EP2459866B1 - Soupape d'injection de carburant pour moteurs à combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs à combustion interne Download PDF

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Publication number
EP2459866B1
EP2459866B1 EP10720789.6A EP10720789A EP2459866B1 EP 2459866 B1 EP2459866 B1 EP 2459866B1 EP 10720789 A EP10720789 A EP 10720789A EP 2459866 B1 EP2459866 B1 EP 2459866B1
Authority
EP
European Patent Office
Prior art keywords
collar
valve
pressure chamber
valve needle
fuel injection
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
EP10720789.6A
Other languages
German (de)
English (en)
Other versions
EP2459866A1 (fr
Inventor
Matthias Burger
Hans-Christoph Magel
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
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2459866A1 publication Critical patent/EP2459866A1/fr
Application granted granted Critical
Publication of EP2459866B1 publication Critical patent/EP2459866B1/fr
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    • 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
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines, as it is preferably used for the injection of fuel directly into a combustion chamber of a high-speed, self-igniting internal combustion engine, GB 2 277 779 ).
  • Fuel injection valves which are used for injecting fuel under high pressure directly into a combustion chamber of an internal combustion engine, are operated at ever higher pressure. Partial injection pressures of more than 2000 bar are already achieved today.
  • the fuel pressure is generated by a high-pressure pump, which conveys the compressed fuel into a high-pressure accumulator, the so-called rail. From this rail usually several injectors are fed, which have a movable valve needle, controlled by the injection openings are opened and controlled by an electric control valve, so that fuel is injected at the desired time and in the desired dosage in the combustion chamber. Due to the high fuel pressure that surrounds the valve needle, acting on the valve needle large hydraulic forces, which are increasingly difficult to control.
  • valve needle closes quickly.
  • this is achieved in that a low-pressure stage is provided, so that the hydraulic pressure in a control chamber which acts on the valve needle and exerted by means of the closing force on the valve needle is greater than the forces acting in the opening direction on the valve needle. This excess of hydraulic closing force allows the valve needle to close quickly and thus achieve a clean injection.
  • the valve needle With increasing pressure, however, the problem arises that it leads to increased leakage to the low-pressure space, which must be compensated by additional pump power and ultimately leads to a fuel consumption of the vehicle.
  • the valve needle if you simply leave the low-pressure stage, then the valve needle, if it closes the control valve at the end of the injection by the high fuel pressure builds up again in the control room, largely pressure-balanced.
  • the closing force could be applied in this case only in other ways, for example by a spring.
  • the spring since the injector must open even at low pressures, the spring must not be too strong, so that only a small force is exerted on the valve needle, which makes a fast closing impossible by the spring force.
  • a fuel injection valve which has a throttle collar.
  • the throttle collar is disposed near the valve seat, from which the injection openings go out, so that between the collar and the wall of the pressure chamber in which the valve needle is arranged, a throttle gap is formed.
  • the injection valve is open, that is, when the valve needle has lifted from the valve seat, this results in a pressure drop, so that the pressure downstream of this throttle gap is lower than upstream.
  • the hydraulic force on the valve sealing surface of the valve needle decreases, so that now, when the control valve closes and the fuel pressure is rebuilt in the control chamber, the closing force is sufficient to build a closing force on the valve needle, which leads to a rapid closing.
  • the object of the present invention is thus to provide a fuel injection valve in which the throttle gap is formed by a collar on the valve needle, which is easy to manufacture and is insensitive to tolerance deviations.
  • the fuel injection valve according to the invention solves the problem set by the valve needle has a collar, which has an inlet-side surface and an outlet-side surface, wherein the inlet-side surface is rounded or conical.
  • This has several advantages: Firstly, such a rounded or conical inlet-side surface is cheaper to manufacture than a sharp-edged, so at right angles to the valve needle protruding surface. On the other hand, such a designed surface is stable against flow separation, so that no cavitation phenomena arise that influence the flow resistance at the gap choke uncontrolled.
  • a cylindrical section adjoins the inlet-side surface, between which and the wall of the pressure chamber the smallest flow cross-section is formed, which is formed either only over part of the waist circumference or over the entire circumference of the waistband.
  • the cylindrical portion can be easily grinded by material removal on the outside to an exact diameter or form corresponding passages through polished so that the size of the desired gap choke is easily adjustable.
  • the outlet-side surface of the collar is formed by a conical surface or a rounded, which adjoins directly to the cylindrical portion.
  • a ratio of the gap of the gap throttle to the hydraulic diameter of> 2 and ⁇ 20 is optimal, since so a high temperature independence is achieved and the gap choke is still in an order of magnitude, which is associated with manufacturing technology reasonable effort.
  • FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section, wherein only the part of the injection valve is shown, which faces the combustion chamber in the installed position in an internal combustion engine.
  • the fuel injection valve 1 has a valve body 2, in which a pressure chamber 5 is formed in the form of a bore.
  • the pressure chamber 5 is delimited on the combustion chamber side by a substantially conical valve seat 9, from which several injection openings 7 originate.
  • a longitudinally displaceable valve needle 3 is arranged, which is rotationally symmetrical with respect to the longitudinal axis of the pressure chamber 5.
  • the valve needle 3 is guided in a guide section 103 in the pressure chamber 5, wherein the fuel flow past the guide section 103 is ensured by a plurality of bevels 14, which are formed on the outside of the guide section 103.
  • the valve needle 3 has at its valve seat facing the end of a valve sealing surface 11, with which the valve needle 3 cooperates for opening and closing the injection openings 7 with the valve seat 9.
  • a collar 17 is formed on the valve needle 3, which has an edge 18 on its outer side. Between the edge 18 and the wall of the pressure chamber 5, a gap throttle 15 is formed, which represents the smallest flow cross section with respect to the fuel flow through the pressure chamber 5 to the injection openings 7.
  • the gap throttle 15 is designed here as an annular gap throttle having an inner diameter D i and an outer diameter D a .
  • the intended for injection fuel is compressed by a high-pressure pump, not shown in the drawing and fed to a high-pressure accumulator, also not shown in the drawing, with which the injection valve is connected. From the high-pressure accumulator, the compressed fuel is passed into the pressure chamber 5, where it flows through the pressure chamber 5 and, accordingly, through the gap throttle 15 and the bevels 14 in the direction of the valve seat 9. In the closed state of the injection valve, that is, when the valve needle 3 is seated on the valve seat 9, the valve needle 3 closes the injection openings 7.
  • valve needle 3 If the valve needle 3 is moved away from the valve seat 9, which with the help of a also not shown in the drawing - but well-known from the prior art - control valve is performed, the injection ports 7 are connected to the pressure chamber 5, and fuel is injected through the injection ports 7 into a combustion chamber of the internal combustion engine.
  • the collar 17 Through the gap throttle 15, there is a throttling of the fuel flow when the valve needle 3 has lifted from the valve seat 9, so that a pressure difference between the areas before and after the collar 17 in the pressure chamber 5 occurs. This pressure difference is about 50 to 100 bar at an injection pressure of 1600 to 2000 bar.
  • the shape of the collar 17 with the edge 18 causes the throttling at the gap throttle 15 is largely independent of the Reynolds number. The following conditions must be fulfilled for this.
  • the effect of a gap choke is determined by two variables: First, by the hydraulically effective diameter D Hyd and the other by the length of the gap choke L.
  • the length L of the edge 18 is defined by the length of the gap throttle 15, in which the flow-through cross-section is smaller than 1.2 times the minimum flow cross-section.
  • the ratio L to D Hyd must be ⁇ 20.
  • Such a gap choke is also referred to as hydraulically short.
  • FIG. 2 shows an enlarged view of the collar 17 and the valve needle 3 of a first embodiment, said area in Fig. 1 marked with II.
  • the collar 17 can be divided into three sections: an inlet side surface 20, a cylindrical section 22 and an outlet side surface 24.
  • the inlet side surface 20 is rounded and formed in the region in which it merges into the cylindrical portion 22 with a radius R rounded.
  • the radius R is advantageously about 0.2 to 0.3 mm.
  • the rounding of the inlet-side surface 20 of the collar 17 can be made lighter and thus more cost-effective and beyond there is the advantage that the flow at entry into the gap throttle 15 is stable against flow separation, so that it regardless of the flow velocity to no instabilities in Area of the gap choke 15 comes.
  • the cylindrical portion 22 is substantially the length L of the throttle gap again, but - as mentioned above - the length L of the gap choke is defined as the length in which the flow-through cross-section is smaller than 1.2 times the minimum flow cross-section , This is in FIG. 2 indicated that the length L is slightly larger than the thickness of the cylindrical portion 22nd
  • the outlet-side surface 24 is formed by a first conical surface 124, which adjoins directly to the cylindrical portion 22, and by a second conical surface 224, which forms the end of the collar 17. Due to the shape of the first conical surface 124, an edge 26 is formed at the transition from the cylindrical surface 22, which ensures that the flow of the fuel through the gap throttle 15 always at the same point, namely at the edge 26, detaches. As a result, the throttle effect of the gap choke 15 is robust against influences such as surface condition and fuel properties. In this case, an angle difference between the first conical surface 124 and the cylindrical surface 22 of 20 ° to 30 ° is advantageous.
  • FIG. 3 a further embodiment of the Federal 17 is shown.
  • the inlet-side surface 20 ' is formed here as a conical surface, which forms an angle ⁇ with the longitudinal axis of the valve needle 3. This angle ⁇ is preferably in the range of 60 ° to 80 °.
  • the outlet-side surface 24 ' is also designed here as a simple conical surface.
  • the cone of the inlet-side surface 20 ' causes similar advantages as the rounded inlet-side surface 20 in Fig. 2 In particular, such a surface is easier to produce than an exactly perpendicular to the valve needle aligned inlet side surface.
  • FIG. 4 shows a further embodiment of the gap choke 15 and the collar 17 according to the invention in a cross section.
  • the gap throttle 15 is formed here only over portions of the circumference, which are formed by lateral polished sections 28, so that the collar 17 has a substantially triangular shape in cross section.
  • the gap between the collar 28 and the wall of the pressure chamber 5 is so small that practically a seal is achieved.
  • the polished sections 28 are shown exaggerated here for the sake of clarity, wherein the length K of these bevels 25 of course depends on the length L of the collar 17 in order to obtain the desired hydraulic diameter. It can take 28 instead of three, as in Fig. 4 shown, a larger or smaller number of bevels 28 may be provided, for example, 1, 2, 4, 5 or 6.
  • the chosen dimensions achieve a sufficient compromise between achievable manufacturing tolerances and the effect of a gap choke, which is formed by a sharp edge.
  • An absolute independence of the Reynolds number could only be achieved if the edge 18 of the collar 17 would be ideally sharp-edged, which, however, manufacturing technology is not represented.

Landscapes

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

Claims (5)

  1. Soupape d'injection de carburant pour moteurs à combustion interne, comprenant un corps de soupape (1), dans lequel est réalisée une chambre de pression (5) dans laquelle est disposé de manière mobile longitudinalement un pointeau de soupape (3), lequel coopère, par une surface d'étanchéité de soupape (11) réalisée sur le pointeau de soupape (3), avec un siège de soupape (9) qui délimite la chambre de pression (5), un flux de carburant jusqu'à au moins un orifice d'injection (7) étant rendu possible ou interrompu par la coopération du pointeau de soupape (3) avec le siège de soupape (9), le flux de carburant s'écoulant entre le pointeau de soupape (3) et la paroi de la chambre de pression (5) jusqu'aux orifices d'injection (7), et un épaulement (17) étant réalisé sur le pointeau de soupape (3), de sorte qu'une fente d'étranglement (15) soit réalisée entre la paroi de la chambre de pression (5) et l'épaulement (17), l'épaulement (17) présentant une surface côté entrée (20) et une surface côté sortie (24), la surface côté entrée (20) étant réalisée de manière arrondie ou conique et la fente d'étranglement (15) n'étant réalisée que sur des régions partielles de la périphérie qui sont formées par des biseaux latéraux (28), et aux endroits où aucun biseau (28) n'est présent, la fente entre l'épaulement (17) et la paroi de la chambre de pression (5) étant si petite qu'une étanchéité soit pratiquement obtenue, caractérisée en ce que le rapport de la longueur (L) de la fente d'étranglement (15) au diamètre hydraulique DHyd est supérieur à 2 et inférieur à 20.
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que la surface côté entrée (20) est, considérée en section transversale, arrondie avec un rayon (R) de 0,2 à 0,3 mm.
  3. Soupape d'injection de carburant selon la revendication 1 ou 2, caractérisée en ce qu'une portion cylindrique (22) se raccorde à la surface côté entrée (20) de l'épaulement (17), entre laquelle portion cylindrique et la paroi de la chambre de pression (5) est réalisée la plus petite section transversale d'écoulement.
  4. Soupape d'injection de carburant selon la revendication 3, caractérisée en ce que la surface côté sortie (24) de l'épaulement (17) est formée par une surface conique (124 ; 24'), la surface conique (124 ; 24') se raccordant directement à la portion cylindrique (22).
  5. Soupape d'injection de carburant selon la revendication 4, caractérisée en ce que la différence de l'angle d'ouverture de la surface conique (124 ; 24') et de la portion cylindrique (22) vaut 20° à 30°.
EP10720789.6A 2009-07-30 2010-06-01 Soupape d'injection de carburant pour moteurs à combustion interne Active EP2459866B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009028122 2009-07-30
DE102009029562A DE102009029562A1 (de) 2009-07-30 2009-09-18 Kraftstoffeinspritzventil für Brennkraftmaschinen
PCT/EP2010/057634 WO2011012355A1 (fr) 2009-07-30 2010-06-01 Soupape d'injection de carburant pour moteurs à combustion interne

Publications (2)

Publication Number Publication Date
EP2459866A1 EP2459866A1 (fr) 2012-06-06
EP2459866B1 true EP2459866B1 (fr) 2014-12-17

Family

ID=43402338

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10720789.6A Active EP2459866B1 (fr) 2009-07-30 2010-06-01 Soupape d'injection de carburant pour moteurs à combustion interne

Country Status (4)

Country Link
EP (1) EP2459866B1 (fr)
CN (1) CN102472222B (fr)
DE (1) DE102009029562A1 (fr)
WO (1) WO2011012355A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2568157A1 (fr) 2011-09-08 2013-03-13 Delphi Technologies Holding S.à.r.l. Buse à injection

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT288784B (de) * 1966-10-20 1971-03-25 Bosch Gmbh Robert Elektromagnetisch betätigtes Kraftstoff-Einspritzventil für Brennkraftmaschinen
JP3136829B2 (ja) * 1993-05-06 2001-02-19 株式会社デンソー 燃料噴射弁
DE10055651A1 (de) * 2000-11-10 2002-05-23 Bosch Gmbh Robert Druckgesteuerter Injektor mit optimierten Einspritzverlauf über den Hubweg
DE102007032741A1 (de) 2007-07-13 2009-01-15 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
US7690588B2 (en) * 2007-07-31 2010-04-06 Caterpillar Inc. Fuel injector nozzle with flow restricting device
DE102009000206A1 (de) * 2009-01-14 2010-07-15 Robert Bosch Gmbh Kraftstoffinjektor für Brennkraftmaschinen
EP2216542A1 (fr) * 2009-02-06 2010-08-11 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection et soupape d'injection

Also Published As

Publication number Publication date
CN102472222B (zh) 2015-07-22
WO2011012355A1 (fr) 2011-02-03
CN102472222A (zh) 2012-05-23
DE102009029562A1 (de) 2011-02-03
EP2459866A1 (fr) 2012-06-06

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