EP0478099B1 - Einspritzvorrichtung einer Brennkraftmaschine - Google Patents

Einspritzvorrichtung einer Brennkraftmaschine Download PDF

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Publication number
EP0478099B1
EP0478099B1 EP91250240A EP91250240A EP0478099B1 EP 0478099 B1 EP0478099 B1 EP 0478099B1 EP 91250240 A EP91250240 A EP 91250240A EP 91250240 A EP91250240 A EP 91250240A EP 0478099 B1 EP0478099 B1 EP 0478099B1
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EP
European Patent Office
Prior art keywords
high pressure
working oil
pressure
valve
oil
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
EP91250240A
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English (en)
French (fr)
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EP0478099A2 (de
EP0478099A3 (en
Inventor
Yasutaka c/o Yokohama Dockyard Machin.Wrks Irie
Shigemi c/o Yokohama Dockyard Machin.Wrks Ono
Etsuo c/o Nagasaki Techn. Inst. Kunimoto
Youzou c/o Nagasaki Techn. Inst. Tosa
Yoshinori c/o Nagasaki Techn. Inst. Nagae
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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
Priority claimed from JP25733690A external-priority patent/JP2703103B2/ja
Priority claimed from JP2269369A external-priority patent/JP2766722B2/ja
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP0478099A2 publication Critical patent/EP0478099A2/de
Publication of EP0478099A3 publication Critical patent/EP0478099A3/en
Application granted granted Critical
Publication of EP0478099B1 publication Critical patent/EP0478099B1/de
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
    • F02M59/02—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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement

Definitions

  • the present invention relates to a fuel injection system for an internal combustion engine.
  • a fuel injection system for an internal combustion engine is known from the GB-A-2067681. And in Japanese Patent Application Laid-Open No.59-173512 (No.173512/1984) a fuel injection system is also described.
  • This fuel injection system is composed of a working oil feeding pump, a filter, a working oil tank pressure regulating valve and an accumulator.
  • the working oil feeding pump is driven by an engine through a belt.
  • this system is provided with a fuel feeding device S having a fuel feeding pump 69 which is driven by an internal combustion engine 68, a working oil feeding device P having a working oil pump 76 which is driven by the internal combustion engine, an injector device T having an injector 32 which pressurizes the fuel oil which is sent by pressure from the fuel feeding device S by means of an oil pressure servo mechanism 33 and injects the fuel oil from a nozzle valve 2 and a solenoid valve portion 31 which actuates the oil pressure servo mechanism 33 so as to control communication of the working oil, a valve device X consisting of a valve mechanism portion 62 which drives an exhaust valve 36 to open and close with oil pressure and a valve drive unit 61 having a solenoid valve portion 63 which actuates the valve mechanism portion 62 so as to control communication of the working oil, and a controller R having a computer 65 which controls a solenoid coil 12 of the solenoid valve portion 31 of the injector device T and a solenoid coil 48 of a solenoid valve portion
  • the working oil pump 76 always discharges a constant quantity of high pressure working oil, and the discharge pressure is regulated by releasing the discharge oil by means of a pressure regulating valve 75, thus producing big loss in the driving power.
  • the fuel injector device T is composed as one body of the injector portion 32, the oil pressure servo mechanism 33 and the solenoid valve 31, and the structure thereof is complicated. Furthermore, the injector device T has to be replaced entirely even in case a trouble happens even at any one location. Therefore, not only economical disadvantages are caused, but also deterioration of the working oil is not avoidable because the working oil and the fuel oil are existent in a mixed state in the injector device T.
  • valve device X is composed of the valve mechanism portion 62, the solenoid valve portion 63 and the valve drive unit 61 as one body.
  • the epitome of the present invention for achieving above-mentioned objects is as stated in the following.
  • a fuel injection system for an internal combustion engine comprises a a plurality of high pressure pumps, working oil sources for feeding working oil to said high pressure pumps;an accumulator or gathering pipe for accumulating high pressure working oil discharged from the respektive high pressure pumps;a pressure detector for detecting the pressure of working oil in said accumulator or gathering pipe;an actuator for adjusting the discharge quantity of said high pressure pumps; and a controller for controlling said pressure of working oil to a predetermined pressure by adjusting the discharge quantity of said high pressure pumps by said actuator on the basis of deviations of said pressure detected by said pressure detector from said predetermined pressure, said high pressure pumps are disposed around a crank shaft of the engine, said high pressure pumps are driven by a cam having a plurality of lobes integrally fixed to the outer circumference of said crank shaft, so that the number of discharge times from said high pressure pumps per one revolution of the engine is expressed by the product of the number of said high pressure pumps and the number of said lobes of the cam, there are further provided:a crank angle detector for detecting detecting the
  • the oil pressure in the gathering pipe is detected and the discharge quantity of the high pressure pump is controlled through the pump rack based on the deviation from a predetermined pressure so that the working oil is discharged by the quantity corresponding to the consumption quantity, there is an advantage that the loss of driving power of the high pressure pump may be made small.
  • the present invention being constructed as described above, such effects are obtainable that driving loss of high pressure pumps is eliminated, discharge pressure fluctuation of the high pressure pumps may be made small, the volume of an accumulator or a gathering pipe may also be reduced, high safety may be achieved because a plurality of high pressure pumps are installed, and suspension of feeding working oil may be prevented.
  • a fuel injection system for an internal combustion engine comprises a valve device of the oil pressure drive type; and a switching valve for connection between a pressure chamber of said valve device and said accumulator or gathering pipe so that said switching valve can be opened and closed by the predetermined timing by said controller on the basis of signals from said crank angle detector, thereby opening and closing an exhaust valve via said valve device.
  • a fuel injection system for an internal combustion engine comprises a starting booster which feeds high pressure working oil to above-mentioned accumulator or gathering pipe at the time of starting said engine based on an instruction of said controller.
  • a valve device M being composed of two stages, a large diameter piston for opening an exhaust valve and a small diameter piston for maintaining lift, consumption of the working oil is small.
  • the discharge quantity of the high pressure working oil pump is controlled by the controller through the valve actuator so as to discharge only a required quantity corresponding to a set pressure of the accumulator. Therefore, the driving power of the high pressure working oil pump can be reduced by a large margin, which is advantageous economically. Furthermore, since a plurality of high pressure working oil pumps are provided, the pump may be replaced individually even during operation and it is not required to suspend the engine.
  • the fuel injector is separated independently into a fuel regulating valve, a fuel pressurizer and a fuel valve. Therefore, parts to be repaired or to be replaced against individual trouble are small in number.
  • the fuel injection system is economical, and is able to prevent the fuel oil from mixing into the working oil before it happens.
  • the exhaust valve device is also separated independently into a valve regulating valve and a valve actuator, and parts to be repaired or to be replaced against individual trouble ate small in number, which is economical.
  • starting can be performed surely and easily because the high pressure working oil flows into an accumulator C from a starting booster at the time of starting.
  • the present invention being composed as described above, such effects are obtained that consumption of accumulated working oil may be reduced to the irreducible minimum of the demand, thus eliminating driving power of a high pressure working oil pump. Furthermore, repair and parts replacement to the irreducible minimum of the demand may be performed without suspension of an engine by separating composition of equipments independently, and it is also possible to avoid deterioration of working oil by preventing fuel oil from mixing into the working oil, and to prevent accidents from occurring by suspending fuel injection in a cylinder after defective operation of the discharge valve occurs.
  • Fig. 1 is a structural view of a rear end portion of an engine, which is a sectional view taken along a line I-I in Fig. 2
  • Fig. 2 (a) is a perspective view seen in a direction shown at II a in Fig. 1
  • Fig. 2 (b) is a sectional view taken along a line II b -II b in Fig. 1 showing a general structural view of a fuel injection system.
  • a numeral 1 denotes a crank shaft
  • 2 denotes a thrust collar formed with the crank shaft 1 as one body
  • 3 denotes a plurality of thrust pads which form a thrust bearing which receives the thrust collar 2 and moves forward and rearward
  • 4 denotes a cam which has a plurality of lobes 4a fastened to the outer periphery of the thrust collar 2 through a key 5 as one body with bolts and is divided into halves
  • 6 denotes a journal bearing which receives the crank shaft 1.
  • a spring 14 presses the roller 11 against the cam 4 through the pin 12.
  • a plurality of high pressure pumps 9 are arranged radially at a pitch ⁇ , and pump racks 9a of respective high pressure pumps 9 are joined with each other and one end thereof is coupled with an actuator 15, and the discharge quantity of these high pressure pumps is controlled through feedback by means of a controller 16 so that the pressure of a gathering pipe 17 becomes a set value.
  • the high pressure pump 9 shown with a broken line shows a case in which the number of pumps is reduced in an engine having a small number of cylinders, and is shielded with a cover 18.
  • the high pressure pump 9 has a low pressure oil gateway 19, and the low pressure oil is fed from a tank 20 by a motor-driven oil pump 22 through a filter 21, and circulates in the high pressure pump, and the oil pressure is regulated by a pressure regulating valve 23.
  • the filter 21 and the oil pump 22 are provided against emergency.
  • Fig. 3 is a sectional view showing a jerk type high pressure pump.
  • a plunger 30 is guided slidably along a plunger barrel 32 having an oil filler port 32a fixed to the body 31.
  • the plunger 30 is pressed against the slide cylinder 13 at the lower portion thereof by means of a spring 33, moves vertically by the cam 4, rotates the plunger 30 through a sleeve 34 by the pump rack 9a and changes the position of a lead 35 so as to control the discharge quantity of the high pressure pump 9.
  • a discharge valve 38 which is fastened with a bolt 39 through a cap metal fittings 36 and pressed downward by a spring 37 is provided in an upper part of a barrel 32, and 40 indicates a high pressure oil outlet.
  • the coefficient of pressure fluctuation ⁇ p of the high pressure oil produced by the discharge of the working oil is determined by the coefficient of flow rate fluctuation ⁇ q of the discharge, and ⁇ q is expressed by the number of discharge times Y as shown in Fig. 4.
  • Fig. 4 shows discharge at equal intervals, and the pressure fluctuation becomes the minimal in the case of equal intervals.
  • Fig. 5 shows a high pressure pump arrangement drawing (upper drawing) and a high pressure pump discharge interval drawing (lower drawing) when the number of lobes of the cam is 4, and the number of high pressure pumps is 4 in Fig. 5 (a), 3 in Fig. 5 (b) and 2 in Fig. 5 (c) (the number of high pressure pumps is increased and decreased in accordance with the number of cylinders).
  • Fig. 5 (c) the configuration shows that high pressure pumps shown in Fig. 5 (a) are thinned out, and thus common elements such as a fitting base shown in Fig. 5 (a) may be used. Accordingly, commonness may be planned, thus curtailing the cost.
  • the controller 16 controls one end of the rack 9a through the actuator 15 so that the deviation becomes zero by comparing a set pressure and a detected pressure in the gathering pipe 17, the high pressure pump 9 feeds the working oil in the quantity corresponding to the consumption quantity, and the driving loss of the high pressure pumps is small.
  • Fig. 6 is a general structural view of an electronic oil pressure control system of a fuel injection system
  • Fig. 7 is a structural view of a valve regulating valve in Fig. 6
  • Fig. 8 is a structural view of a fuel regulating valve in Fig. 6
  • Fig. 9 is a perspective view seen in a direction shown at IX in Fig. 6 showing an arrangement diagram of high pressure working oil pumps
  • Fig. 10 is a sectional view of a jerk type high pressure hydraulic oil pump.
  • A indicates an oil pressure source consisting of a plurality of high pressure working oil pumps A4 which are driven by a multi-lobe cam A2 fixed as one body on an outer periphery of a thrust collar A1 at a rear portion of a crank shaft through a roller A3.
  • low pressure working oil is fed with circulation to the oil pressure source A from a working oil feeding source B consisting of a filter B1, an electric pump B2, a pressure regulating valve B3 and a tank B4.
  • C indicates an accumulator which accumulates high pressure working oil which has been fed with pressure from the oil pressure source A
  • D indicates a fuel regulating valve which consists of an injection starting logic valve D2 and an injection terminating logic valve D3 which are opened and closed through working oil by means of a 5-way electromagnetic valve D1 controlled by a controller E
  • F indicates a valve regulating valve, which includes a valve opening logic valves F3 and a valve opening logic valve F4 which are opened and closed through working oil by means of 3-way electromagnetic valves F1 and F2.
  • G indicates a fuel pressurizer, which is fixed to a body G1 and includes a barrel G3 for guiding a plunger G2, a pump rack G4 which rotates the plunger G2 and regulates discharge quantity of high pressure fuel oil, a spring G5 which energizes the plunger G2 downward, an injection pump G10 having a discharge valve G6, and a piston G8 guided by a cylinder G7 which receives working oil controlled by the fuel regulating valve D and drives the injection pump G10.
  • Low pressure fuel oil is fed with circulation to the injection pump G10 from a fuel feeding source H consisting of a filter H1, an electric pump H2, a pressure regulating valve H3 and a tank H4.
  • the fuel oil pressurized to a high pressure is injected into a cylinder not shown by means of the injection pump G10 from a plurality of fuel valves L through a high pressure pipe J and a branching metal mountings K.
  • N indicates a valve actuator and is composed of a two-stage piston M3 guided by a cylinder M2 fixed to a body M1 and a check valve M4.
  • the two-stage piston M3 has a small diameter piston M3a and a large diameter piston M3b
  • the cylinder M2 has a small diameter piston feeding hole M2a and a large diameter piston feeding hole M2b.
  • the valve actuator M has the two-stage piston M3 and oil cushions M6 and M5 at upper and lower moving ends.
  • N indicates an exhaust valve, which is fixed to a cylinder cover N1 and consists of a valve rod guide N3 which guides a valve rod N2 and an air spring N4, and the air spring N4 is fed with air from a guide tank N5.
  • P indicates a starting booster, which receives low pressure working oil from the working oil feeding source B and sends with pressure high pressure working oil to the accumulator C temporarily at the time of starting an engine based on an instruction of the controller E.
  • A5 indicates an actuator, in which discharge quantity of the high pressure working oil pump A4 is controlled by means of the controller E with a signal of a pressure detector C1 so that the pressure in the accumulator becomes a set pressure.
  • A6 indicates a crank angle detector, which outputs a signal for the controller E to control the 5-way electromagnetic valve D1 and 3-way electromagnetic valves F1 and F2.
  • Z indicates an operation detector of the exhaust valve N and outputs a signal notifying of defective operation of the exhaust valve to the controller E.
  • Fig. 7 shows a concrete construction of a valve opening logic valve F3, a valve closing logic valve F4 and 3-way electromagnetic values F1 and F2, and Fig. 8 shows a concrete construction of an injection starting logic valve D2, an injection terminating logic valve D3, a 5-way electromagnetic valve D1 and an accumulator C.
  • Fig. 9 is an arrangement drawing of high pressure working oil pumps A4.
  • A4a denotes a body
  • A4b denotes a barrel
  • A4c denotes a plunger guided by the barrel A4b
  • A4d denotes a pump rack which regulates discharge quantity by rotating the plunger A4c
  • A4e denotes a spring which energizes the plunger A4c downward
  • A4f denotes a discharge valve.
  • the working oil is fed to high pressure working oil pumps A4 under low pressure from the working oil feeding source B and pressurized by the high pressure working oil pumps A4 during engine operation, and the working oil is pressurized temporarily by means of a starting booster P and accumulated in the accumulator C.
  • the controller E controls pump racks A4d of high pressure working oil pumps A4 through an actuator A5 based on a signal of a pressure detector C1 so that the accumulator pressure becomes a set value, and regulates the discharge quantity of high pressure working oil pumps A4 to a required quantity.
  • the accumulated oil is controlled by the switching valve D in accordance with an instruction of the controller E based on a signal of a crank angle detector A6 and is fed to a fuel pressurizer G by the injection starting logic valve D2 at the time of fuel injection, and has the piston G8 stroke. Feeding is suspended at the completion of stroke of the piston G8 corresponding to the fuel injection quantity.
  • the working oil fed to the fuel pressurizer G is discharged by the injection terminating logic valve D3, and the piston G8 returns to the initial position by the urging force of a spring G5.
  • the injection pump G10 pressurizes the fuel oil fed from a fuel feeding source H under a low pressure by upward movement of the piston G8 and injects it into a cylinder not shown from fuel valves L through a high pressure pipe J and a branching metal mounting K. Further, the injection pump G10 makes the injection quantity zero through an actuator G9 so as to sustain the engine by means of the controller E of the pump racks G4 and an independent device not shown upon an abnormal state of the controller E. Incidentally, the following methods of checking abnormal state may be considered.
  • the valve regulating valve F controls the accumulated oil in accordance with an instruction of the controller E based on a signal of the crank angle detector A6.
  • the accumulated oil is fed to the valve actuator M by the valve opening logic valve F3 at the time of opening the exhaust valve so as to have an exhaust valve N stroke, and the stroke is suspended after completion of required strokes.
  • the working oil in the valve actuator M is discharged by the valve closing logic valve F4 at the time of closing the exhaust valve, and the two-stage piston M3 is returned to the initial position by the energizing force of the air spring N4, thus completing the operation of the exhaust valve N.
  • the injection quantity of fuel injection thereafter in the cylinder is made zero by means of a device not shown which makes the pump rack G4 independent of the controller E so as to suspend the engine, thereby to prevent accident from occurring.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (4)

  1. Kraftstoffeinspritzsystem für einen Verbrennungsmotor (8), bestehend aus:
    einer Anzahl von Hochdruckpumpen (9, A4),
    einer Druckölquelle (20) zur Versorgung der Hochdruckpumpen mit Drucköl,
    einem Druckspeicher (C) oder einem Druckspeicherrohr (17) zur Aufnahme von mit hohem Druck beaufschlagtem Drucköl, das von den entsprechenden Hochdruckpumpen gefördert wurde,
    einem Druckmeßfühler (C1) zum Messen des Drucks des Drucköls in dem Druckspeicher bzw. Druckspeicherrohr,
    einem Stellantrieb (15, 9a, A5, A4d) zum Anpassen der Fördermenge der Hochdruckpumpen und einem Regler (16, E) zum Regeln des Drucköldrucks auf einen bestimmten Druck, was mit Hilfe des Stellantriebs durch Anpassen der Fördermenge der Hochdruckpumpen anhand der Abweichung des mit Hilfe des Druckmeßfühlers gemessenen Drucks vom vorgegebenen Druck geschieht,
    dadurch gekennzeichnet, daß die Hochdruckpumpen um eine Kurbelwelle (1, A1) herum angeordnet sind, wobei die Hochdruckpumpen durch einen Nockenkörper (4, A2) angetrieben werden, der eine Anzahl von Nockenerhebungen (4a) hat, die am äußeren Umfang integriert auf der Kurbelwelle angeordnet sind, so daß die Förderstoßanzahl der Hochdruckpumpen je Motorumdrehung durch das Produkt aus der Anzahl der Hochdruckpumpen und der Anzahl der Nockenerhebungen ausgedrückt werden kann, wobei des weiteren als Bestandteile vorgesehen sind:
    ein Kurbelwinkelmeßfühler (A6) zum Messen des Kurbelwinkels, eine druckölbetriebene Kraftstoffeinspritzpumpe (G10) und ein Schaltventil (D) zwischen einem Druckraum der Kraftstoffeinspritzpumpe und dem Druckspeicher bzw. dem Druckspeicherrohr, so daß das Schaltventil durch Signale von dem Kurbelwinkelmeßfühler durch den Regler geöffnet und geschlossen werden kann, wodurch mit Hilfe der Einspritzdüse die erforderliche Menge Kraftstoff in die Zylinder des Verbrennungsmotors eingespritzt wird.
  2. Kraftstoffeinspritzsystem für einen Verbrennungsmotor nach Anspruch 1, bei dem die Hochdruckpumpen (9, A4) in gleichmäßigen Abständen um den Nockenkörper (4, 12) herum angeordnet sind.
  3. Kraftstoffeinspritzsystem für einen Verbrennungsmotor nach Anspruch 1, bei dem des weiteren ein Startverstärker (P) vorgesehen ist, der zum Zeitpunkt des Anlassens des Motors auf einen Befehl vom Regler (16, E) dem Druckspeicher bzw. dem Druckspeicherrohr unter hohem Druck Drucköl zuführt.
  4. Kraftstoffeinspritzsystem für einen Verbrennungsmotor nach Anspruch 1, bei dem des weiteren als Bestansteile vorgesehen sind:
    eine druckölbetriebene Ventileinrichtung (M) und ein Schaltventil (F) zur Herstellung der Verbindung zwischen einem Druckraum (M2) der Ventileinrichtung und dem Druckspeicher bzw. Druckspeicherrohr, so daß das Schaltventil entsprechend der Taktung, die durch den Regler durch die Signale vom Kurbelwinkelmeßfühler vorgegeben wird, geöffnet oder geschlossen wird, wodurch über die Ventileinrichtung ein Auslaßventil (N) geöffnet und geschlossen wird.
EP91250240A 1990-09-28 1991-08-29 Einspritzvorrichtung einer Brennkraftmaschine Expired - Lifetime EP0478099B1 (de)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP257336/90 1990-09-28
JP25733690A JP2703103B2 (ja) 1990-09-28 1990-09-28 内燃機関の高圧油発生装置
JP25733690 1990-09-28
JP269369/90 1990-10-09
JP26936990 1990-10-09
JP2269369A JP2766722B2 (ja) 1990-10-09 1990-10-09 内燃機関の電子油圧制御装置

Publications (3)

Publication Number Publication Date
EP0478099A2 EP0478099A2 (de) 1992-04-01
EP0478099A3 EP0478099A3 (en) 1994-09-14
EP0478099B1 true EP0478099B1 (de) 2000-07-12

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP91250240A Expired - Lifetime EP0478099B1 (de) 1990-09-28 1991-08-29 Einspritzvorrichtung einer Brennkraftmaschine

Country Status (4)

Country Link
EP (1) EP0478099B1 (de)
KR (1) KR940004358B1 (de)
DE (1) DE69132307T2 (de)
DK (1) DK0478099T3 (de)

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US5960756A (en) * 1997-01-27 1999-10-05 Aisin Seiki Kabushiki Kaisha Valve control device for an internal combustion engine
US5865156A (en) * 1997-12-03 1999-02-02 Caterpillar Inc. Actuator which uses fluctuating pressure from an oil pump that powers a hydraulically actuated fuel injector
US6050248A (en) * 1997-12-03 2000-04-18 Caterpillar Inc. Exhaust gas recirculation valve powered by pressure from an oil pump that powers a hydraulically actuated fuel injector
DE10010945B4 (de) * 2000-03-06 2004-07-22 Robert Bosch Gmbh Pumpe zur Versorgung eines Kraftstoffeinspritzsystems und einer hydraulischen Ventilsteuerung für Brennkraftmaschinen
CN108443126B (zh) * 2018-04-27 2024-02-23 廊坊市华海石油技术开发有限公司 水力活塞泵、井下泵机组及井下排液测试系统

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DE3001154A1 (de) * 1980-01-15 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Mit pumpeduese arbeitende kraftstoffeinspritzanlage
JPS59173512A (ja) * 1983-03-19 1984-10-01 Yanmar Diesel Engine Co Ltd 内燃機関の電子油圧制御装置
JPS59176412A (ja) * 1983-03-26 1984-10-05 Yanmar Diesel Engine Co Ltd 内燃機関の電子油圧制御装置
DE3800003A1 (de) * 1987-01-02 1988-07-28 Elsbett L Regelgestaenge von einspritzpumpenregler und versteller der pumpenelemente eines axialmotors
DE3700003A1 (de) * 1987-01-02 1988-07-14 Elsbett L Einspritzpumpenanordnung eines axialmotors

Also Published As

Publication number Publication date
EP0478099A2 (de) 1992-04-01
DE69132307D1 (de) 2000-08-17
KR940004358B1 (ko) 1994-05-23
DE69132307T2 (de) 2001-02-01
EP0478099A3 (en) 1994-09-14
DK0478099T3 (da) 2000-09-18
KR920006613A (ko) 1992-04-27

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