EP0657643A2 - 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
EP0657643A2
EP0657643A2 EP94113011A EP94113011A EP0657643A2 EP 0657643 A2 EP0657643 A2 EP 0657643A2 EP 94113011 A EP94113011 A EP 94113011A EP 94113011 A EP94113011 A EP 94113011A EP 0657643 A2 EP0657643 A2 EP 0657643A2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
injection
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.)
Granted
Application number
EP94113011A
Other languages
German (de)
English (en)
Other versions
EP0657643B1 (fr
EP0657643A3 (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 is based on a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • a high-pressure fuel pump delivers fuel from a low-pressure chamber into a high-pressure collection chamber, which is connected via high-pressure lines to the individual injection valves projecting into the combustion chamber of the internal combustion engine to be supplied, this common pressure storage system being kept at a certain pressure by a pressure control device.
  • an electrically controlled control valve is inserted into the high-pressure lines, which controls the opening and closing of the high-pressure fuel injection at the injection valve.
  • the control valves on the injection valves are designed as solenoid valves, which open the connection of the high-pressure line to the injection valve at the start of injection and close it again at the end of injection.
  • control valves on the known fuel injection devices have the disadvantage that they are on Immediately release the entire opening cross-section at the start of the injection, so that a large amount of fuel reaches the combustion chamber of the internal combustion engine to be supplied at the start of the injection, which leads in a known manner to high pressure peaks at the start of the combustion.
  • 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 control 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.
  • 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.
  • 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.
  • a further advantage is achieved by arranging an additional pressure storage space on each injection valve, the design of which allows the injection course to be shaped during the injection process.
  • 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 with one conical valve seat 35 cooperates.
  • a 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 at its end facing away from the annular web 33 limited 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 chamber 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 through 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 closed injection valve 15, the solenoid 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 high-pressure fuel chamber 60 and the constantly with the Pressure line 73 to the injection valve 15 connected pressure chamber 49 is closed and the connection from the pressure chamber 49 into the relief channel 55 is opened.
  • 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 connection of the pressure chamber 49 to the relief channel 55 closed and turned on to the pressure line 73, so that the high fuel pressure now continues from the annular space 60 via the pressure space 49 and the pressure line 73 to the pressure space 75 of the injection valve 15 and there by lifting the valve member 79 from its valve seat in a known manner the injection at the injection openings 85 takes place.
  • 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.

Landscapes

  • 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)
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 true EP0657643A2 (fr) 1995-06-14
EP0657643A3 EP0657643A3 (fr) 1995-12-06
EP0657643B1 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)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10031571A1 (de) * 2000-06-29 2002-01-17 Bosch Gmbh Robert Injektor mit zentralem Hochdruckanschluß
EP1176306A2 (fr) * 2000-07-27 2002-01-30 Robert Bosch Gmbh Système d'injection de combustible pour moteurs à combustion interne
DE10120804A1 (de) * 2001-04-27 2002-11-07 Bosch Gmbh Robert Injektor zum Einspritzen von Kraftstoff mit sequentiellem Aufbau
WO2006072757A1 (fr) 2005-01-07 2006-07-13 Delphi Technologies, Inc. Appareil d’injection de carburant

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
DE10201470A1 (de) * 2002-01-16 2003-08-07 Bosch Gmbh Robert Doppeltschaltendes Ventil für Kraftstoffeinspritzanlagen
US20060196974A1 (en) * 2005-03-01 2006-09-07 Caterpillar Inc. Fuel injector having a gradually restricted drain passageway

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2336575A1 (de) * 1971-07-08 1975-02-06 Peugeot Betaetigungsvorrichtung fuer eine einspritzduese von kolbenbrennkraftmaschinen
US4129254A (en) * 1977-09-12 1978-12-12 General Motors Corporation Electromagnetic unit fuel injector
FR2449795A1 (fr) * 1979-02-24 1980-09-19 Huber Motorenbau Inst Systeme d'injection pour moteur a combustion interne

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1004217A (fr) * 1947-03-20 1952-03-27 Genevet & Cie Perfectionnements apportés aux brûleurs à mazout
AU444015B2 (en) * 1968-11-15 1973-12-19 Pritchard Edward Improvements in or relating to pressure jet burner control systems
US4572433A (en) * 1984-08-20 1986-02-25 General Motors Corporation Electromagnetic unit fuel injector
US4605166A (en) * 1985-02-21 1986-08-12 Stanadyne, Inc. Accumulator injector
JPH0264147A (ja) * 1988-08-30 1990-03-05 Idemitsu Petrochem Co Ltd 共重合ポリエステル組成物

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2336575A1 (de) * 1971-07-08 1975-02-06 Peugeot Betaetigungsvorrichtung fuer eine einspritzduese von kolbenbrennkraftmaschinen
US4129254A (en) * 1977-09-12 1978-12-12 General Motors Corporation Electromagnetic unit fuel injector
FR2449795A1 (fr) * 1979-02-24 1980-09-19 Huber Motorenbau Inst Systeme d'injection pour moteur a combustion interne

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10031571A1 (de) * 2000-06-29 2002-01-17 Bosch Gmbh Robert Injektor mit zentralem Hochdruckanschluß
EP1176306A2 (fr) * 2000-07-27 2002-01-30 Robert Bosch Gmbh Système d'injection de combustible pour moteurs à combustion interne
EP1176306A3 (fr) * 2000-07-27 2003-03-05 Robert Bosch Gmbh Système d'injection de combustible pour moteurs à combustion interne
DE10120804A1 (de) * 2001-04-27 2002-11-07 Bosch Gmbh Robert Injektor zum Einspritzen von Kraftstoff mit sequentiellem Aufbau
WO2006072757A1 (fr) 2005-01-07 2006-07-13 Delphi Technologies, Inc. Appareil d’injection de carburant

Also Published As

Publication number Publication date
DE59407646D1 (de) 1999-02-25
JP3502456B2 (ja) 2004-03-02
JPH07189850A (ja) 1995-07-28
DE4341545A1 (de) 1995-06-08
EP0657643B1 (fr) 1999-01-13
EP0657643A3 (fr) 1995-12-06
US5524826A (en) 1996-06-11

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