EP2133552B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2133552B1
EP2133552B1 EP09100243A EP09100243A EP2133552B1 EP 2133552 B1 EP2133552 B1 EP 2133552B1 EP 09100243 A EP09100243 A EP 09100243A EP 09100243 A EP09100243 A EP 09100243A EP 2133552 B1 EP2133552 B1 EP 2133552B1
Authority
EP
European Patent Office
Prior art keywords
chamber
pressure chamber
nozzle needle
fuel
plunger
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.)
Not-in-force
Application number
EP09100243A
Other languages
German (de)
English (en)
Other versions
EP2133552A1 (fr
Inventor
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2133552A1 publication Critical patent/EP2133552A1/fr
Application granted granted Critical
Publication of EP2133552B1 publication Critical patent/EP2133552B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/161—Means for adjusting injection-valve lift
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a fuel injector according to the preamble of claim 1.
  • the object of the invention is to provide a fuel injector according to the preamble of claim 1 for comparatively low design effort and reduced energy consumption for the actuator.
  • the low-pressure chamber arranged in a coupling space-side end face of the slave piston open blind bore of the slave piston and completed by a protruding into the blind bore relatively stationary plunger and a plunger passing through the axial bore with the relatively pressureless fuel reservoir in combination.
  • the actuating forces to be applied by the actuator during the opening stroke of the nozzle needle or the like can be comparatively low, so that comparatively little energy is required for the control stroke.
  • the degree of necessary force or energy during the opening stroke can be adjusted to the actuator.
  • additional measures are provided to keep the actuator forces required during the closing stroke of the nozzle needle or the like low.
  • a throttle is arranged within a flow path of the fuel connecting the high-pressure chamber with the inlet side of the nozzles.
  • a pressure difference occurs at this throttle, wherein the input side of the throttle is substantially an input pressure corresponding to the pressure in the high-pressure chamber and output side substantially an output pressure approximated to the comparatively low combustion chamber pressure, so that supportive hydraulic forces must occur in the closing stroke of the nozzle needle or the like ,
  • the flow path between the inner circumference of a subsequent to the high-pressure chamber nozzle needle chamber and the outer circumference of the nozzle needle or the like arranged and the throttle between a nozzle needle side flange or flange and the inner circumference formed or arranged.
  • the said throttle may be formed as an annular gap throttle between the inner circumference of the nozzle needle chamber and the outer periphery of a fixed to the nozzle needle or the like annular collar-shaped flange.
  • the plunger with an end piece which has a relation to the cross section of the blind bore and the plunger enlarged cross section, on one of the coupling chamber side end face of the slave piston axially opposed to the stationary surface on the injector housing and between the end piece and the stationary surface a substantially disc-shaped and communicating with the relatively pressureless fuel reservoir space with respect to the diameter of the blind bore or the plunger larger disc diameter may be formed.
  • the single FIGURE shows a schematic axial section of a particularly preferred embodiment of the fuel injector according to the invention.
  • the fuel injector 1 shown in the drawing has an injector body 2, which receives a first pressure chamber 3, a second pressure chamber 4 and an adjoining third pressure chamber 5.
  • the pressure chambers 3-5 are communicatively connected to each other by a between the first and second pressure chamber 4 arranged intermediate bottom 6 of the injector body 2 is penetrated by an axial bore 7 connecting the pressure chambers 3 and 4.
  • the pressure chamber 5 serves as an axial guide of a nozzle needle 8, which controls the arranged in the drawing lower end of the pressure chamber 5 injectors 9, via which the pressure chamber 5 is connected to a combustion chamber, not shown, of an internal combustion engine.
  • the nozzle needle 8 takes its nozzle 9 shut-off closing position in which the nozzle-side end of the nozzle needle 8 is seated with a nozzle-side annular edge tight on a the inputs of the nozzles 9 with radial spacing enclosing annular nozzle needle seat, so that within the pressure chamber 5 a Nozzle input space 10 is separated from a remaining between the axial inner wall of the pressure chamber 5 and the outer circumference of the nozzle needle 8 annular space.
  • This annular space communicates constantly with the pressure chamber 4.
  • the nozzle needle is guided in an axially adjacent to the pressure chamber 4 extended upper axial portion of the pressure chamber 5 with arranged on the nozzle needle axial webs or the like, between which the aforementioned annular space with the pressure chamber 4 connecting Free spaces remain.
  • the nozzle needle 8 assumes its lifted from the seat to the injectors 9 open position, the nozzle inlet chamber 10 via the pressure chambers 5 and 4 and the axial bore 7 in the intermediate bottom 6 and the pressure chamber 3 is connected to a high-pressure fuel reservoir 11, which typically as so-called Common Rail is formed and communicates via a connecting line 12 with the first pressure chamber 3. This can be under high pressure Fuel are injected via the injectors 9 in the combustion chamber of the internal combustion engine.
  • valve needle 8 To actuate the valve needle 8 is a trained in the example as a piezoelectric element actuator 13 which is connected via electrical lines 14 to an electrical voltage source and is hydraulically coupled to the valve needle 8.
  • This hydraulic coupling is effected by a positive displacement by means of the actuator 13 master piston 15 in a coupling chamber 16 which communicates via a the intermediate bottom 6 passing through line 17 with a coupling chamber 18, in which a arranged on the nozzle needle 8 slave piston 19 works displacer effective.
  • the master piston 15 performs a downward movement reducing the coupling space 16
  • fluid is expelled from the coupling space 16 via the conduit 17 into the coupling space 18, so that the slave piston 19 with the nozzle needle 8 performs a downward movement in the direction of the closed position of the nozzle needle 8.
  • the coupling space 16 receives fluid from the coupling space 18 during upward movement of the master piston 15, wherein the slave piston 19 with the valve needle 8 in the upward direction, i. moved in an open position of the valve needle 8. Since the displacement effective piston cross sections of the master and slave pistons 15 and 19 are different, a corresponding stroke ratio is effected, wherein the gear ratio is inverse to the ratio of the cross sections.
  • the coupling chamber 16 is separated from the pressure chamber 3 by a sealing sleeve 20 which is displaceably guided on the master piston 15 and by means of a helical compression spring 21 which is clamped between an annular collar arranged on the master piston 15 and the facing end edge of the sealing sleeve 20 against the master piston 15 facing Front side of the false floor 6 is stretched, the sealing sleeve 20 is tightly seated with a sharp annular edge on a ring line zone of the false floor.
  • the coupling space 18 is separated from the pressure chamber 4 by a sealing sleeve 22 which slidably guided on the slave piston 19 and by means of a clamped between an annular collar on the slave piston 19 and the facing end edge of the sealing sleeve 22 helical compression spring 23 against the slave piston 19 facing end side of the Intermediate tray 6 is tensioned, wherein the sealing sleeve 22 is tightly seated with a sharp edge of the ring on a corresponding ring line zone on the lower end face of the intermediate bottom 6 in the drawing.
  • axial blind bore 24 is arranged, which is shut off from the coupling space 18 by a protruding into the blind bore 24, stationary supported on the intermediate bottom 6 plunger 25.
  • the plunger 25 is penetrated by an axial bore, which is connected via a the intermediate bottom 6 passing through line 26 with a relatively pressureless fuel reservoir, such as a fuel tank (not shown). Accordingly, a low pressure space 27 remaining between the bottom of the blind bore 24 and the facing front end of the plunger 25 is constantly below the virtually vanishing pressure of the fuel reservoir or fuel tank.
  • the plunger 25 is held on the facing side of the intermediate bottom 6 by fluidic forces.
  • the intermediate bottom 6 facing the end of the plunger 25 has a relation to the cross section of the plunger 25 and the blind bore 24 significantly enlarged cross-section, within the intermediate bottom 6 facing side of said end piece a disc-shaped space 28 is recessed, the diameter clearly larger than the outer diameter of the plunger 25 and the inner diameter of the blind bore 24 is.
  • This disc-shaped space 28 is in communication with the line 26 to the relatively pressureless fuel reservoir or tank, so that the present in the coupling chamber 18, the pressure in the pressure chambers 3 and 4 corresponding pressure, which substantially corresponds to the pressure in the pressure accumulator 11, the End of the plunger 25 presses with a correspondingly large force against the facing end face of the intermediate bottom 6, wherein the end piece with a disk-shaped space 28 comprehensive sharp annular edge on a ring-shaped zone of the false bottom 6 is tightly seated.
  • said end piece of the plunger 25 is still tensioned against the intermediate bottom 6 by a helical compression spring 29 accommodated in the low-pressure space 27 and clamped between the bottom of the blind bore 24 and the facing front end of the plunger 25.
  • the helical compression spring 29 essentially serves only as a mounting aid and may be correspondingly weak dimensioned.
  • the helical compression spring 29 for the start of the end piece of the plunger 25 against the facing side of the intermediate bottom 6 is practically meaningless.
  • the illustrated fuel injector 1 functions as follows:
  • the coupling chambers 16 and 18 are filled with fuel during operation and are substantially under the same pressure as the fuel in the pressure accumulator 11.
  • the piezoelectric actuator 13 is subjected to an electrical voltage via the electrical leads 14, he holds the master piston 15 in the lower position shown in the drawing, and the nozzle needle 8 assumes the illustrated closed position.
  • the injection nozzles 9 are shut off from the pressure accumulator 11.
  • the piezoelectric actuator 13 pulls the master piston 15 in the direction of its top dead center position, ie the master piston 15 leads in the drawing Upstroke from which the slave piston 19 with the nozzle needle 8 with 19 by the ratio of the displacer cross sections of the master and slave piston 15, 19 given Hubüber ? That is, the nozzle needle 8 lifts from its nozzle-side seat, so that the nozzle input space 10 is connected to the pressure accumulator 11 and fuel is injected via the nozzles 9 in the adjacent combustion chamber. If subsequently the piezoelectric actuator 13 is acted upon again via the electrical connection lines 12 with an electrical voltage, the master piston 15 and the nozzle needle 8 are in turn pushed into the positions shown in the drawing.
  • the dimensioning of the cross-section of the low-pressure chamber 27 or the cross-section of the blind bore 24 and the plunger 25 displaceable therein is essential.
  • the forces which are necessary to bring the nozzle needle 8 located in the closed position in the open position are essentially determined by the difference between the cross section of the nozzle inlet chamber 10, that is, the cross section of the nozzle needle seat, and the cross section of the low pressure chamber 27.
  • the cross section of the low-pressure chamber 27 is about 60 - 80% of the cross-section of the nozzle input space 10.
  • a bypass throttle 30 is provided between the pressure chambers 4 and 5.
  • a flange 31 is arranged to form the bypass throttle 30 on the nozzle needle 8, which is dimensioned such that between its outer circumference and the inner circumference of the pressure chamber 5, a throttle-effective annular gap is formed.
  • the energy required for the closing stroke of the nozzle needle 8 and on the other hand, the energy requirements for the opening stroke of the nozzle needle 8 can be kept low, so that a correspondingly smaller cost-effective actuator 13 for the operation of the fuel injector 1 is sufficient.
  • the hydraulic coupling of the master and slave pistons 15, 19 described above also effects a compensation of thermal expansions without further design measures, so that no further measures for compensating fluctuations in the operating temperature of the injector 1 become necessary.
  • a throttle is preferably arranged, which exerts a damping effect on the piston strokes.
  • the upper end position of the nozzle needle should preferably be defined by a stop. This can for example be realized in that the intermediate bottom 6 facing end face of the slave piston 19 in the upper end position stop-like cooperates with the tail at the upper end of the plunger 25.
  • a nip is formed between the mutually facing surfaces of the slave piston 19 and said end piece, from the fluid is displaced during the upward stroke of the slave piston 19 under damping of the upward movement, so that the slave piston 19 and the nozzle needle 8 are braked damped shortly before taking their upper end position.

Claims (7)

  1. Injecteur de carburant (1) comprenant :
    - un boîtier ou corps d'injecteur (2) ainsi qu'un espace haute pression (4, 5) disposé dans celui-ci, qui communique constamment avec une source haute pression (11) de carburant et qui peut être connecté à une chambre de combustion par le biais de buses (9) pour l'injection de carburant, commandées par une aiguille de buse (8) ou similaire,
    - un actionneur (13), qui est accouplé hydrauliquement à l'aiguille de buse (8) ou similaire en vue de son actionnement, l'actionneur étant connecté par entraînement à un maître-piston (15), qui fonctionne dans un espace d'accouplement (16, 18) séparé dans l'espace haute pression, et l'aiguille de buse (8) ou similaire étant connectée par entraînement à un piston récepteur (19) fonctionnant dans l'espace d'accouplement, et
    - un espace basse pression (27) sur le piston récepteur (19) fonctionnant dans celui-ci en tant que corps de déplacement, le volume de l'espace basse pression lors de la course d'ouverture de l'aiguille de buse (8) ou similaire diminuant,
    caractérisé en ce que
    l'espace basse pression (27) est disposé dans un alésage borgne (24) ouvert vers le côté frontal du piston récepteur (19) du côté de l'espace d'accouplement, et est terminé par un plongeur (25) pénétrant dans l'alésage borgne, et communique par le biais d'un alésage axial traversant le plongeur avec le réservoir de carburant relativement sans pression.
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce
    qu'un papillon d'étranglement (30) est disposé à l'intérieur d'un chemin d'écoulement du carburant reliant l'espace haute pression à un espace d'entrée de buse (10).
  3. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    le chemin d'écoulement est disposé entre la périphérie intérieure d'un espace de pression (5) se raccordant à l'espace haute pression (3, 4) et la périphérie extérieure de l'aiguille de buse (8) ou similaire, et le papillon d'étranglement (30) est disposé ou réalisé entre un épaulement ou une bride (31) du côté de l'aiguille de buse et la périphérie intérieure.
  4. Injecteur de carburant selon la revendication 3,
    caractérisé en ce que
    le papillon d'étranglement (30) est réalisé sous forme d'étranglement à fente annulaire.
  5. Injecteur de carburant selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que
    le plongeur (25) est supporté axialement avec un embout qui présente une section transversale agrandie par rapport à la section transversale de l'alésage borgne (24), sur une surface d'une pièce (6) du boîtier ou du corps d'injecteur (2) ou d'un élément d'accouplement ou du maître-piston (15) opposée au côté frontal du côté de l'espace d'accouplement du piston récepteur (19), et entre l'embout et la surface est réalisé un espace (28) essentiellement en forme de disque et communiquant avec le réservoir de carburant relativement sans pression, avec un diamètre de disque agrandi par rapport au diamètre de l'alésage borgne (24).
  6. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que
    l'embout repose sur la surface avec une arête d'étanchéité disposée du côté frontal, entourant de manière annulaire l'espace en forme de disque (28).
  7. Injecteur de carburant selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que
    la section transversale du plongeur (25) ou de l'alésage borgne (24) a une dimension qui représente approximativement 60 à 80 % de la section transversale d'un siège d'étanchéité de l'aiguille de buse (8) ou similaire sur les buses d'injection (9).
EP09100243A 2008-06-13 2009-04-22 Injecteur de carburant Not-in-force EP2133552B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008002419A DE102008002419A1 (de) 2008-06-13 2008-06-13 Kraftstoffinjektor

Publications (2)

Publication Number Publication Date
EP2133552A1 EP2133552A1 (fr) 2009-12-16
EP2133552B1 true EP2133552B1 (fr) 2010-10-27

Family

ID=41171200

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09100243A Not-in-force EP2133552B1 (fr) 2008-06-13 2009-04-22 Injecteur de carburant

Country Status (3)

Country Link
EP (1) EP2133552B1 (fr)
AT (1) ATE486211T1 (fr)
DE (2) DE102008002419A1 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005012940A1 (de) * 2005-03-21 2006-09-28 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE102005020597A1 (de) * 2005-05-03 2006-11-09 Robert Bosch Gmbh Kraftstoffinjektor mit direkt steuerbarem Einspritzventilglied und Temperaturausgleichselement
DE102006022803A1 (de) * 2006-05-16 2007-11-22 Robert Bosch Gmbh Einspritzdüse
DE102006062216A1 (de) 2006-12-22 2008-06-26 Robert Bosch Gmbh Kraftstoffinjektor

Also Published As

Publication number Publication date
EP2133552A1 (fr) 2009-12-16
DE102008002419A1 (de) 2009-12-17
DE502009000146D1 (de) 2010-12-09
ATE486211T1 (de) 2010-11-15

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