fr)
JP (1) JP4395319B2 (fr)
DE (1) DE10218022A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004040128A1 (fr) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression
US7387109B2 (en) * 2003-10-21 2008-06-17 Robert Bosch Gmbh High-pressure fuel pump for an internal combustion engine
DE102004028999A1 (de) * 2004-06-16 2006-01-05 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
EP1674716B1 (fr) * 2004-12-23 2010-12-15 C.R.F. Società Consortile per Azioni Système d'injection de carburant comprenant une pompe à carburant à haute pression à débit variable
DE102005033638A1 (de) * 2005-07-19 2007-01-25 Robert Bosch Gmbh Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine
JP4870015B2 (ja) * 2006-06-13 2012-02-08 京三電機株式会社 圧力調整弁
DE102007004605B4 (de) * 2007-01-30 2009-08-13 Continental Automotive Gmbh Hochdruckpumpe und Einspritzanlage für eine Brennkraftmaschine mit einer Hochdruckpumpe
US8234784B2 (en) * 2008-02-13 2012-08-07 Younger Steven W Valve piston repositioning apparatus and method
EP2226491B1 (fr) * 2009-02-16 2011-01-26 C.R.F. Società Consortile per Azioni Système d'injection de carburant pour moteur à combustion interne
DE102009028023A1 (de) * 2009-07-27 2011-02-03 Robert Bosch Gmbh Hochdruck-Einspritzsystem mit Kraftstoffkühlung aus Niederdruckbereich
US10012228B2 (en) * 2014-04-17 2018-07-03 Danfoss Power Solutions Gmbh & Co. Ohg Variable fluid flow hydraulic pump
JP2020118093A (ja) * 2019-01-24 2020-08-06 株式会社デンソー 燃料噴射ポンプ
DE102021212771A1 (de) 2021-11-12 2023-05-17 Robert Bosch Gesellschaft mit beschränkter Haftung Pumpe, insbesondere Kraftstoffhochdruckpumpe

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001040657A1 (fr) * 1999-11-30 2001-06-07 Robert Bosch Gmbh Pompe hydraulique haute pression a carburant

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59504990D1 (de) * 1994-03-23 1999-03-11 Siemens Ag Anordnung zur einspritzung von kraftstoff in die zylinder einer brennkraftmaschine
DE19846157A1 (de) * 1998-10-07 2000-04-13 Bosch Gmbh Robert Pumpenanordnung zur Kraftstoffhochdruckerzeugung
DE19848035A1 (de) * 1998-10-17 2000-04-20 Bosch Gmbh Robert Radialkolbenpumpe für Kraftstoffhochdruckerzeugung
DE19902259B4 (de) * 1999-01-21 2006-02-23 Siemens Ag Montageverfahren
DE19941850B4 (de) 1999-09-02 2005-03-31 Siemens Ag Einspritzanlage für eine Brennkraftmaschine
US6764286B2 (en) * 2001-10-29 2004-07-20 Kelsey-Hayes Company Piston pump with pump inlet check valve

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001040657A1 (fr) * 1999-11-30 2001-06-07 Robert Bosch Gmbh Pompe hydraulique haute pression a carburant

Also Published As

Publication number Publication date
EP1357283A3 (fr) 2004-09-22
JP2003314409A (ja) 2003-11-06
EP1357283A2 (fr) 2003-10-29
DE10218022A1 (de) 2003-11-06
US6959694B2 (en) 2005-11-01
US20030213471A1 (en) 2003-11-20
JP4395319B2 (ja) 2010-01-06

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