EP0898649B1 - Flüssigkraftstoffeinspritzvorrichtung für verbrennungsmotor - Google Patents

Flüssigkraftstoffeinspritzvorrichtung für verbrennungsmotor Download PDF

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Publication number
EP0898649B1
EP0898649B1 EP97924099A EP97924099A EP0898649B1 EP 0898649 B1 EP0898649 B1 EP 0898649B1 EP 97924099 A EP97924099 A EP 97924099A EP 97924099 A EP97924099 A EP 97924099A EP 0898649 B1 EP0898649 B1 EP 0898649B1
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EP
European Patent Office
Prior art keywords
injection
chamber
pressure
shut
liquid fuel
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EP97924099A
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English (en)
French (fr)
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EP0898649A1 (de
Inventor
Jean Frédéric Melchior
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Individual
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Individual
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    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection 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
    • 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
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/06—Other fuel injectors peculiar thereto
    • 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
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the present invention relates to a device injection of liquid fuel for combustion engine internal.
  • the injection of liquid fuel in an internal combustion engine includes fuel pressure setting means in the form of an injection pump capable of put fuel under cyclic pressure in a room of variable volume arranged in a pump cylinder and delimited by a piston actuated by a camshaft kinematically linked with the main shaft or engine crankshaft.
  • Compressed fuel is injected through an injection nozzle which communicates by a plurality injection holes, with the working chamber or combustion of the engine, this nozzle comprising a chamber which communicates with the cylinder of the injection pump, in general through unidirectional passage means such as a non-return valve. Communication between this room and the working room or combustion is interrupted by a sliding needle supported by the action of recall means elastic, on a conical seat arranged in said nozzle upstream of said injection holes.
  • This needle has a cylindrical body sliding in a bore arranged in the nozzle and diameter greater than that of the conical seat of the needle on its seat, so that when the fuel pressure exceeds a certain value, called set pressure of the injector, it lifts from its seat to allow injection.
  • set pressure of the injector a certain value
  • an injection device of the type proposed in FR-A-1 351 593 the fuel from the means of establishing pressure, such as a pump or accumulator, is addressed to an injection chamber delimited by a piston moving against a powerful spring, so filling the chamber with pressurized fuel during the non-injection phase.
  • This room is directly open on the injector cavity, in which move the sealing means, such as a needle, whose lifting can be controlled, either by a circuit independent hydraulic system, either by a circuit using the combustible.
  • the needle moves, on a long run, until it comes up against against the piston of the injection chamber, the latter as it advances which pushes back the fuel from the injection chamber to the injection nozzle, coming to close the needle.
  • DOS 1,944 862 an injection device comprising a chamber injection, in which a differential piston moves, and who is in direct communication with the injector, control means allowing, during the non-injection phase, filling the injection chamber against the pressure of an accumulator of fuel kept in charge by a high pump pressure.
  • this device has drawbacks notables.
  • the injection pressure is not that a fraction of the pressure supplied by the pump and the end of the piston injection stroke is ensured by a pressure drop difficult to obtain with precision, especially in the case of very high pressures.
  • an accumulator is constantly filled with fuel under high pressure by means of high pressure generators of combustible, and communicates permanently with the room of the injection nozzle upstream of the seat against which applies, thanks to control means, the range of the injection needle.
  • a distributor allows you to make communicate said room with another room bounded by the upper side of the needle, so the needle is pressed on its seat under the effect of the pressure prevailing in the accumulator.
  • the distributor is tilted, so as to communicate said chamber delimited by the upper face of the needle with low pressure supply means to drop the pressure exerted on the upper face of the needle, so that the needle lifts.
  • injection pressure is independent engine speed.
  • the invention proposes to remedy these disadvantages and provide an injection device allowing the fuel to be injected under high pressure, for practically the entire duration of the injection regardless of engine speed.
  • Another object of the invention is to realize such a device allowing, in an extremely simple, to deliver a precise and determined dose of fuel in a very short time and at very high pressure.
  • Another object of the invention is to realize such a device in which the injection can be secured under very strong pressure during the entire injection.
  • Yet another objective of the invention is to make such a device in which we can ensure very rapid injection using means relatively slow high pressure build-up.
  • Yet another objective of the invention is to make such a device with a reduced number of classic components and, in particular, to use a single pumping and metering element to supply a plurality of injectors, thus guaranteeing good balancing of the flows injected into the different cylinders.
  • Another object of the invention is to realize such a device in which we can do vary, in a simple way, the injection rate in progress injection, in particular to ensure the start of injection at low flow, then further injection at more high flow, according to the technique sometimes called spleen shaping.
  • Another objective of the invention is to obtain the advantages of common rail with a low level leak.
  • Another object of the invention is to reduce the energy consumption of the injection device.
  • Another objective of the invention is to obtain these advantages without the use of electronic means, poorly adapted to certain environments.
  • said movable element the wall delimits the aforesaid injection chamber, is formed by a piston sliding in a cylinder to delimit said room. Because the pressures of share and others of the piston can be practically balanced, the risk of leakage from the piston can be practically deleted.
  • the fluid under pressure contained in the volume and exerting its booster can be fuel kept under pressure in an accumulator.
  • the movable element or piston can be designed to seal any leaks between the room injection and said volume of liquid fuel under pressure, when applied to its stop.
  • the pressurized fluid can act on said mobile element by means of a multiplication means, in particular a differential piston.
  • the injection nozzle can advantageously be a conventional type nozzle, containing three cavities, know a first room or bag communicating by injection ports with the combustion chamber, a second bedroom communicating with the first bedroom and having a seat, said chamber being delimited by the lower part of a sliding needle, the end has a scope which may apply on said seat to interrupt this communication, and a third cylindrical chamber in which slides a part, forming a piston, of the needle, of so as to form a third above the needle room associated with control means.
  • the sealing means formed, for example, by such a needle, can be ordered, for their opening, by electromagnetic means like this is in itself known.
  • sealing means can be sensitive at the pressure of the liquid fuel in the cavity nozzle, for example the aforesaid second chamber, of so that when a high pressure is established in this cavity, the needle lifts up against its return means to a stop position.
  • This solution is preferred in the present invention and can be simply obtained by direct communication and permanent between said nozzle cavity and said chamber injection.
  • Said sealing means can be sensitive, for their closure, to a return spring.
  • They can also be sensitive, for their closing, by the action of a pressurized fluid, especially liquid fuel.
  • said means shutter can be sensitive, for their closure, to the direct action of the aforesaid movable element of the room injection, so that the movable element, when returns to its stop position, moves the sealing means to a sealing position.
  • This solution is particularly advantageous, because it ensures that the injection of liquid fuel sprayed into the combustion chamber is ensured at high pressure, including in the very last moments of the injection.
  • the stop of the movable element can then be constituted by said sealing means, such as the needle, when they arrive in their closed position.
  • said sealing means such as the needle
  • Fuel delivery means liquid under high pressure can be quite conventional and in particular include a simple pump usual alternative injection whose piston is in constant contact with the cam of a camshaft. advantageously this pump can be metered, for example by comprising, as is known for injection pumps, a helical discharge ramp and an adjustment of angular position of the pump piston.
  • said cyclic communication means arranged between said means for delivering liquid fuel under high pressure and said volume injection chamber variable include a one-way means of communication.
  • they may, in particular include a valve arranged upstream of said unidirectional means and arranged so as to put said means high pressure establishment in communication with a low pressure discharge, causing the closing of said unidirectional means, so that said metered amount of fuel can be determined by the duration of closure of said valve.
  • Said valve may simply be a valve two-way.
  • a valve preferably the above-mentioned valve disposed upstream of said unidirectional means, can be provided, to put said cavity in communication with a discharge to authorize the opening of said means shutter.
  • the same valve controls the setting to the discharge of said high establishment means pressure and said fuel-containing cavity liquid acting, for the closing operation, on said shutter means, so that when said valve is closed, said delivery means deliver the high pressure liquid fuel at said injection chamber through said communication means unidirectional, while the opening of said valve causes the end of said delivery and, simultaneously, authorizes the opening of said sealing means and injecting the fuel into the combustion chamber.
  • valve two tracks can be ensured by a rotating distributor classic pump and electrically controlled valve becomes useless.
  • the invention is remarkably suitable for when injecting liquid fuel into a several cylinders including injection nozzles specific to each cylinder.
  • the pump or means of delivery of high pressure liquid fuel is then connected separately to each nozzle by conduits identical specifics, and means are arranged for address the fuel successively to the different nozzles.
  • These means can be simply constituted of a single conventional dispenser pump and it's remarkable that we can advantageously connect this pump to a low pressure discharge by a single valve two-way whose simple command allows to determine all the operations of the injection cycles, less adopting the purely hydromechanical solution defined above.
  • the aforementioned means of recall elastic elements of the movable elements are preferably constituted by a single centralized means, for example, a single accumulator containing liquid fuel under high pressure and acting on said elements mobile, the mobile elements being preferably arranged in the respective nozzles in coaxial alignment with the means for closing said nozzles.
  • the aforesaid one-way means of communication are then advantageously arranged, individually, at each nozzle to reduce the quantity of fuel compressed and not injected.
  • the device can advantageously include means for bringing fuel from from the injection chamber to the nozzle cavity with a flow rate limited in such a way that at the start of the injection, the injection rate is equal to a determined rate from the injection chamber, reduced by a flow corresponding to the increase in volume in the cavity of nozzle caused, for example, by the lifting of the means sealing the injector.
  • This means can itself be a throttle slowing the evacuation of fluid from shutter control.
  • This means can possibly be arranged as a variable section choke so as to ensure lifting the needle according to a determined time profile.
  • the injection device described is associated to a cylinder 1 of a diesel engine, in which slides a piston 2 and delimiting, above it, a chamber combustion and working 3 closed by a cylinder head 4.
  • a cylinder head 4 Preferably placed centrally and coaxially to the chamber in which the driving piston 2 slides, is finds an injector 6 which can be produced in any way quite conventional.
  • This injector has a nozzle 7, the lower end of which opens into the chamber working 3 and which has an internal cavity forming a succession of three rooms, namely a first chamber or bag 8 of low volume, in communication permanent with working chamber 3 through holes injection 9, a second chamber 10 located above a conical seat 11 and a third cylindrical chamber 12 on the bottom, forming a stop, from which rests a spring 13 which pushes back towards the bearing surface 11 a conventional shutter needle 14 sliding in the cylindrical chamber 12, the front end of which, narrowed, has a bearing range 15 which is applied from tight against the seat 11.
  • the device also includes a pump 16 of a classic type allowing the establishment of a high fuel pressure.
  • This pump is made up a pump cylinder 17 in which can slide a delivery piston 18 returned to its neutral position bottom by a spring 19 against the cam 20 of a camshaft 21 kinematically attached to the crankshaft (not shown) of the motor.
  • the compression chamber 17 communicates via a conduit 22 in which is arranged a simple two-position valve 23 with the low pressure fuel supply 24.
  • the compression chamber 17 communicates directly with the aforesaid third bedroom 12 by through a conduit 25, opening into a conduit 30.
  • the device according to the invention comprises another cavity or injection chamber 26 in which slides a movable member 27, consisting of a piston, to encounter a powerful reminder 28, which could be a spring, but which is according to the invention a volume of pressurized fluid, for example a filled accumulator pressurized liquid fuel, preferably arranged to urge the piston 27 with force substantially constant throughout the useful stroke of the piston.
  • the injection chamber 26 communicates constantly with the aforesaid second chamber 10 via a conduit 29
  • the communication between room 26 and room compression 17 is provided by the conduit 31 in which is interposed a one-way valve 32.
  • the stop 33 achieves a sealing seat, so that in this position the piston 27, no leakage from accumulator 28 to the room 10 is not possible.
  • the operation is as follows.
  • the injection piston 27 moves back by compressing its elastic means 28 by force constant and storing in room 26 of the fuel from chamber 17.
  • valve at two positions 23 is quickly reopened as shown in figure 3.
  • Room 17 and third room 12 are immediately put on low pressure, notwithstanding a possible continuation of the descent of the pump piston 18. Immediately, the one-way valve 32 closes and room 26 is isolated from the room pumping 17.
  • the third bedroom 12 is low pressure, the high pressure prevailing in chamber 10 will raise the injection needle 14 which will compress its return spring 13, until it comes to rest on its upper stop, establishing communication, through the first chamber 8 and the injection orifices 9, with the engine working chamber. Consequently, the liquid fuel under high injection pressure is injected and sprayed into the working chamber.
  • Dosage and start of injection may be regulated independently of each other by the only control of a simple two-position valve 23.
  • the injection phases are, moreover, completely independent of the position of the cam 20.
  • Pump 16 can therefore be rustic and low flow since it has a large part of the engine cycle to deliver fuel to the chamber injection.
  • the pump 16 is not directly arranged to deliver an adjustable dose of fuel, this dose being quantified by the stroke of the piston 18 traveled during the valve closing time ⁇ t.
  • This embodiment is intended for injections in several stages, for example with a pre-injection, limiting leaks and losses mechanical, and minimizes the influence of compressibility of liquid fuel on operation of the device.
  • the conduit 30 is removed and the pipe 25 coming from the pump 16 opens through a one-way valve 32, directly in a room 34 which constitutes, at the times the second chamber of injector 12 and the chamber injector replacing chamber 26.
  • the needle has an extension 48 whose diameter is greater than that of the seat of the needle 14 and which is likely to slide through a hollow movable piston 50 forming the movable element of the injection chamber 34 and which can itself slide in a cylinder forming a chamber 35 into which a fuel accumulator opens liquid under high pressure 28.
  • Extension 48 has, in chamber 35, a flange 49, the diameter is significantly smaller than that of the chamber 35 and which allows the thrust of a spring to be received reminder 13 for the needle.
  • the upper end of the extension 48, beyond the flange, slides in a cylinder for determining the third chamber 12 of the needle to form a piston whose diameter is intermediate between that of the needle seat and that of the extension 48.
  • the first and second valves 23, 52 are closed and the pump 16 delivers fuel under strong pressure through the conduit 25 in the chamber 34 of so that the piston 50 moves in the direction of the arrow and pushes back the fuel located in the room 35 towards accumulator 28. All the forces formed by fuel and spring 13 on the needle 14 keeps it pressed against its seat 11. After the top dead center of the pump the valve 32 closes and the cam recovers compression energy from the volume of fuel contained in the chamber 17 and the conduit 25. The pressure in the different injector cavities 6 is then determined by the pressure in the accumulator 28. Opening the first valve 23 causes the valve to drop the pressure in the pump. We can then open the valve 52 as seen in Figure 6.
  • valve 52 You can then quickly close the valve 52, as shown in Figure 7, so that this first injection phase, which constitutes a pre-injection, ends, the needle 14 being pushed towards its seat, due to the increased pressure in chamber 12 and the action of spring 13.
  • the end of the injection is obtained, as the shows figure 8, when the entire injectable dose contained in room 34 was ejected and the piston 50 came into sealing abutment on its seat 33, so that the pressure in chamber 34, reduced at its minimum volume, drop and the needle closes quickly under the effect of spring 13 and pressure which is exerted on the differential surface between the extension 48 and the chamber 12.
  • the valve 52 is then closed.
  • Figures 9 to 12 represent embodiments in which the needle is closed positively by the movable element of the injection chamber.
  • Figure 10 shows a device similar to that of FIG. 9, but in which the needle 14 has a second bearing sealing 62 which cooperates with a seat provided in the room 12 and prevents leaks likely to come from of accumulator 28 by the clearance between needle 14 and the nozzle body 7.
  • the device of FIG. 11 is analogous to that of FIG. 9 except for the fact that the piston 27 abuts on a seat 33 in the injection chamber 26 after putting needle 14 in compression.
  • a short stroke spring 13 is shown in the chamber 12 so as to press the needle 14 onto its seat 11, even in the case where, the accumulator 28 is not under pressure, the piston 27 is not stressed.
  • length and diameter of the rod 37 are chosen so that the needle 14 is applied against its seat 11 by the piston 27 shortly before that it has reached its stop position 33, the rest of the needle descent being authorized by deformation under compressive stress of the rod 37.
  • Figure 12 is similar to that of Figure 5 except that the needle 14 is closed, as on the Figure 9, by the impact of the injection piston 50 on the stop 56 presented by the needle.
  • the nozzle, injection chamber and its movable element, and the pump generating the high pressure are coaxially aligned on the axis of the nozzle 7.
  • the piston 18 of the pump slides in a cylindrical chamber 17 defined inside the element mobile 65 with differential piston recalled in direction injection by the elastic return means constituted by the pressurized fluid 35, for example air, in communication with an accumulator 36.
  • Communication between the arrival of low pressure fluid by the valve at two channels 23 and the pump chamber 17 takes place at through a radial passage in the movable element 34 and communicating with the valve 23 via of a longitudinal light formed in the surface of the movable element 65.
  • the injection chamber 26 is arranged under the movable piston 65 and we see its end stop race 33.
  • the conduit 31 making it possible to communicate the pump 16 and the chamber 26 is an axial duct which runs in an extension 43 which exceeds, towards nozzle, beyond the active piston surface of the Exhibit 65 which delimits room 26 and which presents, at its free end, a radial notch 44.
  • a valve unidirectional 32 sealingly sliding on said extension 43 and normally applied against the face nozzle 7 by a spring such as, for example, a belleville washer. When this valve lifts the channel 31 puts the pump 16 in communication with the chamber 26.
  • the needle 14, which is represented in the figure in its raised position presents its upper end with respect to a volume 12 located under the end of the extension 43 containing the channel 31, volume also delimited by the valve 32 when it is in its closed position.
  • the cam 20 is in a position which allows the pump piston 18 to lift and suck fuel from the source low pressure 24 through valve 23 in position of communication so that the pump chamber 17 fill.
  • the cam 20 After a certain time, the cam 20 having turned, the piston 18 will move down. Has a instant t during this downward movement we close the two-way valve 23.
  • the fuel present in the pump will then be pressurized so that the valve 32 lifts against its return means and that the fuel pressurized in the pump is transferred to room 26, so the room mobile 65 lifts and the volume of chamber 26 increases, while high pressure is established in chamber 10, as well as in volume 12 located above of needle 14 through which the fuel gaining chamber 26. Needle 14 remains therefore strongly applied to its seat.
  • the piston 65 comes from the lower end of its end piece 43, make contact with needle 14 in its position raised shown in the figure.
  • the pursuit of lowering of the moving part 65 then drives the needle 14 down until it is applied to its seat, which allows a sudden closure of the needle while the pressure in chamber 10 remains still at its high value, so that we get a end of injection of excellent quality.
  • the moving part 65 goes down again slightly down, thanks to elastic compression of its extension 43 containing the channel 31 then stops definitively by contacting the stop 33.
  • the device shown is particularly compact and fuel paths at the outlet of the pump 16 are particularly reduced, which minimizes the influence of the compressibility of the fuel on the accuracy of the injected dose and also allows, in the case of an engine with several cylinders, to provide injection devices practically identical and therefore delivering doses practically identical in each cylinder, including during diets where only very small doses are injected.
  • two of the four injectors 6, of a device according to the invention designed for a four-cylinder engine are, for example, identical to that of FIG. 1.
  • the piston 27 of each injector delimits, by its other wall, a recall chamber 38. All of the booster 38 are connected directly to a single accumulator high pressure liquid fuel 39.
  • the device includes a pump common distributor 40 actuated by a motor shaft.
  • the pump 40 is of a conventional type for multi-cylinder engine injection devices and therefore does not need to be described. It includes a rotor 41 with four radial pistons 42 sliding in the pump cylinders 57 in which they move during the rotation of the rotor, under the effect of a cam fixed 58 whose known profile is determined by the number cylinders and therefore injectors 6.
  • the lower part of the rotor forms a distributor 59 capable of sending pressurized liquid fuel successively to the different injectors 6 by conduits 60 which replace the conduits 25 in FIG. 1 and terminate to the conduit 30 of the different injectors.
  • the pump chamber 57 communicates permanently with a central duct 61 connected to a fuel source low pressure 24 through a two-way valve positions 23, and in parallel, of a conduit 63 with a one-way valve 64.
  • This pump 40 can also be used to maintain the high pressure in the accumulator 39, through a set communicating with the conduit 61 and comprising a unidirectional means 46 and a conventional pressure control valve 47 for such accumulators, and connected to the accumulator by a conduit 45.
  • valve 23 makes it possible to address successively to each of the injectors 6 a quantity metered fuel which reaches via line 60 and the one-way valve 32 to the injection chamber 26 of the injector.
  • Each injector works as in the case of the device shown in Figures 1 to 4.
  • valve 23 In particular we can provide for replacement of valve 23 by the rotary distributor and using the return of the pump pistons to open injectors.
  • the injection advance will then be set by the angular position of the cams 58 of the pump 40 in a manner known per se.
  • a second nozzle 66 is arranged in the shutter needle lever control line 30 14.
  • nozzles 65 and / or 66, 67 could be functionally replaced by a adequate dimensioning (diameter and length, and by pressure loss consequence), lines 29 and 30.

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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 (34)

  1. Vorrichtung zum diskontinuierlichen und zyklischen Einspritzen von zerstäubtem flüssigem Kraftstoff unter hohem Druck in eine Verbrennungskammer (3) eines Verbrennungsmotors mit variablem Arbeitsvolumen, aufweisend
    eine Einspritzdüse (7), die für jede Arbeitskammer aufweist:
    Einen Düsenhohlraum (10, 34), der mit der Verbrennungskammer durch zumindest eine Einspritzöffnung (9) in Verbindung steht,
    Verschlussmittel (14) zum zyklischen Unterbrechen und Wiederherstellen der Verbindung zwischen dem Düsenhohlraum (10, 34) und der Verbrennungskammer (3),
    und Mittel (46) zum Fördern von flüssigem Kraftstoff unter hohem Druck, die dazu ausgelegt sind, eine dosierte Menge von flüssigem Kraftstoff unter hohem Druck zyklisch zu fördern,
    wobei die Fördermittel (16, 40) durch die zyklischen Verbindungsmittel mit einer Verbrennungskammer (26, 34) variablen Volumens verbunden sind, die durch eine Wand eines beweglichen Elements (27, 50, 65) begrenzt ist, das bei jedem Zyklus durch elastische Rückstellmittel (28, 36, 39) bis zu einem feststehenden Anschlag (33, 37, 56) unter Bereitstellung des minimalen Werts des variablen Volumens der Einspritzkammer rückgestellt wird, und die dauerhaft mit dem Düsenhohlraum (10, 34) verbunden ist, wobei die Einspritzkammer dazu bestimmt ist, vorübergehend die dosierte Kraftstoffmenge aufzunehmen, wobei eine Einspritzkammer (36, 34) für jede Arbeitskammer vorgesehen ist,
    wobei die dosierte flüssige Kraftstoffmenge zyklisch durch die Fördermittel (16, 40) in der Einspritzkammer während der zyklischen Verschließphase der Verschlussmittel (14) der Einspritzdüse gefördert wird,
    dadurch gekennzeichnet, dass die elastischen Rückstellmittel ein druckfreies Fluidvolumen umfassen, das auf das mobile Element einwirkt.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die elastischen Rückstellmittel (28, 36, 39) einen Sammelbehälter für unter Druck stehendes Fluid umfassen.
  3. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die bewegliche Wand durch einen Kolben (27, 50, 65) gebildet ist, der in einem Zylinder gleitverstellbar vorgesehen ist.
  4. Vorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Düsenhohlraum und die Einspritzkammer eine gemeinsame Kammer (34) bilden.
  5. Vorrichtung nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass der Kolben (50) ein ausgenommener Kolben ist, der dazu ausgelegt ist, um einen Teil (48) der Verschlussmittel (14) herum zu gleiten.
  6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die elastischen Rückstellmittel (28, 36, 39) des beweglichen Elements (27, 50, 65) das bewegliche Element mit einer im wesentlichen konstanten Kraft während der gesamten Einspritzung der Kraftstoffdosis zurückdrängen, die in der Einspritzkammer (26, 34) enthalten ist.
  7. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass zum Variieren der Austragmenge des eingespritzten Kraftstoffs Querschnittsverminderungsmittel (65) derart vorgesehen sind, dass das durch die Verschlussmittel (14) verschobene Volumen während seiner Öffnung die Austragmenge in der Kammer bei Einspritzbeginn verringert, wobei die normale Austragmenge erreicht ist, wenn die Verschlussmittel (14) die feststehende Anschlagposition einnehmen.
  8. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass Mittel (66, 67) zur konstanten oder variablen Querschnittsverminderung am Durchlass (30) vorgesehen sind, der mit einer Steuerkammer (12) der Verschlussmittel (14) verbunden ist, um die Anhubgeschwindigkeit der Verschlussmittel zu steuern.
  9. Vorrichtung nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass das bewegliche Element (27, 65) mit einem Anschlag (33) zusammenwirkt, der die Funktion eines Abdichtungssitzes sicherstellt, der die Leckage zwischen der Einspritzkammer und dem unter Druck stehenden Rückstellfluid begrenzt.
  10. Vorrichtung nach einem der Ansprüche 2 bis 9, dadurch gekennzeichnet, dass das unter hohem Druck stehende Fluid, das in einem Sammelbehälter (28, 36, 39) mit im wesentlichen konstantem Druck enthalten ist, der flüssige Kraftstoff ist.
  11. Vorrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass die Verschlussmittel (14) der Düse auf eine Druckdifferenz zwischen dem Düsenhohlraum (10, 34) und einem Steuerhohlraum (12) ansprechen.
  12. Vorrichtung nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass die Verschlussmittel (14) durch elektromagnetische Mittel gesteuert sind.
  13. Vorrichtung nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die Verschlussmittel (14) für ihren Schließvorgang auf eine Rückstellfeder (13) ansprechen.
  14. Vorrichtung nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass die Verschlussmittel (14) für ihren Verschließvorgang auf die Wirkung eines unter Druck stehenden Fluids, insbesondere des flüssigen Kraftstoffs ansprechen.
  15. Vorrichtung nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass die Verschlussmittel (14) für ihren Verschließvorgang auf die Wirkung des beweglichen Elements (27, 50) derart ansprechen, dass das bewegliche Element (43), wenn es seine Anschlagposition erreicht, die Verschlussmittel (14) in Richtung auf eine Abdichtungsposition verschiebt.
  16. Vorrichtung nach Anspruch 15, dadurch gekennzeichnet, dass der feststehende Anschlag (37, 56) des beweglichen Elements (27, 50) durch die Verschlussmittel (14) in ihrer verschlossenen Position gebildet ist.
  17. Vorrichtung nach Anspruch 15, dadurch gekennzeichnet, dass das bewegliche Element (27, 50) die Verschlussmittel (14) auf ihrem Sitz (14) vor Erreichen ihres Anschlags (33) unter Druck setzt.
  18. Vorrichtung nach einem der Ansprüche 1 bis 17, dadurch gekennzeichnet, dass die Fördermittel für unter Druck stehenden flüssigen Kraftstoff eine Kolbenpumpe (16, 40) umfassen, die durch eine durch den Motor angetriebene Welle betätigt ist.
  19. Vorrichtung nach Anspruch 18, dadurch gekennzeichnet, dass die Pumpe eine Dosierpumpe, insbesondere vom Rampen-Typ mit spiralförmigem Ablauf und Regelung der Winkelposition des Kolbens ist.
  20. Vorrichtung nach einem der Ansprüche 1 bis 19, dadurch gekennzeichnet, dass die zyklischen Verbindungsmittel, die zwischen den Fördermitteln (16, 40) für unter hohem Druck stehenden Kraftstoff und der Einspritzkammer (26, 34) mit variablem Volumen ein Einwegverbindungsmittel (32) umfassen.
  21. Vorrichtung nach Anspruch 20, dadurch gekennzeichnet, dass die zyklischen Verbindungsmittel ein Ventil (23) umfassen, das stromaufwärts von dem Einwegverbindungsmittel (32) angeordnet und derart ausgelegt ist, dass die Mittel zum Bereitstellen von hohem Druck in Verbindung mit einem Austrag (24) unter niedrigem Druck das Verschließen der Einwegverbindungsmittel derart auslöst, dass die dosierte Kraftstoffmenge durch den durch den Pumpenkolben während der Verschließdauer des Ventils (23) zurückgelegten Weg bestimmt ist.
  22. Vorrichtung nach Anspruch 21, dadurch gekennzeichnet, dass das Ventil (23) ein Zweiwegeventil ist.
  23. Vorrichtung nach Anspruch 14, für sich genommen oder in Kombination mit einem der Ansprüche 17 bis 21, dadurch gekennzeichnet, dass ein Hohlraum (12), der flüssigen Kraftstoff enthält, auf den die Verschlussmittel (14) für ihren Schließvorgang ansprechen, dazu ausgelegt ist, in Verbindung mit einem Austrag (24) mittels eines Ventils (23, 52) gebracht zu werden, um das Öffnen der Verschlussmittel zu ermöglichen.
  24. Vorrichtung nach einem der Ansprüche 21 bis 23, dadurch gekennzeichnet, dass dasselbe Ventil (23) die Durchführung des Austrags (24) der Mittel (16) zum Bereitstellen von hohem Druck und des Hohlraums (12) steuert, der den flüssigen Kraftstoff enthält, der für die Schließposition auf die Verschlussmittel (14) derart einwirkt, dass das Ventil geschlossen ist, wobei die Verbrennungsmittel den flüssigen Kraftstoff unter hohem Druck zu der Einspritzkammer (26) durch die Einwegverbindungsmittel (32) fördert, wobei die Öffnung dieses Ventils das Ende der Förderung auslöst und gleichzeitig die Öffnung der Verschlussmittel bis zu ihrem Anschlag und das Einspritzen des Kraftstoffs in die Verbrennungskammer freigibt.
  25. Vorrichtung nach Anspruch 23, dadurch gekennzeichnet, dass der Hohlraum (12), der den flüssigen Kraftstoff enthält, der für die Schließposition auf die Verschlussmittel (14) einwirkt, in Verbindung mit einem Volumen (28, 35) steht, das unter Druck stehenden Kraftstoff enthält, der als elastisches Rückstellmittel des beweglichen Elements (50) wirkt.
  26. Vorrichtung nach Anspruch 25, dadurch gekennzeichnet, dass die Kammer (12), die flüssigen Kraftstoff enthält, auf den die Verschlussmittel für ihre Steuerung ansprechen, dazu ausgelegt ist, mit einem Austrag (24) durch ein zweites Ventil (52) in Verbindung stehen, und dass die Verbindung der Kammer (12) mit dem unter Druck stehenden Kraftstoffvolumen (35, 28) auf ein Mittel zur Querschnittsverminderung einwirkt.
  27. Vorrichtung nach Anspruch 24, dadurch gekennzeichnet, dass das Profil der Nocke, die auf den Kolben einwirkt, einen flachen Teil aufweist, der es erlaubt, den Druck in dem Hohlraum (12) aufrechtzuerhalten, auf welchem die Verschlussmittel ansprechen, so dass der Öffnungszeitpunkt des Ventils und dadurch der Einspritzzeitpunkt auf dem flachen Teil gewählt werden können, indem er vom Ende der Befüllung der Einspritzkammer verschoben wird.
  28. Vorrichtung nach Anspruch 10, für sich genommen oder in Verbindung mit einem der Ansprüche 11 bis 27, wobei die Mittel zum Bereitstellen des hohen Drucks eine Kolbenpumpe umfassen, dadurch gekennzeichnet, dass die Verschlussmittel für ihren Öffnungsvorgang auf den Druckabfall ansprechen, der durch den Rückstellhub des Pumpenkolbens zur Bereitstellung des hohen Drucks ausgelöst ist.
  29. Vorrichtung nach einem der Ansprüche 1 bis 28, dadurch gekennzeichnet, dass die Einspritzdüse und die Einspritzkammer (26, 34) koaxial fluchten.
  30. Vorrichtung nach Anspruch 23, dadurch gekennzeichnet, dass das Mittel (16) zum Bereitstellen des hohen Drucks koaxial mit der Einspritzdüse fluchtet.
  31. Vorrichtung nach einem der Ansprüche 1 bis 30, dadurch gekennzeichnet, dass sie für einen Motor mit mehreren Arbeitskammern mehrere Einspritzdüsen (6) und gemeinsame zentrale Mittel (40) zur Förderung und Dosierung des flüssigen Kraftstoffs unter Druck aufweisen, die jeweils bzw. getrennt mit jeder Düse durch eine im wesentlichen identische spezielle Leitung (60) verbunden sind, wobei die Mittel zum Bereitstellen des hohen Drucks dazu ausgelegt sind, den unter hohem Druck stehenden flüssigen Druck sukzessive an die Düsen anzulegen.
  32. Vorrichtung nach Anspruch 31, dadurch gekennzeichnet, dass die elastischen Rückstellmittel der beweglichen Elemente (27) einen gemeinsamen Sammelbehälter (39) umfassen, der den unter hohem Druck stehenden flüssigen Kraftstoff enthält und auf die beweglichen Elemente (27) einwirkt.
  33. Vorrichtung nach Anspruch 32, dadurch gekennzeichnet, dass die gemeinsamen und zentralen Mittel (40) zur Förderung des unter hohem Druck stehenden flüssigen Kraftstoffs mit dem Sammelbehälter (39) verbunden sind, um die Aufrechterhaltung des hohen Drucks in diesem Sammelbehälter aufrechtzuerhalten, und zwar über einen Druckregler und ein Einweg(verbindungs)mittel.
  34. Vorrichtung nach Anspruch 32 oder 33, dadurch gekennzeichnet, dass die Mittel (40) zum Bereitstellen des hohen Drucks durch eine gemeinsame Pumpe (40) gebildet sind, die dem Verteiler (59) zugeordnet bzw. mit diesem verbunden ist, und dass die Pumpe mit einem Niederdruckversorgungsmittel durch ein Ventil (23) verbunden ist, welches sukzessive die Funktion sämtlicher Einspritzdüsen der Vorrichtung sicherstellt.
EP97924099A 1996-05-17 1997-05-14 Flüssigkraftstoffeinspritzvorrichtung für verbrennungsmotor Expired - Lifetime EP0898649B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9606159 1996-05-17
FR9606159A FR2748783B1 (fr) 1996-05-17 1996-05-17 Dispositif d'injection de combustible liquide pour moteur a combustion interne
PCT/FR1997/000861 WO1997044583A1 (fr) 1996-05-17 1997-05-14 Dispositif d'injection de combustible liquide pour moteur a combustion interne

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EP0898649A1 EP0898649A1 (de) 1999-03-03
EP0898649B1 true EP0898649B1 (de) 2002-08-14

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CN (1) CN1077220C (de)
DE (1) DE69714722T2 (de)
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WO (1) WO1997044583A1 (de)

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CN100353050C (zh) * 2004-09-30 2007-12-05 浙江大学 缸内直喷式发动机燃料高压产生装置
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US8496191B2 (en) * 2008-05-19 2013-07-30 Caterpillar Inc. Seal arrangement for a fuel injector needle valve
DE102010062883A1 (de) * 2010-09-14 2012-04-26 Robert Bosch Gmbh Verfahren zum Betreiben einer Einspritzanlage
EP2844875B1 (de) * 2012-05-01 2020-09-02 Eaton Corporation Druckausgleichssteuerung einer verdrängerpumpe mit fester verdrängung in einem pump- und messsystem sowie zugehöriges verfahren
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CN104061213A (zh) * 2014-05-18 2014-09-24 胡千桥 一种球状气体、蒸汽、液体粒子流生成技术
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WO1997044583A1 (fr) 1997-11-27
CN1223711A (zh) 1999-07-21
FR2748783A1 (fr) 1997-11-21
DE69714722T2 (de) 2003-04-24
FR2748783B1 (fr) 1998-08-14
US6152109A (en) 2000-11-28
EP0898649A1 (de) 1999-03-03
DE69714722D1 (de) 2002-09-19
CN1077220C (zh) 2002-01-02

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