EP0243931A2 - Dispositif d'injection de combustible pour un moteur à combustion interne - Google Patents

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

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Publication number
EP0243931A2
EP0243931A2 EP87106141A EP87106141A EP0243931A2 EP 0243931 A2 EP0243931 A2 EP 0243931A2 EP 87106141 A EP87106141 A EP 87106141A EP 87106141 A EP87106141 A EP 87106141A EP 0243931 A2 EP0243931 A2 EP 0243931A2
Authority
EP
European Patent Office
Prior art keywords
valve member
valve
fuel injection
injection device
bore
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
EP87106141A
Other languages
German (de)
English (en)
Other versions
EP0243931B1 (fr
EP0243931A3 (en
Inventor
Reda Rizk
Hans-Gottfried Michels
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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 Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to AT87106141T priority Critical patent/ATE63976T1/de
Publication of EP0243931A2 publication Critical patent/EP0243931A2/fr
Publication of EP0243931A3 publication Critical patent/EP0243931A3/de
Application granted granted Critical
Publication of EP0243931B1 publication Critical patent/EP0243931B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87265—Dividing into parallel flow paths with recombining
    • Y10T137/87378—Second valve assembly carried by first valve head
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87265—Dividing into parallel flow paths with recombining
    • Y10T137/87507—Electrical actuator

Definitions

  • the invention relates to a fuel injection device for an air-compressing internal combustion engine, in particular a diesel internal combustion engine according to the preamble of claim 1.
  • Fuel injection devices of this type have an electromagnetically actuated valve device between the injection pump and the injection nozzle in order to determine the start of delivery and the end of delivery of an injection cycle as a function of electrical control signals from a central control unit.
  • Such a fuel injection device is known from DE-OS 33 02 294.
  • a connecting channel which can be closed by the valve member is provided between the control channel and the high-pressure channel, the valve member being designed as a slide and having a shoulder which, together with a valve seat arranged in the housing, forms a seat valve.
  • the seat valve in the connection channel is closed during the injection process.
  • the end of the injection process is achieved by opening the connecting channel, for which purpose a prestressed firing pin accelerates the valve member with a high initial pulse, so that the seat valve is opened abruptly.
  • the start of delivery of an injection cycle is determined by the closing of the seat valve.
  • the valve member In order to achieve short switching times, the valve member is moved into its closed position with high acceleration, the impact energy present when the valve is seated on imperfect elastic materials being partly converted into heat and partly into potential energy ("suspension work” or "rebound”). Rebound movements in particular lead to an "oscillating closing" of the valve, so that the start of injection cannot be determined correctly.
  • a multi-cylinder pump due to production - different damping of the valve member due to uneven friction conditions in the individual guides and different closing forces due to spring preload tolerances occur. This leads to different rebound movements at the valve seat from element to element and thus to start of delivery scatter. This also results in different leaks in the closing process (loss of quantity) from element to element as well as an impairment of the equal conveyance of the elements.
  • the invention has for its object to develop the fuel injection device according to the preamble of claim 1 such that a precise control of the start of delivery is possible while achieving the smallest delivery angle.
  • the second connecting channel creates a further possibility of relieving the pressure from the high-pressure channel, the second connecting channel being controlled by a second valve member.
  • the start of delivery can be achieved by closing one connection channel and the end of delivery by opening the other connection channel.
  • a suitable valve device can be provided for the start or end of the conveyance, which is more adapted to the different requirements of the start or end of the ice spraying process.
  • the valve member controlling the second connecting channel is designed as a slide which advantageously controls the start of injection.
  • the second connection channel is suddenly closed
  • the spool can be provided with such a coverage area that a sufficient sealing effect (small amounts of leakage) is achieved.
  • the seat valve controlled by the first valve member is used, which ensures a sudden opening of the first connecting channel to the control channel at the end of the injection process.
  • Such a sudden opening at the end of the injection process is not possible with the slide valve without dead travel. Due to the larger overlap area - in order to achieve low leakage quantities - the spool must be moved a dead travel before the control edge releases control openings. This is not necessary with the poppet valve.
  • the seat valve for determining the end of delivery and the piston slide for determining the start of delivery are therefore advantageously used.
  • a structurally simple design with the smallest spatial dimensions is achieved in that the second connecting channel is arranged in the first valve member and the valve members lie coaxially one inside the other. In this way, the size of the valve can remain unchanged compared to that of the prior art according to DE-OS 33 02 294.
  • the fuel injection device shown in section in the drawing consists essentially of a housing 1 with a through bore 2, which serves to receive valve members 3, 6.
  • the bore 2 is crossed by a high-pressure duct 7, which supplies the fuel delivered by a high-pressure fuel pump in the direction of the arrow 8 through a pressure-maintaining valve 9 and an injection line 10 to an injection nozzle 11.
  • a control duct 12 opens into the bore 2, from which fuel can be discharged in the direction of the arrow 13.
  • the control channel 12 opens into the bore 2 via an annular space 14, which is provided as a circumferential groove in the wall of the bore 2.
  • annular space 14 which is provided as a circumferential groove in the wall of the bore 2.
  • the entry and exit of the high-pressure channel 7 into the bore 2 is designed as a common annular space 15, which is also provided as a circumferential groove in the wall of the bore 2.
  • the bore 2 essentially consists of two sections of different diameters, the annular space 15 being arranged in the section of the larger diameter and the annular space 14 in the section of the smaller diameter.
  • a valve seat 5 is formed, which faces the section with a larger diameter.
  • a piston valve is arranged in the bore 2 as the first valve member 3, this valve member - corresponding to the bore 2 - also having two sections of different diameters.
  • the shoulder 4 resulting from the jump in diameter is designed as a valve member assigned to the valve seat 5;
  • the first valve member 3 rests on the valve seat 5 in a pressure-tight manner and blocks the first connecting channel 16, which connects the high-pressure channel 7 to the control channel 12 and is formed by the bore 2 in the housing 1.
  • the first valve member 3 has an axially continuous bore 20, which correspond to radially extending transverse bores 21 and 22.
  • the transverse bores 21 and 22 lie - in the closed position of the valve member 3 - in the area of the annular spaces 14 and 15.
  • the transverse bore 22 assigned to the annular space 14 lies approximately in the middle of the annular space 14.
  • a second valve member 6 - designed as a spool - is axially displaceably guided.
  • the piston slide 6 has in its outer jacket a circumferential groove 23, the axial width of which corresponds at least to the distance between the transverse bores 21 and 22 in the first valve member 3.
  • the width of the circumferential groove 23 is preferably provided such that in one position of the second valve member 6 both transverse bores 21 and 22 open into the circumferential groove 23 over their full passage cross section. This position of the second valve member 6 denotes its open position.
  • the edge of an axial end face of the circumferential groove 23 closest to the cross bores 21 forms the control edge 24 of the second valve member 6. In the position shown, this control edge lies between the cross bores 21 and 22, so that the fluid flow through the through the cross bores 21 and 22 and the bore 20 or the circumferential groove 23 formed second connection channel between the high pressure channel 7 and the control channel 12 is interrupted.
  • An electromagnetic actuating device 30 or 31 is arranged on both ends of the bore 2 in the housing 1, each having a movable armature 32 or 33.
  • the electromagnetic actuating devices 30 and 31 are attached to the housing 1 with the interposition of sealing rings or similar sealing arrangements at both ends of the bore 2.
  • the electromagnetic actuating device 30 has an intermediate flange 34 which is fixed on the housing 1.
  • the intermediate flange 34 is of two-stage diameter, the smaller-diameter section 36 corresponding to the diameter of the armature 32 and, together with a pole core 37, serving as a carrier for the winding 35 of the electromagnetic actuating device 30.
  • the actuation path x of the armature 32 is limited on the one hand by the pole core 37 and on the other hand by the end face of the section 36 facing the armature.
  • the armature 32 is coaxial with the valve members 3 and 6 and is axially fixed to the second valve member 6 via a rod-shaped connecting member 17.
  • a head 27 of the connecting member 17 takes the armature 32 in the direction of arrow 26.
  • Coil springs are arranged between the valve members 3 and 6 and the intermediate flange 34, which force the valve members in the direction of their closed positions.
  • the equally long coil springs 18 and 19 lie coaxially to the connecting member 17 on one side in a cylindrical recess of the intermediate flange 34 and on the other side against the valve members 3 and 6.
  • the helical spring 19 rests on the free end face of the second valve member 6 facing it, the outer diameter of the helical spring 19 being slightly smaller than the outer diameter of the second valve member 6.
  • the helical spring 18 assigned to the first valve member 3 lies in the valve member 3 at a step which is formed by widening the axial bore 20.
  • the inside diameter of the helical spring 18 corresponds approximately to the inside diameter of the bore 20.
  • the helical spring 18 which is supported on the intermediate flange fixed to the housing presses the first valve member 3 with its shoulder 4 sealingly onto the valve seat 5, so that the first connecting channel 16 is closed.
  • the spring 19 like the helical spring 18 - also acts in the direction of arrow 26 and holds the second valve member 6 in its closed position. Due to the force of the spring 19, the second valve member 6 is displaced in the direction of the arrow 26 and takes the armature 32 with it via the connecting member 17 or its head 27 until it strikes the section 36 of the intermediate flange 34. In this closed position, the control edge 24 of the second valve member 6 lies between the transverse bores 21 and 22, so that the second connecting channel 25 is closed by the second valve member 6.
  • the second actuating device 31 arranged on the opposite end of the bore 2 likewise has an intermediate formed in two stages in diameter flange 28, the portion 27 of smaller diameter together with the pole core 29 in turn serves as a carrier for the winding 38 of the electromagnetic actuating device 31.
  • the stroke y of the armature 33 is determined on the one hand by the pole core 29 and on the other hand by the end face of the section 27 of the intermediate flange 28 facing the armature.
  • the armature 33 is fixedly connected to a firing pin 40 which passes axially through the intermediate flange 28 and has an enlarged head 41 which is located in the enlarged end of the bore 2 opposite the free end face of the first valve member 3.
  • the firing pin 40 like the armature 33, is coaxial with the valve members 3 and 6.
  • the outer diameter of the firing pin 41 is slightly smaller than the diameter of the bore 2, so that it can dip into the bore 2.
  • the actuating device 31 magnetized in the exemplary embodiment shown holds the armature 33 on the pole core 29, as a result of which a spring 43, which is supported between the bottom of a cylindrical recess in the intermediate flange 28 and the head 41 of the firing pin 40, is tensioned.
  • the end face of the head 41 facing the first valve member 3 lies at a distance z from the end face of the first valve member 3; the distance z is smaller than the stroke y of the electromagnetic actuation device.
  • the mode of operation of the fuel injection device according to the invention is as follows:
  • the electromagnetic actuation device 31 has current flowing through it the electromagnetic actuator 30 is de-energized.
  • the firing pin 40 is displaced by the stroke y in the direction of arrow 26 against the force of the spring 43 and lies opposite the end face of the first valve member 3 at a distance z.
  • the first valve member 3 is held by the spring 18 with its shoulder 4 in contact with the valve seat 5 and blocks the first connecting channel 16.
  • the spring 19 moves the second valve member 6 in the direction of the arrow 26 until the armature 32 abuts the section 36 of the intermediate flange 34; in this position, the control edge 24 lies between the transverse bores 21 and 22, so that the second connecting channel 25 is also closed.
  • both connecting channels 16 and 25 are closed to the control channel 12, the amount of fuel delivered in the direction of arrow 8 into the high-pressure channel 7 is delivered via the pressure-maintaining valve 9 screwed into the housing 1 and the injection line 10 to the fuel injection nozzle 11, which feeds the fuel into the combustion chamber (not shown) Injecting internal combustion engine.
  • the excitation current of the electromagnetic actuating device 31 is switched off, so that the armature 31 drops off and the spring 43 accelerates the firing pin 40 together with the armature 33 in the direction of the first valve member 3.
  • the head 41 hits the first valve member 3 and accelerates it suddenly in the opposite direction of the arrow 26, as a result of which the first connecting channel 16 is opened abruptly.
  • the one under high pressure under high pressure Channel 7 fuel is suddenly relieved via the first connecting channel 16 opening into the control channel 12, as a result of which the end of injection is determined.
  • the actuating device 3 is switched on again. As a result, the firing pin 40 is returned to its starting position and the first valve member 3, under the action of the coil spring 18, closes the first connecting channel. If one assumes a state which corresponds to the pumping process of the pump in the region of the idle stroke, the valve member 6 is held in the open position by excitation of the actuating device 30. The armature 32 bears against the pole core 37. The valve member 6 is moved against the force of the coil spring 19 against the direction of arrow 26.
  • the circumferential groove 23 in the second valve member 6 connects the transverse bores 21 and 22 to one another, so that the second connecting channel 25 is open and the fuel delivered under high pressure into the channel 7 via the second connecting channel 25 Discharge line 12 can be discharged.
  • the current through the winding 35 of the electromagnetic actuating device 30 is switched off, so that the armature 32 falls off the pole core 37 and travels through the stroke x under the action of the coil spring 19.
  • the control edge 24 passes over the cross bores 21 and blocks the second connecting channel 25 abruptly, so that the fuel in the high-pressure channel 7 is supplied to the injection nozzle 11 via the pressure holding valve 9 and the injection line 10.
  • the current through the winding 38 is again switched off, whereupon the firing pin 40 moves the first valve member 3 and opens the first connecting channel 16 abruptly.
  • all parts of the arrangement are provided with axially continuous bores except for the pole core 29.
  • the axial bore in the pole core 37 serves as an unpressurized drain port.

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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)
EP19870106141 1986-04-29 1987-04-28 Dispositif d'injection de combustible pour un moteur à combustion interne Expired - Lifetime EP0243931B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87106141T ATE63976T1 (de) 1986-04-29 1987-04-28 Kraftstoffeinspritzvorrichtung fuer eine brennkraftmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863614495 DE3614495A1 (de) 1986-04-29 1986-04-29 Kraftstoffeinspritzvorrichtung fuer eine brennkraftmaschine
DE3614495 1986-04-29

Publications (3)

Publication Number Publication Date
EP0243931A2 true EP0243931A2 (fr) 1987-11-04
EP0243931A3 EP0243931A3 (en) 1989-10-18
EP0243931B1 EP0243931B1 (fr) 1991-05-29

Family

ID=6299787

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870106141 Expired - Lifetime EP0243931B1 (fr) 1986-04-29 1987-04-28 Dispositif d'injection de combustible pour un moteur à combustion interne

Country Status (6)

Country Link
US (1) US4785787A (fr)
EP (1) EP0243931B1 (fr)
JP (1) JPS6325364A (fr)
AT (1) ATE63976T1 (fr)
DE (2) DE3614495A1 (fr)
SU (1) SU1494876A3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2224786A (en) * 1988-09-21 1990-05-16 Toyota Motor Co Ltd A fuel injection device

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3910793C2 (de) * 1989-04-04 1996-05-23 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzvorrichtung
DE4322546A1 (de) * 1993-07-07 1995-01-12 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US6308690B1 (en) * 1994-04-05 2001-10-30 Sturman Industries, Inc. Hydraulically controllable camless valve system adapted for an internal combustion engine
US6161770A (en) 1994-06-06 2000-12-19 Sturman; Oded E. Hydraulically driven springless fuel injector
US6257499B1 (en) 1994-06-06 2001-07-10 Oded E. Sturman High speed fuel injector
US5479901A (en) * 1994-06-27 1996-01-02 Caterpillar Inc. Electro-hydraulic spool control valve assembly adapted for a fuel injector
DE4425295A1 (de) * 1994-07-18 1996-01-25 Bosch Gmbh Robert Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine
US5720261A (en) * 1994-12-01 1998-02-24 Oded E. Sturman Valve controller systems and methods and fuel injection systems utilizing the same
US6148778A (en) 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
US5709342A (en) * 1995-11-09 1998-01-20 Caterpillar Inc. Vented armature/valve assembly and fuel injector utilizing same
DE19641952C5 (de) * 1996-10-11 2005-06-02 Daimlerchrysler Ag Kraftstofführung für eine mehrzylindrige Brennkraftmaschine mit Aufnahmebohrungen für Steckpumpen
US6167869B1 (en) * 1997-11-03 2001-01-02 Caterpillar Inc. Fuel injector utilizing a multiple current level solenoid
US6085991A (en) 1998-05-14 2000-07-11 Sturman; Oded E. Intensified fuel injector having a lateral drain passage
US6116209A (en) * 1998-05-27 2000-09-12 Diesel Technology Company Method of utilization of valve bounce in a solenoid valve controlled fuel injection system
US5924407A (en) * 1998-07-29 1999-07-20 Navistar International Transportation Corp. Commanded, rail-pressure-based, variable injector boost current duration
DE19908102C1 (de) * 1999-02-25 2000-05-04 Daimler Chrysler Ag Ventil mit variablem Ventilquerschnitt
DE10046040A1 (de) * 2000-09-18 2002-04-04 Bosch Gmbh Robert Einrichtung zur Verbesserung der Reproduzierbarkeit der Einspritzdauer an Einspritzsystemen
DE10054202A1 (de) * 2000-11-02 2002-05-29 Siemens Ag Injektor zum Einspritzen von Kraftstoff in einen Brennraum
KR100590688B1 (ko) 2006-03-24 2006-06-19 재단법인 한국조선기자재연구원 고온고압 벙커씨유의 급속개폐제어밸브.

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1462158A (fr) * 1961-11-20 1966-04-15 Perfectionnements aux dispositifs d'injection de combustible dans les moteurs à combustion
CH444604A (de) * 1965-12-16 1967-09-30 Karl Marx Stadt Ind Werke Elektrohydraulisches Regelventil
FR2188065A1 (fr) * 1972-06-08 1974-01-18 Bendix Corp
US3851635A (en) * 1969-05-14 1974-12-03 F Murtin Electronically controlled fuel-supply system for compression-ignition engine
EP0089301A1 (fr) * 1982-03-16 1983-09-21 RENAULT VEHICULES INDUSTRIELS Société dite: Système pour la commande de l'injection sur un moteur diesel
FR2530734A1 (fr) * 1982-07-22 1984-01-27 Renault Vehicules Ind Dispositif pour l'injection electronique du combustible d'un moteur a combustion interne

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CH178320A (fr) * 1933-07-12 1935-07-15 Atlas Diesel Ab Dispositif pour l'alimentation en combustible d'un moteur à combustion interne.
DE1917927A1 (de) * 1969-04-09 1970-10-29 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen
FR2230526B1 (fr) * 1973-05-24 1976-04-23 Ferodo Sa
CH635167A5 (de) * 1979-01-25 1983-03-15 Sulzer Ag Einspritzeinrichtung eines dieselmotorzylinders.
WO1981000283A1 (fr) * 1979-07-16 1981-02-05 Caterpillar Tractor Co Appareil d'injection de combustible commande electriquement
US4418670A (en) * 1980-10-10 1983-12-06 Lucas Industries Limited Fuel injection pumping apparatus
DE3302294A1 (de) * 1983-01-25 1984-07-26 Klöckner-Humboldt-Deutz AG, 5000 Köln Kraftstoffeinspritzvorrichtung fuer luftverdichtende, selbstzuendende brennkraftmaschinen
US4505243A (en) * 1983-07-04 1985-03-19 Nissan Motor Company, Limited Electromagnetic injection control valve in unit fuel injector
US4644968A (en) * 1983-08-29 1987-02-24 J. I. Case Company Master clutch pressure and lubrication valve
US4674536A (en) * 1986-04-25 1987-06-23 Sealed Power Corporation Electrohydraulic valves for use in a system
US6226650B1 (en) * 1998-09-17 2001-05-01 Synchrologic, Inc. Database synchronization and organization system and method

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1462158A (fr) * 1961-11-20 1966-04-15 Perfectionnements aux dispositifs d'injection de combustible dans les moteurs à combustion
CH444604A (de) * 1965-12-16 1967-09-30 Karl Marx Stadt Ind Werke Elektrohydraulisches Regelventil
US3851635A (en) * 1969-05-14 1974-12-03 F Murtin Electronically controlled fuel-supply system for compression-ignition engine
FR2188065A1 (fr) * 1972-06-08 1974-01-18 Bendix Corp
EP0089301A1 (fr) * 1982-03-16 1983-09-21 RENAULT VEHICULES INDUSTRIELS Société dite: Système pour la commande de l'injection sur un moteur diesel
FR2530734A1 (fr) * 1982-07-22 1984-01-27 Renault Vehicules Ind Dispositif pour l'injection electronique du combustible d'un moteur a combustion interne

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2224786A (en) * 1988-09-21 1990-05-16 Toyota Motor Co Ltd A fuel injection device
US5076241A (en) * 1988-09-21 1991-12-31 Toyota Jidosha Kabushiki Kaisha Fuel injection device
GB2224786B (en) * 1988-09-21 1992-09-23 Toyota Motor Co Ltd A fuel injection device

Also Published As

Publication number Publication date
JPS6325364A (ja) 1988-02-02
EP0243931B1 (fr) 1991-05-29
DE3770331D1 (de) 1991-07-04
DE3614495A1 (de) 1987-11-05
EP0243931A3 (en) 1989-10-18
SU1494876A3 (ru) 1989-07-15
US4785787A (en) 1988-11-22
ATE63976T1 (de) 1991-06-15

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