EP0281580A1 - Dispositif d'injection de carburant pour un moteur diesel. - Google Patents

Dispositif d'injection de carburant pour un moteur diesel.

Info

Publication number
EP0281580A1
EP0281580A1 EP87905420A EP87905420A EP0281580A1 EP 0281580 A1 EP0281580 A1 EP 0281580A1 EP 87905420 A EP87905420 A EP 87905420A EP 87905420 A EP87905420 A EP 87905420A EP 0281580 A1 EP0281580 A1 EP 0281580A1
Authority
EP
European Patent Office
Prior art keywords
piston
fuel
pump
control
line
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
EP87905420A
Other languages
German (de)
English (en)
Other versions
EP0281580B1 (fr
Inventor
Peter Fuchs
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.)
MAN B&W Diesel AS
Original Assignee
Nova Werke 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 Nova Werke AG filed Critical Nova Werke AG
Priority to AT87905420T priority Critical patent/ATE63614T1/de
Publication of EP0281580A1 publication Critical patent/EP0281580A1/fr
Application granted granted Critical
Publication of EP0281580B1 publication Critical patent/EP0281580B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • 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
    • 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
    • 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 a diesel internal combustion engine, in each of which an injection nozzle is connected to a fuel pump via a pressure line, the fuel umpe a cylinder with at least one fuel line for the inflow and outflow of fuel and a pump chamber and a Has a pump piston, and the pump piston is connected to and driven by an axial piston unit acted upon by a pressure medium.
  • a large number of fuel injection devices for diesel internal combustion engines are known, and in most of these devices the pump piston is driven by a camshaft.
  • a fuel injection device is known from Swiss Patent No. 539 778, in which the pump pistons are driven by means of an axial piston unit acted upon by a pressure medium.
  • This device comprises a feed pump for the fuel, which is part of a line system for supplying fuel to one or more fuel nozzles.
  • the feed pump is connected to a fuel accumulator and a pressure regulating valve which regulates the feed pressure in the fuel line system.
  • the fuel is fed from the feed pump to an electromagnetically actuated hydraulic valve, then to a slide valve and then to a servo piston and the injection nozzle.
  • the solenoid valve is with a Electrical control unit connected, which outputs control signals for the start and end of the injection to the solenoid valve.
  • the slide valve connected to the solenoid valve has two control edges which control the inflow of fuel to the piston surface of the servo piston.
  • the slide of the slide valve is acted upon by fuel with the pressure of the feed pump on the one hand, and on the other hand with a spring force which is less than the " force generated by the feed pressure of the pump.
  • the servo piston is directly with the pump piston of the injection pump The amount of fuel flowing into the pump space is determined by the pressure prevailing at the feed pump and a throttle arranged in the line.
  • the solenoid valve is brought into a position by a control signal in which the slide valve is pressurized by the feed pump and thereby the slide of the slide valve releases passage from the fuel line to the working surface of the servo piston.
  • the servo piston, and thus the pump piston is set in motion and the injection process is started.
  • a second signal is sent to the solenoid valve via the electrical control device, as a result of which it assumes a different switching position and relieves the slide valve of fuel pressure from the feed pump.
  • the slide of the slide valve is moved by the spring force and releases a passage that connects the working surface of the servo piston with a pressure-free return line of the fuel system.
  • the injection stroke is interrupted and the pump piston, and thus the servo piston, is pushed back by the delivery pressure in the fuel system.
  • the return path of the servo piston is determined by the amount of fuel flowing in, which in turn is determined by the throttle arranged in the inlet.
  • Fuel injectors of the type described enable relatively small solenoid valves to be used by installing the slide valve. However, they have the disadvantage that the exact metering of the injection quantity is associated with difficulties. " The electrical control and the entire fuel system have to be coordinated very precisely so that the fuel can be fed into the combustion chamber in the right quantity and at the right time, especially in the case of fast running diesel engines
  • the invention is based on the object of avoiding the disadvantages mentioned and of creating a fuel injection device with a pump piston driven by a pressure medium, which can be operated both with fast and long sam running diesel engines and can be used for all types of fuels, in which the amount of fuel injected is determined volumetrically and not volumetrically, and which also has an emergency running device if the electrical part fails.
  • the pump piston is provided with at least one control edge connected to the pump chamber and can be rotated about its longitudinal axis
  • the axial piston unit is connected via a hydraulic system to a pressure source that is independent of the fuel system, and in this hydraulic system between the pressure source and the axial piston unit a mechanically and / or electrically switchable control device with at least one main slide is arranged
  • the control device has at least one return piston connected to the pump chamber via a connecting line and acted upon by fuel, and at least one in the fuel lines connected to the pump chamber further control device is arranged and connected to the pump chamber via lines.
  • the principle of the pump piston provided with control edges is connected to a drive unit which has a drive piston acted upon by a pressure medium.
  • the fuel system of the fuel pump and the pressure medium system of the axial piston unit are mutually independent systems which are linked to one another via a control device.
  • the control device can be switched mechanically and / or electrically and also has a return piston which is connected to the pump chamber and is acted upon by fuel. With the control edge on the pump piston, this connecting line from the pump chamber to the return piston of the control device has a direct influence on the pressure medium system by the fuel system.
  • the control device is acted upon by fuel under high pressure at a desired point in time and the pressure medium system of the axial piston unit is controlled. This arrangement ensures that the injection process is terminated as soon as the pump piston has covered a desired distance, and thus a precisely determined volume of fuel has been expelled.
  • the main slide of the control device has control spaces and control edges for opening and closing the pressure medium lines to the axial piston, and this main slide acts at one end with a push rod and at the other end with the fuel-loaded and connected to the pump chamber. a reset piston. At least part of the
  • Push rod forms the core of a magnet coil, and this magnet coil is connected to an electrical pulse generator. Furthermore, the push rod is part of a mechanical locking device, and this locking device fixes the push rod and the control edges of the main slide in a control position.
  • a preferred embodiment of the invention is characterized in that the control device in the hydraulic system is connected to a control camshaft and the cam disc acts on the push rod of the control device.
  • a low mass camshaft can be used because it only moves the controls. This is in contrast to injectors, in which the camshaft drives the pump pistons, and which require a heavy and complex construction.
  • the control camshaft acts directly on the push rod of the main slide and serves as an actuator for the main slide or as an emergency control in the event of a failure of the solenoid.
  • the axial piston is double-acting and the pressure medium supply line to the working space with the fully loaded piston surface is over the control device leads to the pressure source and the pressure medium supply line to the annular space with the annular surface of the piston directly to the pressure source.
  • a further improvement of the fuel injection device can be achieved in that the upper end face of the pump piston forms a first control edge, in the direction of the longitudinal axis on the jacket of the pump piston a channel running obliquely to the longitudinal axis is arranged with a second control edge and is connected to the pump chamber via a channel, and at least one passage for fuel is arranged in the pump cylinder, which is located at the bottom dead center of the pump piston above the first control edge and at top dead center of the pump piston below the second control edge.
  • the passage into the fuel line with the control edges forms the second control device and is connected via the connecting line to the reset piston of the control device of the hydraulic system.
  • An improved embodiment of the second control device is characterized in that this second control device in the fuel line consists of an overflow / suction valve and a switching piston acting on the valve stem of the overflow / suction valve, the overflow / suction valve via a feed line is connected to the upper end of the pump chamber and the piston chamber of the switching piston is connected via a line to the passage in the pump cylinder.
  • the passage in the 0 pump cylinder can be dimensioned so that it is optimally matched to its control function.
  • the inflow and outflow of fuel into the pump chamber takes place via the feed line at the upper end of the pump chamber, their dimensions and the dimensions of the overflow / suction valve 5 also being optimally dimensioned for these inflow and outflow processes.
  • the pump piston When the fuel injection device according to the invention is operated, the pump piston is brought into a position, depending on the engine output, by means of a control device known per se, in which the control edges effect the injection of the desired amount of fuel.
  • the start of the injection process is effected via the control device in the pressure medium system by means of an electrical pulse via the magnet coil or by means of the control camshaft.
  • the control device releases the pressure medium inflow to the axial piston unit and this moves the pump piston, the fuel being pressurized in the pump chamber.
  • the inflow valve to the injection nozzle opens and the fuel is introduced into the diesel engine.
  • the pump chamber is coupled to the control device via the connecting line, and the pressure surge causes the main slide to be reset via the reset piston, thereby blocking the supply of pressure medium to the fully loaded piston surface of the axial piston unit.
  • the annular surface continues to be acted upon and brings about an immediate retraction of the axial piston and an immediate reduction in pressure in the pump chamber.
  • connection of the bevel edge control on the pump piston with a pressure unit acted upon by pressure medium results in a very high level of operational reliability and constructive independence.
  • a major advantage of this fuel injection device is that all components are arranged axially to one another that can, and if several injection devices are arranged, each is independent of the other.
  • the heavy and complex drive camshafts are completely eliminated, which is particularly important in the case of large and fast-running diesel engines. Nevertheless, the emergency control via the camshaft control with a light camshaft is guaranteed.
  • FIG. 1 shows a schematic representation of a section through a fuel pump with drive unit, main slide and pressure medium system
  • FIG. 2 shows a schematic representation of a section through the fuel pump with the second control device in the fuel system
  • FIG. 3 shows the control device of the pressure medium system in longitudinal section with the main slide valve. Locking device and camshaft control
  • FIG. 1 shows a fuel injection device with an injection nozzle 1, a fuel pump 3, an axial piston unit 20 and a control device 31.
  • the fuel pump 3 consists of a pump cylinder 4 with a pump chamber 6, in which a pump piston 7 is guided.
  • the pump cylinder 4 is provided with a fuel line, which consists of a supply line 15, a fuel channel 5 and a discharge line 16. These fuel lines are part of a fuel system in which the fuel is conveyed by a feed pump at a relatively low pressure.
  • a check valve 17 is installed in the fuel feed line 15, which prevents fuel from flowing back into the feed line 15 and pressure surges occurring in the fuel channel 5 are transmitted to the fuel feed line 15.
  • a throttle 18 is installed in the fuel discharge line 16 to reduce pressure surges.
  • Pump chamber 6 leads a pressure line 2 to the injection nozzle 1.
  • a control valve 19 is switched on, which releases the flow to the injection nozzle 1 when a certain pressure in the pump chamber 6 is reached and, when the pressure drops, the pressure line 2 is switched off again. closes.
  • the pump piston 7 is connected at its lower end to the axial piston 22 of the axial piston unit 20.
  • the pump piston 7 is not only displaceable in the axial direction, but can be rotated about the longitudinal axis 8 by means of an adjusting device 60.
  • the adjusting device 60 is a device known for fuel injection pumps with inclined edge controls.
  • the axial piston unit 20 consists of a cylinder 21, the
  • the axial piston 22 is double-acting and has a piston surface 23 directed towards the working space 25, which is opposite an annular surface 24 assigned to the annular space 26.
  • the axial piston unit 20 is part of a pressure medium system in which any known pressure medium can be used. In the present example high pressure hydraulic oil is used.
  • the pressure medium is supplied to the axial piston unit 20 via the pressure medium lines 27, 28, which are fed by a pressure source 29.
  • a control device 31 is installed between the pressure source 29 and the pressure medium line 27.
  • the control device 31 comprises a main slide 32, a return piston 34, a magnetic coil 38 with an associated magnetic core 39, a mechanical locking device 41 and a camshaft control 61.
  • the hydraulic fluid-containing system is separated from the fuel system, and the working movements of the axial piston 22 are achieved by the main slide 32 controlled.
  • This main slide 32 is shown in more detail in FIG. 3 and has two slide bodies 62, 63 with control edges 64, 65.
  • the slide body 62 is a Control room 66, and a control room 67 assigned to the slide body 63.
  • a third control chamber 68 is located in between.
  • Pressure relief chambers 69, 70 and sealing pistons 71, 72 are arranged behind each of the slide bodies 62 and 63, the pressure relief chambers 69, 70 being connected to a leak line 88.
  • the slider body 62, 63 and the sealing piston 71, 72 are arranged at the correct distance from one another by means of a core 73 and are connected to one another.
  • At one end of the main slide 32 there is a push rod 37 which is connected to the slide body 63, part of the push rod 37 forming the core 39 of the solenoid 38.
  • the push rod 37 extends beyond the magnetic coil 38 and is enclosed by the mechanical locking device 41.
  • the camshaft control 61 is connected to this mechanical locking device 41.
  • the return piston 34 interacts with the slide body 62 via a pin 74.
  • a piston chamber 75 belonging to the resetting piston 34 is connected to the fuel system via a connecting line 33.
  • this connecting line 33 is introduced into a passage 14 in the pump cylinder 4, which leads into the pump chamber 6.
  • the pressure medium system is operated by means of the pressure source 29, a pressure control valve 30 being provided for controlling the pressure in this system.
  • a pressure line 35 leads from the pressure source 29 to the main slide 32 and a further pressure medium line 28 leads to the annular space 26 of the axial piston unit 20.
  • a return line 36 leads from the main slide 32 to a pressure medium container 76.
  • the slide body 62 releases the connection between the control chamber 66 and the control chamber 68, and on the other hand the slide body 63 closes the connection between the control chamber 68 and the control chamber 67.
  • pressure medium flows from the pressure line 35 under high pressure to the pressure medium line 27 and thus into the working space 25 of the axial piston unit 20.
  • the axial piston 22 moves upward and pushes the pump piston 7 in the direction of the upper end of the pump chamber 6.
  • the passage 14 in the pump cylinder 4 is closed, and in the Pump chamber 6 pressure is built up.
  • the control valve 19 opens and fuel is injected into the combustion chamber of a diesel internal combustion engine via the injection nozzle 1.
  • the pressure prevailing in the pump chamber 6 is supplied to a channel 11 having a control edge 12 via a channel 13 attached to the jacket of the pump piston 7.
  • a pressure surge develops in the fuel duct 5 and in the connecting line 33, which spreads at the speed of sound.
  • This pressure surge penetrates into the piston chamber 75 on the control device 31 and, via the reset piston 34, causes the main slide 32 to be immediately displaced in the direction of the solenoid 38.
  • the pressure line 35 and the control chamber 66 are thereby blocked by the slide body 62 , and the slide body 63 with the
  • Control edge 65 provides the connection between the control chamber 68 and the control chamber 67, and thus between the pressure line 27 and the return line 36 free.
  • the pressure drops immediately, and the pressure in the annular space 26 causes the axial piston 22 to stop and the backward movement to begin.
  • the pressure in the pump chamber 6 is reduced and the control valve 19 closes the pressure line 2 at a certain value.
  • the pump chamber 6 is filled with fuel again and the pump piston / axial piston unit remains in the waiting position until a new injection cycle begins at bottom dead center.
  • the fuel injection device shown in FIG. 2 has a second control device 42.
  • the pump piston 7, the axial piston unit 20 and the control device 31 are of the same design as in the example shown and described in FIG. 1.
  • the second control device 42 comprises an overflow / suction valve 43 with an overflow space 53, a switching piston 44 and a compensating valve 54.
  • the overflow space 53 is connected on the one hand via the flow line 52 to the fuel channel 5 and on the other hand to the fuel discharge line 16 .
  • a piston chamber 45 arranged below the switching piston 44 is connected to the passage 14 via the line 47.
  • the switching piston 44 abuts the valve stem 48, the overflow / suction valve 43 being held in the closed position by a spring 50.
  • a further spring 49 which presses the switching piston 44 against the valve stem 48, is arranged below the switching piston 44.
  • the compensating valve 54 is designed as a check valve and is connected to the piston chamber 45 via a bore 55. If there is a lower pressure in the piston chamber 45 than in the line 16, the valve 54 opens and releases the valve seat 56, whereby Fuel flows into the piston chamber 45 and the lines 47 and 33.
  • the control edge 10 closes the passage 14, and the valve 43 is pressed against the valve seat 51 by the pressure built up in the pump chamber 6.
  • the pressure surge spreads via the line 33 to the return piston 34 in the control device 31 and via the line 47 into the piston chamber 45, and thus onto the switching piston 44.
  • the movement of the axial piston is interrupted via the control device 31.
  • the pressure surge on the switching piston 44 brings about an immediate opening of the overflow / suction valve 43 via the valve stem 48, as a result of which the pressure prevailing in the pump chamber 6 is relieved via the line 46 into the overflow chamber 53 and thus the fuel line 16.
  • the result of this pressure drop in the pump chamber 6 is that the control valve 19 closes immediately and at a precisely determined point in time and prevents fuel from flowing into the injection nozzle 1.
  • FIG. 3 shows the mechanical locking device 41 and the camshaft control 61.
  • the mechanical locking device 41 essentially consists of a locking body 78, pawls 79 and unlocking bolt 80.
  • the push rod 37 projects into the locking body 78 and has a shoulder 81 in the area thereof. If the push rod 37 is moved to the left by means of the magnetic coil 38, the shoulder 81 takes the locking body 78 with it, and the spring-loaded pawls 79 engage in the cams 82. As a result, the power supply to the magnetic coil 38 can be interrupted and there is no risk of overloading or overheating.
  • the push rod 37 is reset at the end of the injection process via the return piston 34, which is acted upon by the injection pressure.
  • the push rod 37 is counter to the force of the spring 83 pressed to the right, and the unlocking bolts 80 driven outwards. These unlocking bolts 80 raise the pawls 79 and thereby release the cams 82 on the locking body 78. The spring 77 now pushes the locking body 73 back into its starting position.
  • a camshaft control 61 is arranged in addition to the solenoid 38 of the injection control.
  • This consists of the cam disk 84 with the cam 85 and the idler roller 86 fastened to the blocking body 78.
  • the camshaft is driven by a drive, not shown, which is connected to the crank drive.
  • the cam 85 drives the blocking body 78 via the idler roller 86, and thus the push rod 37 to the left at the start of the injection process.
  • the movement of the locking body 78 and the push rod 37 requires only slight forces, and the camshaft and its control 61 can therefore be built easily and without great kinematic effort.
  • the push rod 37 is reset at the end of the injection process in the same way as described above.
  • a second magnet coil 87 is arranged in addition to the magnet coil 38. Both receive electrical pulses from the electrical pulse generator 40 via the electrical line 89. By actuating this solenoid 87 with an electrical pulse, the push rod 37 can be shifted to the right, and the injection process can therefore be stopped prematurely. This enables an emergency stop of the injection device, since this action of the main slide 32 interrupts the action on the axial piston 22 of the axial piston unit 20 and the piston 22 is retracted.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)

Abstract

Une pompe à carburant (3) comprend un piston (7) réglable par rotation. La pompe (3) est actionnée par un système à piston axial (20) sur lequel agit un moyen de pression fluide, et le piston (7) de la pompe peut subir une rotation autour de l'axe (8) imposée par un dispositif de manoeuvre (60). Dans le circuit de fluide de pression, un dispositif (31) de régulation règle l'admission et le refoulement du fluide de pression pour le piston axial (22) à effet double du système à piston axial (20). L'impulsion pour le début de la course d'injection du piston est délivrée au dispositif de régulation (31) par un génératuer d'impulsions (40) électrique ou par un arbre à cames. Un piston de rappel (34) sur le dispositif de régulation (31) est actionné par le carburant et se trouve relié par une conduite (33) avec la chambre de pompe (6). Vers la fin de la course d'injection, une arête de commande (12) laisse ouvert un passage (14), et un à-coup de pression agit par l'intermédiaire de la conduite (33) sur le piston de rappel (34).
EP87905420A 1986-09-09 1987-09-04 Dispositif d'injection de carburant pour un moteur diesel Expired - Lifetime EP0281580B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87905420T ATE63614T1 (de) 1986-09-09 1987-09-04 Brennstoffeinspritzvorrichttung fuer eine dieselbrennkraftmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3616/86 1986-09-09
CH3616/86A CH671809A5 (fr) 1986-09-09 1986-09-09

Publications (2)

Publication Number Publication Date
EP0281580A1 true EP0281580A1 (fr) 1988-09-14
EP0281580B1 EP0281580B1 (fr) 1991-05-15

Family

ID=4259804

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87905420A Expired - Lifetime EP0281580B1 (fr) 1986-09-09 1987-09-04 Dispositif d'injection de carburant pour un moteur diesel

Country Status (9)

Country Link
US (1) US4907555A (fr)
EP (1) EP0281580B1 (fr)
JP (1) JPH0681937B2 (fr)
KR (1) KR940011345B1 (fr)
CN (1) CN1010336B (fr)
CH (1) CH671809A5 (fr)
FI (1) FI882144A0 (fr)
PL (1) PL152523B1 (fr)
WO (1) WO1988002068A1 (fr)

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DE3001155A1 (de) * 1980-01-15 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzanlage fuer selbstzuendende brennkraftmaschine
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JPS61226527A (ja) * 1985-03-30 1986-10-08 Nippon Denso Co Ltd 燃料噴射制御装置
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* Cited by examiner, † Cited by third party
Title
See references of WO8802068A1 *

Also Published As

Publication number Publication date
FI882144A (fi) 1988-05-06
KR880701828A (ko) 1988-11-05
CH671809A5 (fr) 1989-09-29
CN87106777A (zh) 1988-07-13
PL267640A1 (en) 1988-06-09
FI882144A0 (fi) 1988-05-06
US4907555A (en) 1990-03-13
KR940011345B1 (ko) 1994-12-05
PL152523B1 (en) 1991-01-31
JPH0681937B2 (ja) 1994-10-19
WO1988002068A1 (fr) 1988-03-24
CN1010336B (zh) 1990-11-07
EP0281580B1 (fr) 1991-05-15
JPH01500843A (ja) 1989-03-23

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