WO2006106017A2 - Injecteur de carburant dote d'un actionneur piezoelectrique - Google Patents

Injecteur de carburant dote d'un actionneur piezoelectrique Download PDF

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Publication number
WO2006106017A2
WO2006106017A2 PCT/EP2006/060318 EP2006060318W WO2006106017A2 WO 2006106017 A2 WO2006106017 A2 WO 2006106017A2 EP 2006060318 W EP2006060318 W EP 2006060318W WO 2006106017 A2 WO2006106017 A2 WO 2006106017A2
Authority
WO
WIPO (PCT)
Prior art keywords
piston
valve member
actuator
control
injection valve
Prior art date
Application number
PCT/EP2006/060318
Other languages
German (de)
English (en)
Other versions
WO2006106017A3 (fr
Inventor
Friedrich Boecking
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 WO2006106017A2 publication Critical patent/WO2006106017A2/fr
Publication of WO2006106017A3 publication Critical patent/WO2006106017A3/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
    • 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
    • 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
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to a fuel injector with piezoelectric actuator according to the preamble of patent claim 1.
  • a fuel injector controlled by a piezoactuator is known, for example, from EP-A 1 174 615.
  • the fuel injector includes an injection valve member which cooperates with a valve seat to control fuel delivery into the combustion chamber.
  • the fuel injector further comprises a piezo actuator and an amplifier unit for transmitting the movement of the actuator to the valve member.
  • the booster unit comprises a piston on which the booster unit can apply a retracting force, and a control chamber and mechanical connecting elements to connect the movement of the piston with the valve member in applying the retracting force to the piston.
  • the booster unit is configured so that when the pull-back force is applied the valve member with the piston lifts out of the valve seat and the movement of the valve member is decoupled from the piston after the initial movement to allow a variable amplification of the movement of the actuator and the valve member ,
  • a disadvantage of the fuel injector disclosed in EP-A 1 174 615 is that the piezoelectric actuator is energized when the injection opening is closed. The power supply of the piezoelectric actuator is interrupted only for the injection of fuel.
  • the fuel injector according to the invention for injecting fuel into a combustion chamber of an internal combustion engine comprises at least one injection opening which can be closed or released by an injection valve member.
  • the fuel injector is actuated by an actuator, wherein in a unilaterally open booster piston, which is in communication with the actuator, a control piston is movably received.
  • the control piston is at the an annular projection formed in the side facing away from the booster piston, in which the injection valve member is guided, so that at least one injection opening is released when the actuator is energized and the at least one injection opening is closed when the actuator is not energized.
  • Advantage of the inventively embodied fuel injector is that the piezoelectric actuator is energized only for the injection of fuel. This also ensures that when not operated internal combustion engine, the at least one injection opening of the fuel injector is closed.
  • the actuator is a piezoelectric actuator.
  • the booster piston defines a coupler space with an end wall facing away from the actuator, preferably a ring.
  • the coupler space encloses the annular projection of the control piston.
  • a first control chamber is preferably formed in the booster piston, which is limited by the booster piston and the control piston.
  • a first spring element is accommodated in the first control chamber, which is preferably a compression spring designed as a spiral spring and is supported with one side against the booster piston and with the other side against the control piston.
  • the first spring element By the first spring element, the movement of the control piston is supported in the direction of at least one injection opening and thus ensures a rapid closing of the at least one injection opening.
  • the first spring element is also achieved that the diameter position in the closed state always remains the same, especially at start of the system. This prevents undesired fuel from entering the combustion chamber of the internal combustion engine in the closed state of the injection valve member.
  • a second control chamber is preferably formed, which is delimited by the control piston, the annular projection and the injection valve member.
  • a second spring element is received in a preferred embodiment, which is supported with one side against the control piston and with the other side against the injection valve member.
  • the second spring element is also preferably one designed as a spiral spring compression spring.
  • the fuel supply of the first control chamber is preferably carried out via a passage opening designed as a bore in the booster piston, which is arranged so that the first control chamber is hydraulically connected via the passage opening with the fuel inlet.
  • the fuel supply of the second control chamber is preferably via a channel in the injection valve member.
  • a throttle point is preferably formed in the channel in the injection valve member.
  • the channel with the throttle point formed therein preferably opens into a third control chamber, which encloses the injection valve member and which is bounded by an end face of the annular projection on the control piston.
  • the channel in the injection valve member designed as a blind hole, in which a bore opens in a smaller diameter.
  • the hole with a smaller diameter acts as a throttle point.
  • the channel in the injection valve member opens into a third control chamber, which is bounded on one side by the annular projection on the control piston.
  • the third control chamber is hydraulically connected via the channel with the throttle point in the injection valve member with the second control chamber. This causes the pressure in the second control chamber to decrease as soon as the pressure in the third control chamber drops. Due to the throttle point in the channel, the pressure in the second control chamber decreases with a time delay to the pressure in the third control chamber.
  • the single FIGURE shows a section through an inventively designed fuel injector.
  • a fuel injector 1 as shown in the single figure, comprises an actuator 2, which acts on a booster piston 3.
  • the actuator 2 is in a preferred embodiment, a piezoelectric actuator.
  • the booster piston 3 is open on one side, that is pot-shaped, whereby in the booster piston 3, a first control chamber 4 is formed.
  • a control piston 5 is added, which limits the first control chamber 4 on the side facing away from the actuator 2.
  • the actuator 2 and the booster piston 3 are accommodated in an actuator chamber 6.
  • the actuator chamber 6 is preferably connected to a high-pressure accumulator, which provides fuel under system pressure.
  • the system pressure is preferably in the range of 200 to 2500 bar.
  • the actuator chamber 6 is filled with fuel under system pressure.
  • the actuator chamber 6 is connected to a pump-nozzle unit, which provides the under system pressure fuel.
  • a preferably designed as a bore passage opening 7 is the first control chamber 4 with the actuator chamber 6 in hydraulic communication. Via the passage opening 7, fuel that is under system pressure passes into the first control chamber 4, so that in the first control chamber 4 system pressure also prevails.
  • the booster piston 3 is preferably enclosed by a compression spring element 8.
  • the compression spring element 8 is supported against a shoulder 9 on the booster piston 3 and against an end face 10 of a likewise the booster piston 3 enclosing sleeve 11 from. With the help of the compression spring element 8, the booster piston 3 is pressed against an end face 12 of the actuator 2.
  • the sleeve 11 is connected to a biting edge 13 on a lower housing part 14th
  • a coupler space 15 is further limited, which on the lower housing part 14 opposite side of a forehead surface 16 of the booster piston 3 and a shoulder 17 of the control piston 5 is limited.
  • the coupler space 15 is annular in the embodiment shown here and encloses an annular projection 18 of the control piston fifth
  • the injection valve member 19 defines a second control chamber 20, which is formed in the control piston 5.
  • an edge 21 is formed, which cooperates with a seat 22 in the lower housing part 14. Once the edge 21 is in the seat 22, the at least one injection opening 23 is closed, via which fuel is injected into a combustion chamber of an internal combustion engine.
  • the injection valve member 19 is surrounded by a nozzle chamber 24.
  • the nozzle chamber 24 is connected via a high pressure line 25 to the actuator chamber 6. In this way, fuel under system pressure reaches the nozzle chamber 24 from the actuator chamber 6 via the high-pressure line 25.
  • a shoulder 26 is formed, on which a ring 27 rests.
  • the ring 27 is received in a groove 28 in the injection valve member 19.
  • the ring 27 serves as a mechanical driver and causes the second control chamber 20 has a larger diameter than the injection valve member 19th
  • the second control chamber 20 is hydraulically connected to a third control chamber 31.
  • the third control chamber 31 protrudes an end face 32 of the annular projection 18 of the control piston fifth
  • a first spring element 33 is received in the first control chamber 4, which is preferably a compression spring designed as a spiral spring.
  • the first spring element 33 is supported with one side against the booster piston 3 and with the other side against the control piston 5.
  • a second spring element 34 is received to support the movement of the injection valve member 19.
  • the second spring element 34 is also preferably a compression spring designed as a spiral spring.
  • the second spring element 34 is supported on one side against the control piston 5 and on the other side against the injection valve member 19 from.
  • an annular bearing 35 is received, wherein the outer diameter of the annular support 35 preferably the diameter of the second control chamber 20 corresponds, wherein a free movement of the annular support 35 in the second control chamber 20 must be ensured.
  • a second annular projection 36 is formed on the side facing in the first control chamber 4 side.
  • the second annular projection 36 preferably terminates flush with the underside of the passage opening 7 when the injection opening 23 is closed.
  • the passage opening 7 is at least partially closed by the second annular projection 36. In this way, a throttling of the fuel flowing through the passage opening 7 takes place.
  • the actuator 2 which is preferably in the form of a piezoactuator, is not energized.
  • the actuator 2 is energized.
  • the booster piston 3 is moved in the direction of the at least one injection opening 23.
  • the end face 16 of the booster piston 3 moves into the coupler space 15.
  • the volume in the coupler space 15 is reduced, whereby the pressure in the coupler space 15 increases.
  • the increasing pressure in the coupler space 15 acts on the shoulder 17 of the control piston 5.
  • the control piston 5 is moved in the axial direction in the direction of the actuator 2 in the first control chamber 4.
  • the first spring element 33 designed as a compression spring is compressed by the movements of the booster piston 3 and the control piston 5. Due to the decreasing volume in the first control chamber 4, the pressure increases therein. As long as the passage opening 7 is not closed by the second annular projection 36 on the control piston 5, a pressure equalization takes place between the first control chamber 4 and the actuator chamber 6.
  • the ratio in which the force is translated from the booster piston 3 to the control piston 5 results in a circular cross-section of the pistons 3, 5 from the outer diameter d] of the booster piston 3, the outer diameter d 2 of the control piston 5 and the outer diameter d 3 of the annular projection 18.
  • the gear ratio then results in (d! 2 -d 2 2 ) / (d 2 2 -d 3 2 ).
  • system pressure also prevails when the injection opening 23 is open in the nozzle chamber 24.
  • the system pressure acts on the injection port 23 facing side of the injection valve member 19. Due to the lower pressure in the second control chamber 20, the injection valve member 19 is moved into the second control chamber 20.
  • the second spring element 34 which is designed as a compression spring, compressed.
  • the opening cross-section in the region of the edge 21 is increased, thereby reducing the throttling effect.
  • the power supply to the actuator 2 is terminated.
  • the actuator 2 contracts.
  • the booster piston 3, supported by the compression spring element 8, is moved with the end face 16 out of the coupler space 15.
  • the volume in the coupler chamber 15 increases, whereby the pressure drops in it.
  • the control piston 5 is moved with the shoulder 17 into the coupler space 15.
  • the end face 32 of the annular projection 18 moves into the third control chamber 31.
  • the pressure in the third control chamber 31 increases. Due to the increasing pressure in the control chamber 20, the injection valve member 19 is supported by the second spring element 34 in the direction of the seat 22 moves until the injection valve member 19 with the edge 21 in the Seat 22 is and so the at least one injection port 23 closes.
  • the filling of the coupler chamber 15 with fuel takes place via leakage flows between the booster piston 3 and the sleeve 3 surrounding the booster piston 3 or via a leakage flow between the booster piston 3 and the control piston 5.

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 un injecteur de carburant permettant d'injecter du carburant dans une chambre à combustion d'un moteur à combustion interne et comprenant au moins un orifice d'injection (23) pouvant être fermé ou libéré par un obturateur (19) de soupape d'injection. L'obturateur (19) de soupape d'injection est commandé par un actionneur (2). Un piston multiplicateur (3), ouvert d'un côté et en liaison avec l'actionneur (2), abrite un piston de commande (5) mobile. Un talon (18) annulaire est formé sur la face du piston de commande (5) opposée au piston multiplicateur (3). L'obturateur (19) de la soupape d'injection est guidé dans ce talon de telle façon que, lorsque l'actionneur (2) est sous tension, le ou les orifices d'injection (23) est/sont libéré(s) et, lorsque l'actionneur (2) n'est pas sous tension, le ou les orifices d'injection (23) est/sont fermé(s).
PCT/EP2006/060318 2005-04-06 2006-02-28 Injecteur de carburant dote d'un actionneur piezoelectrique WO2006106017A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510015731 DE102005015731A1 (de) 2005-04-06 2005-04-06 Kraftstoffinjektor mit Piezoaktor
DE102005015731.9 2005-04-06

Publications (2)

Publication Number Publication Date
WO2006106017A2 true WO2006106017A2 (fr) 2006-10-12
WO2006106017A3 WO2006106017A3 (fr) 2007-07-12

Family

ID=36143431

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/060318 WO2006106017A2 (fr) 2005-04-06 2006-02-28 Injecteur de carburant dote d'un actionneur piezoelectrique

Country Status (2)

Country Link
DE (1) DE102005015731A1 (fr)
WO (1) WO2006106017A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2022976A1 (fr) * 2007-07-23 2009-02-11 Robert Bosch GmbH Injecteur

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007011693B4 (de) * 2007-03-09 2008-11-13 Continental Automotive Gmbh Verfahren und Vorrichtung zum Steuern einer Brennkraftmaschine
JP5051102B2 (ja) * 2008-11-17 2012-10-17 株式会社日本自動車部品総合研究所 燃料噴射弁
JP5024320B2 (ja) * 2009-03-25 2012-09-12 株式会社デンソー 燃料噴射弁
DE102009024596A1 (de) 2009-06-10 2011-04-07 Continental Automotive Gmbh Einspritzventil mit Übertragungseinheit
DE102009024595A1 (de) 2009-06-10 2011-03-24 Continental Automotive Gmbh Einspritzventil mit Übertragungseinheit

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1174615A2 (fr) 2000-07-18 2002-01-23 Delphi Technologies, Inc. Injecteur de combustible

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19519191C2 (de) * 1995-05-24 1997-04-10 Siemens Ag Einspritzventil
DE10145620B4 (de) * 2001-09-15 2006-03-02 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
DE10326259A1 (de) * 2003-06-11 2005-01-05 Robert Bosch Gmbh Injektor für Kraftstoff-Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren
DE10336327B4 (de) * 2003-08-07 2016-03-17 Robert Bosch Gmbh Injektor für Kraftstoff-Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1174615A2 (fr) 2000-07-18 2002-01-23 Delphi Technologies, Inc. Injecteur de combustible

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2022976A1 (fr) * 2007-07-23 2009-02-11 Robert Bosch GmbH Injecteur

Also Published As

Publication number Publication date
DE102005015731A1 (de) 2006-10-12
WO2006106017A3 (fr) 2007-07-12

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