EP0077235B1 - 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
EP0077235B1
EP0077235B1 EP82401738A EP82401738A EP0077235B1 EP 0077235 B1 EP0077235 B1 EP 0077235B1 EP 82401738 A EP82401738 A EP 82401738A EP 82401738 A EP82401738 A EP 82401738A EP 0077235 B1 EP0077235 B1 EP 0077235B1
Authority
EP
European Patent Office
Prior art keywords
injection
chamber
piston
pressure
injector
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
EP82401738A
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English (en)
French (fr)
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EP0077235A1 (de
Inventor
Jean-Pierre Jourde
Pedro Campo-Garraza
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Regie Nationale des Usines Renault
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Regie Nationale des Usines Renault
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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 a high injection pressure, in particular for operating points at low speed and at low load, that is to say for low quantities injected.
  • Injection pumps in line or rotary, do not allow to obtain sufficient pressures in this case.
  • Conventional type injectors give significantly higher pressures in this operating case, but they are still not sufficient.
  • the mechanical pump injectors present great difficulties as regards the setting of the injection advance.
  • Document GB-A 2030222 describes an injection pump sending a predosed quantity of fuel to a needle injector of the type comprising a piston and a discharge chamber.
  • This pump comprises a discharge piston mechanically controlled by cam, this piston discharging fuel into a discharge chamber, and an injection piston actuated exclusively by the pressure prevailing in the discharge chamber and by an opposing return spring, this piston pushing back the fuel in an injection chamber intended to feed the injector.
  • Document DE-B 1103685 describes a piston pump with a pressure regulator limiting the pressure in the delivery chamber.
  • 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 providing, in addition to a delivery piston mechanically controlled by cam or eccentric which delivers the fuel into a delivery chamber, and an injection piston which is actuated only by this delivery pressure and by an antagonistic spring, and which compresses the fuel in an injection chamber communicating with the injector, a calibrated relief valve keeping the pressure in the discharge chamber constant throughout the duration of the discharge, thus making the pressure in the constant injection chamber independent of the speed and the law of movement of the delivery piston throughout the delivery time.
  • the assembly is 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 of the instant of injection by action on this discharge chamber.
  • the body 1 of the pump injector is in several parts, not shown in FIG. 1, which are assembled together by appropriate means. It contains a pusher 2, which is pushed from top to bottom by a cam or eccentric 3 and returned in the opposite direction by an opposing spring 4, so as to move between a top dead center and a bottom dead center, this stroke being possibly further limited by stops.
  • a suitable 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 ascent 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 delivery chamber 6 when the injection occurs. This amounts to saying that the volume of fuel set in motion by the downward stroke of the delivery piston 5 will always be greater than the volume of fuel set in motion by the injection piston 9 so that the pressure adjusted by the relief valve 19 is kept constant, which already solves the first problem. It remains to ensure the predosing of the quantity of fuel to inject, and the precise triggering of the instant of injection.
  • 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 ensures both the pre-metering and the injection control.
  • the metering takes place 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 at the injection 12.
  • the two chambers 6 and 12 are then supplied with the booster pressure by the non-return valves 8 and 25 but, because 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, so that the fuel cannot enter the chamber 6 by the non-return valve 8 when the delivery piston 5 under the effect of the opposing spring 4 rises, the cam or eccentric 3 moving from its bottom dead center to its top dead center.
  • 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 the injection does not take place until the solenoid valve is energized to move into its second position.
  • the pressure prevailing in the discharge chamber 20 drops and the injection is therefore carried out by 14 under a constant pressure as seen above, and naturally for 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 of the simultaneous pressurization of the discharge chamber 6 and of the injection chamber 12, pressure adjusted 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 set 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 reclosing 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 deten mine precisely 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 delivery.
  • the solenoid valve 26 fulfills 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 opposing springs 4 and the discharge chambers 6 for the number of cylinders considered in the same body as shown in 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 with an injection piston 9 by a high pressure line 53.
  • the delivery chamber 6 of the injector-pump solution is separated 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 injector-pumps on a polycylinder.
  • the discharge valve 19 is integrated into the injector holder, which requires very precise and delicate calibration between several pump injector holders so that the (constant) pressures of injection 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 adjusted without interaction with the other chambers 6a.

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  • 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)

Claims (4)

1. Einspritzpumpe, die eine vordosierte Brennstoffmenge einer Einspritzdüse (17) mit einer Spindel (18) zuführt und die einen Kolben (21) aufweist, eine Auslasskammer (20), einen Druckkolben (5) mit mechanischer Steuerung nach einem beliebigen Steuergesetz durch einen Nocken oder einen Exzenter, der Brennstoff in eine Druckkammer (6) befördert, und mit einem Einspritzkolben (9), der ausschliesslich durch den in der Druckkammer (6) herrschenden Druck betätigt wird mit einer Rückholfeder (13), wobei dieser Kolben seinerseits den Brennstoff in eine Einspritzkammer (12) befördert, die zur Versorgung der Einspritzdüse (17) dient, dadurch gekennzeichnet, dass sie einen Druckregler (19) aufweist, der den Druck in der Druckkammer (6) begrenzt auf einen erhöhten, aber vorgeregelten Wert unabhängig von der Motorbetriebsweise und von dessen Belastung, dass der derart bestimmte konstante Druck in der Einspritzkammer (12) der Einspritzdüse (17) zugeführt wird und zur gleichen Zeit ihrer Auslasskammer (20), um ein Einspritzen zu verhindern, solange ein Elektroventil (26) das Beaufschlagen dieser Auslasskammer mit diesem Druck nicht verhindert, so dass eine sofortige Beaufschlagung des vorgeregelten konstanten Drucks zum exakten, elektrisch festgelegten Zeitpunkt erfolgt, und dass sie ausserdem ein einziges Drei-Wege-Elektronventil (26) aufweist, um sowohl die Vordosierung zu gewährleisten mittels verzögerter Verbindung der Einspritzkammer (12) mit dem Ladedruck (7) als auch die Bestimmung des Einspritzzeitpunktes durch Beseitigung des Drucks in der Auslasskammer (20) der Düse (17), wobei die gemeinsame Leitung (28) des Drei-Wege-Elektroventils (26) dazu mit der Auslasskammer (20) in Verbindung steht, während die beiden anderen Leitungen (27 und 29) mit der Einspritzkammer (12) bzw. mit dem Ladedruck (7) verbunden sind und die Erregung dieses Elektroventils (26) von einem einzigen Rechteckimpuls pro Zyklus gesteuert wird, dessen beide Flanken, die ansteigende Flanke (34) und die abfallende Flanke (35), von einer elektronischen Vorrichtung festgelegt sind, die unabhängig die Voreinspritzung und die vordosierte Menge regelt.
2. Einspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, dass sie Leitungen (31 und 33) im Einspritzkolben (9) und im Körper (1) aufweist, die derart angeordnet sind, dass sie gerade vor dem Hubende dieses Kolbens die Einspritzkammer (12) mit dem Ladedruck (7) verbinden, um so den Stauraum (16) der Einspritzdüse für ein schnelles Schliessen der Spindel (18) zu entleeren.
3. Einspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, dass sie zusätzlich andere Leitungen (30 und 32) im Einspritzkolben (9) und im Körper (1) aufweist, um die Druckkammer (6) mit der Auslasskammer (20) gerade vor dem Hubende des Einspritzkolbens (9) zu verbinden, welches dem Hubende des Druckkolbens (5) vorhergeht, um so die Auslasskammer (20) neu zu beschicken, um das Schliessen der Spindel (18) zu beschleunigen.
4. Einspritzpumpe nach einem der vorhergehenden Ansprüche, jedoch in Mehrfachausführung zur Versorgung eines Motors mit mehreren Zylindern, dadurch gekennzeichnet, dass jede der einem Zylinder zugeordneten Druckkammern in zwei Teile (6a, 6b) unterteilt ist, die durch eine Leitung (53) miteinander verbunden sind, wobei die ersten Teile (6a) und zugehörigen Bauteile (1 bis 5) zu einer einzigen Einheit mit gemeinsamer Nockenwelle (51) im Abstand von den Einspritzdüsen (17) zusammengebaut sind, und einen einzigen Druckregler (19) aufweist, der mit den verschiedenen Kammern (6a) durch Rückschlagventile (50) verbunden ist.
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 EP0077235A1 (de) 1983-04-20
EP0077235B1 true EP0077235B1 (de) 1985-08-14

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

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

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US5333786A (en) * 1993-06-03 1994-08-02 Cummins Engine Company, Inc. Fuel injection device for an internal combustion engine
US5438968A (en) * 1993-10-06 1995-08-08 Bkm, Inc. Two-cycle utility internal combustion engine
EP0962649A1 (de) * 1998-06-04 1999-12-08 Wolfgang Dr. Heimberg Kraftstoffeinspritzvorrichtung
AU4506799A (en) * 1998-06-04 1999-12-20 Wolfgang Heimberg Pumping device

Citations (1)

* 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

Family Cites Families (3)

* 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
US4250857A (en) * 1978-09-13 1981-02-17 The Bendix Corporation Fuel injector for producing shaped injection pulses
JPS6014910B2 (ja) * 1979-12-28 1985-04-16 株式会社デンソー 燃料噴射装置

Patent Citations (1)

* 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

Also Published As

Publication number Publication date
JPH0454064B2 (de) 1992-08-28
FR2514075A1 (fr) 1983-04-08
FR2514075B1 (de) 1983-12-23
EP0077235A1 (de) 1983-04-20
DE3265437D1 (en) 1985-09-19
JPS5874869A (ja) 1983-05-06

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