EP1511932B1 - Soupape d'injection - Google Patents

Soupape d'injection Download PDF

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Publication number
EP1511932B1
EP1511932B1 EP03745746A EP03745746A EP1511932B1 EP 1511932 B1 EP1511932 B1 EP 1511932B1 EP 03745746 A EP03745746 A EP 03745746A EP 03745746 A EP03745746 A EP 03745746A EP 1511932 B1 EP1511932 B1 EP 1511932B1
Authority
EP
European Patent Office
Prior art keywords
valve
injection valve
drive unit
hydraulic
housing
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 - Lifetime
Application number
EP03745746A
Other languages
German (de)
English (en)
Other versions
EP1511932A1 (fr
Inventor
Georg Bachmaier
Bernhard Fischer
Bernhard Gottlieb
Andreas Kappel
Hans Meixner
Enrico Ulivieri
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP1511932A1 publication Critical patent/EP1511932A1/fr
Application granted granted Critical
Publication of EP1511932B1 publication Critical patent/EP1511932B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F02M61/04—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 present invention relates to an injection valve according to the preamble of claim 1.
  • Such an injection valve is known from DE 198 54 508, wherein the valve needle is designed to open outwardly and axially pressure-effective surfaces of the valve needle and the housing are designed so that when changing the pressure of the fluid, the same axial length change to the valve needle and the valve housing occur.
  • the drive chamber, in which the drive unit is arranged, and the fluid chamber, in which the valve needle and the return spring are arranged, are reliably sealed against each other by means of a sealing ring and a drain.
  • the compensation of all pressure forces takes place in order to keep the valve needle as a whole free of pressure forces.
  • a high acting in the opening direction compressive force which is advantageously compensated by a second pressure-loaded surface which generates a force acting in the opposite direction of the same amount.
  • HPDI high-pressure direct injection
  • the hydraulic length compensation is realized by a hydraulic chamber filled with oil.
  • this requires a complex hermetic seal of the equipment, such as silicone oil, compared to the pressurized fuel, which is often realized by a metal bellows.
  • the object of the present invention is to provide a powerful injection valve with a simple hydraulic bearing.
  • the hydraulic pressure applied to the hydraulic chamber is designed to be very stiff in order to be able to absorb very high compressive and tensile forces in the short term, as is required in the rapid opening and closing of the valve.
  • the injection valve can close about 5 - 10 times as fast as a provision by a return spring alone according to the prior art.
  • the losses in Ventilnadelhub by the disadvantageous Elongation of the valve needle due to a high force acting by the return spring restoring force avoided.
  • the fuel pressure-related forces can be adjusted specifically to the valve needle.
  • a fuel pressure related closing force could be adjusted. This would ensure that the valve needle closes the valve safely even with a broken return spring.
  • the fuel flows past the drive unit and, for example, to the multilayer actuator and cools the piezoceramics.
  • Another advantage is therefore the improved temperature behavior of the injector.
  • the direct injection into the combustion chamber exposes the injector to high temperatures.
  • modern injection concepts provide for multiple injections. The trend is towards continuous injection rate molding. Concepts with 5 injections per cycle are already discussed. This creates additional waste heat. Therefore, a cooling of the injector is advantageous, even if no temperature problem has occurred in injectors according to the prior art with silicone oil as the operating means of the hydraulic bearing.
  • the hydraulic chamber is to be realized at least so high that it can compensate for any changes in length expected during the service life.
  • the hydraulic chamber is to be made as low as possible.
  • a typical height of the hydraulic chamber of 200 to 500 microns is selected.
  • FIG. 1 An embodiment of the injection valve according to the invention is described below; the single FIGURE shows the injection valve simplified in a schematic longitudinal section.
  • a high-pressure injector or the single-point valve has a valve seat 3 in an injector housing 1.
  • a diameter of the sealing line d 1 is typically 3 - 5 mm in the case of a fuel injection valve.
  • the valve seat 3 is kept closed in the ground state by a valve disc 7 connected to the lower end section of a valve needle 5 (diameter d 2 ).
  • the valve needle 5 is arranged in the valve housing 1.
  • the closed ground state, one formed by the valve seat 3 and the valve plate 7 frontally on the housing 1 injection nozzle 9 is ensured by a tensioned compression spring 11 with a typical spring force (F S ) of about 150 N.
  • the compression spring is clamped between a bottom plate 13 of a drive unit 15 and a portion of the inner wall of the valve housing 1.
  • the valve needle 5 is rigidly connected to the bottom plate 13, for example via a weld.
  • the fuel supply into an interior of the valve housing 1 is effected by a provided in the injector 1 line bore 17.
  • the drive unit 15 is arranged. This is formed from a piezoelectric multilayer actuator in low-voltage technology (PMA) 19, a tube spring 21, a hydraulic piston 23 and the bottom plate 13.
  • the tube spring 19 is welded to the hydraulic piston 23 and the bottom plate 13, so that the multilayer actuator 19 under a mechanical compression bias stands.
  • Electrical connections 25 of the drive unit 15 are guided upward out of the housing 1, as described below.
  • the hydraulic piston 23 the interior of the valve housing is in a main chamber 27, which receives in particular the PMA 19, and a hydraulic chamber 29 separated.
  • the drive unit 15 is connected to the injector housing 1 by means of a metal bellows 31 having a hydraulic or effective pressure effective diameter d 5 .
  • a metal bellows 31 having a hydraulic or effective pressure effective diameter d 5 .
  • the interior of the valve housing 1 is closed to the environment.
  • the interior is additionally connected in the region of the metal bellows 31 via a transverse line 33 to the conduit bore 17.
  • F D With increasing size of this undesired additional force (F D ), the precise control of the injection process is difficult. Particularly modern concepts with multiple injection are then hardly feasible.
  • F S > 5 • F D Preferably, at least: F S > 5 • F D , in particular F S > 10 • F D.
  • the hydraulic piston 23 is sealingly fitted by a first and a second tight clearance 35, 37 with a larger diameter d 3 and a smaller diameter d 4 in the correspondingly formed injector 1 and forms with the corresponding inner wall portions of the injector 1, the annular hydraulic chamber 29. More Way, the height of the hydraulic chamber h K is set to at least 100 - 500 microns during assembly of the injector.
  • the hydraulic chamber 29 is used, for example, to compensate for thermally induced or caused by aging effects of the PMAs 19 in the injector slow changes in length (eg typical time t> 1 s) of the drive unit 15 and / or the valve needle 5 relative to the injector 1.
  • the hydraulic chamber 29 has due to the compressibility of gasoline a spring action, which leads to an additional loss in the valve lift.
  • the drive unit 15 with the hydraulic piston 23 and the valve needle 5 form a unit which can be displaced almost unhindered with respect to the injector housing when occurring in comparison to the injection slow movements against the seat force (F D + F S ) between the valve seat. 3 and adjusts the valve plate 7.
  • the length of the annular gap is relatively uncritical, with increasing length of the leakage current decreases. Since the leakage increases with the 3rd power of the gap height h, the gap height should be sufficiently small.
  • the function of the injection valve is now as follows: In order to start the injection process, the PMA 19 is charged via the electrical connections 25. Due to the inverse piezoelectric effect of the PMA 19 expands (typical deflection: 30 - 60 microns). In this case, the PMA is supported on the rigid hydraulic chamber 29 in order to lift the valve disk 7 against the spring force F S of the compression spring 11 from the valve seat 3. Now the fuel can escape from the injection nozzle 9. The valve disk 7 is acted upon at its lower, the fuel-remote surface with the pressure of the injection chamber (not shown). As described above, the hydraulic chamber 29 is sufficiently rigid over a typical injection period. To end the injection process, the PMA 19 is discharged again via the electrical connections 25 and the PMA shortens.
  • the hydraulic pressure ( hydraulic tension) and the spring restoring force of the compression spring 11 pull the valve plate 7 in the valve seat 3 and thus close the valve.
  • the injector volume itself serves as a fuel pressure reservoir for the first injection events until the injection pump feeds the necessary fuel pressure into the injector.
  • a magnetostrictive drive can be used to actuate the valve.
  • the device described can in principle also be used for inwardly opening valves.

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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 (12)

  1. Soupape d'injection pour carburant, avec un carter de soupape (1), dans lequel une unité d'actionnement (15) commande le déplacement d'une aiguille de soupape (5) soumise à précontrainte par un ressort (11), et où un palier hydraulique avec une chambre hydraulique (29) est prévu pour l'unité d'actionnement (15), ainsi qu'une chambre principale (27) formée dans le carter de soupape et remplie de carburant agissant comme agent de fonctionnement du palier hydraulique, et dans laquelle est disposée l'aiguille de soupape, caractérisée en ce que le palier hydraulique présente une chambre hydraulique (29) communiquant, bilatéralement et par étranglement, par d'étroites fentes annulaires (35, 37) aussi bien avec la chambre principale (27) qu'avec, à l'opposé, une partie de l'espace intérieur du carter de soupape (1), cette partie de l'espace intérieur étant reliée par l'intermédiaire d'une conduite transversale (33) à une conduite de carburant (17) débouchant dans la chambre principale (27).
  2. Soupape d'injection selon la revendication 1, caractérisée en ce que le refroidissement de l'unité d'actionnement (15) est effectué par le carburant.
  3. Soupape d'injection selon la revendication 1 ou 2, caractérisée en ce que l'unité d'actionnement (15) est disposée à l'intérieur de la chambre principale (27).
  4. Soupape d'injection selon la revendication 1, 2 ou 3, caractérisée en ce que les surfaces de pression axiales de l'aiguille de soupape 5 sont dimensionnées de telle sorte qu'essentiellement les forces de pression résultantes (PD) s'annulent, de sorte que la force axiale résultante (FD) agissant sur l'aiguille de soupape (5) est maintenue petite par rapport à la force (FS) du ressort (11).
  5. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce qu'une soupape de retenue est montée dans un raccordement de l'alimentation en haute pression.
  6. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que l'aiguille de soupape (5) est reliée de façon fixe à l'unité d'actionnement (15).
  7. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que l'unité d'actionnement (15) présente un piston hydraulique (23), formant avec une section de la paroi intérieure du carter (1) la chambre hydraulique (29).
  8. Soupape d'injection selon la revendication 7, caractérisée en ce que la hauteur (hK) de la chambre hydraulique (29) se situe aux alentours de 200 à 500 µm.
  9. Soupape d'injection selon la revendication 7 ou 8, caractérisée en ce que l'unité d'actionnement (15), avec le piston hydraulique (23) et l'aiguille de soupape (5), forment une unité fixe, qui, en comparaison avec des mouvements plus lents apparaissant lors du processus d'injection, et en tenant compte des forces des ressorts, peut presque librement être décalée par rapport au carter de soupape (1).
  10. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que l'unité d'actionnement (15) est fixée à un piston hydraulique (23) partageant l'espace intérieur du carter (1) en une chambre hydraulique (29) et une chambre principale (27).
  11. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que les conducteurs électriques (25) alimentant l'unité d'actionnement (15) passent par une ouverture pratiquée dans le carter (1), et qu'un moyen de joint flexible (31) assurant l'étanchéité entre l'unité d'actionnement (15) et le carter (1) est prévu.
  12. Soupape d'injection selon la revendication 1, caractérisée en ce que la totalité de l'espace intérieur du carter de soupape (1) entre le joint d'étanchéité (31) et d'un siège de soupape (3) disposé à l'opposé est remplie du carburant.
EP03745746A 2002-04-04 2003-04-01 Soupape d'injection Expired - Lifetime EP1511932B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10214931 2002-04-04
DE10214931 2002-04-04
PCT/DE2003/001062 WO2003085253A1 (fr) 2002-04-04 2003-04-01 Soupape d'injection

Publications (2)

Publication Number Publication Date
EP1511932A1 EP1511932A1 (fr) 2005-03-09
EP1511932B1 true EP1511932B1 (fr) 2006-11-29

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Family Applications (1)

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EP03745746A Expired - Lifetime EP1511932B1 (fr) 2002-04-04 2003-04-01 Soupape d'injection

Country Status (5)

Country Link
US (1) US7886993B2 (fr)
EP (1) EP1511932B1 (fr)
JP (1) JP4273003B2 (fr)
DE (1) DE50305852D1 (fr)
WO (1) WO2003085253A1 (fr)

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CN103764995A (zh) * 2011-09-09 2014-04-30 大陆汽车有限公司 阀组件和喷射阀
US9574532B2 (en) 2011-09-09 2017-02-21 Continental Automotive Gmbh Valve assembly and injection valve

Also Published As

Publication number Publication date
JP4273003B2 (ja) 2009-06-03
US20050017096A1 (en) 2005-01-27
JP2005528546A (ja) 2005-09-22
EP1511932A1 (fr) 2005-03-09
US7886993B2 (en) 2011-02-15
DE50305852D1 (de) 2007-01-11
WO2003085253A1 (fr) 2003-10-16

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