EP1491760B1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant Download PDF

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Publication number
EP1491760B1
EP1491760B1 EP20040009262 EP04009262A EP1491760B1 EP 1491760 B1 EP1491760 B1 EP 1491760B1 EP 20040009262 EP20040009262 EP 20040009262 EP 04009262 A EP04009262 A EP 04009262A EP 1491760 B1 EP1491760 B1 EP 1491760B1
Authority
EP
European Patent Office
Prior art keywords
injection valve
fuel injection
fuel
valve according
flexible
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 - Fee Related
Application number
EP20040009262
Other languages
German (de)
English (en)
Other versions
EP1491760A1 (fr
Inventor
Dietmar Schmieder
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1491760A1 publication Critical patent/EP1491760A1/fr
Application granted granted Critical
Publication of EP1491760B1 publication Critical patent/EP1491760B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • 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
    • F02M61/04—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

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • From DE 199 54 537 A1 discloses a fuel injection valve with an actuating strand with an actuator, a valve needle, a hydraulic conversion device and a return spring, which actuate a valve closing body known.
  • the conversion device is used to implement a small Aktorhubs to a larger valve needle and to compensate for different, temperature-induced changes in length of components.
  • On the outflow side and on the upstream side of the actuator in each case at least one flexible section is arranged, which compensates for relative movements of the valve needle relative to the actuator or other components and keeps fuel away from the actuator. Due to the corrugated pipe-shaped design of the flexible sections is to prevent the one side acted upon by fuel with fuel pressure flexible portions exert axial forces on the actuation strand.
  • a disadvantage of this known prior art is that the flexible portions acting as a seal very need to be prepared consuming to achieve a satisfactory fatigue strength.
  • they in order to withstand the radially acting forces of fuel pressure, they must also have a corresponding radial stiffness.
  • This radial rigidity further increases the production costs and the production costs and has an unfavorable effect on the valve dynamics due to the associated axial rigidity. The space of such seals and the surface acted upon by the fuel pressure is increased.
  • the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that can be dispensed with unfavorably large, error-prone, the valve dynamics negatively influencing and consuming produced flexible sections or seals.
  • the manufacturing cost of the fuel injection valve is thereby substantially reduced, the size can be reduced without functional losses and the reliability of the fuel injection valve is increased.
  • the forces of fuel pressure acting in opposite axial directions can be advantageously used to assist or take over operations in the fuel injector.
  • a spring element biasing the actuator alone which extends, for example, as a Bourdon tube around the actuator, can be dimensioned with a lesser pretensioning force or, if appropriate, can be dispensed with altogether.
  • the actuator module can thus be more easily assembled and mounted.
  • the actuation strand has a hydraulic coupler for compensating temperature-induced changes in length of the actuator and / or other components and / or for Hubuma, wherein the coupler is arranged on the inflow side of the actuator in a further development.
  • the fuel injection valve can be designed particularly reliable and easy to set up.
  • the coupler cylinder can thus be arranged in a particularly simple manner, for example in the valve housing.
  • the hydraulic coupler has a compensation chamber, a leakage gap and a membrane space, the leakage gap connecting the compensation chamber with the membrane space, then the hydraulic coupler is constructed in a particularly simple manner.
  • the hydraulic coupler is completely filled with a hydraulic medium and a third flexible section separates the hydraulic medium from fuel.
  • the coupler can thus be designed in particular durable and reliable, since the properties of the hydraulic medium can be largely selected independently of the choice of fuel. As a result, for example, the viscosity and the lubricating properties of the hydraulic medium can be freely selected.
  • the third flexible portion is designed so that it transmits the fuel pressure applied to it on one side for the most part to the hydraulic medium.
  • the fuel pressure can be used in a particularly simple and advantageous manner to keep the expansion chamber filled with hydraulic fluid.
  • the flexible portions are perforated plate-shaped and formed in cross-section substantially U-shaped.
  • the flexibility will increased, thereby the flexible sections can be easily joined and are easy to manufacture.
  • the fuel injection valve can be made particularly compact.
  • the individual flexible sections are connected via flanges to the actuation line.
  • the flexible sections can be particularly easily connected to the actuation strand.
  • the first flexible portion and the second flexible portion are arranged so that the medium and directly acting on the valve closing body fuel pressure in terms of power, in the axial direction of the actuation strand, picks up. Due to the hydraulic force compensation achieved in this way, in particular the spring force of a biasing spring acting on the actuation strand can be selected to be much smaller. Due to the reduced spring force acting opposite to the confirmation direction of the actuator biasing spring, a smaller and less expensive actuator can be used. The power requirement of the actuator is reduced and the heat development in the actuator and in the control unit are reduced.
  • the coupler Due to the reduced spring force acting on the coupler, the coupler can very quickly compensate for temperature-related linear expansion even in cold start phases in which the valve opening times are generally extended, thereby also allowing cold start phases with reduced fuel pressure.
  • the fuel injection valve 1 according to the invention shown schematically in Fig. 1 is particularly suitable as a fuel injection valve 1 for fuel injection systems for mixture-compressing, spark-ignited internal combustion engines for direct injection of fuel into the combustion chamber of the internal combustion engine.
  • the fuel injection valve 1 comprises in particular a piezoelectric, magnetostrictive or electrostrictive actuator 2, which is arranged in an actuator module 22.
  • the actuator 2 or the actuator module 22 is part of a confirmation string, which in this embodiment also has a hydraulic coupler 3 arranged on the inflow side of the actuator module 22 and a valve needle 4 arranged downstream of the actuator module 22.
  • the actuator module 22, the hydraulic coupler 3 and the valve needle 4 are arranged coaxially in a valve housing 6.
  • the valve housing 6 has at its downstream end a nozzle body 5, through which the valve needle 4 coaxially engages and at its downstream end an integrally formed with the nozzle body 5 valve seat body 10 having a spray opening 7 is arranged.
  • a valve seat surface 9 formed on the valve seat body 10 cooperates with a valve closing body 8 formed on the discharge end of the valve needle 4 to form a sealing seat.
  • the fuel injection valve 1 opens to the outside.
  • the valve housing 6 On the inflow side, the valve housing 6 has a valve top 33.
  • the upper valve part 33 is hermetically sealed on the inflow-side end of the valve housing 6 with a first shoulder 34, where it is joined to the valve housing 6, for example by a material fit, and engages with its downstream end into the valve housing 6.
  • Coaxially formed in the upper valve part 33 is a coupler cylinder 23 which is open towards the actuator module 22 and into which a compensating piston 21 engages.
  • the side of the balance piston 21 is located between the balance piston 21 and the coupler cylinder 23, a leakage gap 24.
  • the leakage gap 24 connects a top formed between the coupler cylinder 23 and the balance piston 21 equalization chamber 31 and a bottom, the actuator module 22 oriented toward the membrane space 32nd Die Membranraum 32nd is completed by a third flexible portion 28 downstream or sealed.
  • the membrane-like and hole-plate-shaped third flexible section 28 in the exemplary embodiment is hermetically sealed in the region of the outer circumference with the downstream end of the valve top part 33 engaging below a diameter-reducing second shoulder 35, for example by welding or other cohesive joining methods.
  • the third flexible section 28 is joined hermetically sealed and cohesively on the compensating piston 21, which tapers toward the actuator module 22 and passes through the third flexible section 28.
  • the steel or a steel government existing third flexible section 28 in cross-section on a U-shaped, or wave-shaped course is thereby not claimed to train, but advantageously to bending.
  • the coupler cylinder 23, the balance piston 21, the compensation chamber 31, the leakage gap 24 and the diaphragm space 32 in this embodiment form the hydraulic coupler 3.
  • the hydraulic coupler 3, or the compensation chamber 31, the leakage gap 24 and the diaphragm space 32 are completely with a Hydraulic medium 30 filled.
  • the hydraulic medium 30 is in this embodiment, a good heat-conducting and highly viscous oil.
  • an electrical connection 15 and a fuel inlet 16 which divides into a first fuel channel 17 and a second fuel channel 18.
  • the electrical connection 15 extends further in the valve housing 6 in order to enter the height of the actuator module 22 in this.
  • a hole-plate-shaped first flexible section 25 of substantially U-shaped design and consisting of steel is joined to its outer circumference with a material fit and hermetically sealed.
  • this is on the upper side of a third flange 29, which surrounds the diameter-tapered, downstream end of the balance piston 21, cohesively and hermetically sealed.
  • the third flange 29 engages with its downstream end in a arranged in the top of the actuator module 22 in an actuator base 13 conical recess 27 with which he is ideally in constant contact.
  • annular groove 36 is arranged.
  • the space located between the first flexible section 25 and the third flexible section 28 is completely filled with fuel via the first fuel channel 17.
  • the fuel presses in each case on one side of the first flexible portion 25 and third flexible portion 28.
  • Fuel pressure acts in this way on the compared to the first flexible portion 25 softer, in particular thinner, third flexible portion 28 on the hydraulic medium 30.
  • the between the The third flexible portion 28 and the first flexible portion 25 prevailing fuel pressure also acts on the first flexible portion 25 so that the actuator module 22 is loaded from above via the third flange 29 on the actuator base 13 with a force acting in the ejection direction bias.
  • the valve needle 4 is biased by a biasing spring 11, which acts on the valve needle 4 via a second flange 20, against the discharge direction.
  • the valve closing body 8 is thereby pulled into the sealing seat and the conically shaped, inflow-side end of the valve needle 4 is pressed into a second recess 37 arranged in an actuator head 12.
  • a first flange 19 is materially connected, for example by welding, with the valve needle 4.
  • a second flexible portion 26 with the underside of the first flange 19 is firmly bonded and hermetically sealed. In the region of the outer periphery of the second flexible portion 26, this is connected to the nozzle body 5 cohesively and hermetically sealed.
  • the second flexible portion 26 may be joined in the region of its outer periphery with the valve housing 6.
  • the one-sided to the second flexible section 26 acting fuel pressure pushes the valve needle 4 in the axial direction to the actuator module 22 through the first flange 19, against the Abspritzraum.
  • a belonging to the actuator module 22 spring element 14 biases the actuator foot 13 against the actuator head 12, so that the actuator 2 is under bias.
  • the actuator 2 If the actuator 2 is excited via the electrical connection 15, then it expands in the axial direction and acts on the compensating piston 21 via the actuator foot 13. Due to the speed of movement of the actuator 2 and the relatively narrow leakage gap 24, the hydraulic medium 30 behaves similar to a solid. The changes in length of the actuator 2 can be transmitted almost completely to the valve needle 4, whereby the valve closing body 8 lifts off from the valve seat surface 9 and fuel is injected into the combustion chamber, not shown, of the internal combustion engine, not shown. During slow movements of the actuator 2, for example due to thermal influences, the hydraulic medium 30 is displaced through the leakage gap 24 into the membrane space 32, whereby an arbitrary opening of the fuel injection valve 1 is prevented.
  • the first flexible portion 25 and the second flexible portion 26 are dimensioned and arranged so that the forces of the fuel pressure acting axially, indirectly and directly on the valve closing body 8 cancel each other out substantially.
  • the fuel injection valve 1 can thereby be operated at different fuel pressures without, for example, the spring force of the biasing spring 11 must be made adaptive by consuming measures.
  • FIG. 2 shows a schematic illustration of a second exemplary embodiment of a fuel injection valve 1 according to the invention in the region of the actuator head 12, similar to the first exemplary embodiment from FIG There is no difference between the third flexible section 28 used in the first exemplary embodiment.
  • the fuel passed through the first fuel channel 17 and the annular groove 36 fills the hydraulic coupler 3, with which the hydraulic medium 30 consists of fuel.
  • the structure of the fuel injection valve 1 is thereby simplified.

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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 (14)

  1. Injecteur de carburant (1), en particulier pour l'injection directe de carburant dans une chambre de combustion d'un moteur à combustion interne, comprenant un système d'actionnement qui présente un actionneur (2) piézoélectrique, électrostrictif ou magnétostrictif en liaison active avec un obturateur de soupape (8) qui coopère avec une surface de siège de soupape (9) pour former un siège d'étanchéité, avec au moins un premier segment flexible (25) sollicité d'un côté par la pression du carburant et disposé en amont de l'actionneur (2) et avec au moins un deuxième segment flexible (26) sollicité d'un côté par la pression du carburant et disposé en aval de l'actionneur (2),
    caractérisé en ce que
    le premier segment flexible (25) et le deuxième segment flexible (26) sont disposés pour que les segments flexibles (25, 26) ou la pression du carburant agissant sur eux exercent sur l'actionneur (2) ou sur le système d'actionnement des forces axiales opposées, les segments flexibles (25, 26) présentant une section transversale pour l'essentiel en forme de U.
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le système d'actionnement (2) présente un coupleur hydraulique (3).
  3. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    le coupleur (3) est disposé en amont de l'actionneur (2).
  4. Injecteur de carburant selon la revendication 2 ou 3,
    caractérisé en ce que
    le coupleur hydraulique (3) présente au moins une chambre de compensation (31), au moins un interstice de fuite (24) et une chambre de membrane (32), l'interstice de fuite (24) reliant la chambre de compensation (31) à la chambre de membrane (32).
  5. Injecteur de carburant selon l'une quelconque des revendications 2 à 4,
    caractérisé en ce que
    le coupleur hydraulique (2) est rempli entièrement avec un fluide hydraulique (30), au moins un troisième segment flexible (28) séparant ou rendant le fluide hydraulique (30) étanche par rapport au carburant.
  6. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que
    le troisième segment flexible (28) sépare ou rend la chambre de membrane (32) étanche par rapport au carburant.
  7. Injecteur de carburant selon la revendication 5 ou 6,
    caractérisé en ce que
    le troisième segment flexible (28) transmet la majeure partie de la pression du carburant sur le fluide hydraulique (30).
  8. Injecteur de carburant selon l'une quelconque des revendications 5 à 7,
    caractérisé en ce que
    le fluide hydraulique (30) est une huile.
  9. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    au moins l'un des segments flexibles (25, 26, 28) se présente sous la forme d'une plaque perforée.
  10. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le système d'actionnement (2, 3) traverse au moins l'un des segments flexibles (25, 26, 28).
  11. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la circonférence intérieure d'au moins un des segments flexibles (25, 26, 28) est reliée au système d'actionnement (2, 3) par complémentarité de matériaux et de manière étanche.
  12. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les segments flexibles (25, 26, 28) sont en acier ou en alliage d'acier.
  13. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    au moins un des segments flexibles (25, 26, 28) est en liaison avec le système d'actionnement (2, 3) par une première bride (19), une deuxième bride (20) ou une troisième bride (29).
  14. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le premier segment flexible (25) et le deuxième segment flexible (26) sont disposés et dimensionnés de manière à ce que les forces axiales de la pression de carburant agissant indirectement et directement sur l'obturateur de soupape (8) s'annulent mutuellement pour l'essentiel.
EP20040009262 2003-06-25 2004-04-20 Soupape d'injection de carburant Expired - Fee Related EP1491760B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10328573 2003-06-25
DE10328573A DE10328573A1 (de) 2003-06-25 2003-06-25 Brennstoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP1491760A1 EP1491760A1 (fr) 2004-12-29
EP1491760B1 true EP1491760B1 (fr) 2006-09-27

Family

ID=33394978

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040009262 Expired - Fee Related EP1491760B1 (fr) 2003-06-25 2004-04-20 Soupape d'injection de carburant

Country Status (2)

Country Link
EP (1) EP1491760B1 (fr)
DE (2) DE10328573A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008041544B4 (de) * 2008-08-26 2016-05-12 Robert Bosch Gmbh Ventil zur Zumessung eines flüssigen oder gasförmigen Mediums

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3533085A1 (de) * 1985-09-17 1987-03-26 Bosch Gmbh Robert Zumessventil zur dosierung von fluessigkeiten oder gasen
JPH09287511A (ja) * 1996-04-19 1997-11-04 Futaba Corp 模型用エンジン及び模型用エンジンの制御方法
DE19901711A1 (de) * 1999-01-18 2000-07-20 Bosch Gmbh Robert Brennstoffeinspritzventil und Verfahren zum Betreiben eines Brennstoffeinspritzventils
DE19912665A1 (de) * 1999-03-20 2000-09-21 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19928916B4 (de) * 1999-06-24 2017-12-14 Robert Bosch Gmbh Brennstoffeinspritzventil
DE19940054C2 (de) * 1999-08-24 2003-11-27 Siemens Ag Dosierventil für ein unter Druck stehendes Fluid
DE19946869A1 (de) * 1999-09-30 2001-04-05 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19954537A1 (de) * 1999-11-12 2001-05-17 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19962177A1 (de) * 1999-12-22 2001-07-12 Siemens Ag Hydraulische Vorrichtung zum Übertragen einer Aktorbewegung
DE10003863B4 (de) * 2000-01-28 2004-11-18 Robert Bosch Gmbh Einspritzdüse
DE10007733A1 (de) * 2000-02-19 2001-08-23 Daimler Chrysler Ag Einspritzventil
DE10039543C2 (de) * 2000-08-12 2003-06-18 Conti Temic Microelectronic Einspritzventil
DE10141136A1 (de) * 2001-04-07 2002-10-10 Continental Teves Ag & Co Ohg Ventil.insbesondere für hydraulische Kraftfahrzeugbremsen
DE10129375B4 (de) * 2001-06-20 2005-10-06 Mtu Friedrichshafen Gmbh Injektor mit Piezo-Aktuator
DE10158789A1 (de) * 2001-11-30 2003-07-10 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10159749A1 (de) * 2001-12-05 2003-06-12 Bosch Gmbh Robert Brennstoffeinspritzventil

Also Published As

Publication number Publication date
EP1491760A1 (fr) 2004-12-29
DE10328573A1 (de) 2005-01-13
DE502004001567D1 (de) 2006-11-09

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