EP0077716B1 - Dispositif d'injection pression-temps à prédosage - Google Patents

Dispositif d'injection pression-temps à prédosage Download PDF

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Publication number
EP0077716B1
EP0077716B1 EP82401861A EP82401861A EP0077716B1 EP 0077716 B1 EP0077716 B1 EP 0077716B1 EP 82401861 A EP82401861 A EP 82401861A EP 82401861 A EP82401861 A EP 82401861A EP 0077716 B1 EP0077716 B1 EP 0077716B1
Authority
EP
European Patent Office
Prior art keywords
injection
chamber
pressure
injector
way
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
Application number
EP82401861A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0077716A1 (fr
Inventor
Jean-Pierre Jourde
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.)
Renault SA
Original Assignee
Regie Nationale des Usines Renault
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 Regie Nationale des Usines Renault filed Critical Regie Nationale des Usines Renault
Priority to AT82401861T priority Critical patent/ATE13580T1/de
Publication of EP0077716A1 publication Critical patent/EP0077716A1/fr
Application granted granted Critical
Publication of EP0077716B1 publication Critical patent/EP0077716B1/fr
Expired 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically

Definitions

  • the invention relates to the direct injection of fuel into internal combustion engines, in particular diesel engines.
  • each injector two electromagnetic solenoid valves or servovalves, one being reserved for controlling the start of the injection and the other having the role of ensuring the end of the injection.
  • These two control members perfectly perform the injection function but then have other drawbacks: firstly, the injector holder has a relatively large size making it difficult to mount in the engine cylinder heads, mainly on passenger car engines; second, the inevitable dispersion of response times leads to irregularities between the injector holders; Finally, the very design of the electromagnetic solenoid valves or servo-valves which must have a very low response time inevitably leads to leaks not at the seats but by the cylinder-piston games, leaks which have a very great influence on the quantity injected for the same order time.
  • EP-A-032 168 describes a pressure-time injection device with electromagnetic control using a high pressure and a low booster pressure, this device comprising a medium pressure source intermediate between said high and low pressures, a rotary distributor , and on each injector holder a metering piston whose injection chamber is connected to the needle capacity of the corresponding injector.
  • the document EP-A-0 024 115 relates to an injection device provided with a rotary distributor with two stages for controlling the start, the end and the duration of the fuel injection.
  • the object of the invention is to eliminate the above drawbacks by providing a pre-metering press.on-time injection device which isolates the high pressure of the pump from the injection pressure, allowing a pre-metering of the quantity injected. , avoiding most of the harmful hydraulic phenomena on the high pressure and on the control, and finally by using only one electromagnetic element per cylinder, the hydraulic circuit being designed in such a way that the inevitable leaks of this electromagnetic element do not affect the quantity injected.
  • the invention consists on the one hand, to provide in a manner known per se, the usual high injection pressure and low booster pressure, a medium pressure intermediate between the two preceding ones, and on each injector holder a metering piston with an injection chamber in connection with the capacity of the injector needle, and on the other hand, to use a double rotary distributor driven in synchronism with the camshaft and alternately distributing the high pressure and the low pressure in a single pipe for each injector; in connecting the delivery chamber of this metering piston with said single pipe, with, in a known manner, discharge passages for this needle capacity and for the control chamber of the needle at the end of the piston stroke ; finally to bring this control chamber together by a non-return valve at medium supply pressure and by a three-way solenoid valve alternately with medium pressure at the start of injection and with the metering chamber at the start of metering, the instant of the end of the metering being determined by the end of the distribution of the low pressure by the distributor, and the end of the injection being determined by
  • the device taken as an example corresponds to a four-cylinder engine, and it comprises a single distributor pump assembly corresponding to the box on the left in FIG. 1 designated by the reference EPD, this assembly being joined by four pipes Ci, C 2 , C 3 , C 4 to four EPI injector holder assemblies, only one of which is shown in FIG. 1, and each corresponding to one of the cylinders.
  • the EPD distributor pump assembly comprises two pumps 2 and 4 rotating synchronously while being driven by the engine, either at engine speed, or at half speed like the camshaft.
  • the fuel is sucked into the tank via a filter 1 by the booster pump 2.
  • the discharge pressure of this booster pump, or BP pressure (5 to 10 bars) is regulated by the regulator 3.
  • the fuel is then brought to high pressure HP (for example up to 1000 bars) by pump 4, this high pressure HP being regulated by regulator 5.
  • a third regulator 6 giving rise to an average pressure MP of the order of 30 to 40 bars.
  • the stator 40 of the distributor pump has a bore in which a rotor 41 can rotate at half the engine speed for a four-stroke engine or at the engine speed for a two-stroke engine.
  • This rotor has two stages, namely a high pressure stage A and a low pressure stage B.
  • the high pressure fuel HP penetrates axially into stage A and it is led by a radial bore 32 in a hole 33 of 15 to 20 ° of arc.
  • the stator 40 is pierced with conduits 36, 37, 38 and 39 connected to the pipe Ci, the conduits 38 and 37 corresponding respectively to stages A and B.
  • the central bore of stage B is connected to the low pressure BP and radial conduits 34 distribute this pressure in a large light obscured over approximately 20 ° by the circular boss 35.
  • the light 33 and the boss 35 are determined and wedged on the rotor 41 in such a way that, when the conduits 38, 39 and 36 are in communication with the HP, the latter cannot pass to the BP through the conduit 37, and only when the conduits 36 and 37 are in communication with the BP, conduit 38 cannot receive the HP.
  • the operation of the assembly which is obviously cyclical, periodically includes injection phases, and pre-dosing phases interspersed with the previous ones.
  • the edge X of the boss 35 of the low pressure stage B of the distributor closes the conduit 37, then the edge Z of the high pressure side A uncovers the conduit 38, allowing the high pressure HP by the conduits 39 and 36 to enter the discharge chamber 21, which, on the one hand, by means of the injection piston 8, puts the injection chamber 22 under identical pressure since the fuel cannot go from the chamber 22 to the control chamber 31 due to the non-return valve 50, and on the other hand puts under the same pressure the control chamber 31 by the conduit 53 and the solenoid valve 9 which is in the rest position and authorizes the communication between 28 and 24 (fig. 2).
  • the non-return valve 10 prevents this high pressure from discharging in the medium pressure, and the pipe 23 also transmits this high pressure to the needle capacity 7. This is therefore in the exposed case higher where the pressi ons at 22, 31 and 7 are equal to the high pressure and, as we have seen, the control thrust, much greater than the hydraulic lifting force of the needle, keeps it in contact with its seat. This is illustrated by the diagram in fig. 3.
  • the solenoid valve 9 is energized which puts the conduits 24 and 26 into communication, allowing the high pressure prevailing in the control chamber 31 to drop to the level of the medium pressure.
  • This new state is illustrated in fig. 4. We are therefore in the case described above where the medium pressure prevails at 31, and the high pressure at 7, and where, as we have seen, the control thrust becomes much less than the hydraulic lifting force , the latter then lifting the needle to allow fuel to be injected.
  • the quantity of fuel previously predosed in the injection chamber 22 is then discharged under the high pressure HP by the piston 8. Simultaneously, or with appropriate offsets, on the one hand the lower edge of the piston 8 closes the conduit 23 while the hole 20b puts the conduit 43 in communication with the medium pressure, and on the other hand the fuel remaining in the chamber 22 can be discharged into the control chamber 31 through the conduit 19 thanks to the hole 20a, which has for effect of ensuring a good rapid closure of the injector under the combined effect of its spring 12, of the pressure drop in 7 and of the pressure increase in 31, and at the same time of avoiding any rebound of the needle thanks to this recharging of the control chamber 31.
  • This phase is illustrated in FIG. 5.
  • stage B of the distributor which determines the end of the injection at the precise instant when the edge X comes to close off the conduit 37, as illustrated in FIG. 8, which interrupts the upward movement of the piston 8, therefore ends the metering in the injection chamber 22.
  • the electronic computer which is synchronized with the engine cycle, knows exactly when the conduit 37 is closed and can so accurately calculate the time of dosage.
  • the invention thus allows injection under very high pressure, perfectly constant and regulated, and precise pre-dosing while using for each cylinder only one solenoid valve, which opens and closes only once per cycle, serving both to trigger the start of injection and the start of dosing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Infusion, Injection, And Reservoir Apparatuses (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Injection Moulding Of Plastics Or The Like (AREA)
EP82401861A 1981-10-15 1982-10-11 Dispositif d'injection pression-temps à prédosage Expired EP0077716B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82401861T ATE13580T1 (de) 1981-10-15 1982-10-11 Zeitdruck-einspritzvorrichtung mit vordosierung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8119395A FR2514827A1 (fr) 1981-10-15 1981-10-15 Dispositif d'injection pression-temps a predosage
FR8119395 1981-10-15

Publications (2)

Publication Number Publication Date
EP0077716A1 EP0077716A1 (fr) 1983-04-27
EP0077716B1 true EP0077716B1 (fr) 1985-05-29

Family

ID=9263063

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82401861A Expired EP0077716B1 (fr) 1981-10-15 1982-10-11 Dispositif d'injection pression-temps à prédosage

Country Status (8)

Country Link
US (1) US4440133A (enrdf_load_stackoverflow)
EP (1) EP0077716B1 (enrdf_load_stackoverflow)
JP (1) JPS5879663A (enrdf_load_stackoverflow)
AT (1) ATE13580T1 (enrdf_load_stackoverflow)
DE (1) DE3263913D1 (enrdf_load_stackoverflow)
ES (1) ES8307336A1 (enrdf_load_stackoverflow)
FR (1) FR2514827A1 (enrdf_load_stackoverflow)
PT (1) PT75579B (enrdf_load_stackoverflow)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3438965A1 (de) 1983-10-26 1985-05-09 Kabushiki Kaisha Komatsu Seisakusho, Tokio/Tokyo Brennstoff-einspritzanlage fuer eine brennkraftmaschine
US4640252A (en) * 1984-01-28 1987-02-03 Mazda Motor Corporation Fuel injection system for diesel engine
JPS60204961A (ja) * 1984-03-29 1985-10-16 Mazda Motor Corp デイ−ゼルエンジンの燃料噴射装置
JPH0759919B2 (ja) * 1986-04-04 1995-06-28 日本電装株式会社 デイ−ゼルエンジン用燃料噴射制御装置
IT1208413B (it) * 1987-04-28 1989-06-12 Iveco Fiat Sistema di iniezione del combustibile per motori a combustione interna particolarmente per motori ad accensione per compressione di autoveicoli industriali
US4971016A (en) * 1988-09-23 1990-11-20 Cummins Engine Company, Inc. Electronic controlled fuel supply system for high pressure injector
US5299919A (en) * 1991-11-01 1994-04-05 Paul Marius A Fuel injector system
US5499608A (en) * 1995-06-19 1996-03-19 Caterpillar Inc. Method of staged activation for electronically actuated fuel injectors
GB9805854D0 (en) 1998-03-20 1998-05-13 Lucas France Fuel injector
DE602004002106T2 (de) * 2004-06-30 2007-02-08 C.R.F. S.C.P.A. Kraftstoffdruckregelsystem für eine Brennkraftmaschine
US11933257B2 (en) * 2022-03-18 2024-03-19 Caterpillar Inc. Fuel injector lift control

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0032168A1 (de) * 1980-01-12 1981-07-22 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen, insbesondere für Dieselmotoren

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1522293A (fr) * 1967-02-22 1968-04-26 Dispositif d'injection de combustible pour moteurs à combustion interne
DE2759187A1 (de) * 1977-12-31 1979-07-12 Bosch Gmbh Robert Kraftstoffeinspritzanlage mit mindestens einem kraftstoffeinspritzventil, insbesondere fuer grossmotoren
WO1981000431A1 (en) * 1979-08-08 1981-02-19 Caterpillar Tractor Co Rotary fuel injection apparatus
US4295449A (en) * 1979-09-24 1981-10-20 Caterpillar Tractor Co. Rotary fuel injection with sequencing
US4273087A (en) * 1979-10-22 1981-06-16 Caterpillar Tractor Co. Dual fuel rotary controlled pilot and main injection
DE3001154A1 (de) * 1980-01-15 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Mit pumpeduese arbeitende kraftstoffeinspritzanlage
DE3024963A1 (de) * 1980-07-02 1982-01-28 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen, insbesondere fuer dieselmotoren
JPS5726261A (en) * 1980-07-24 1982-02-12 Diesel Kiki Co Ltd Fuel injector of internal combustion engine
US4372272A (en) * 1981-07-31 1983-02-08 The Bendix Corporation Fuel delivery system with feed and drain line damping

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0032168A1 (de) * 1980-01-12 1981-07-22 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen, insbesondere für Dieselmotoren

Also Published As

Publication number Publication date
ATE13580T1 (de) 1985-06-15
ES516408A0 (es) 1983-06-16
FR2514827A1 (fr) 1983-04-22
FR2514827B1 (enrdf_load_stackoverflow) 1983-12-23
JPS5879663A (ja) 1983-05-13
PT75579B (fr) 1984-11-26
ES8307336A1 (es) 1983-06-16
JPH0579824B2 (enrdf_load_stackoverflow) 1993-11-04
DE3263913D1 (en) 1985-07-04
PT75579A (fr) 1982-10-01
EP0077716A1 (fr) 1983-04-27
US4440133A (en) 1984-04-03

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