WO2005121545A1 - Soupape d'injection dont l'aiguille est soumise a une pression de fermeture - Google Patents

Soupape d'injection dont l'aiguille est soumise a une pression de fermeture Download PDF

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Publication number
WO2005121545A1
WO2005121545A1 PCT/EP2005/005698 EP2005005698W WO2005121545A1 WO 2005121545 A1 WO2005121545 A1 WO 2005121545A1 EP 2005005698 W EP2005005698 W EP 2005005698W WO 2005121545 A1 WO2005121545 A1 WO 2005121545A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
throttle
pressure
chamber
spring chamber
Prior art date
Application number
PCT/EP2005/005698
Other languages
German (de)
English (en)
Inventor
Maximilian Kronberger
Robert SCHÄPERS
Original Assignee
Volkswagen Mechatronic Gmbh & Co. Kg
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 Volkswagen Mechatronic Gmbh & Co. Kg filed Critical Volkswagen Mechatronic Gmbh & Co. Kg
Publication of WO2005121545A1 publication Critical patent/WO2005121545A1/fr

Links

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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the invention relates to an injection valve according to the preamble of patent claim 1.
  • Injectors especially modern diesel injectors, require very precise control of the injection processes for the clean combustion of the injected fuel.
  • the main parameters here are the injection time, the end of injection and the dynamic behavior of the valve needle at the start and end of the injection.
  • a pump-nozzle arrangement is known from EP 0 675 282 B1, in which a fuel pump controls the injection process in cooperation with a control valve.
  • fuel is made available to the fuel pump from a fuel tank via the control valve.
  • the fuel pump is connected via a further line to a pressure chamber in which the injection needle of the injection valve is arranged.
  • the injection needle has pressure areas in the pressure chamber, the fuel pressure applied to the pressure areas lifting the injection needle off the sealing seat.
  • the injection needle is prestressed against the sealing seat by means of a prestressing spring which is arranged in a spring space.
  • the spring chamber is connected to the supply line via a fuel line, which connects the check valve to the control valve.
  • the supply line is connected to a fuel return via a check valve.
  • the injection needle By coupling the spring chamber to the supply line, the injection needle is also biased against the sealing seat via the fuel pressure in addition to the biasing spring.
  • the fuel compressed by the fuel pump is returned to the pressure chamber or via the supply line and the check valve to the fuel tank.
  • An injection is started when, during the compression process of the fuel pump, the control valve is closed and the fuel pressure in the pressure chamber rises above a specified value, so that the injection needle is lifted from the sealing seat due to the pressure in the pressure chamber against the preload of the pretensioning spring and against the fuel pressure in the spring chamber ,
  • the check valve is replaced by a valve which is formed by a spring plate as a closing member.
  • the spring plate is coupled to the valve needle via a spring piston and the biasing spring is supported on the spring plate for biasing the valve needle. If the injection needle is on the sealing seat so that no injection takes place, the valve is open so that the fuel compressed by the fuel pump is conveyed back to the fuel tank via the spring chamber past the spring plate via the spring chamber. If an injection takes place, the injection needle is lifted off the sealing seat. If the control valve is now opened, the fuel pressure provided by the fuel pump is directed via the control valve into the spring chamber and thus onto the spring plate. Since the spring-loaded valve is closed, the fuel pressure in the spring chamber acts on the injection needle and supports the closing process of the injection needle until the spring-loaded valve is opened.
  • the object of the invention is to provide an improved injection valve.
  • the object of the invention is achieved by the injection valve according to claim 1.
  • One advantage of the described injection valve is that the injection needle is biased via a fuel pressure in the spring chamber, which is damped and coupled to the fuel pressure that prevails in the inlet channel to the control valve. An improved function of pressurizing the injection needle is thereby achieved.
  • This advantage is achieved in that the spring chamber is connected to the inlet channel via a spring chamber throttle, which connects the control valve to a fuel reservoir.
  • an inlet throttle is provided in the inlet channel, which tapers the inlet channel over a short section.
  • the spring chamber throttle is connected to the inlet duct between the inlet throttle and the control valve.
  • the arrangement of the inlet throttle increases the fuel pressure between the control valve and the inlet throttle during a flushing process in which the control valve is open to pump fuel from the pump via the control valve back into the fuel reservoir. In this situation, the fuel pressure acting on the injection needle via the inlet channel and the inlet throttle is thus increased. In this way it is achieved that, even in the situation in which no injection takes place, the injection needle is held securely on the sealing seat.
  • This has the advantage that the minimum fuel pressure required to lift the injection needle can be reduced.
  • the control valve is closed, the minimum fuel pressure at which the injection needle lifts off the sealing seat and starts an injection is essentially determined by the biasing force of the biasing spring.
  • the spring chamber throttle and the inlet throttle are preferably arranged in an intermediate disk which delimits the spring chamber at the top.
  • a pump chamber throttle which connects the fuel pump to the pressure channel, is also arranged in the intermediate disk. In this way, a precise and economical manufacture of the chokes is possible.
  • a spring plate is provided which provides a larger effective area for transmitting the pressure prevailing in the spring chamber to the injection needle. A pressure increase acting on the injection needle is thus achieved. This supports the preload force that acts on the injection needle even at low pressures in the spring chamber.
  • the spring plate is spaced from the inner wall of the spring chamber via a circumferential sealing gap.
  • the area of the spring chamber, which is formed between the spring plate and the injection needle, is connected to the inlet channel via a second spring chamber plug.
  • the second spring chamber throttle opens into the inlet channel between an inlet area of the inlet channel and the inlet throttle.
  • a side wall of the spring plate which is assigned to the inner wall of the spring chamber, is rounded.
  • the biasing spring is clamped between the spring plate and a sleeve pressed into the spring chamber.
  • An opening is provided in the sleeve through which a piston rod is guided.
  • the piston rod is attached to the spring plate and guides the spring plate in the spring chamber.
  • the inlet throttle and the first spring chamber throttle have approximately the same cross section. This leads to favorable pressure conditions, which support an efficient prestressing of the injection needle.
  • the second spring chamber throttle has a smaller cross section than the first spring chamber throttle. This results in improved pressure conditions in the spring chamber.
  • the second spring chamber throttle preferably opens into the inlet channel between an inlet region of the inlet channel and the inlet throttle.
  • the first spring chamber throttle opens into the inlet channel directly after the inlet throttle.
  • Figure 1 shows a cross section through a pump-nozzle unit
  • Figure 2 shows a section of a second embodiment of a pump-nozzle unit.
  • FIG. 1 shows in cross section a pump-nozzle unit 1, which is essentially constructed from an injection valve 2, an actuator 3, a fuel pump 5 and a control valve 4.
  • the actuator 3 is designed in the form of a piezoelectric actuator which opens or closes depending on the energization of the control valve 4.
  • the pump-nozzle unit also has the fuel pump 5, which is actuated by a camshaft.
  • an inlet channel 6 is provided, which is led to the control valve 4.
  • the inlet channel 6 is connected to a pressure channel 7 via the control valve 4.
  • the pressure channel 7 is connected to a pump chamber 9 of the fuel pump 5 via a pump throttle 8.
  • the pressure channel 7 is guided into a pressure chamber 10, which is introduced between an injection needle 11 and a nozzle body 13.
  • a needle chamber 12 is formed in the nozzle body 13, in which the injection needle 11 is slidably arranged.
  • the injection needle 11 is associated with a sealing surface which is arranged at the tip of the injection needle 11, a sealing seat 14 which is formed on an inner wall of the needle chamber 12.
  • the sealing seat 14 is arranged between an injection hole 15 and the pressure chamber 10.
  • Fuel channels are formed between the injection needle 11 and the nozzle body 13 and, when the injection needle 11 is lifted off the sealing seat 14, establish a connection between the injection hole 15 and the pressure chamber 10 for an injection.
  • the injection needle 11 is guided upwards into a spring chamber 17 via a needle piston 16.
  • the injection needle 11 has pressure surfaces 18 in such a way that the pressure prevailing in the pressure chamber 10 prestresses the injection needle 11 away from the sealing seat 14.
  • the spring chamber 17 is essentially designed as a cylindrical bore, a biasing spring 19 being arranged in the spring chamber 17.
  • the bias spring 19 is clamped between a spring plate 20 and a sleeve 21.
  • the spring plate 20 is operatively connected to the needle piston 16.
  • the sleeve 21 is arranged in the upper end region of the spring chamber 17 and is preferably held by means of a press fit.
  • the sleeve 21 has a central bore 22 which connects the area above the sleeve 21 to the area below the sleeve 21 in which the spring plate 20 is arranged.
  • a spring chamber throttle 23 is provided, which connects the spring chamber 17 above the sleeve 21 to the inlet channel 6.
  • An inlet throttle 27 is arranged in the inlet channel 6, a damping section 26 being formed between the control valve 4 and the inlet throttle 27.
  • the spring chamber throttle 23 preferably opens between the inlet throttle 27 and the control valve 4 into the inlet channel 6.
  • the spring chamber throttle 23 opens into the inlet channel 6 directly at the inlet throttle 27.
  • a plate 24 is provided, which is a part represents the injection valve 2 and limits the spring space 17 towards the top.
  • the inlet throttle 27, the spring space throttle 23 and the pump throttle 8 are preferably arranged in the plate 24. Furthermore, the inlet channel 27 and the pressure channel 7 are guided through the plate 24. Instead of one
  • Plate 24 can also be any other type of component in which the aforementioned elements are contained.
  • the arrangement of the inlet throttle 27 and the spring chamber throttle 23 in a plate 24 component has the advantage that the throttles can be machined easily and precisely.
  • a pump piston (not shown), which is driven by the fuel pump 5, is guided in the pump chamber 9.
  • the control valve 4 When the control valve 4 is open, the fuel is sucked into the inlet channel 6 via an inlet 25 during an intake stroke of the fuel pump 5. The fuel is fed via the inlet throttle 6 into the damping section 26 of the inlet channel 6. On- finally the fuel is sucked through the control valve 4 to the pressure channel 7 and via the pump throttle 8 into the pump chamber 9. If the control valve 4 is not closed even during a compression stroke of the piston, in which the piston moves downward and pushes the fuel out of the pump chamber 9, part of the fuel is pressed back into the inlet channel 6.
  • the spring chamber 17 Due to the spring chamber throttle 23, the spring chamber 17 is always coupled to the fuel pressure which prevails in the damping section 26 between the inlet throttle 27 and the control valve 4.
  • pressure fluctuations occur both in the damping section 26 and in the pressure channel 7 due to the chronological succession of the intake and compression cycles of the fuel pump 5.
  • the pressure fluctuations are led to the pressure surfaces 18 via the pressure channel 7.
  • the pressure at which the injection needle 11 is lifted off the sealing seat has been set relatively high so that the pressure fluctuations do not lead to the injection valve being opened unintentionally. This is determined, for example, by the size of the pressure surfaces 18 and the bias of the bias spring 19.
  • the injection needle 11 in the described injection valve is prestressed with pressure in the direction of the sealing seat via the spring chamber throttle 23.
  • the inlet throttle 27 is provided, which causes a pressure increase in the damping section 26 when fuel is pushed out into the inlet channel 6.
  • the pressure prevailing in the spring chamber 17 is directly on the Needle piston 16 guided without the spring plate 20 produces a pressure-increasing effect.
  • a further increase in pressure is achieved in that the spring plate 20 is spaced a sealing gap 30 from the inner wall of the spring chamber 17 and the pressure transmission is thereby improved.
  • a second spring chamber throttle 28 is provided below the spring plate 20, which connects the area of the spring chamber, which is arranged below the spring plate 20, to the inlet channel 6.
  • the inlet throttle 27 and the spring chamber throttle 23 have the same cross section.
  • the second spring chamber throttle 28 preferably has a smaller cross section than the first spring chamber throttle 23.
  • Favorable values for the cross sections of the inlet throttle 27 and the first spring chamber throttle 23 are in the range from 0.8 to 1.5 mm.
  • the circular cross section of the inlet throttle 27 preferably has a diameter of 0.9 to 1.1 mm and the diameter of the circular cross section of the first spring chamber throttle 23 has a diameter of 1.1 to 1.3 mm.
  • the pump throttle has a circular cross section, the diameter of which is in the range from 1.0 to 1.4 mm.
  • the side surface of the spring plate 20 is preferably rounded, so that tilting of the spring plate 20 in the spring chamber 17 is avoided.
  • the side surface of the spring plate 20 has a
  • the sealing gap 30 between the spring plate 20 and the wall of the spring chamber 17 is preferably in the range from 3 to 10 / im.
  • Figure 2 shows a schematic representation of a section of a cross section of the injection valve 2, in which the spring plate 20 is designed in the form of a piston and is guided over a sealing gap 30 in the spring chamber 17.
  • a piston rod 29 is provided, which is attached to the spring plate 20 and is guided upwards through the bore 22 of the sleeve 21. The piston rod 29 is guided in the bore 22 and the spring plate

Landscapes

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

Abstract

L'invention concerne une unité pompe-gicleur (1) où un conduit sous pression (7) est alimenté en carburant au moyen d'une pompe à carburant (5) par l'intermédiaire d'un conduit d'alimentation (6) et d'une soupape de distribution (4). Le conduit sous pression (7) est couplé à une aiguille d'injection (11) précontrainte qui, lorsque le carburant est soumis à une pression prédéfinie, se soulève d'un siège d'étanchéité (14) associé et commence l'injection. Lorsque la soupape de distribution (4) est ouverte, le carburant projeté par la pompe à carburant (5) dans le système de compression retourne dans la conduite d'alimentation (6) et dans le conduit de pression (7), provoquant ainsi des variations de pression. Afin de diminuer ces variations de pression, un étrangleur (27) est monté dans la conduite d'alimentation. Pour que la pression d'injection servant à l'ouverture de l'aiguille d'injection soit réglée à un niveau relativement faible, l'aiguille d'injection (11) est en outre soumise par une chambre à ressort (17) à l'action de la pression du carburant régnant dans la conduite d'alimentation (6), en direction du siège d'étanchéité (14). De plus, la chambre à ressort (17) est reliée à la conduite d'alimentation (6) par un étranglement (23), et dans la chambre à ressort (17) se trouve le ressort de précontrainte (19) qui agit sur l'aiguille d'injection (11) en direction du siège d'étanchéité (14).
PCT/EP2005/005698 2004-06-09 2005-05-27 Soupape d'injection dont l'aiguille est soumise a une pression de fermeture WO2005121545A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200410028195 DE102004028195A1 (de) 2004-06-09 2004-06-09 Einspritzventil mit Schließdruckbeaufschlagung der Ventilnadel
DE102004028195.5 2004-06-09

Publications (1)

Publication Number Publication Date
WO2005121545A1 true WO2005121545A1 (fr) 2005-12-22

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ID=34970334

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/005698 WO2005121545A1 (fr) 2004-06-09 2005-05-27 Soupape d'injection dont l'aiguille est soumise a une pression de fermeture

Country Status (2)

Country Link
DE (1) DE102004028195A1 (fr)
WO (1) WO2005121545A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111051681A (zh) * 2017-07-20 2020-04-21 利勃海尔零部件代根多夫有限公司 用于控制喷射器的装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4572433A (en) * 1984-08-20 1986-02-25 General Motors Corporation Electromagnetic unit fuel injector
EP0269289A2 (fr) * 1986-11-28 1988-06-01 Diesel Technology Corporation Pompe-injecteur pour moteur diesel à fermeture assistée de l'aiguille d'injecteur par la pression de décharge
US5042718A (en) * 1988-11-10 1991-08-27 Daimler-Benz Ag Solenoid-valve-controlled fuel injection device, for an air-compressing internal combustion engine
GB2299620A (en) * 1995-04-04 1996-10-09 Lucas Ind Plc I.c.engine fuel injection system
EP0675282B1 (fr) 1994-03-03 1998-08-12 Lucas Industries Public Limited Company Circuits de carburant
WO1999004160A1 (fr) * 1997-07-16 1999-01-28 Cummins Wartsila S.A. Dispositif d'injection de combustible pour moteurs diesel
US20040065294A1 (en) * 2001-08-25 2004-04-08 Joachim Winter Fuel injection device for an internal combustion engine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10158659A1 (de) * 2001-11-30 2003-06-12 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10211439A1 (de) * 2002-03-15 2003-10-02 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10224694A1 (de) * 2002-06-04 2003-12-18 Bosch Gmbh Robert Brennkraftmaschine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4572433A (en) * 1984-08-20 1986-02-25 General Motors Corporation Electromagnetic unit fuel injector
EP0269289A2 (fr) * 1986-11-28 1988-06-01 Diesel Technology Corporation Pompe-injecteur pour moteur diesel à fermeture assistée de l'aiguille d'injecteur par la pression de décharge
US5042718A (en) * 1988-11-10 1991-08-27 Daimler-Benz Ag Solenoid-valve-controlled fuel injection device, for an air-compressing internal combustion engine
EP0675282B1 (fr) 1994-03-03 1998-08-12 Lucas Industries Public Limited Company Circuits de carburant
GB2299620A (en) * 1995-04-04 1996-10-09 Lucas Ind Plc I.c.engine fuel injection system
WO1999004160A1 (fr) * 1997-07-16 1999-01-28 Cummins Wartsila S.A. Dispositif d'injection de combustible pour moteurs diesel
US20040065294A1 (en) * 2001-08-25 2004-04-08 Joachim Winter Fuel injection device for an internal combustion engine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111051681A (zh) * 2017-07-20 2020-04-21 利勃海尔零部件代根多夫有限公司 用于控制喷射器的装置
CN111051681B (zh) * 2017-07-20 2022-04-19 利勃海尔零部件代根多夫有限公司 用于控制喷射器的装置
US11608805B2 (en) 2017-07-20 2023-03-21 Liebherr-Components Deggendorf Gmbh Device for controlling an injector

Also Published As

Publication number Publication date
DE102004028195A1 (de) 2005-12-29

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