EP0657644B1 - Dispositif d'injection de combustible pour moteurs à combustion interne - Google Patents

Dispositif d'injection de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP0657644B1
EP0657644B1 EP94113012A EP94113012A EP0657644B1 EP 0657644 B1 EP0657644 B1 EP 0657644B1 EP 94113012 A EP94113012 A EP 94113012A EP 94113012 A EP94113012 A EP 94113012A EP 0657644 B1 EP0657644 B1 EP 0657644B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
injection device
fuel injection
sealing surface
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
EP94113012A
Other languages
German (de)
English (en)
Other versions
EP0657644A2 (fr
EP0657644A3 (fr
Inventor
Peter Dipl.-Ing. Müller
Jaroslaw Dipl.-Ing. Hlousek
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 EP0657644A2 publication Critical patent/EP0657644A2/fr
Publication of EP0657644A3 publication Critical patent/EP0657644A3/fr
Application granted granted Critical
Publication of EP0657644B1 publication Critical patent/EP0657644B1/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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a fuel injection device for Internal combustion engines according to the preamble of claim 1.
  • Fuel injection device promotes a high-pressure fuel pump Fuel from a low-pressure chamber into a high-pressure collection chamber, of the high pressure lines with the individual, in projecting the combustion chamber of the internal combustion engine to be supplied Injector is connected, this common pressure storage system by a pressure control device on a particular one Pressure is maintained.
  • a pressure control device on a particular one Pressure is maintained.
  • the Control valves on the injection valves are solenoid valves executed the connection of the at the start of injection Open the high pressure line with the injection valve and open it on Close the injection end again.
  • the control valve a piston-shaped valve member with two, with two fixed Valve seats interacting valve sealing surfaces, wherein a first valve sealing surface connects the high pressure line the connection to the injection valve and a second valve sealing surface of the injection valve with a relief chamber.
  • the control valves on the known fuel injection devices however, the disadvantage of that with them is not possible, the injection process at the injection valve to shape.
  • the main problem there is that the Injector valve high fuel pressure not fast enough can be relaxed, causing inaccuracies in control at the end of injection can result.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that the end of injection can be safely controlled by means of a relief valve upstream of the relief valve.
  • This return suction collar removes fuel from the pressure line to the injection valve during the closing movement of the control valve member, so that a rapid pressure drop at the injection end is ensured there.
  • a further advantage is achieved by arranging an annular shoulder in the pressure chamber in the opening direction of the valve to open the connection between the high-pressure line and the injection valve, by means of which a safety function can be integrated into the control valve.
  • This annular shoulder is designed so that when a predetermined maximum pressure in the high-pressure line and in the pressure chamber is exceeded, the opening cross-section to the annular space is released to a small extent, which is so small that the opening cross-section does not control the valve seat controlling the connection of the annular space to a relief chamber is completely closed, so that the excess fuel pressure from the annular space relaxes in the relief space and further into a return line to the low-pressure fuel space.
  • FIG. 1 shows a schematic representation of the fuel injection device with a longitudinal section through the control valve and the injection valve and FIG. 2 shows an enlarged section of the control valve of FIG. 1, in which the arrangement of an additional annular shoulder on the valve member is shown.
  • a high-pressure fuel pump 1 is connected on the suction side via a fuel supply line 3 to a fuel-filled low-pressure chamber 5 and on the pressure side via a delivery line 7 to a high-pressure collecting chamber 9.
  • High-pressure lines 13 lead from the high-pressure plenum 9 to the individual injection valves 15 projecting into the combustion chamber of the internal combustion engine to be supplied, an electric control valve 17 being inserted into each injection valve 15 in the respective high-pressure line 13 to control the injection process.
  • a further pressure storage space 19 is provided in each high-pressure line 13 between the high-pressure collecting space 9 and the control valve 17, the dimensioning of which allows the injection course at the injection valve to be shaped.
  • the control valve 17 is designed as a 3/2 way valve, the piston-shaped valve member 21 of which is actuated by an electric actuating magnet 25 acting on its one end face.
  • the actuating magnet 25 is fastened to the valve member via an anchor plate 27 by means of a screw 29 in an axial blind bore of the valve member 21 and counteracts a return spring clamped between the housing 23 and a spring plate 31, which is arranged in a spring chamber 35 of the control valve 17.
  • the piston-shaped valve member 21 has two mutually facing valve sealing surfaces, of which a first conical valve sealing surface 37 interacts with a conical valve seat 39.
  • This conical valve sealing surface 37 is formed by a conical cross-sectional reduction of a guide piston part 41, which slides sealingly in a guide bore 43 and projects into the spring chamber 35 with its end facing away from the conical valve sealing surface 37.
  • the conical valve seat 39 is formed by a reduction in the diameter of the guide bore 43, the sealing being effected via the outside diameter on the valve seat 39 when the valve is closed.
  • the second valve sealing surface is designed as a flat sealing surface 45 and interacts with a flat valve seat 47.
  • the flat valve sealing surface 45 is arranged on an axial annular surface facing the conical valve sealing surface 37 of an annular web 49 delimiting the valve member 21 on the side facing away from the actuating magnet 25.
  • the flat valve seat 47 is formed by a ring shoulder on the guide bore 43 designed as a stepped bore.
  • the annular web 49 borders on a first annular groove 51, which on the other hand is delimited by a suction collar 53.
  • This suckback collar 53 has only a slightly smaller outside diameter than the guide bore 43 designed as a stepped bore in this area and thus forms on its circumferential surface a throttle section 55 connected upstream of the flat seat valve, which opens into an annular space 57 on the side facing away from the first annular groove 51 the arrangement of a second annular groove 59 on the valve member 21 between the conical valve sealing surface 37 and the suction collar 53 is formed in the guide bore 43 and from which a pressure line 61 leads to the injection valve 15.
  • the throttle 55 can also be formed by a small difference in diameter between the suction collar 53 and the guide piston part 41 with the same diameter of the guide bore 43 in these areas, the diameter of the guide piston part 41 then being about 5 to 30 ⁇ m larger than the diameter of the suction collar 53, so that there is a corresponding throttle ring gap on the throttle 55.
  • a pressure chamber 63 adjoins the larger diameter of the conical valve sealing surface 37, into which the high-pressure line 13 opens.
  • the ring web 49 protrudes with its end facing away from the flat valve seat 47 into a relief chamber 65 which continues axially in the direction facing away from the actuating magnet 25 into a spring chamber 67 of the injection valve 15, in which a valve spring 71 acting on a valve member 69 of the injection valve 15 in the closing direction is arranged and from which a return line 73 leads into the low-pressure chamber 5.
  • the valve member 69 of the injection valve 15 is provided in a known manner with a conical pressure shoulder 75 which projects into a pressure chamber 77 connected to the pressure line 61 in such a way that the pressure in the pressure chamber 77 acts on the valve member 69 in the opening direction.
  • an injection channel 79 leads from the pressure chamber 77 along the valve member 69 to one or more injection openings 81 of the injection valve 15, which are controlled by the sealing surface at the tip of the valve member 69, into the combustion chamber, not shown, of the internal combustion engine to be supplied.
  • the spring chamber 35 of the control valve 17 is connected to the return line 73 via a connecting bore 83, so that the end faces of the valve member 21 are pressure-balanced.
  • the stroke movement of the valve member 21 is in each case limited by the contact of the valve sealing surfaces 37, 45 on one of the valve seats 39, 47.
  • the fuel injection device according to the invention works in the following way.
  • the high-pressure fuel pump 1 conveys the fuel from the low-pressure chamber 5 into the high-pressure collection chamber 9 and thus builds up a high-pressure fuel in the latter. This high fuel pressure continues via the high-pressure lines 13 into the pressure chamber 63 of the individual control valves 17 at the injection valves 15 and also fills the respective pressure storage spaces 19.
  • the actuating magnet 25 on the control valve 17 is switched off that the return spring 33 holds the valve member 21 via the spring plate 31 with the conical valve sealing surface 37 in contact with the conical valve seat 39, so that the connection between the high pressure fuel chamber 63 and the annular chamber 57 permanently connected to the pressure line 61 to the injection valve 15 is closed and the connection from the annular space 57 into the relief space 65 is open. If an injection is to take place at the injection valve 15, the actuating magnet 25 is energized and displaces the valve member 21 of the control valve 17 against the restoring force of the spring 33 until its flat valve sealing surface 45 abuts the flat valve seat 47.
  • connection of the annular space 57 to the relief space 65 is closed and opened to the pressure line 61, so that the high fuel pressure now propagates from the pressure space 63 via the annular space 57 and the pressure line 61 to the pressure space 77 of the injection valve 15 and there by lifting the valve member 69 from its valve seat in a known manner the injection at the injection openings 81st he follows. If the injection is to be ended, the actuating magnet 25 is again de-energized and the return spring 33 moves the valve member 21 back against the conical valve sealing surface 37 against the conical valve seat 39.
  • the suction collar 53 releases a specific suction volume at the annular space 57 that the high-pressure fuel volume in the pressure line 61 relaxes, so that the fuel pressure in the pressure line 61 and on the injection valve 15 drops very quickly below the closing pressure of the injection valve 15 and the injection valve 15 closes safely.
  • the further outflow of the fuel from the annular space 57 or the pressure line 61 now takes place via the throttle 55 on the suction collar 53, so that a certain residual pressure remains in the pressure line 61 until the following injection process.
  • This ring shoulder 91 serves as a relief or safety valve that works at an overpressure in the high pressure line 13 of about 10% opening the conical Valve seat 39 causes. This relief can also the pressure peaks occurring at the end of injection in the pressure storage chamber 19 are dismantled.
  • the ring shoulder 91 is dimensioned so that it causes only a small opening stroke of the valve member 21, so that the flat seat valve does not close completely and the Overpressure from the pressure chamber 63 into the annular space 57 and further into the Relief chamber 65 can relax.

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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 (15)

  1. Installation d'injection de carburant pour des moteurs à combustion interne comprenant une pompe à carburant à haute pression (1) transférant le carburant d'une chambre basse pression (5) dans une chambre collectrice haute pression (9), et qui est reliée par une conduite haute pression (13) à des injecteurs (15) venant dans la chambre de combustion du moteur à combustion interne alimentée, et dont le mouvement d'ouverture et de fermeture est commandé chaque fois par une soupape de commande (17) à commande électrique, montée dans la conduite haute pression (13) au niveau de l'injecteur (15),
    la soupape de commande (17) ayant un organe d'obturation (21) en forme de piston et deux surfaces d'étanchéité de soupape tournées l'une vers l'autre et coopérant avec deux sièges de soupape, et la première de ces surfaces d'étanchéité (37) commande l'ouverture de la communication entre la conduite haute pression (13) et la soupape d'injection (15) et la seconde surface d'étanchéité de soupape (45) commande l'ouverture de la communication de l'injecteur (15) avec une chambre de décharge (65),
    caractérisée en ce que
    la seconde surface d'étanchéité de soupape (45) est précédée par une collerette de réaspiration (53) prévue sur l'organe d'obturation (21), et qui lors du soulèvement de la seconde surface d'étanchéité (45) par rapport à son siège (47) à la fin de l'injection, libère un volume de réaspiration dans lequel se détend une partie de la quantité de carburant qui se trouve devant l'injecteur (15).
  2. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    la surface périphérique de la collerette de réaspiration (53) ne présente qu'un faible jeu par rapport à la paroi d'un perçage de guidage (43) aboutissant à l'organe d'obturation (21) et constitue ainsi un organe d'étranglement (55) en amont du siège de soupape (47) coopérant avec la seconde surface d'étanchéité (45).
  3. Installation d'injection de carburant selon les revendications 1 et 2,
    caractérisée en ce que
    la première surface d'étanchéité de l'organe d'obturation est une surface d'étanchéité (37), conique, assurant l'étanchéité au niveau du diamètre extérieur du cône, et coopérant avec un siège de soupape (39), conique prévu dans le perçage de guidage (43).
  4. Installation d'injection de carburant selon les revendications 1 et 2,
    caractérisée en ce que
    la seconde surface d'étanchéité de soupape est réalisée sur l'organe d'obturation (21) sous la forme d'une surface d'étanchéité plate (45) qui est prévue sur une surface annulaire axiale tournée vers la surface d'étanchéité conique (37) et appartenant à une nervure annulaire (49) délimitant l'organe d'obturation (21) et coopérant avec un siège de soupape plat (47) formé sur un épaulement du perçage de guidage (43).
  5. Installation d'injection de carburant selon les revendications 3 et 4,
    caractérisée en ce qu'
    entre la collerette de réaspiration (53) et la nervure annulaire (49) il est prévu une première rainure annulaire (51) et entre la surface d'étanchéité (37), conique et la collerette de réaspiration (53), il est prévu une seconde rainure annulaire (59).
  6. Installation d'injection de carburant selon la revendication 3,
    caractérisée en ce que
    du côté de la surface d'étanchéité conique (37) non tournée vers le siège de soupape conique (39), fait suite une partie de piston de guidage (41) qui coulisse de manière étanche dans le perçage de guidage (43).
  7. Installation d'injection de carburant selon la revendication 6
    caractérisée en ce que
    le siège de soupape conique (39) est adjacent au niveau de son plus grand diamètre à une chambre de pression (63) entourant la partie de piston de guidage (41) et dans laquelle débouche la conduite haute pression (13).
  8. Installation d'injection de carburant selon la revendication 5,
    caractérisée en ce que
    le siège de soupape conique (39) est adjacent par son petit diamètre à un volume annulaire (57) formé entre la seconde rainure annulaire (59) et la paroi du perçage de guidage (43), volume relié par une conduite de pression (61) à l'injecteur (15) et dont l'autre extrémité est délimitée par la collerette de réaspiration (53).
  9. Installation d'injection de carburant selon la revendication 8,
    caractérisée en ce que
    le siège de soupape plat (47), est adjacent par son côté non tourné vers le volume annulaire (57) à une chambre de décharge (65) reliée par une conduite de retour (73) à la chambre basse pression (5).
  10. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    la course de l'organe d'obturation (21) est délimitée par la venue en appui des surfaces d'étanchéité (37, 45) contre l'un des sièges de soupape (39, 47).
  11. Installation d'injection de carburant selon la revendication 8,
    caractérisée en ce que
    les différents composants de l'organe d'obturation (21) sont reliés à l'aide d'une vis (29) pénétrant dans un perçage borgne axial de l'organe d'obturation (21) à une plaque d'induit (27) d'un électroaimant d'actionnement (25) actionnant la soupape de commande (17).
  12. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    dans chacune des conduites haute pression (13) reliant la chambre collectrice à haute pression (9) et la soupape de commande (17), il est prévu au niveau de chaque injecteur (15), une chambre accumulatrice de pression (19).
  13. Installation d'injection de carburant selon la revendication 7,
    caractérisée en ce que
    sur la partie de piston de guidage (41), dans la zone de la chambre de pression (63) reliée en permanence à la conduite de haute pression (13), il est prévu un épaulement annulaire (91) sollicité par la pression de la chambre de pression (63) dans le sens de l'ouverture de la surface d'étanchéité conique (37) par rapport au siège de soupape (39).
  14. Installation d'injection de carburant selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    le diamètre de la partie de piston de guidage (41) est égal ou légèrement supérieur à celui de la collerette de réaspiration (53).
  15. Installation d'injection de carburant selon la revendication 14,
    caractérisée en ce que
    la différence entre les diamètres de la partie de piston de guidage (41) et de la collerette de réaspiration (53) on a un intervalle annulaire d'étranglement au niveau de l'organe d'étranglement (55) ayant une largeur d'intervalle comprise entre 5 µm et 30 µm.
EP94113012A 1993-12-07 1994-08-20 Dispositif d'injection de combustible pour moteurs à combustion interne Expired - Lifetime EP0657644B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4341546 1993-12-07
DE4341546A DE4341546A1 (de) 1993-12-07 1993-12-07 Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP0657644A2 EP0657644A2 (fr) 1995-06-14
EP0657644A3 EP0657644A3 (fr) 1995-12-06
EP0657644B1 true EP0657644B1 (fr) 1999-01-13

Family

ID=6504297

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94113012A Expired - Lifetime EP0657644B1 (fr) 1993-12-07 1994-08-20 Dispositif d'injection de combustible pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US5538187A (fr)
EP (1) EP0657644B1 (fr)
JP (1) JP3742669B2 (fr)
DE (2) DE4341546A1 (fr)

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AT408132B (de) * 1995-09-14 2001-09-25 Avl Verbrennungskraft Messtech Speichereinspritzsystem für eine brennkraftmaschine
DE19547877A1 (de) * 1995-12-21 1997-06-26 Bosch Gmbh Robert Kraftstoffhochdruckspeichersystem für ein in Brennkraftmaschinen eingesetztes Kraftstoffeinspritzsystem
US5788154A (en) * 1996-05-02 1998-08-04 Caterpillar Inc. Method of preventing cavitation in a fuel injector having a solenoid actuated control valve
GB9609382D0 (en) * 1996-05-03 1996-07-10 Lucas Ind Plc Fuel injection system
JP3823391B2 (ja) * 1996-08-31 2006-09-20 いすゞ自動車株式会社 エンジンの燃料噴射装置
DE19712135C1 (de) 1997-03-22 1998-08-13 Mtu Friedrichshafen Gmbh Kraftstoffeinspritzsystem für eine Brennkraftmaschine
US5860597A (en) * 1997-03-24 1999-01-19 Cummins Engine Company, Inc. Injection rate shaping nozzle assembly for a fuel injector
DE19728111A1 (de) 1997-07-02 1999-01-07 Bosch Gmbh Robert Kraftstoffeinspritzsystem
DE19732070C2 (de) * 1997-07-25 2001-02-01 Daimler Chrysler Ag Direkteinspritzendes Kraftstoffeinspritzventil mit Magnetventilsteuerung für eine mehrzylindrige Brennkraftmaschine
WO1999034111A1 (fr) * 1997-12-23 1999-07-08 Siemens Aktiengesellschaft Soupape d'injection a vanne de controle
US5967413A (en) * 1998-02-11 1999-10-19 Caterpillar Inc. Damped solenoid actuated valve and fuel injector using same
GB9812889D0 (en) * 1998-06-15 1998-08-12 Lucas Ind Plc Fuel injector
US6029632A (en) * 1998-07-21 2000-02-29 Daimlerchrysler Ag Fuel injector with magnetic valve control for a multicylinder internal combustion engine with direct fuel injection
US6113000A (en) * 1998-08-27 2000-09-05 Caterpillar Inc. Hydraulically-actuated fuel injector with intensifier piston always exposed to high pressure actuation fluid inlet
DE19842067A1 (de) * 1998-09-15 2000-03-16 Daimler Chrysler Ag Kraftstoffeinspritzanlage für eine Dieselbrennkraftmaschine
GB9823134D0 (en) * 1998-10-23 1998-12-16 Lucas Ind Plc Valve
DE19907544C2 (de) * 1999-02-22 2002-12-05 Siemens Ag Injektor für eine Einspritzanlage einer Brennkraftmaschine
DE19928846A1 (de) * 1999-06-24 2001-03-08 Bosch Gmbh Robert Common-Rail-Injektor
DE19951554A1 (de) * 1999-10-26 2001-05-10 Bosch Gmbh Robert Kraftstoffinjektor mit integrierter Durchflussbegrenzung
DE19963367B4 (de) * 1999-12-28 2008-07-31 Robert Bosch Gmbh Common-Rail-Injektor
DE10001828A1 (de) 2000-01-18 2001-07-19 Fev Motorentech Gmbh Direktgesteuerte Kraftstoffeinspritzeinrichtung für eine Kolbenbrennkraftmaschine
DE10065221B4 (de) * 2000-12-27 2007-11-29 Robert Bosch Gmbh Direkt gesteuertes 2-Sitzventil für Kraftstoffeinspritzsysteme
US7278593B2 (en) * 2002-09-25 2007-10-09 Caterpillar Inc. Common rail fuel injector
FI117349B (fi) * 2002-08-02 2006-09-15 Waertsilae Finland Oy Polttoaineen syöttöjärjestelmä
DE10342698A1 (de) * 2003-09-16 2005-04-28 Bosch Gmbh Robert Druckgesteuerter CR-Injektor
JP5043761B2 (ja) 2008-06-18 2012-10-10 本田技研工業株式会社 燃料噴射装置
CN107524551B (zh) * 2017-08-31 2020-01-31 重庆红江机械有限责任公司 一种带保压结构的微喷电控喷油器
CN108150662A (zh) * 2018-02-05 2018-06-12 潍坊力创电子科技有限公司 双阀门气体喷射阀

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Also Published As

Publication number Publication date
JP3742669B2 (ja) 2006-02-08
DE59407647D1 (de) 1999-02-25
US5538187A (en) 1996-07-23
EP0657644A2 (fr) 1995-06-14
EP0657644A3 (fr) 1995-12-06
DE4341546A1 (de) 1995-06-08
JPH07189851A (ja) 1995-07-28

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