EP0077235A1 - Einspritzpumpe mit konstantem Einspritzdruck und Vordosierung und eine Anlage hierzu - Google Patents

Einspritzpumpe mit konstantem Einspritzdruck und Vordosierung und eine Anlage hierzu Download PDF

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Publication number
EP0077235A1
EP0077235A1 EP82401738A EP82401738A EP0077235A1 EP 0077235 A1 EP0077235 A1 EP 0077235A1 EP 82401738 A EP82401738 A EP 82401738A EP 82401738 A EP82401738 A EP 82401738A EP 0077235 A1 EP0077235 A1 EP 0077235A1
Authority
EP
European Patent Office
Prior art keywords
injection
chamber
pressure
injector
piston
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
EP82401738A
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English (en)
French (fr)
Other versions
EP0077235B1 (de
Inventor
Jean-Pierre Jourde
Pedro Campo-Garraza
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 SAS
Regie Nationale des Usines Renault
Original Assignee
Renault SAS
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 Renault SAS, Regie Nationale des Usines Renault filed Critical Renault SAS
Publication of EP0077235A1 publication Critical patent/EP0077235A1/de
Application granted granted Critical
Publication of EP0077235B1 publication Critical patent/EP0077235B1/de
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
    • 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
    • F02M59/32—Varying fuel delivery in quantity or timing fuel delivery being controlled by means of fuel-displaced auxiliary pistons, which effect injection
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • the invention relates to injection engines and more particularly to direct injection diesel engines which require high injection pressure, in particular for operating points at low speed and at low load, that is to say for small amounts injected.
  • Injection pumps in line or rotary, "do not allow sufficient pressures to be obtained in this case.
  • Conventional pump injectors give significantly higher pressures in this operating case, but they are still not sufficient
  • mechanical pump injectors present great difficulties with regard to setting the injection advance.
  • the object of the invention is to remedy the above drawbacks, that is to say to produce an injection device which makes it possible to obtain high pressures, even for the small quantities injected, and very high precision on the instant the injection begins.
  • the invention essentially consists in combining a discharge piston with mechanical cam or eccentric control which discharges the fuel into a discharge chamber, with an injection piston which is actuated only by this discharge pressure and by an opposing spring, and which compresses the fuel in an injection chamber communicating with the injector, further providing a calibrated relief valve keeping the pressure in the discharge chamber constant throughout the duration of the discharge, thus making the pressure in the pressure chamber constant and independent injection of the speed and the law of movement of the delivery piston throughout the delivery time.
  • the assembly is advantageously combined with a discharge chamber of known type ensuring rapid closure of the injection needle, with in addition a single solenoid valve ensuring both the pre-metering of the fuel in the injection chamber and the control from the instant of injection by action on this discharge chamber.
  • the body 1 of the pump injector is made of several parts, not shown in FIG. 1, which are assembled together by suitable means. It contains a pusher 2, which is pushed up and down by a cam or eccentric 3 and returned in the opposite direction by an opposing spring 4, so as to move between one. top dead center and bottom dead center, this stroke possibly being further limited by stops.
  • An appropriate light makes it possible to secure this pusher to the head of a delivery piston 5, which therefore moves in the same movement and which slides in a bore of the body 1 by driving the fuel into a delivery chamber 6 during the downward movements. , while during the upward movements of the assembly 2 and 5 the fuel is admitted into this delivery chamber 6 from the booster pressure arriving at 7 by a non-return valve 8.
  • an injection piston 9 is placed, the stroke of which is limited by an upper stop 10 and a lower stop 11 arranged in the bottom of an injection chamber 12, further containing an opposing return spring 13 urging the injection piston 9 towards its upper stop 10.
  • the injection chamber 12 communicates by a pipe 14, in which a plane valve 15 is possibly interposed, with the capacity 16 of the injector 17 provided with a conventional injection needle 18.
  • the discharge chamber 6 comprises a pressure relief valve constituted by a discharge valve 19 calibrated for a well determined high pressure.
  • the diameter of the delivery piston 5 is greater by a determined value than that of the injection piston 9 so that, whatever the engine speed and the law of movement defined by the cam or eccentric 3, the injection pressure prevails. between 12 and 16 can be kept constant and equal to the value prevailing in the discharge chamber 16 when the injection occurs.
  • an injector 17 of known type comprising a discharge chamber 20 in which slides a discharge piston 21 which pushes, by means of a pusher 22 provided with a needle spring 23, the needle 18 in the closing direction.
  • a stop 24 in the blind bottom of the discharge chamber 20 precisely limits the needle lift, while the needle spring 23 allows the needle lift 18 only if the injection pressure at 16 is sufficient , and if in addition this lifting is not prohibited by the application of high pressure in the discharge chamber 20.
  • the entire volume containing the underside of the piston 21 as well as the pusher 22, the top of the 'needle 18 and the needle spring 23 is joined to the booster pressure.
  • the same solenoid valve 26 makes it possible to ensure both the pre-metering and the control of the injection.
  • the metering occurs, during the ascent of the delivery piston 5, the injection piston 9 only going up if the solenoid valve 26 is in its first position to allow the fuel to arrive from the booster pressure to the injection 12. 12.
  • the two chambers 6 and 12 are then supplied with the booster pressure by the non-return valves 8 and 25 , but due to the presence of the opposing return spring 13, the pressure prevailing in the chamber 6 is greater than the pressure prevailing in the chamber 12, which means that the fuel cannot penetrate into the chamber 6 by the check valve.
  • the predosed quantity therefore depends exclusively only on the calibrated passage sections of conduits and on the time elapsing between the return of the solenoid valve 26 to its first position and the moment when the delivery piston 2 reaches its top dead center. There is therefore the possibility of controlling this time with precision by means of an electronic device taking into account the speed of the motor.
  • the discharge chamber 20 like the injection chamber 12, is subjected to the high pressure regulated by 19 , so that injection does not take place until the solenoid valve is energized to pass into its second position tion.
  • the pressure prevailing in the discharge chamber 20 drops and the injection is therefore carried out by 14 under a constant pressure as we saw above, and naturally during the time necessary for the flow of the predosed quantity.
  • injection piston 9 for the conduits 30 and 31 and in the body 1 for communications 32 and 33 enabling the injection piston 9 to communicate at the end of the low stroke.
  • discharge chamber 6 with the discharge chamber 20 and on the other hand the injection chamber 12 with the booster pressure, which has the effect of completely discharging the pressure of the capacity 16 of the injector and at the same time force the needle to lower to ensure rapid closure.
  • Fig. 4 corresponds to the start of the discharge and the simultaneous pressurization of the discharge chamber 6 and of the injection chamber 12, pressure regulated by the pressure limiter 19. In this phase the needle 18 cannot rise because the same pressure prevails in the discharge chamber 20 and in the capacity 16.
  • Fig. 5 corresponds to the precise instant when the injection by excitation of the valve 26 is triggered.
  • the discharge capacity 20 is discharged, allowing the needle 18 to rise, and the quantity of fuel predosed in the chamber.
  • injection 12 is injected at the constant pressure regulated by 19.
  • fig. 6 corresponds to the end of travel of the injection piston 9, which precedes the end of travel of the piston 5; position in which the injection chamber 12 and the capacity 16 of the injector, as well as. the corresponding pipes are completely discharged whereas, on the contrary, the discharge chamber 20 is partially recharged by the end of the delivery of the piston 5 into the delivery chamber 6. This therefore corresponds to the rapid closure of the needle.
  • Figs. 7 and 8 show the stroke and speed curves of the pusher and of the delivery piston 5 (measured positively downwards) in the case of an eccentric control imposing a sinusoidal law, any other law of movement also being usable.
  • fig. 9 shows the control signal of the solenoid valve as a function of the rotation cycle of the camshaft. It can be seen in particular that the rising edge 34 of the supply slot of the solenoid valve precisely determines the start of the injection, naturally with an advance to the injection, while the falling edge 35 corresponds to the predosing which ends. with the beginning of the repression. Although the solenoid valve 26 performs two functions, it therefore receives only one pulse per cycle, the two edges, rising and falling, are determined separately and electronically according to the running conditions of the engine: injection advance, speed and charge.
  • the present invention relates to a pump injector, but it is conceivable for a polycylindrical engine to group all the elements, cams or eccentrics 3, the counter springs 4 and the discharge chambers 5 for the number of cylinders considered in the same body as shown in the fig. 10 which situates the example of a four-cylinder engine.
  • the shaft 51 supporting the cams or eccentrics 3 set according to the engine cycle is driven at half speed for a four-stroke engine and at the same speed for a two-stroke engine.
  • a delivery piston 5 is obviously associated to an injection piston 9 by a high pressure line 53.
  • the delivery chamber 6 of the pump injector solution is dissociated into two chambers 6a and 6b connected by line 53.
  • the operating principle is identical to that of the pump injector, only the regulation of the high pressure is different; this difference bringing in the present version an advantage compared to several pump injectors on a polycylinder.
  • the discharge valve 19 is integrated in the injector holder which requires a very precise and delicate calibration between several pump-injector holders so that the (constant) injection pressures are identical.
  • the chambers 6a are connected via conduits 54 and non-return valves 50 to a ramp 52. At the end of which is connected the single discharge valve 19; the valve 50 being arranged in such a way that the high pressure prevailing in one of the chambers 6a can be regulated without interaction with the other chambers 6a.

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)
EP82401738A 1981-10-01 1982-09-27 Einspritzpumpe mit konstantem Einspritzdruck und Vordosierung und eine Anlage hierzu Expired EP0077235B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8118558 1981-10-01
FR8118558A FR2514075A1 (fr) 1981-10-01 1981-10-01 Injecteur pompe a pression d'injection constante et predosage et systeme derive

Publications (2)

Publication Number Publication Date
EP0077235A1 true EP0077235A1 (de) 1983-04-20
EP0077235B1 EP0077235B1 (de) 1985-08-14

Family

ID=9262668

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82401738A Expired EP0077235B1 (de) 1981-10-01 1982-09-27 Einspritzpumpe mit konstantem Einspritzdruck und Vordosierung und eine Anlage hierzu

Country Status (4)

Country Link
EP (1) EP0077235B1 (de)
JP (1) JPS5874869A (de)
DE (1) DE3265437D1 (de)
FR (1) FR2514075A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0240353A2 (de) * 1986-04-04 1987-10-07 Nippondenso Co., Ltd. Kraftstoffeinspritzsteuervorrichtung
EP0629776A1 (de) * 1993-06-03 1994-12-21 Cummins Engine Company, Inc. Kraftstoffeinspritzventil für Verbrennungsmotor
EP0724688A1 (de) * 1993-10-06 1996-08-07 Bkm, Inc. Zweitaktbrennkraftmaschine für geräte
EP0962649A1 (de) * 1998-06-04 1999-12-08 Wolfgang Dr. Heimberg Kraftstoffeinspritzvorrichtung
WO1999063217A1 (de) * 1998-06-04 1999-12-09 Wolfgang Heimberg Pumpenvorrichtung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2558789A1 (de) * 1975-12-24 1977-07-14 Bosch Gmbh Robert Hochdruck-kraftstoffeinspritzeinrichtung fuer dieselmotoren
GB2030222A (en) * 1978-09-13 1980-04-02 Bendix Corp Fuel injector for an internal combustion engine for producing fuel injection pulses which have a time-variable flow rate

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1103685B (de) * 1956-12-13 1961-03-30 Pierre Etienne Bessiere Selbstregelnde Kolbenpumpe zur Brennstoffeinspritzung bei Brennkraftmaschinen
JPS6014910B2 (ja) * 1979-12-28 1985-04-16 株式会社デンソー 燃料噴射装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2558789A1 (de) * 1975-12-24 1977-07-14 Bosch Gmbh Robert Hochdruck-kraftstoffeinspritzeinrichtung fuer dieselmotoren
GB2030222A (en) * 1978-09-13 1980-04-02 Bendix Corp Fuel injector for an internal combustion engine for producing fuel injection pulses which have a time-variable flow rate

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0240353A2 (de) * 1986-04-04 1987-10-07 Nippondenso Co., Ltd. Kraftstoffeinspritzsteuervorrichtung
EP0240353A3 (en) * 1986-04-04 1989-10-11 Nippondenso Co., Ltd. A fuel injection control device
EP0629776A1 (de) * 1993-06-03 1994-12-21 Cummins Engine Company, Inc. Kraftstoffeinspritzventil für Verbrennungsmotor
EP0724688A1 (de) * 1993-10-06 1996-08-07 Bkm, Inc. Zweitaktbrennkraftmaschine für geräte
EP0724688A4 (de) * 1993-10-06 1997-07-09 Bkm Inc Zweitaktbrennkraftmaschine für geräte
EP0962649A1 (de) * 1998-06-04 1999-12-08 Wolfgang Dr. Heimberg Kraftstoffeinspritzvorrichtung
WO1999063217A1 (de) * 1998-06-04 1999-12-09 Wolfgang Heimberg Pumpenvorrichtung

Also Published As

Publication number Publication date
JPH0454064B2 (de) 1992-08-28
FR2514075A1 (fr) 1983-04-08
EP0077235B1 (de) 1985-08-14
FR2514075B1 (de) 1983-12-23
DE3265437D1 (en) 1985-09-19
JPS5874869A (ja) 1983-05-06

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