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EP1226354B1 - Dispositif de commande hydraulique, en particulier pour un injecteur - Google Patents

Dispositif de commande hydraulique, en particulier pour un injecteur Download PDF

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Publication number
EP1226354B1
EP1226354B1 EP00982991A EP00982991A EP1226354B1 EP 1226354 B1 EP1226354 B1 EP 1226354B1 EP 00982991 A EP00982991 A EP 00982991A EP 00982991 A EP00982991 A EP 00982991A EP 1226354 B1 EP1226354 B1 EP 1226354B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
control device
pressure
hydraulic control
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
EP00982991A
Other languages
German (de)
English (en)
Other versions
EP1226354A2 (fr
Inventor
Friedrich Boecking
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
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 EP1226354A2 publication Critical patent/EP1226354A2/fr
Application granted granted Critical
Publication of EP1226354B1 publication Critical patent/EP1226354B1/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
    • 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
    • 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
    • F02M47/025—Hydraulically 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion

Definitions

  • the invention relates to a hydraulic control device according to DE-A-19 803 910, in particular for an injector of a fuel injection system in motor vehicles according to the preamble of claim 1.
  • a hydraulic control device is already known from DE 196 24 001 A1.
  • This control device consists of a piezoelectric actuator and a directional control valve controlled by the actuator with a valve member guided displaceably in a valve bore.
  • the directional control valve is designed as a conventional seat valve and controls a pressure medium connection between a fuel under high pressure leading pressure medium channel and a return. In the non-activated state of the actuator, the valve member is lifted from the valve seat and thus releases the above-mentioned pressure medium connection.
  • the pressure level drops in an injection nozzle also coupled to the high-pressure medium channel.
  • a pressure-controlled closing element of the injection nozzle releases injection openings. Through these injection openings enters fuel into a combustion chamber of an internal combustion engine. With the closing of the valve seat by an electrical control of the actuator, the injection process is terminated.
  • A-valves have fluidic disadvantages, since the closing movement takes place against high pressure and the actuator must be performed correspondingly powerful and voluminous. In addition, A-valves are more expensive to produce.
  • the hydraulic control device according to the invention with the characterizing features of claim 1 has the advantage that it is designed as an inwardly opening I-valve.
  • I-valves the pressure gradient on the valve seat is directed opposite to the direction of movement of the valve member.
  • the lifting movement of the valve member is supported when opening the directional control valve by an additional hydraulic force, so that actuators are sufficient with lower actuation forces for valve control.
  • Such actuators build accordingly smaller and more compact and take on a lower electrical power. This reduces the load on the actuators, making them more robust and reliable.
  • FIG. 1 shows a schematic simplified representation of a fuel injection system 10. This consists of a driven pressure generator 12 and a pressure accumulator 14 coupled thereto. The latter is connected to an injector 16. Furthermore, an electronic control unit 18 is provided which keeps the pressure in the pressure accumulator 14 constant with the aid of a pressure sensor 20 and a pressure regulating valve 22. Several injectors 16 can be connected to the pressure accumulator 14, but only one of these injectors 16 is shown by way of example in FIG.
  • This injector 16 has a housing 24, in whose interior 26 a needle 28 is arranged.
  • the latter controls with its tip injection openings 30, which open into the combustion chamber of a not shown internal combustion engine.
  • the needle 28 is mechanically acted upon by a closing spring 32, which on the wall of the interior 26 and at one, formed at the inner end of the needle 28 plate 34 is supported.
  • acting on the plate 34 is a coaxial with the closing spring 32 arranged plunger 36 a.
  • This is guided in a cylinder bore 38 of the housing 24.
  • the cylinder bore 38 is connected via a branch passage 40 with a throttle arranged therein 42 with the interior 26 in hydraulic communication, so that the plunger 36 is hydraulically resilient.
  • pressure medium channel 44 supplies the interior 26 and the cylinder bore 38 with fuel under high pressure. Its pressure is loaded via the plunger 36, the needle 28. Together with the force of the closing spring, the resulting force on the needle 28 is sufficient to keep them in the illustrated closed position.
  • valve bore 48 branches from the cylinder bore 38 into a valve bore 48 opening branch channel 46 from.
  • valve bore 48 is acted upon by a piezoelectric actuator 52 valve member 50 is guided. This closes in the activated state of the actuator 52 at the discharge point of the branch channel 46 formed in the valve bore 48 valve seat 54 and thus interrupts a pressure medium connection to a return 56, which also branches off from the valve bore 48.
  • a piezoelectric actuator 52 valve member 50 is guided.
  • valve member 50 With the withdrawal of the electrical control of the actuator 52, the valve member 50 lifts off the valve seat 54 and opens the above-mentioned pressure medium connection. The high pressure in the injector then breaks down and the force acting on the plunger 36 hydraulic pressure force is eliminated. The applied by the closing spring 32 mechanical pressure force alone is not enough to the needle 28 in its closed position to keep. The needle 28 therefore opens and releases the injection openings 30.
  • valve seat 54 is closed again by the valve member 50, as a result of which pressure builds up again in the interior 26 of the injector 16.
  • the thus hydraulically loaded needle 28 closes the injection openings 30 again and terminates the injection process.
  • valve seat 54 When the valve seat 54 is open, the pressure gradient is accordingly rectified for the lifting movement of the valve member 50.
  • This valve member 50 thus forms an outwardly opening A-valve.
  • An injection process is initiated by canceling the activation of the actuator 52 and terminated by its activation.
  • the actuator 52 must close the valve member 50 against high pressure and must be designed accordingly powerful. In addition to the burden of the actuator 52 thereby increases the volume of construction.
  • FIG. 2 is designed as an inward-opening I-valve.
  • This control device 60 in which the actuator is shown symbolically only by means of a force arrow F, has a hydraulic booster 62.
  • the latter consists of a pot-shaped first piston 64 and guided in the interior of a second piston 66 smaller pressure surface.
  • the pistons 64, 66 delimit with their end faces a pressure medium-filled booster chamber 68, which lies outside of an enclosed by the two pistons 64 and 66 and vented cavity 70 outside.
  • a closing spring 72 is housed, which is supported on both pistons 64 and 66.
  • the piston 66 is connected to the valve member 74 of a directional control valve 75 or integrally formed with such, wherein the valve member 74 is slidably guided in a valve bore 76.
  • This valve member 74 has a translator 62 facing the control head 78, which merges with increasing distance from the piston 66 in a constriction 80 and then into a guide portion 82.
  • the guide portion 82 is provided on its outer periphery with a flat 84.
  • the constriction 80 is divided into a control head 78 facing waist 81 and a cylinder portion 83 adjacent to the guide portion 82 with a smaller outer diameter than the valve bore 76th
  • a leading to a not shown injector pressure medium channel 86 branches off in the region of the constriction 80 from the valve bore 76, while a fuel supply channel 88 opens in the region of the control head 78 in the valve bore 76.
  • an annular channel 90 is provided as a groove-shaped extension of the valve bore 76 in the region of the guide section 82. This is connected via the flattening 84 with a return 92, which branches off from a pressure chamber 94 formed at the end of the valve bore 76.
  • This first control cross-section 97 is open in the basic position, as shown in FIG. The injector not visible in Figure 2 is thus pressure relieved.
  • valve bore 76 is withdrawn at the transition from the control head 78 to the constriction 80 in its outer diameter.
  • the resulting change in diameter is designed as a chamfer, which acts as a valve seat 98. This forms a controllable by the control head 78 of the valve member 74 second control cross-section 99, which is closed in the illustrated basic position.
  • valve member 74 With the withdrawal of the activation of the actuator 52, the piston member 66 coupled to the valve member 74 is given a lifting movement, which is directed opposite to the deflection movement of the actuator 52.
  • the valve member 74 releases the second control cross-section 99 and simultaneously blocks the first control cross-section 97 with its control edge 96.
  • the resulting fluid connection between the fuel supply channel 88 and the pressure medium channel 86 causes the injector passes under high pressure and assumes its closed position.
  • the pressure fluid flow at the open valve seat 98 is therefore directed I-valve typical opposite to the lifting movement of the valve member 74.

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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)
  • Valve Device For Special Equipments (AREA)

Claims (11)

  1. Dispositif de commande hydraulique (60) pour un injecteur (16) d'un système d'injection de carburant (10), qui comprend un générateur de pression (12) à commande extérieure, un accumulateur de pression (14) hydrauliquement couplé au générateur de pression (12) et plusieurs injecteurs (16) branchés à l'accumulateur de pression (14) et associés chacun à une chambre de combustion d'un moteur à combustion, avec un actionneur (52) piézoélectrique et une soupape à 3/2 voies (75) commandée par l'actionneur (52), et dont l'alésage de soupape (76) loge un organe de soupape (74) guidé en déplacement pour alimenter l'organe d'injecteur (28) en pression de commande en direction de la fermeture par l'intermédiaire d'une section transversale de commande (99) commandée par un élément de siège de soupape de l'organe de soupape (74), et pour décharger l'organe d'injecteur vers un retour par l'intermédiaire d'une autre section transversale de commande (97) commandée par l'organe de soupape (74), les sections transversales de commande (97, 99) étant dégagées ou obturées en alternance par l'organe de soupape,
    caractérisé en ce qu'
    entre l'actionneur (52) et l'organe de soupape (74) un amplificateur hydraulique (62) inverse le mouvement d'excursion de l'actionneur (52) dans la direction spatiale opposée, l'organe de soupape (74) présente une rampe de commande (96) pour commander l'autre section transversale de commande (97), et le gradient de pression au niveau d'une section transversale de commande (99) ouverte est orienté à l'opposé du mouvement de levage de l'organe de soupape (74).
  2. Dispositif de commande hydraulique selon la revendication 1 ou 2,
    caractérisé en ce que
    l'amplificateur (62) présente des pistons (64, 66) avec des surfaces de piston de tailles différentes, le premier piston (64) a la forme d'un pot et le deuxième piston (66) est guidé à l'intérieur de celui-ci, un ressort de fermeture (72) est enserré entre les deux pistons (64 et 66), et les pistons (64, 66) délimitent une chambre d'amphficateur (68) commune.
  3. Dispositif de commande hydraulique selon la revendication 2,
    caractérisé en ce que
    l'organe de soupape (74) est ancré sur le deuxième piston (66).
  4. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    l'organe de soupape (74) présente une tête de commande (78) d'un diamètre extérieur renforcé, un rétrécissement (80) et un segment de guidage (82), le diamètre extérieur du segment de guidage (82) est supérieur à celui du rétrécissement (80) mais inférieur à celui de la tête de commande (78), et le segment de guidage (82) est muni au moins d'un aplatissement (84) prévu à la périphérie extérieure.
  5. Dispositif de commande hydraulique selon la revendication 4,
    caractérisé en ce que
    le siège de soupape (98) est formé au niveau du point de passage de la tête de commande (78) vers le rétrécissement (80) sur la paroi intérieure adaptée en conséquence de l'alésage de soupape (76) et se situe entre un canal d'alimentation en carburant (88) et un canal de fluide de pression (86) vers l'injecteur (16).
  6. Dispositif de commande hydraulique selon la revendication 4 ou 5,
    caractérisé en ce que
    l'alésage de soupape (76) est muni d'un évasement (90) en forme de rainure, qui est commandé par la rampe de commande (96) de l'organe de soupape (74) et formé sur l'alésage de soupape (76) dans la zone du point de passage du rétrécissement (80) vers le segment de guidage (82) de l'organe de soupape (74).
  7. Dispositif de commande hydraulique selon l'une quelconque des revendications 4 à 6,
    caractérisé en ce qu'
    un canal d'alimentation en carburant (88) débouche dans la zone de la tête de commande (78) dans l'alésage de soupape (76), et un canal de fluide de pression (86) dérive de l'alésage de soupape (76) vers l'injecteur (16) dans la zone du rétrécissement (80) et un retour (92) dérive dans la zone du segment de guidage (82) de l'organe de soupape (74).
  8. Dispositif de commande hydraulique selon l'une quelconque des revendications 4 à 7,
    caractérisé en ce que
    la tête de commande (78) est tournée vers le deuxième piston (66) et le segment de guidage (82) est à l'opposé du deuxième piston (66), et le rétrécissement (80) est disposé entre la tête de commande (78) et le segment de guidage (82).
  9. Dispositif de commande hydraulique selon l'une quelconque des revendications 4 à 8,
    caractérisé en ce que
    le rétrécissement (80) est composé d'un col (81) tourné vers la tête de commande (78) et d'un segment cylindrique (83) tourné vers le segment de guidage (82), dont le diamètre extérieur est inférieur au diamètre intérieur de l'alésage de soupape (76).
  10. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 9,
    caractérisé en ce que
    l'alésage de soupape (76) est un trou borgne se terminant dans une chambre de commande (94) dans laquelle plonge l'organe de soupape (74) et de laquelle dérive un retour (92).
  11. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 10,
    caractérisé en ce que
    dans la position de base du dispositif de commande (60) les surfaces de sections transversales de commande (97, 99) sollicitées hydrauliquement présentent les mêmes dimensions.
EP00982991A 1999-10-22 2000-10-12 Dispositif de commande hydraulique, en particulier pour un injecteur Expired - Lifetime EP1226354B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19951004A DE19951004A1 (de) 1999-10-22 1999-10-22 Hydraulische Steuervorrichtung, insbesondere für einen Injektor
DE19951004 1999-10-22
PCT/DE2000/003590 WO2001029395A2 (fr) 1999-10-22 2000-10-12 Dispositif de commande hydraulique, en particulier pour un injecteur

Publications (2)

Publication Number Publication Date
EP1226354A2 EP1226354A2 (fr) 2002-07-31
EP1226354B1 true EP1226354B1 (fr) 2005-09-21

Family

ID=7926577

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00982991A Expired - Lifetime EP1226354B1 (fr) 1999-10-22 2000-10-12 Dispositif de commande hydraulique, en particulier pour un injecteur

Country Status (8)

Country Link
US (1) US6820820B1 (fr)
EP (1) EP1226354B1 (fr)
JP (1) JP2003512573A (fr)
CN (1) CN1196857C (fr)
AT (1) ATE305090T1 (fr)
CZ (1) CZ295509B6 (fr)
DE (2) DE19951004A1 (fr)
WO (1) WO2001029395A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105508082B (zh) * 2015-11-27 2018-07-24 哈尔滨工程大学 增压无泄漏电磁控制式燃气喷射装置

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DE10032924A1 (de) * 2000-07-06 2002-01-24 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10145622B4 (de) * 2001-09-15 2009-09-10 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
DE10212396A1 (de) * 2002-03-20 2003-10-09 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung mit 3/2-Wege-Ventil
ITBO20020497A1 (it) 2002-07-30 2004-01-30 Magneti Marelli Powertrain Spa Iniettore di carburante per un motore a combustione interna con attuazione idraulica dello spillo
DE10333696A1 (de) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10337574A1 (de) * 2003-08-14 2005-03-10 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE10340137A1 (de) * 2003-09-01 2005-04-07 Robert Bosch Gmbh Verfahren zur Bestimmung der Ansteuerspannung eines piezoelektrischen Aktors eines Einspritzventils
JP3997983B2 (ja) 2003-11-10 2007-10-24 株式会社デンソー 圧電素子駆動による３方向切替弁およびその３方向切替弁を用いた燃料噴射弁
ITBO20040466A1 (it) 2004-07-23 2004-10-23 Magneti Marelli Holding Spa Iniettore di carburante con attuazione elettromagnetica
DE102004044462A1 (de) * 2004-09-15 2006-03-30 Robert Bosch Gmbh Steuerventil für einen Injektor
ITBO20040649A1 (it) 2004-10-20 2005-01-20 Magneti Marelli Powertrain Spa Iniettore di carburante con attuazione elettromagnetica dello spillo
DE102005020598A1 (de) * 2005-05-03 2006-11-09 Robert Bosch Gmbh Ventilanordnung einer Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE102005025953A1 (de) * 2005-06-06 2006-12-07 Siemens Ag Einspritzventil und Ausgleichselement für ein Einspritzventil
JP4475331B2 (ja) * 2008-01-10 2010-06-09 株式会社デンソー 燃料噴射装置
ATE551521T1 (de) 2008-04-18 2012-04-15 Magneti Marelli Spa Kraftstoffeinspritzdüse mit direkter verschlussbetätigung für verbrennungsmotoren
CN102151627B (zh) * 2011-04-01 2012-12-19 上海大学 用于双流体喷射器的液体控制系统
DE102011078657A1 (de) * 2011-07-05 2013-01-10 Robert Bosch Gmbh Dosiersystem sowie 3/2-Wegeventil für ein Dosiersystem
CN105221314B (zh) * 2015-10-29 2017-11-07 常州机电职业技术学院 防积碳喷油器

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US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
DE19701879A1 (de) * 1997-01-21 1998-07-23 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE29708369U1 (de) * 1997-05-09 1997-07-10 FEV Motorentechnik GmbH & Co. KG, 52078 Aachen Steuerbares Einspritzventil für die Kraftstoffeinspritzung an Brennkraftmaschinen
US5979803A (en) * 1997-05-09 1999-11-09 Cummins Engine Company Fuel injector with pressure balanced needle valve
US5884848A (en) * 1997-05-09 1999-03-23 Cummins Engine Company, Inc. Fuel injector with piezoelectric and hydraulically actuated needle valve
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105508082B (zh) * 2015-11-27 2018-07-24 哈尔滨工程大学 增压无泄漏电磁控制式燃气喷射装置

Also Published As

Publication number Publication date
DE19951004A1 (de) 2001-04-26
CN1196857C (zh) 2005-04-13
WO2001029395A3 (fr) 2001-12-27
CN1382249A (zh) 2002-11-27
US6820820B1 (en) 2004-11-23
JP2003512573A (ja) 2003-04-02
CZ295509B6 (cs) 2005-08-17
DE50011226D1 (de) 2005-10-27
WO2001029395A2 (fr) 2001-04-26
EP1226354A2 (fr) 2002-07-31
ATE305090T1 (de) 2005-10-15
CZ20021334A3 (cs) 2003-10-15

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