EP0375928B1 - Dispositif d'injection de combustible - Google Patents

Dispositif d'injection de combustible Download PDF

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Publication number
EP0375928B1
EP0375928B1 EP89121483A EP89121483A EP0375928B1 EP 0375928 B1 EP0375928 B1 EP 0375928B1 EP 89121483 A EP89121483 A EP 89121483A EP 89121483 A EP89121483 A EP 89121483A EP 0375928 B1 EP0375928 B1 EP 0375928B1
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EP
European Patent Office
Prior art keywords
working
piston
space
pressure
working 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.)
Expired - Lifetime
Application number
EP89121483A
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German (de)
English (en)
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EP0375928A3 (en
EP0375928A2 (fr
Inventor
Helmut Rembold
Ernst Linder
Manfred Dr. Wier
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0375928A2 publication Critical patent/EP0375928A2/fr
Publication of EP0375928A3 publication Critical patent/EP0375928A3/de
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Publication of EP0375928B1 publication Critical patent/EP0375928B1/fr
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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
    • F02M59/18—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps characterised by the pumping action being achieved through release of pre-compressed springs
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps 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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies

Definitions

  • the invention is based on a fuel injection device according to the preamble of claim 1.
  • a fuel injection device is known from DE-B 11 40 404.
  • the working piston is actuated by a drive piston, which is designed as a stepped piston and comes with its small end face to bear against the working piston and is acted upon on its rear side by the drive spring, which is introduced by pressure medium in the separate working space between the drive piston and the stepped bore receiving it is compressible.
  • the suction stroke of the pump piston and the delivery stroke of the pump piston are controlled by a mechanically controlled valve which, in its one position, allows pressure medium to flow into the separate working chamber for pretensioning the return spring, whereby the pump piston also advances fuel into the pump working chamber to carry out its suction stroke following the drive piston and in its other position relieves the separate work space via a branch line, whereby the delivery stroke of the pump piston is started.
  • the delivery stroke begins only after the fuel feed opening in the wall of the working space is closed by means of the front edge of the pump piston.
  • the pump work chamber is connected to the fuel injection nozzle via a pressure control valve and, after a variable delivery stroke of the pump piston, can be relieved by a relief line running in the pump piston.
  • the variable delivery stroke can be mechanically fixed by an adjusting screw due to the rotary position of the pump piston.
  • the fuel injection quantity that is delivered to the injection nozzle under high pressure can thus be set.
  • the valve in the pressure medium line which establishes the connection between the pressure medium line and the branch line, determines the start of high-pressure delivery. This beginning of the High-pressure delivery can be set mechanically by changing the assignment of the valve member of the valve to its drive.
  • the known injection pump has a relatively complex structure, but does not offer a universal adjustability of the start of injection and fuel injection quantity that can be changed during operation of the fuel injection pump as a function of operating parameters.
  • the invention aims to provide a fuel injection device with which the start of injection and fuel injection quantity can be precisely adjusted independently of one another during the operation of the fuel injection pump.
  • the training can be such that the separate working space of the working piston is connected via a pressure medium line with the interposition of a Filling solenoid valve and / or a distributor valve can be acted upon by pressure medium from a pressure medium source.
  • the second, electrically controlled valve can be actuated to relieve the load on the separate work area, and the injection process can be divided into several partial injections by intermittent work load relief.
  • the training is advantageously made such that the relief line of the separate working chamber of the working piston opens into the fuel supply line to the nozzle chamber, with a sufficient lifting volume having to be ensured for a corresponding lifting movement of the working piston for carrying out the injection.
  • the control of the injection process can, as already mentioned above, take place via a control bore connecting the end face of the working piston facing the nozzle space with a location of the jacket, for which purpose a corresponding bore in the cylinder of the working piston must naturally be provided as an overflow opening.
  • the same overflow bore or control bore on the wall of the cylinder can also be used for other purposes and the design according to the invention is advantageously made such that a control bore is arranged within the maximum displacement path of the working piston in the cylinder wall surrounding it, which is provided by a the end face of the working piston delimiting the separate working space and / or the control bore or groove connected to the end face of the working piston facing the nozzle space can be ground.
  • a structurally particularly simple design for supplying the nozzle chamber with fuel can be achieved in that the check valve is arranged in the fuel supply line for the nozzle chamber in an axial bore or opening in the working piston and in that the fuel supply line is connected to the spring chamber of the working piston.
  • the fuel supply can be over the spring chamber of the working piston take place, but in this case care must be taken that this spring chamber may only be filled with low pressure, which must also be kept constant by means of a pressure control valve, so as not to impede the loading stroke of the working piston.
  • the design can be such that a common feed pump with a lower delivery pressure than the opening pressure of the injection nozzle is arranged for the pressure medium supply line to the separate work space and the fuel supply line to the nozzle space.
  • a separate high-pressure side for the loading and tensioning of the spring is dispensable and it is only necessary to install a check valve which closes to the line in the separate work space when the same is relieved, when using a common feed line to the nozzle needle space and the separate work space of the working piston to ensure safe ejection.
  • the stepped piston which is preferably used can be formed in two parts in a particularly simple manner, the two parts of the working piston being mounted such that they can be pressed resiliently against one another.
  • the smaller part of the working piston facing the nozzle space can be supported by a spring in the interior of the injection nozzle space.
  • a supply of several such working pistons, each associated with an injection nozzle, can be achieved in a conventional manner via a distributor shaft, whereby when using accumulators in the high-pressure side for the supply of pressure medium to the separate working space, several such working pistons can also be preloaded simultaneously, or as it is it also appears preferred that the loading or tensioning of a spring of a working piston of an injection nozzle can take place to an extent which is at least two pre-injections and / or main injections by next loading or tensioning of the spring loading the piston.
  • the design is advantageously made such that the pressure medium source for acting on the separate working space of the working piston as a high-pressure pump connected in particular to a storage unit is trained.
  • the use of high pressure for the bias of the spring or the loading of the pressure accumulator enables extremely rapid tensioning, and the fact that such a pressure medium source with high pressure only for loading or tensioning the spring, but not during the actual injection process to achieve the Injection is used, leads to a perfect separation of high pressure lines from the injection process.
  • the design can be made in a simple manner so that the pressure medium source for acting on the separate working space of the working piston is designed as a single-cylinder eccentric pump, the drive shaft of which is equipped with a rotatable distributor valve in the Pressure medium line is coupled to the separate working space of the working piston.
  • the injection quantity for several injection processes and the corresponding compression quantities are stored in advance with each loading process, and with such an embodiment, pre-injection processes can be relocated far into the intake stroke of the individual cylinders via the rotatable distributor valve. Due to the size of the working area of the pump, an additional storage can be dispensed with.
  • 1 shows a first embodiment of a fuel injection device according to the invention
  • 2 shows a modified embodiment of a fuel injection device according to the invention
  • 3 shows a further modified embodiment, in which the fuel is fed into the nozzle chamber via the spring chamber of the working piston
  • 4 shows an embodiment of a fuel injection device according to the invention, in which the pressure medium supply to the separate work space and the fuel supply to the nozzle space takes place via a common feed pump
  • 5 shows a diagram of the injection times of an internal combustion engine with four cylinders with a fuel injection device according to FIG.
  • FIG. 4 shows a two-part working piston for arrangement in a fuel injection device according to the invention
  • 7 shows a design with a single-cylinder eccentric pump
  • 8 shows a section through a distributor shaft used in an embodiment according to FIG. 7
  • FIG. 9 shows a diagram of the injection times in a configuration according to FIGS. 7 and 8.
  • 1 denotes an injection nozzle, in the nozzle chamber 2 of which a nozzle needle 3 releases 5 injection openings against the force of a spring 4 when appropriately loaded with fuel under high pressure by lifting off a valve closing member.
  • Fuel is fed into the nozzle chamber or nozzle needle chamber 2 from a tank 6 by a pump 7 via a check valve 9 which is switched into the supply line 8, a pressure relief valve 11 being provided in a bypass 10 of the pump 7.
  • the supply pressure of the fuel supplied via line 8 is below the opening pressure for the nozzle needle.
  • the nozzle space 2 is filled with fuel and at the same time the nozzle space 3 or spring space 2 of the nozzle needle 3 is flushed via a channel 13 provided in a metering piston 12 designed as a stepped piston, which connects the Work chamber 14 facing the nozzle chamber 2 of the stepped piston 12 with a control groove or annular groove 16 provided on the jacket of the guide bore 15 of the stepped piston 12.
  • the return of fuel introduced into the nozzle chamber 2 and the working chamber 14 into a return or a tank takes place via the channel 13 and the control bore or groove 16 via a further check valve 17.
  • the stepped piston 12 is held in its initial position by a spring 18.
  • pressure medium is fed via a pressure line 19 under a pressure of, for example, 250 bar into a separate and larger diameter working chamber 20 of the working piston 12.
  • the pressure medium under such a high pressure is fed from a high-pressure pump 21 via a check valve 22 to a reservoir 23, from which the pressure medium via a solenoid valve 24 and a distributor shaft 25 coupled in a simple manner to the high-pressure pump 21 through the respective line 19 via Check valve 26 is fed to the separate working space 20 of the metering piston or working piston 12.
  • the distributor shaft 25 is coupled to the drive of the high-pressure pump 21, as indicated by the shaft 27, and depending on the rotational position of the distributor shaft 25 when the solenoid valve 24 is open, there is a connection between the pressure accumulator 23 or the high-pressure pump 21 and the Larger diameter working chamber 20 of a certain working piston 12.
  • the quantity supplied to the working chamber 20 and thus the extent of the displacement movement of the working piston 12 can be adjusted according to the requirements via the solenoid valve 24, as a result of which the fuel quantity subsequently available for injection in Nozzle room 2 and in the working room 14 is set.
  • a relief line 28 is off the space 29 accommodating the spring 18 and facing away from the working spaces 20 and 14 is provided in the tank 6.
  • a branch line 30 is connected to the line 19 between the check valve 26 and the separate working space 20 of the working piston 12, in which a solenoid valve 31 and a check valve 32 are provided in series.
  • the solenoid valve 31 i.e. when the connection between the separate working space 20 of the working piston 12 and the tank 6 is opened, the spring 18 pushes the metering piston 12 in the direction of the nozzle needle 3, as a result of which the fuel contained in the space 14 and in the nozzle space 2 is pressurized. After exceeding the nozzle opening pressure, a corresponding amount is sprayed out via the nozzle needle opening outwards.
  • a reaction in the feed line 8 is avoided during the pressure build-up and the injection process, just as the check valve 26 in the feed line to the separate working space 20 of the working piston 12 prevents feedback to the distributor shaft 25 or to the solenoid valve 24.
  • the injection process can take place by re-closing the solenoid valve 31, so that the injection process can be easily separated into a pre-injection and main injection by specifying the opening time and the opening duration of the solenoid valve 31.
  • the injection process can be ended at any time before this, in any case ending of the injection, by closing the solenoid valve 31.
  • the time of injection is thus determined via the solenoid valve 31, while the injection quantity is determined both via the Duty cycle of the solenoid valve 24 and thus the filling time of the separate working space 20 of the working piston as well as the duty cycle of the solenoid valve 31 can be determined.
  • the advantage of the injection resulting from the targeted relief of the metering piston or working piston 12 is that after the working piston 12 has been preloaded there is no longer a connection to the high-pressure accumulator 23 via the distributor shaft 25, so that any pressure waves that occur no longer have a disruptive influence on the injection quantity exercise.
  • the connection to the feed pump 7, which can be designed as an electric fuel pump, is closed via the check valve 9, so that in the nozzle space 2 and the associated work space 14 of the working piston 12 defined amount of fuel with a predetermined pressure is included.
  • FIG. 2 shows a modified embodiment of the fuel injection device, in which the metering via the solenoid valve upstream of the distributor shaft 25 is dispensed with.
  • the working piston is now prestressed up to an upper stop 33 in accordance with the rotational position of the distributor shaft.
  • the filling of the nozzle needle chamber 2 or of the working chamber 14 takes place analogously to the design according to FIG. 1.
  • a discharge line 34 is connected to the nozzle chamber 2, which in a shaft position of a 2/3 solenoid valve 35 corresponding to the prestressed position of the working piston 12 with the branch line 30 to the tank 6 upstream of the the non-return valve 32 holding the rinsing pressure is connected.
  • This solenoid valve 35 serves at the same time as a relief valve of the working chamber 20 of the working piston 12, which is of a larger diameter, the injection timing and the injection quantity being determined only via the solenoid valve 35 by the switch-on time and the switch-on duration will. Appropriate control can again be used to separate the injection into the pre-injection and the main injection.
  • the stroke of the working piston 12 is chosen so that the lower stop, ie a complete relief of the working space 20 is not reached.
  • the 3/2-type solenoid valve also provides the defined relief of the nozzle interior 2 to end an injection.
  • fuel is supplied into the working space 14 or the nozzle space 2 via the space 29 receiving the spring 18 for acting on the working piston 9 via an essentially axial channel 36 inside the working piston 12, which is a for Room 29 and check valve 37 closing to the supply line 8.
  • the biasing of the working piston 12 by introducing pressure medium under high pressure takes place as in the embodiment according to FIG. the metering piston or working piston 12 is moved to its upper stop.
  • the relief of the separate working space 20 and thus the initiation of an injection process takes place in turn via a solenoid valve 38, which is designed in a simple manner as a 2/2 valve, the relief line 30 connected to the feed line 19 in this exemplary embodiment in the spring chamber 29 of the working piston 12 flows.
  • a common pressure medium source 39 is used for prestressing the working piston 12, that is to say for filling the separate and larger diameter working chamber 20 and for filling the nozzle chamber 2 and the working chamber 14 of the working piston 12
  • a low pressure pump with a maximum pressure of about 60 bar is formed. It is important that this maximum pressure of the low pressure pump 39 below the nozzle opening pressure of about 120 bar.
  • a reservoir 23 is used again, and the working piston 12 is filled and preloaded again via a distributor shaft 25. In this embodiment, the separate pump for the fuel supply to the interior of the nozzle is therefore omitted.
  • a line 40 leading into the nozzle chamber 2 and to the working chamber 14 of the working piston is connected to the feed line 19, in which a check valve 41 that closes to the outside is provided, which takes over the function of the check valve 9 of the previous embodiments.
  • a solenoid valve 42 is again used, which is arranged in a branch line 30 of the pressure line 19 according to FIG. 1 upstream of the check valve 32.
  • the pressure generated by the spring 18 acting on the working piston 12 when the work chamber 20 is relieved should be approximately 200 bar, this being achieved by appropriate dimensioning of the step surface, i.e. can be realized by appropriate dimensioning of the piston surfaces facing the working space 14 or 20.
  • FIG. 5 schematically shows an injection diagram of an internal combustion engine equipped with four cylinders, which has a fuel injection device according to the configuration according to FIG. 4.
  • the crankshaft angle is plotted on the abscissa and the corresponding angular ranges for the individual cylinders are in which the working piston 12 is prestressed and in which a prestressing or. a main injection takes place, made visible by different hatching.
  • the position of the solenoid valve 42 assigned to a first cylinder is also indicated, with a pre-injection or main injection taking place in the open position of the solenoid valve 42.
  • the spring 46 which acts on the piston 44 facing the nozzle needle 3 is supported on the housing of the injection nozzle 1 in a manner fixed to the housing.
  • appropriate dimensioning of the spring forces of the springs 45 and 46 and the dimensions of the pistons 43 and 44 must ensure that the piston facing the nozzle needle 3 is taken care of 44 acting pressure is not sufficient for a corresponding displacement of the piston 44 in the direction of the nozzle needle, in order to a pressure exceeding the opening pressure of the nozzle needle 3 Build work room 14 or nozzle room 2. Rather, for a defined mode of operation, the spring 46 should be dimensioned sufficiently to ensure that the piston 44 abuts the piston 43 even when the piston 43 is preloaded.
  • FIG. 7 A solution is now shown in FIG. 7 in which this is realized with a single-cylinder eccentric pump, the basic structure of which corresponds to the known prior art.
  • a drive shaft 48 with a drive cam 49 is mounted in bearings 50 in a pump housing 47, a pump piston 51 being actuated by the drive cam.
  • a storage piston 53 is integrated directly into a screw plug 52 that closes the pump work chamber 58 in front of the pump piston 51 and is biased by a spring 54 in accordance with a response pressure on the part of the pump work chamber 58 of approximately 60 bar.
  • FIG. 8 shows a section through the distributor shaft 25 used in the embodiment of the pump according to FIG. 7 with the control angle of the distributor shaft 25 related to the individual cylinders.
  • a distributor bore 56 can be seen, which is connected to individual feed lines 19 to the cylinders in the corresponding rotational position of the distributor shaft in each case over an angular range correspondingly defined by control grooves 57.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (8)

  1. Pompe d'injection de carburant avec un piston de travail (12), qui délimite dans un alésage de guidage (15) une chambre de travail (14), laquelle est reliée à un injecteur (1) et par l'intermédiaire d'une canalisation d'alimentation en carburant (8) à une source d'alimentation en carburant (7), ce piston de travail (12) étant susceptible d'être déplacé par un ressort (18) dans le sens du refoulement et par un fluide sous pression d'une source de fluide sous pression contre l'action du ressort dans le sens de la course d'aspiration, ce fluide sous pression étant amené par l'intermédiaire d'une canalisation de fluide sous pression (19) comportant une première vanne commandée (24, 25) dans une chambre de travail séparée (20) ménagée entre une partie du piston de travail à gradins (12) et un alésage de guidage (15) recevant la partie de plus grand diamètre du piston de travail à gradins, et ce fluide sous pression étant susceptible d'être déchargé par l'intermédiaire d'une canalisation dérivée (30) comportant une autre vanne commandée (31), pour commander la course de refoulement du piston de la pompe, pompe d'injection de carburant caractérisée en ce qu'une chambre de travail (14) est directement reliée à l'injecteur (1), en ce qu'une soupape de retenue (9) ouvrant en direction de la chambre de travail (14) est disposée sur la canalisation d'alimentation en carburant (8), et en ce qu'entre la première vanne commandée (25, 24) et la ramification de la canalisation dérivée (30), à partir de la canalisation de pression (19), est disposée une soupape de retenue (26) fermant dans la direction de la première vanne commandée, la première vanne commandée (24, 25) et l'autre vanne commandée (31) étant des vannes commandées électriquement.
  2. Dispositif d'injection de carburant selon la revendication 1, caractérisé en ce que la chambre de travail séparée (20) du piston de travail (12) est susceptible d'être alimentée en fluide sous pression à partir d'une source de fluide sous pression (23) par l'intermédiaire de la canalisation de fluide sous pression (19) avec interposition d'une vanne électromagnétique de remplissage (24) et/ou d'une vanne distributrice (25).
  3. Dispositif d'injection de carburant selon la revendication 1 ou la revendication 2, caractérisé en ce que la canalisation dérivée (30) de la chambre de travail séparée (20) du piston de travail (12) débouche dans la canalisation d'alimentation en carburant (8, 29) vers la chambre d'injecteur (2).
  4. Dispositif d'injection de carburant selon une des revendications 1 à 3, caractérisé en ce qu'à l'intérieur du trajet de déplacement maximal du piston de travail (12) dans l'alésage de guidage (15) qui l'entoure, est disposé un perçage de commande (16) sur lequel est susceptible de glisser une surface frontale du piston de travail (12) délimitant la chambre de travail séparée (20) et/ou le perçage de commande ou la gorge de commande relié à la surface frontale, tournée vers la chambre d'injecteur (2), du piston de travail.
  5. Dispositif d'injection de carburant selon une des revendications 1 à 4, caractérisé en ce que la soupape de retenue (37) sur la canalisation d'alimentation en carburant pour la chambre d'injecteur (2) est disposée dans un perçage ou évidement axial (36) du piston de travail (12) et en ce que la canalisation d'alimentation en carburant (8) est raccordée à la chambre de ressort (29) du piston de travail (12).
  6. Dispositif d'injection de carburant selon une des revendications 1 à 5, caractérisé en ce que pour la canalisation d'alimentation en fluide sous pression, vers la chambre de travail séparée (20) et la canalisation d'alimentation en carburant vers la chambre d'injecteur (2), il est prévu une pompe de refoulement commune (39) avec une pression de refoulement inférieure à la pression d'ouverture de l'injecteur.
  7. Dispositif d'injection de carburant selon une des revendications 1 à 6, caractérisé en ce que la source de fluide sous pression pour l'alimentation de la chambre de travail séparée (20) du piston de travail (12) est réalisée sous la forme d'une pompe haute pression (21) reliée à un accumulateur (23).
  8. Dispositif d'injection de carburant selon la revendication 7, caractérisé en ce que la pompe haute pression est réalisée sous la forme d'une pompe à excentrique mono-cylindrique, dont l'arbre d'entraînement (48) est couplé avec une vanne distributrice (25) susceptible de tourner, qui est disposée sur la canalisation de fluide sous pression (19) allant vers la chambre de travail séparée (20) du piston de travail (12).
EP89121483A 1988-12-30 1989-11-21 Dispositif d'injection de combustible Expired - Lifetime EP0375928B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3844365 1988-12-30
DE3844365A DE3844365A1 (de) 1988-12-30 1988-12-30 Kraftstoffeinspritzvorrichtung

Publications (3)

Publication Number Publication Date
EP0375928A2 EP0375928A2 (fr) 1990-07-04
EP0375928A3 EP0375928A3 (en) 1990-11-07
EP0375928B1 true EP0375928B1 (fr) 1993-05-12

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP89121483A Expired - Lifetime EP0375928B1 (fr) 1988-12-30 1989-11-21 Dispositif d'injection de combustible

Country Status (4)

Country Link
US (1) US5020498A (fr)
EP (1) EP0375928B1 (fr)
JP (1) JP3124280B2 (fr)
DE (2) DE3844365A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE19531870A1 (de) * 1995-08-30 1997-03-06 Bosch Gmbh Robert Kraftstoffeinspritzsystem

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WO1993013309A1 (fr) * 1991-12-23 1993-07-08 Caterpillar Inc. Procede de dosage de la quantite de combustible ejecte d'un injecteur de combustible
US5697341A (en) * 1995-11-20 1997-12-16 Caterpillar, Inc. Fill metered hydraulically actuated fuel injection system and method of fuel injection
US6386463B1 (en) 1996-05-13 2002-05-14 Universidad De Sevilla Fuel injection nozzle and method of use
US6189803B1 (en) 1996-05-13 2001-02-20 University Of Seville Fuel injection nozzle and method of use
US6792940B2 (en) * 1996-05-13 2004-09-21 Universidad De Sevilla Device and method for creating aerosols for drug delivery
US6116516A (en) 1996-05-13 2000-09-12 Universidad De Sevilla Stabilized capillary microjet and devices and methods for producing same
US6187214B1 (en) 1996-05-13 2001-02-13 Universidad De Seville Method and device for production of components for microfabrication
US6299145B1 (en) 1996-05-13 2001-10-09 Universidad De Sevilla Device and method for fluid aeration via gas forced through a liquid within an orifice of a pressure chamber
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Also Published As

Publication number Publication date
JPH02221672A (ja) 1990-09-04
JP3124280B2 (ja) 2001-01-15
DE58904349D1 (de) 1993-06-17
EP0375928A3 (en) 1990-11-07
EP0375928A2 (fr) 1990-07-04
DE3844365A1 (de) 1990-07-05
US5020498A (en) 1991-06-04

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