EP0657643B1 - 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
EP0657643B1
EP0657643B1 EP94113011A EP94113011A EP0657643B1 EP 0657643 B1 EP0657643 B1 EP 0657643B1 EP 94113011 A EP94113011 A EP 94113011A EP 94113011 A EP94113011 A EP 94113011A EP 0657643 B1 EP0657643 B1 EP 0657643B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
space
injection device
fuel injection
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
EP94113011A
Other languages
German (de)
English (en)
Other versions
EP0657643A3 (fr
EP0657643A2 (fr
Inventor
Peter Dipl.-Ing. Mueller
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 EP0657643A2 publication Critical patent/EP0657643A2/fr
Publication of EP0657643A3 publication Critical patent/EP0657643A3/fr
Application granted granted Critical
Publication of EP0657643B1 publication Critical patent/EP0657643B1/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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped

Definitions

  • the invention relates to a fuel injection device for Internal combustion engines according to the preamble of claim 1.
  • a fuel injector known from FR-A-2 449 795 this type 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, protruding into 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.
  • an electrically controlled control valve in the high pressure lines used that with its opening and closing the High-pressure fuel injection on the injection valve controls.
  • 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 has a piston-shaped valve member with two facing away from each other Valve surfaces with corresponding fixed valve seats work together.
  • control valves on the known fuel injection devices have the disadvantage that they immediately release the entire opening cross section at the beginning of the injection, so that already at the start of the injection a large amount of fuel reaches the combustion chamber of the internal combustion engine to be supplied, which there, in a known manner, leads to high pressure peaks Start of combustion leads.
  • the known control valves have the disadvantage that their valve members are acted upon on one side by the high delivery pressure in the open position, so that large actuating forces are necessary to close the control valves at the end of the injection, which can only be achieved with large actuating magnets or return springs. It is therefore not sufficiently possible with control valves of the known fuel injection devices to carry out an injection curve shaping on the injection valve.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that the course of the injection can be shaped by the design of the control valve, in particular at the beginning and end of injection. This is achieved there in a structurally simple manner by arranging a damping space formed when the flat seat valve is open, between the flat valve sealing surface on the collar and the flat valve seat interacting with it, this damping space in each case via a throttle section with a relief space and with the pressure line to the injection valve at all times connected pressure chamber is connectable.
  • the throttled outflow of fuel from the damping chamber enables a delayed opening movement of the valve member on the conical valve seat, which opens the connection between the high-pressure line and the injection valve, at the beginning of the injection, this delay being adjustable via the dimensioning of the throttle cross-section in the relief duct.
  • a small part of the delivery volume can flow into the relief channel via the throttle cross-section on the circumferential surface of the federal government at the start of injection when the flat seat valve is not yet fully closed, which also contributes to a reduction in the initial injection pressure and thus the injection amount at the start of injection.
  • the injection end can be influenced by the design of the throttle cross-section of the throttle upstream of the flat valve seat at the collar, the outflow quantity being at least so large that a rapid pressure drop in the injection valve below the injection pressure and thus reliable closing is ensured.
  • a further advantage is achieved by decoupling the injection valve from the high system pressure in the high-pressure line, it being possible to set the outflow quantity and thus the residual pressure remaining at the injection valve via the throttle cross section at the collar of the valve member.
  • FIG. 1 shows a schematic illustration of the fuel injection device with a longitudinal section through the control valve and the injection valve.
  • a high-pressure fuel pump 1 is connected on the suction side to a fuel-filled low-pressure chamber 5 via a fuel supply line 3 and on the pressure side to a high-pressure collecting chamber 9 via a delivery line 7.
  • 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 in each injection valve 15 into 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 and is integrated in a housing 21 of the control valve 17.
  • the control valve 17 is designed as a 3/2-way valve, the piston-shaped valve member 23 of which is actuated by an electric actuating magnet 29 acting on its one end, counter to a compression spring which is supported on the valve member 23 between the housing 21 and a spring plate 25.
  • the piston-shaped valve member 23 has two axial sealing surfaces facing away from one another, of which a first conical sealing surface 31 is arranged on an annular web 33 and cooperates with a conical valve seat 35.
  • first annular groove 37 on the valve member 23 which is delimited on its side facing away from the annular web 33 by a collar 39 which, on the other hand, adjoins a reduced-diameter piston skirt, the remaining axial annular surface on the side of the collar 39 facing the piston skirt 41 forms a second, flat sealing surface 43 on the valve member 23, which cooperates with a flat valve seat 47 surrounding a bore 45.
  • the collar 39 and the ring web 33 are arranged in a pressure chamber 49 delimited by the conical valve seat 35 and flat valve seat 47, which is designed such that it has only a slight clearance to the circumferential surface of the valve member 23 in the region of the collar 39 and thus a throttle section 51 for the fuel flowing from the pressure chamber 49 in the direction of the flat valve seat 47.
  • a damping space 53 is formed between the flat sealing surface 43 on the collar 39 and the flat valve seat 47 when the flat seat valve is open and can be connected via a relief channel 55 to a spring space 57 receiving the compression spring 27.
  • This relief channel 55 is formed by the remaining play between the wall of the bore 45 and the piston skirt 41 guided therein, the passage cross section of the relief channel 55 being so small that the fuel flowing through is throttled, and this throttling section 51 downstream also throttling can be done directly on the flat valve seat 47.
  • a second annular groove 59 on the valve member 23 which, together with the wall of a guide bore 63, forms an annular space 60 into which the high-pressure line 13 opens.
  • the second annular groove 59 which has the same diameter as the first annular groove 37, is delimited at its end facing away from the annular web 33 by a guide piston part 61 which is sealingly guided in the guide bore 63 and which, with its end face facing away from the annular groove 59, delimits a relief space 65 which is connected to the low-pressure chamber 5 via a return line 67.
  • a through bore 69 is provided in the valve member 23, which is cut by a transverse bore 71 in the region of the piston skirt 41 and via which the fuel can flow out of the relief channel 55 into the relief chamber 65.
  • the outer diameter of the collar 39 is of the same size as the diameter of the guide piston part 61.
  • the injection valve 15 arranged at right angles to the axis of the valve member 23 has, in a known manner, a piston-shaped valve member 79 acted upon in the closing direction by a valve spring 77, which projects with a pressure shoulder 81 into a pressure chamber 75, which via a pressure line 73 constantly communicates with the pressure chamber 49 on the control valve 17 is connected, the pressure in the pressure chamber 75 acting on the valve member 79 in the opening direction.
  • An injection channel 83 leads from the pressure chamber 75 along the valve member 79 to one or more injection openings 85 of the injection valve 15, which are controlled by the sealing surface at the tip of the valve member 79, into the combustion chamber, not shown, of the internal combustion engine to be supplied.
  • 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 annular space 60 of the individual control valves 17 on the injection valves 15 and also fills the respective pressure storage spaces 19.
  • the actuating magnet 29 on the control valve 17 is de-energized, so that the compression spring 27 holds the valve member 23 with the conical sealing surface 31 in contact with the conical valve seat 35, so that the connection between the annular space 60 under high fuel pressure and the pressure space 49 permanently connected to the pressure line 73 to the injection valve 15 is closed and the connection from the pressure space 49 is opened in the relief channel 55.
  • the actuating magnet 29 is energized and displaces the valve member 23 of the control valve 17 against the restoring force of the compression spring 27 until it rests with its flat valve sealing surface 43 on the flat valve seat 47.
  • the opening movement of the valve member 23 can be delayed when opening the connection from the high-pressure line 13 to the injection valve 15 through the cross section of the relief channel 55, via which the fuel located in the damping chamber 53 at the beginning of the opening movement flows out towards the relief chamber 65.
  • the actuating magnet 29 is again de-energized and the compression spring 27 brings the pressure-compensated valve member 23 of the control valve 17 back into contact with the conical valve seat 35.
  • the opening cross-section on the flat valve seat 47 is opened and the opening is high Pressure fuel relaxes from the pressure line 73 via the pressure chamber 49, the relief channel 55 and the transverse and longitudinal bores 71, 69 in Valve member 23 in the relief chamber 65, from where the fuel flows out via the return line 67 into the low pressure chamber 5.
  • the course of the pressure relief of the pressure line 73 or the injection valve 15 is determined by the degree of throttling at the throttle section 51, the passage cross section of which is at least so large that a rapid drop in the pressure below the closing pressure of the injection valve 15 and thus a reliable closing of the injection valve 15 is ensured.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (9)

  1. Installation d'injection de carburant pour des moteurs à combustion interne comprenant une pompe à carburant à haute pression (1) prenant le carburant d'une chambre basse pression (5) pour le transférer à une chambre collectrice à haute pression (9) cette dernière étant reliée par des conduites à haute pression (13) aux injecteurs (15) associés aux chambres de combustion du moteur, et le mouvement d'ouverture et de fermeture des injecteurs est commandé par une vanne de commande (17) à commande électrique, montée chaque fois dans la conduite à haute pression (13) sur l'injecteur (15), la vanne de commande (17) ayant un organe d'obturation (23) en forme de piton avec deux surfaces d'étanchéité de soupape, respectivement opposées,
    caractérisée en par
    une première surface d'étanchéité conique (31) prévue sur une entretoise annulaire (33) et coopérant avec un siège conique (35) ainsi qu'une seconde surface d'étanchéité plate (34) prévue sur une collerette (39) coopérant avec un siège d'étanchéité plat (47) entourant un perçage (45) ainsi qu'une chambre de pression (49), délimitée par le siège plat et le siège conique (47, 35), par l'entretoise annulaire (33) et la collerette (39), et dont la paroi au niveau de la collerette (39) présente un faible jeu par rapport à la surface périphérique pour former un moyen d'étranglement (51), et
    entre la surface d'étanchéité (43) de la collerette (39) et le siège de soupape plat (47) lorsque le siège de soupape plat est ouvert, il se forme une chambre d'amortissement (53) reliée par un canal d'évacuation (55) raccordé au siège plat (47), entre le perçage (45) et la tige de piston (41) du tiroir (23) guidée dans ce perçage, pour être reliée à la chambre de décharge (65).
  2. Installation d'injection de carburant selon la revendication 1,
    caractérisée par
    une rainure annulaire (37) prévue dans le tiroir (23) entre la collerette (39) et la nervure annulaire (33), le diamètre intérieur de cette rainure étant égal au diamètre d'une seconde rainure annulaire (59), adjacente à la surface conique (31) du tiroir (23), et cette rainure est délimitée à son extrémité opposée à la nervure annulaire (33) par une partie de guidage en forme de piston (61) du tiroir (23) qui est guidé de façon étanche dans un perçage de guidage (63).
  3. Installation d'injection de carburant selon la revendication 2,
    caractérisée en ce que
    le diamètre extérieur de la collerette (39) est égal au diamètre extérieur de la nervure annulaire (33).
  4. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce qu'
    une conduite de pression (73) relie la chambre de pression (49) à l'injecteur (15).
  5. Installation d'injection de carburant selon la revendication 2,
    caractérisée par
    un volume annulaire (60) formé entre le tiroir (23) et la paroi du perçage de guidage (63) au niveau de la seconde rainure annulaire (59) et dans lequel débouche la conduite à haute pression (13).
  6. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    le tiroir (23) comporte un perçage traversant (69), axial avec un perçage transversal (71) coupant celui-ci au niveau du canal d'évacuation (55) et reliant le canal d'évacuation (55) avec la chambre d'évacuation (65) délimitée par la partie de piston de guidage (61), chambre reliée par une conduite de retour (67) à la chambre basse pression (5).
  7. Installation d'injection de carburant selon la revendication 1,
    caractérisée par
    une chambre accumulatrice de pression (19) supplémentaire au niveau de chaque injecteur (15), dans la conduite de pression (13) entre la chambre collectrice à haute pression (9) et la vanne de commande (17).
  8. Installation d'injection de carburant selon la revendication 7,
    caractérisée en ce que
    la chambre accumulatrice de pression (19) est prévue dans le corps (21) de la vanne de commande (17).
  9. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    le tiroir (23) de la vanne de commande (17) est disposé à l'équerre par rapport à l'axe de l'organe d'obturation (79) de l'injecteur (15).
EP94113011A 1993-12-07 1994-08-20 Dispositif d'injection de combustible pour moteurs à combustion interne Expired - Lifetime EP0657643B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4341545A DE4341545A1 (de) 1993-12-07 1993-12-07 Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE4341545 1993-12-07

Publications (3)

Publication Number Publication Date
EP0657643A2 EP0657643A2 (fr) 1995-06-14
EP0657643A3 EP0657643A3 (fr) 1995-12-06
EP0657643B1 true EP0657643B1 (fr) 1999-01-13

Family

ID=6504296

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94113011A Expired - Lifetime EP0657643B1 (fr) 1993-12-07 1994-08-20 Dispositif d'injection de combustible pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US5524826A (fr)
EP (1) EP0657643B1 (fr)
JP (1) JP3502456B2 (fr)
DE (2) DE4341545A1 (fr)

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US5954487A (en) * 1995-06-23 1999-09-21 Diesel Technology Company Fuel pump control valve assembly
GB9600771D0 (en) * 1996-01-13 1996-03-20 Lucas Ind Plc Fuel pump
US5788154A (en) * 1996-05-02 1998-08-04 Caterpillar Inc. Method of preventing cavitation in a fuel injector having a solenoid actuated control valve
DE19706469A1 (de) * 1997-02-19 1998-08-27 Daimler Benz Ag Speichereinspritzsystem für eine mehrzylindrige Brennkraftmaschine mit magnetventilgesteuerten Kraftstoffeinspritzventilen
DE19734354A1 (de) * 1997-08-08 1999-02-11 Mtu Friedrichshafen Gmbh Kraftstoffeinspritzsystem für eine Brennkraftmaschine
US6276610B1 (en) * 1998-12-11 2001-08-21 Diesel Technology Company Control valve
US6158419A (en) * 1999-03-10 2000-12-12 Diesel Technology Company Control valve assembly for pumps and injectors
US6089470A (en) * 1999-03-10 2000-07-18 Diesel Technology Company Control valve assembly for pumps and injectors
DE19928906A1 (de) * 1999-06-24 2001-01-11 Bosch Gmbh Robert Common-Rail-Injektor
US6616064B2 (en) * 2000-06-29 2003-09-09 Robert Bosch Gmbh Injector with a control face on the outlet side
DE10031571A1 (de) * 2000-06-29 2002-01-17 Bosch Gmbh Robert Injektor mit zentralem Hochdruckanschluß
DE10036578A1 (de) * 2000-07-27 2002-02-07 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
DE10037388A1 (de) * 2000-08-01 2002-02-21 Bosch Gmbh Robert Ventilanordnung, insbesondere für ein Kraftstoffeinspritzsystem einer Verbrennungsmaschine
DE10040522A1 (de) * 2000-08-18 2002-02-28 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
JP2002168160A (ja) * 2000-12-01 2002-06-14 Mitsubishi Electric Corp 燃料噴射弁
DE10060811A1 (de) * 2000-12-07 2002-06-13 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
US6450778B1 (en) 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
DE10105031A1 (de) * 2001-02-05 2002-08-14 Bosch Gmbh Robert Vorrichtung zur Dämpfung von Druckpulsationen in Hochdruckeinspritzsystemen
DE10120804A1 (de) * 2001-04-27 2002-11-07 Bosch Gmbh Robert Injektor zum Einspritzen von Kraftstoff mit sequentiellem Aufbau
DE10201470A1 (de) * 2002-01-16 2003-08-07 Bosch Gmbh Robert Doppeltschaltendes Ventil für Kraftstoffeinspritzanlagen
WO2006072757A1 (fr) 2005-01-07 2006-07-13 Delphi Technologies, Inc. Appareil d’injection de carburant
US20060196974A1 (en) * 2005-03-01 2006-09-07 Caterpillar Inc. Fuel injector having a gradually restricted drain passageway

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JPH0264147A (ja) * 1988-08-30 1990-03-05 Idemitsu Petrochem Co Ltd 共重合ポリエステル組成物

Also Published As

Publication number Publication date
DE59407646D1 (de) 1999-02-25
JP3502456B2 (ja) 2004-03-02
US5524826A (en) 1996-06-11
DE4341545A1 (de) 1995-06-08
EP0657643A3 (fr) 1995-12-06
JPH07189850A (ja) 1995-07-28
EP0657643A2 (fr) 1995-06-14

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