EP2126333B1 - Injecteur de carburant à coupleur - Google Patents

Injecteur de carburant à coupleur Download PDF

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Publication number
EP2126333B1
EP2126333B1 EP07858229A EP07858229A EP2126333B1 EP 2126333 B1 EP2126333 B1 EP 2126333B1 EP 07858229 A EP07858229 A EP 07858229A EP 07858229 A EP07858229 A EP 07858229A EP 2126333 B1 EP2126333 B1 EP 2126333B1
Authority
EP
European Patent Office
Prior art keywords
coupler
valve member
injection valve
fuel injector
valve 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.)
Active
Application number
EP07858229A
Other languages
German (de)
English (en)
Other versions
EP2126333A1 (fr
Inventor
Andreas Kellner
Holger Rapp
Martin Katz
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 EP2126333A1 publication Critical patent/EP2126333A1/fr
Application granted granted Critical
Publication of EP2126333B1 publication Critical patent/EP2126333B1/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
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • 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

Definitions

  • Out DE 196 50 865 A1 is a solenoid valve for controlling the fuel pressure in a control chamber of an injection valve, such as for a common rail injection system, known. Via the fuel pressure in the control chamber, a stroke movement of a valve piston is controlled, with which an injection opening of the injection valve is opened or closed.
  • the solenoid valve comprises an electromagnet, a movable armature and a valve member which is moved with the armature and acted upon by a valve closing spring in the closing direction, which cooperates with the valve seat of the solenoid valve and thus controls the fuel drain from a control chamber.
  • a fuel injector which has a coupler, with which the force of a piezoelectric actuator is transmitted to a valve needle by the piezoelectric actuator moves a coupler piston and the movement of the coupler piston is transmitted through a fuel-filled coupler space on the valve needle.
  • the hydraulic coupler comprises a coupler sleeve with an internal bore in which the valve piston is guided.
  • the diameter of the coupler sleeve is larger than the outer diameter of the needle-shaped injection valve member.
  • the coupler sleeve rests on a nozzle body at its lower end with a sealing edge formed on its end face and thus encloses a coupler volume.
  • the coupler sleeve is employed in the idle state with a small, applied via a coil spring force to an end face of the nozzle needle.
  • the coupler sleeve or the coupler is surrounded by fuel under system pressure.
  • system pressure is meant the fuel pressure level generated in a fuel injection system, such as via a high pressure pump, within a high pressure reservoir body (common rail).
  • valve piston If the fuel injector is activated, the valve piston first moves upwards. This upward movement creates a negative pressure in the coupler volume compared to the external system pressure level. Due to the negative pressure follows the needle-shaped formed injection valve member to the valve piston and, as a result, rests again on its front side opposite the preferred needle-shaped injection valve member. As the valve piston stroke increases, the pressure in the coupler volume decreases because, due to the difference in diameter between the inner bore of the coupler sleeve and the outer diameter of the needle-shaped injection valve member, the available fuel volume in the coupler increases. After the end of the control, the valve piston and the needle-shaped injection valve member move back in the closing direction downwards.
  • the coupler sleeve on the valve piston with a comparatively large guide clearance on the order of a few microns, z. B. 8 microns, and over a length of a few mm, such. B. 5 mm, out.
  • the inner diameter of the coupler sleeve is about 3.8 mm and the outer diameter of the needle-shaped injection valve member is 3.5 mm.
  • a leak-free fuel injector which by means of an actuator, such as. B. a solenoid valve, is operable, wherein the difference in diameter between the inner diameter of the coupler sleeve and the outer diameter of the preferably needle-shaped injection valve member is not more than 0.2 mm.
  • the guide play between the injection valve member enclosing the coupler sleeve and the valve piston guided therein is reduced, in particular to a value of a few microns, such. B. to values of less than 5 microns. Due to the fact that the inflow volume flow is proportional to the pressure difference over the guide length but inversely proportional to the third power of the guide game, this measure is highly effective in terms of the flow of fuel into the coupler.
  • the guide length between the coupling needle sleeve which surrounds the preferably needle-shaped injection valve member and the needle-shaped injection valve member can be increased to values of more than 5 mm. Since the time delay until the needle-shaped injection valve member opens increases more and more as the volume of the coupler increases, the volume of the coupler remains limited to ⁇ 40 mm 3 in the idle state.
  • the subsequent flow of fuel into the coupler is largely reduced by the solution proposed by the invention during the injection process.
  • the volume of fuel contained in the coupler or the dead volume present there is kept small without the fuel afterflow in order to achieve the most direct possible coupling of the valve needle to reach with the valve piston.
  • a transition region is formed on the valve piston of the coupler, within which the diameter of the valve piston passes in a diameter corresponding to the diameter of a bore formed in the nozzle body, in which the injection valve member is guided with the outer diameter.
  • FIG. 1 is an embodiment of a coupler for a fuel injector according to the prior art can be seen.
  • FIG. 1 shows that a fuel injector 10 comprises a particular needle-shaped injection valve member 12.
  • the needle-shaped injection valve member 12 is guided in a bore 14 of a nozzle body 18.
  • the fuel injector 10 includes a cavity 16 in which system pressure p sys prevails.
  • the system pressure p sys corresponds to a pressure level which z. B. by a high pressure pumping unit in a storage body (common rail) is generated.
  • the nozzle body 18 comprises a bore 14, in which the particular needle-shaped injection valve member 12 is guided, and which has an end face 20.
  • An axis of the particular needle-shaped injection valve member 12 is denoted by reference numeral 22 and extends coaxially to the axis of a valve piston 24.
  • the valve piston 24 includes an end face 26 which faces an end face 28 of the particular needle-shaped injection valve member 12.
  • the valve piston 24 is enclosed by a coupler sleeve 30.
  • the coupler which comprises the valve piston 24 and the coupler sleeve 30 surrounding it, the stroke movement of an actuator, such as an electromagnet, for example or a piezoelectric actuator, to which in particular needle-shaped injection valve member 12 transmit.
  • an actuator such as an electromagnet, for example or a piezoelectric actuator
  • the coupler sleeve 30 comprises a first end face 32 and a second end face 34.
  • a biting edge 36 is formed on the second end face 34 of the coupler sleeve 30. With the biting edge 36, the coupler sleeve 30 is set against the end face 20 of the nozzle body 18.
  • the coupler sleeve 30 is a in FIG. 1 not shown biasing element acted upon by a biasing force. From the illustration according to FIG. 1 It can be seen that the valve piston 24, which is part of the hydraulic coupler, comprises a constriction 38.
  • the in FIG. 1 shown fuel injector 10 has between the inner diameter of the coupler sleeve 30 and the outer diameter of the injection valve member 12 has a diameter difference in the order of 0.3 mm.
  • This guide clearance leads to a lag of the coupler pressure with respect to the system pressure p sys by about 100 ⁇ s. Due to the guide clearance, which results from the difference in diameter in the order of 0.3 mm, runs during the lifting movement of the valve piston 24, a fuel quantity after. Since the coupler sleeve 30 lifts off after each injection of the end face 20 of the nozzle body 18, the coupler sleeve 30 is found after each injection a slightly different position, wherein the shape of the guide gap changes from injection to injection process.
  • the amount of fuel flowing into the coupler volume influences the closing movement and the closing time of the preferably needle-shaped injection valve member 12, which leads to lift / stroke spreads that are significantly greater compared to conventional injectors.
  • the valve piston is surrounded by fuel at low pressure (low pressure). This results in a continuous leakage from the control chamber along the valve piston guide on the one hand and from the high-pressure chamber along the injection valve member along the guide of the injection valve member in the surrounding the valve piston volume.
  • the volume surrounding the valve piston is connected to the high pressure area.
  • the leakage is omitted due to the lack of a pressure gradient on the guides of the relatively movable components.
  • FIG. 2 The representation according to FIG. 2 is a section through a proposed inventions coupler.
  • the needle-shaped injection valve member 12 includes, which is guided in the bore 14 of the nozzle body 18.
  • pressure p sys prevails.
  • the coupler sleeve 30 is employed at the end face 20 of the nozzle body 18. Their first end face is indicated by reference numeral 32 and the second end face by reference numeral 34.
  • Coupler sleeve 30 shown has the coupler sleeve 30 used in accordance with the invention proposed fuel injector 10 has a substantially rectangular cross-section.
  • the axis of the preferably needle-shaped injection valve member 12 is designated by reference numeral 22.
  • the biting edge 36 is located on the second end face 34 of the coupler sleeve 30, which has a substantially rectangular cross-section.
  • the coupler sleeve 30 is set against the end face 20 of the nozzle body 18 due to the effect of an adjusting force 50. From the illustration according to FIG. 2 moreover, it is apparent that a guide play 40 between the inner diameter 46 of the coupler sleeve 30 and the outer diameter of the valve piston 24 is ⁇ 5 ⁇ m.
  • the valve piston 24 has in the region, ie its guide length 58, in which this is guided in the coupler sleeve 30, the diameter 46, taking into account the guide clearance 40 of ⁇ 5 microns on the coupler sleeve 30.
  • a transition region 42nd indicated within which the diameter of the valve piston 24 merges into a diameter which corresponds to the diameter of the nozzle body 18 formed in the bore 14 and which corresponds substantially to the outer diameter 44 of the injection valve member 12. From the illustration according to FIG. 2 shows that in the illustrated stage of the lifting phase of the preferably needle-shaped injection valve member 12 and the valve piston 24 of the coupler, the end face 26 of the valve piston 24 abuts an end face 28 of the preferably needle-shaped injection valve member 12.
  • a coupler space 54 is formed, which has a coupler volume which is of the order of ⁇ 40 mm 3 .
  • the bore 14, in which a part of the valve piston 24 of the coupler and the preferably needle-shaped injection valve member 12 in Nozzle body 18 are guided, has a chamfer 52 on the end face 20.
  • a bevel 56 may be formed on the end face 26 of the valve piston 24 of the coupler.
  • the end faces 26 and 28 of the valve piston 24 or preferably needle-shaped injection valve member 12 executed plan.
  • 2 shown Kraftstoffinjektor 10 has on the one hand a difference in diameter between the inner diameter 46 of the coupler sleeve 30 and the outer diameter 44 of the preferably needle-shaped injection valve member 12 between 0.2 mm and 0 mm. Because of this small remaining difference in diameter, the pressure drop within the coupler during the lifting movement of the preferably needle-shaped injection valve member 12 is reduced. If the difference in diameter between the inner diameter 46 of the coupler sleeve 30 and the outer diameter 44 of the preferably needle-shaped injection valve member 12 0 mm, creates a pressure difference ⁇ p only during the lifting of the preferably needle-shaped injection valve member 12 from its seat and disappears again as soon as the preferably needle-shaped Injector valve member has left the seat throttle area.
  • the guide clearance 50 between the coupler sleeve 30 and the valve piston 24 is reduced to values ⁇ 5 ⁇ m, so that the volume flow flowing in via the reduced guide clearance 50 into the coupler space 54 is effectively reduced. Furthermore - as in FIG. 2 shown - the guide length 58, within which the valve piston 24 of the coupler is guided in the coupler sleeve 30, in comparison to in FIG. 1 shown guide length considerably extended. In order to achieve a lag-free as possible lagging the preferably needle-shaped injection valve member 12 relative to the valve piston 24, the fuel volume within the coupler sleeve 30 in the closed state of the fuel injector to values ⁇ 40 mm 3 is limited.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Feeding And Controlling Fuel (AREA)

Claims (9)

  1. Injecteur de carburant (10) comprenant un coupleur (24, 30) pour transférer le mouvement de course d'un actionneur à un organe de soupape d'injection (12) réalisé notamment en forme de pointeau, qui est guidé dans un corps de buse (18), le coupleur (24, 30) comprenant un piston de soupape (24) et une douille de coupleur (30), l'organe de soupape d'injection (12) présentant un diamètre extérieur (44) et la douille de coupleur (30) un diamètre intérieur (46), le piston de soupape (24) étant guidé dans le diamètre intérieur (46) de la douille de coupleur (30), et le diamètre intérieur (46) de la douille de coupleur (30) étant supérieur au diamètre extérieur (44) de l'organe de soupape d'injection (12), caractérisé en ce que la différence entre le diamètre intérieur (46) de la douille de coupleur (30) et le diamètre extérieur (44) de l'organe de soupape d'injection (12) vaut au maximum 0,2 mm et une zone de transition (42) est réalisée sur le piston de soupape (24) du coupleur, à l'intérieur de laquelle le diamètre du piston de soupape (24) se prolonge avec un diamètre qui correspond au diamètre d'un alésage (14) pratiqué dans un corps de buse (18), dans lequel est guidé l'organe de soupape d'injection (12) avec le diamètre extérieur (44).
  2. Injecteur de carburant (10) selon la revendication 1, caractérisé en ce qu'un espace de coupleur (54) est réalisé entre le piston de soupape (24), la douille de coupleur (30) et l'organe de soupape d'injection (12), et en ce que le volume de coupleur de l'espace de coupleur (54) vaut au maximum 40 mm3.
  3. Injecteur de carburant (10) selon la revendication 1 ou 2, caractérisé en ce qu'un jeu de guidage (40) entre la douille de coupleur (30) et le piston de soupape (24) vaut au maximum 5 µm.
  4. Injecteur de carburant (10) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une longueur de guidage (58), à l'intérieur de laquelle sont guidés le piston de soupape (24) et la douille de coupleur (30), vaut au moins 5 mm.
  5. Injecteur de carburant (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'alésage (14) présente un biseau (52) dans la région d'un côté frontal (20) du corps de buse (18).
  6. Injecteur de carburant (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que la douille de coupleur (30) est avancée avec une force de précontrainte (50) contre un côté frontal (20) du corps de buse (18).
  7. Injecteur de carburant (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que la douille de coupleur (30) présente une arête d'attaque (36).
  8. Injecteur de carburant (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que le piston de soupape (24) présente un biseau (56) sur son côté frontal (26) tourné vers l'organe de soupape d'injection (12).
  9. Injecteur de carburant (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que la douille de coupleur (30) présente, parallèlement à son axe de symétrie, une section transversale essentiellement rectangulaire.
EP07858229A 2007-01-16 2007-12-28 Injecteur de carburant à coupleur Active EP2126333B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007002282A DE102007002282A1 (de) 2007-01-16 2007-01-16 Kraftstoffinjektor mit Koppler
PCT/EP2007/064641 WO2008086941A1 (fr) 2007-01-16 2007-12-28 Injecteur de carburant à coupleur

Publications (2)

Publication Number Publication Date
EP2126333A1 EP2126333A1 (fr) 2009-12-02
EP2126333B1 true EP2126333B1 (fr) 2010-09-29

Family

ID=39481238

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07858229A Active EP2126333B1 (fr) 2007-01-16 2007-12-28 Injecteur de carburant à coupleur

Country Status (9)

Country Link
US (1) US7992810B2 (fr)
EP (1) EP2126333B1 (fr)
JP (1) JP5002023B2 (fr)
CN (1) CN101583790A (fr)
AT (1) ATE483106T1 (fr)
BR (1) BRPI0718797B1 (fr)
DE (2) DE102007002282A1 (fr)
RU (1) RU2452867C2 (fr)
WO (1) WO2008086941A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10620106B2 (en) * 2017-12-15 2020-04-14 Microjet Technology Co., Ltd. Particulate matter measuring device
CN114135430B (zh) * 2021-12-08 2023-01-06 一汽解放汽车有限公司 一种燃料喷射阀

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0262539B1 (fr) * 1986-09-25 1991-01-09 Ganser-Hydromag Soupape d'injection de combustible
DE4026721A1 (de) * 1990-08-24 1992-02-27 Bosch Gmbh Robert Einspritzventil und verfahren zur herstellung eines einspritzventils
DE19500706C2 (de) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen
DE19650865A1 (de) 1996-12-07 1998-06-10 Bosch Gmbh Robert Magnetventil
DE19946827C1 (de) * 1999-09-30 2001-06-21 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10145620B4 (de) * 2001-09-15 2006-03-02 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
DE102004035280A1 (de) 2004-07-21 2006-03-16 Robert Bosch Gmbh Kraftstoffinjektor mit direkter mehrstufiger Einspritzventilgliedansteuerung
DE102005007543A1 (de) 2005-02-18 2006-08-24 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine
RU2280781C1 (ru) * 2005-03-05 2006-07-27 Федеральное государственное образовательное учреждение высшего профессионального образования Воронежский государственный аграрный университет им. К.Д. Глинки Электрогидравлическая форсунка для дизеля

Also Published As

Publication number Publication date
WO2008086941A1 (fr) 2008-07-24
DE502007005235D1 (de) 2010-11-11
RU2452867C2 (ru) 2012-06-10
RU2009131122A (ru) 2011-02-27
BRPI0718797B1 (pt) 2018-08-07
DE102007002282A1 (de) 2008-07-17
US20100090032A1 (en) 2010-04-15
BRPI0718797A2 (pt) 2013-12-03
JP5002023B2 (ja) 2012-08-15
EP2126333A1 (fr) 2009-12-02
ATE483106T1 (de) 2010-10-15
US7992810B2 (en) 2011-08-09
CN101583790A (zh) 2009-11-18
JP2010515855A (ja) 2010-05-13

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