EP0478099A2 - Hochdruckölerzeugungsvorrichtung einer Brennkraftmaschine - Google Patents

Hochdruckölerzeugungsvorrichtung einer Brennkraftmaschine Download PDF

Info

Publication number
EP0478099A2
EP0478099A2 EP91250240A EP91250240A EP0478099A2 EP 0478099 A2 EP0478099 A2 EP 0478099A2 EP 91250240 A EP91250240 A EP 91250240A EP 91250240 A EP91250240 A EP 91250240A EP 0478099 A2 EP0478099 A2 EP 0478099A2
Authority
EP
European Patent Office
Prior art keywords
high pressure
working oil
oil
pressure
internal combustion
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
EP91250240A
Other languages
English (en)
French (fr)
Other versions
EP0478099B1 (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
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
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

Links

Images

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 high pressure oil generating apparatus which drives a fuel injector, an exhaust valve and the like with oil pressure.
  • a conventional high pressure oil generating apparatus is described in Japanese Patent Application Laid-Open No.59-173512(No.173512/1984)for instance.
  • This apparatus 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 items (1) and (2) in a high pressure oil generating apparatus of an internal combustion engine for driving valves or devices installed in the internal combustion engine with hydraulic oil.
  • the working oil discharge number of times from the high pressure pumps in one revolution is expressed by the product of the number of high pressure pump sets and the number of cam lobes, and the construction is such that the number of discharge times is increased and the arrangement of high pressure pumps is made to have an optimum pitch with respect to the number of high pressure pumps and the number of cam lobes so that discharge interval becomes identical.
  • 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 high pressure oil generating apparatus of the present invention comprises an oil pressure driven valve device, a switching valve provided between a pressure chamber of the valve device and above-mentioned accumulator or gathering pipe and a controller which opens and closes the switching valve at a predetermined timing based on a signal of the crank angle detector.
  • a high pressure oil generating apparatus comprises a starting booster which feeds high pressure working oil to above-mentioned accumulator or gathering pipe in addition to above-mentioned construction.
  • a valve actuator 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 apparatus 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 are 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 thru Fig. 5 show a first embodiment of the present invention, wherein:
  • 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, and 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 high pressure oil generating apparatus.
  • 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).
  • 360°/4 90° is considered as one unit in case the number of lobes of the cam is 4, and high pressure pump are arranged (shown at positions shown with ⁇ in the upper drawing) at every interval ⁇ 1 (degrees) obtained by dividing 90° by the number of high pressure pumps.
  • 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 high pressure oil generating apparatus
  • 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 valves 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 fuel regulating valve D in accordance with an instruction of the controller E based on a signal of a crank angle detector 6 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.
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
JP25733690 1990-09-28
JP25733690A JP2703103B2 (ja) 1990-09-28 1990-09-28 内燃機関の高圧油発生装置
JP2269369A JP2766722B2 (ja) 1990-10-09 1990-10-09 内燃機関の電子油圧制御装置
JP269369/90 1990-10-09
JP26936990 1990-10-09

Publications (3)

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

Family

ID=26543165

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)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0629777A1 (de) * 1993-06-18 1994-12-21 Yamaha Hatsudoki Kabushiki Kaisha Kraftstoffeinspritzanlage
GB2291121A (en) * 1994-06-27 1996-01-17 Ford Motor Co Engine hydraulic valve operating system
FR2758857A1 (fr) * 1997-01-27 1998-07-31 Aisin Seiki Dispositif de commande de soupape pour un moteur a combustion interne
WO1999028611A1 (en) * 1997-12-03 1999-06-10 Caterpillar Inc. Actuator which uses fluctuating pressure from an oil pump that powers a hydraulically actuated fuel injector
WO1999028612A1 (en) * 1997-12-03 1999-06-10 Caterpillar Inc. Exhaust gas recirculation valve powered by pressure from an oil pump that powers a hydraulically actuated fuel injector
DE10010945A1 (de) * 2000-03-06 2001-09-27 Bosch Gmbh Robert Pumpe zur Versorgung eines Kraftstoffeinspritzsystems und einer hydraulischen Ventilsteuerung für Brennkraftmaschinen
CN108443126A (zh) * 2018-04-27 2018-08-24 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

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2219002A (en) * 1939-08-05 1940-10-22 Beeh Louis Fuel pump
GB2067681A (en) * 1980-01-15 1981-07-30 Bosch Gmbh Robert Fuel injection systems for internal combustion engines operating with pumping nozzles
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
DE3700003A1 (de) * 1987-01-02 1988-07-14 Elsbett L Einspritzpumpenanordnung eines axialmotors
DE3800003A1 (de) * 1987-01-02 1988-07-28 Elsbett L Regelgestaenge von einspritzpumpenregler und versteller der pumpenelemente eines axialmotors

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2219002A (en) * 1939-08-05 1940-10-22 Beeh Louis Fuel pump
GB2067681A (en) * 1980-01-15 1981-07-30 Bosch Gmbh Robert Fuel injection systems for internal combustion engines operating with pumping nozzles
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
DE3700003A1 (de) * 1987-01-02 1988-07-14 Elsbett L Einspritzpumpenanordnung eines axialmotors
DE3800003A1 (de) * 1987-01-02 1988-07-28 Elsbett L Regelgestaenge von einspritzpumpenregler und versteller der pumpenelemente eines axialmotors

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 9, no. 29 (M-356) 7 February 1985 & JP-A-59 173 512 (SAITOU ATSUSHI) *
PATENT ABSTRACTS OF JAPAN vol. 9, no. 34 (M-357) 14 February 1985 & JP-A-59 176 412 (SAITOU ATSUSHI) 5 October 1984 *

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0629777A1 (de) * 1993-06-18 1994-12-21 Yamaha Hatsudoki Kabushiki Kaisha Kraftstoffeinspritzanlage
US5511956A (en) * 1993-06-18 1996-04-30 Yamaha Hatsudoki Kabushiki Kaisha High pressure fuel pump for internal combustion engine
GB2291121A (en) * 1994-06-27 1996-01-17 Ford Motor Co Engine hydraulic valve operating system
GB2291121B (en) * 1994-06-27 1997-12-10 Ford Motor Co Hydraulic system for an internal combustion engine
FR2758857A1 (fr) * 1997-01-27 1998-07-31 Aisin Seiki Dispositif de commande de soupape pour un moteur a combustion interne
WO1999028611A1 (en) * 1997-12-03 1999-06-10 Caterpillar Inc. Actuator which uses fluctuating pressure from an oil pump that powers a hydraulically actuated fuel injector
WO1999028612A1 (en) * 1997-12-03 1999-06-10 Caterpillar Inc. Exhaust gas recirculation valve powered by 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
DE10010945A1 (de) * 2000-03-06 2001-09-27 Bosch Gmbh Robert Pumpe zur Versorgung eines Kraftstoffeinspritzsystems und einer hydraulischen Ventilsteuerung für Brennkraftmaschinen
DE10010945B4 (de) * 2000-03-06 2004-07-22 Robert Bosch Gmbh Pumpe zur Versorgung eines Kraftstoffeinspritzsystems und einer hydraulischen Ventilsteuerung für Brennkraftmaschinen
CN108443126A (zh) * 2018-04-27 2018-08-24 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
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

Also Published As

Publication number Publication date
DE69132307T2 (de) 2001-02-01
EP0478099B1 (de) 2000-07-12
DK0478099T3 (da) 2000-09-18
KR920006613A (ko) 1992-04-27
EP0478099A3 (en) 1994-09-14
DE69132307D1 (de) 2000-08-17
KR940004358B1 (ko) 1994-05-23

Similar Documents

Publication Publication Date Title
EP0375944B1 (de) Hochdruckpumpe mit veränderlichem Abfluss
US4566416A (en) Accumulator nozzle fuel injection system
DE19720731A1 (de) Kraftstoffversorgungsgerät für einen Benzinmotor der direkteinspritzenden Art
EP1365142B1 (de) Hochdruckkraftstoffpumpe
EP1927744B1 (de) Kraftstoffeinspritzvorrichtung für einen Motor und Betriebsverfahren für einen mit der Vorrichtung ausgestatteten Motor
EP0728940B1 (de) Kombiniertes Anlasser-, Bypass- und Sicherheitsdruckentladungsventil für ein Brennstoffsystem
KR20010093297A (ko) 고압펌프의 연료 흡입압력 제어용 밸브 시스템
US5507260A (en) Fuel management system for internal combustion engines
EP0192194B1 (de) Gaseinspritzventil für einen Gasmotor
DE102004017256B4 (de) Druckspeicher-Kraftstoffeinspritzsystem geeignet zum Vermeiden eines abnormal hohen Drucks
EP0478099A2 (de) Hochdruckölerzeugungsvorrichtung einer Brennkraftmaschine
WO2003040548A1 (de) Einspritzanlage mit notlauffunktion sowie zugehöriges notlaufverfahren
EP0607750A1 (de) Anlage zum Betanken eines mobilen Druckbehälters mit einem gasförmigen Kraftstoff und Verfahren zum Betrieb einer derartigen Anlage
DE10034913C2 (de) Brennstoffzuführvorrichtung für variable Förderung
CN101358572A (zh) 用于在共轨型燃料供给系统中控制过压的方法
KR100689947B1 (ko) 왕복동 피스톤 연소기관
WO2007122092A2 (de) Druckregler für gasförmige medien
CN100467857C (zh) 调节装置
EP1793121A1 (de) Kraftstoffeinspritzventil und Dieselmotor damit
US4708116A (en) Injection system for a diesel engine with a high pressure injection pump for each cylinder
CN101400886B (zh) 燃料喷射系统
DE3524980C2 (de) Kraftstoffeinspritzpumpe für eine Brennkraftmaschine
CN87106778A (zh) 具有预喷射的柴油机燃油喷射装置
ITMI991573A1 (it) Sistema trasportatore del combustibile per alimentare con combustibile un motore endotermico
GB2275307A (en) I.c.engine high pressure distributor fuel injection system

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): CH DE DK LI

17P Request for examination filed

Effective date: 19920623

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): CH DE DK LI

17Q First examination report despatched

Effective date: 19950907

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

RTI1 Title (correction)

Free format text: FUEL INJECTION SYSTEM FOR AN INTERNAL COMBUSTION ENGINE

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE DK LI

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: E. BLUM & CO. PATENTANWAELTE

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 69132307

Country of ref document: DE

Date of ref document: 20000817

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

EN Fr: translation not filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20020814

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20020831

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20020904

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030831

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040302

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL