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EP1101033B1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

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

Info

Publication number
EP1101033B1
EP1101033B1 EP99950475A EP99950475A EP1101033B1 EP 1101033 B1 EP1101033 B1 EP 1101033B1 EP 99950475 A EP99950475 A EP 99950475A EP 99950475 A EP99950475 A EP 99950475A EP 1101033 B1 EP1101033 B1 EP 1101033B1
Authority
EP
European Patent Office
Prior art keywords
fuel
channel
fuel injection
control chamber
injection valve
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
EP99950475A
Other languages
German (de)
English (en)
Other versions
EP1101033A2 (fr
Inventor
Andreas Voigt
Günter LEWENTZ
Johannes Fitzner
Jürgen Rink
Gerd Schmutzler
Dirk Baranowski
Raimondo Giavi
Stefan Lehmann
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Publication of EP1101033A2 publication Critical patent/EP1101033A2/fr
Application granted granted Critical
Publication of EP1101033B1 publication Critical patent/EP1101033B1/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
    • 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

Definitions

  • the invention relates to a fuel injection valve according to the preamble of claim 1.
  • the known fuel injection valve has one Servo valve controlled by a piezoelectric actuator the fuel pressure in a control chamber controls, the amount of fuel pressure in the Control chamber opening and closing the injector, or the beginning and end of the injection process in the Combustion chamber of an internal combustion engine determined.
  • the formation of the fuel passages and lines in a throttle body are introduced determine the dynamics of the injection process, z. B. the speed of the opening and closing process of the injector. Due to the high fuel pressure are attached to the pressure resistant seals between the throttle body and its neighboring components and the pressure resistance of the throttle body places high demands.
  • the design of the transitions from fuel-carrying channels in additional channels or cavities affect the compressive strength.
  • EP 0 767 304 A1 EP 0 647 780 A2 and EP 0 331 198 A3 are also generic fuel injection valves known. With this fuel injector is part of the control chamber in the throttle valve educated.
  • the inlet channels each run in a straight line and directly to the respective fuel channel.
  • a fuel injection valve is included a throttle body known.
  • the throttle body is between a nozzle body and an injector head arranged and as Throttle plate designed.
  • the throttle plate has one Fuel channel from which an inlet channel branches off, which in a control chamber opens. Furthermore is in the throttle plate a drain channel is arranged, which opens into the control chamber and is connected to a servo valve.
  • the servo valve will actuated by an actuator and controls the fuel pressure in the tax chamber.
  • the nozzle needle in the fuel injector moves axially depending on the fuel pressure in the Control chamber and controls the fuel flow to the injection holes in the nozzle body.
  • the object of the invention is the compressive strength to increase the fuel injection valve.
  • the object of the invention is achieved with a device as described in claim 1.
  • a fuel injector, especially for diesel fuel must have a high compressive strength to the high To withstand fuel pressure.
  • the compressive strength is dependent on the wall thickness of the components of the fuel injector. Through the formation of curved fuel channels almost meet in the fuel channels perpendicular to each other. This will create areas with thin walls due to diagonally merging Fuel channels (pimples) avoided, which is advantageous high compressive strength is achieved.
  • High pressure transitions are one in the area of the end faces Throttle body arranged with fuel channels, being through the axial bracing of the throttle body between the neighboring ones Bodies on the end faces and the preferred flat design of the end faces a high pressure resistant seal arises, which is advantageously easy to manufacture.
  • the colliding end faces can also be slightly arched be, the bulges are shaped so that in critical Areas the contact surfaces of the clashing End faces with an increased surface pressure are. The high-pressure strength is thereby advantageous same clamping force increased.
  • a deflection of the actuator 100 is via a guided plunger 200 on a closing body 370 of the servo valve 340 transmitted by a conical, central valve seat 350 is raised and a fuel drain from one the central valve chamber 345 connecting the valve seat 350 releases.
  • the valve chamber 345 is via the drain channel 440 connected to the control chamber 540 into which the inlet channel 420 opens, which opens into the fuel channel 410.
  • Valve spring 390 which is introduced into the valve chamber 345, the closing body 370 back on the valve seat 350 and interrupts the fuel drain.
  • the pressure in the control chamber 540 depends on the shape of the inlet channel 420, the outlet channel 440 and the Position of the actuator 100 and acted upon by the piston 590 the nozzle needle 600.
  • a deflection of the actuator 100 leads to Lowering the pressure in the control chamber 540 and causing one axial displacement of the nozzle needle 600 in the direction of the throttle plate 400, which removes the needle tip 610 from the sealing seat 520 lifts off and an injection process is initiated in the combustion chamber becomes.
  • the fuel is in the fuel channel 530 and through recesses in the nozzle bore 515 through at least one in the nozzle tip 518 introduced spray hole 525 in the Headed combustion chamber.
  • the fuel channel 410 occurs on the upper end face of the Throttle plate 400 in and out on the lower end face connects to the fuel channel 320 of the valve body 300 and the fuel passage 530 of the intermediate body 500.
  • the End faces of the throttle plate 400 are preferably perpendicular to the longitudinal axis 800 and preferably connect flat the end faces of the valve body 300 and the intermediate body 500 at. Due to the axial clamping force and the flat connection arise between the throttle plate 400 and the valve body 300 and between the throttle plate 400 and the intermediate body 500 high pressure resistant seals that are easy to manufacture are.
  • the abutting end faces can also be slightly arched, with the curvatures being so shaped are that in critical areas the contact areas of the adjacent end faces with an increased surface pressure are acted upon. This makes the high pressure resistance increased with the same clamping force.
  • the second part of the body of the fuel injection valve is designed as a nozzle body 510, there is no intermediate body 500.
  • the throttle plate 400 is not executed as an independent body, but integrated into the first or the second sub-body of the fuel injection valve.
  • FIG. 2a shows a second embodiment of a throttle plate 400, with the following differences to the throttle plate consist of Figure 1:
  • the throttle plate 400 has a central valve recess 430 which are essentially the same diameter as that Has valve chamber 345 and is open to the valve chamber 345.
  • Valve recess 430 preferably adjoins coaxially Longitudinal axis 800 of the drain channel 440.
  • the drain channel 440 opens approximately vertically into a control chamber recess 460, the side wall 465 of which is at least partially frustoconical is trained.
  • the inlet channel 420, 425 opens approximately perpendicular to the frustoconical section of the side wall 465th
  • the control chamber recess 460 goes into the cylindrical piston recess 450 over, which is essentially the same Diameter as the guide bore 550 and in the one Part of the piston 590 is introduced.
  • the control chamber recess 460 and the piston recess 450 represent in this embodiment the control chamber 540, since depending on the Position of the piston 590, the control chamber recess 460 and the piston recess 450 are filled with fuel.
  • FIG. 2b 465 shown in Figure 2a A further embodiment of the side wall is shown in FIG. 2b 465 shown in Figure 2a, the transition from the piston recess 450 to the heel of the control chamber recess 460 is rounded off by a curve in the side wall 465.
  • the Rounding of the side wall 465 has a rounding radius R of preferably 0.7 to 1mm.
  • Inlet channel 420, 425 opens approximately vertically into the Rounding the side wall 465.
  • the rounding is, for example introduced into the throttle plate 400 by Elysier.
  • the inlet channel 420 opens preferably and approximately vertically into the side wall 465 of the control chamber recess 460, whereby a high compressive strength is advantageously achieved.
  • the inlet channel 420 has an inlet throttle 425 which preferably to the side of the control chamber recess 460 borders.
  • the drain channel 440 has a drain throttle 445, which is preferably adjacent to the side of the valve recess 430.
  • FIG. 3 preferably shows one approximately circularly curved inlet channel 420, which at its first end approximately perpendicular to the fuel channel 410 and at its second end approximately perpendicular to the Side wall 465 of the control chamber recess 460 opens, whereby advantageously a high compressive strength of the throttle plate 400 is achieved.
  • the inlet channel acts 420 simultaneously as inlet throttle 425, which is advantageous manufacturing simplified.
  • the inlet channel 420 is in FIG. 4 in a first, approximately straight part and a second, almost curved part with a smaller diameter divided.
  • the first part flows almost vertically into the Fuel channel 410, is starting from there in the direction of Valve body 300 curved and ends in the throttle plate 400.
  • the second part opens approximately vertically at one end preferably in the side wall 465 of the control chamber recess 460 and at the other end approximately perpendicular in the side wall of the first part.
  • the second part acts as an inlet throttle 425, the length of which is advantageous in connection with the first part to the given parameters, e.g. B. the fuel pressure, can be adjusted.
  • cross sections of those shown in the exemplary embodiments are fuel-carrying, curved or uncurved channels preferably circular and with given diameters executed.
  • FIG. 4 also shows an eroding device 700 with which approximately circularly curved channels, e.g. B. the inlet channel 420, in the material of the fuel injector, preferably of the throttle plate 400.
  • the eroding device 700 has an eroding electrode 701, which corresponds the desired radius of curvature of the inlet channel 420 is approximately circular.
  • the eroding electrode 701 is clamped in an electrode holder 702, which is advanced along an arc, its Center with the center of the desired curvature of the Inlet channel 420 matches.
  • curved eroding electrode 701 push through a fixed, curved electrode guide, which reduces the tendency of the eroding electrode to vibrate 701 reduced and so advantageous small tolerances be reached.
  • Known eroding processes are used as the process for shaping the channels used, e.g. the spark erosion process.
  • the erosion process mentioned above is also used for manufacturing of the curved inlet channel 420 shown in FIG.
  • the compressive strength is also advantageous to increase if the edges in the area of the mouths are also rounded e.g. about electrochemical rounding.

Landscapes

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

Claims (11)

  1. Soupape d'injection de carburant, comportant
    un canal de carburant (320, 410, 530) qui transporte du carburant sous pression élevée.
    un corps d'étranglement, présentant un canal d'arrivée (420), qui est raccordé au canal de carburant (410),
    une chambre de commande (540, 450, 460) dans laquelle débouche le canal d'arrivée (420),
    une aiguille de buse (600), qui, par l'intermédiaire d'un piston (590), est reliée, pour son fonctionnement, à la chambre de commands (540, 450, 460) et est commandée par la pression dans la chambre de commande (540, 450, 460),
       le corps d'étranglement étant réalisé sous la forme d'une plaque d'étranglement (400), qui est installée entre un premier élément partiel et un deuxième élément partiel de la soupape d'injection de carburant,
       une surface frontale supérieure et une surface frontale inférieure de la plaque d'étranglement (400) étant disposées sensiblement perpendiculairement à l'axe longitudinal (800) de la soupape d'injection de carburant et étant mises en pression contre les faces frontales du premier corps partiel et du deuxième corps partiel,
       un canal de carburant (410) traversant la plaque d'étranglement (400), canal qui entre sur la face frontale supérieurs de la plaque d'étranglement (400) et sort sur la face frontale inférieurs de la plaque d'étranglement (400), et
       le canal de carburant (320) du premier corps partiel et le canal de carburant (530) du deuxième corps partiel se raccordant au canal de carburant (410) de la plaque d'étranglement (400),
       caractérisée en ce que le canal d'arrivée (420) est coudé au moins sur une partie de sa longueur et débouche sensiblement perpendiculairement dans le canal de carburant (410).
  2. Soupape d'injection de carburant suivant la revendication 1, caractérisée en ce que le canal d'arrivée (420) est coudé, sensiblement suivant une forme circulaire, en partant vers le bas, en direction de la chambre de commande (540, 450, 460).
  3. Soupape d'injection de carburant suivant la revendication 1 ou 2, caractérisés en ce que
    une première partie du canal d'arrivée (420) est coudée avec une forme sensiblement circulaire,
    une deuxième partie du canal d'arrivée (420, 425) reçoit une forme sensiblement cylindrique.
  4. Soupape d'injection de carburant suivant la revendication 1 ou 3, caractérisée en ce que
    la première partie du canal d'arrivée (420) est coudée en partant, vers le haut, du canal de carburant (410), en s'éloignant en direction de la chambre de commande (540, 450, 460).
  5. Soupape d'injection de carburant suivant l'une des revendications précédentes, caractérisée
    en ce qu'au moins une partie de la chambre de commande (450, 460) est réalisée dans la plaque d'étranglement (400), et
    en ce que le canal d'arrivée (420) débouche sensiblement perpendiculairement dans la paroi latérale (465) de la chambre de commande (450, 460).
  6. Soupape d'Injection de carburant suivant la revendication 5, caractérisée
    en ce que la paroi latérale (465) de la chambre de commande (450, 460) est réalisée, au moins en partie, en forme de tronc de cône, et
    en ce que le canal d'arrivée (420) débouche sensiblement perpendiculairement dans la partie en forme de tronc de cône de la paroi latérale.
  7. Soupape d'injection de carburant suivant la revendication 5, caractérisée
    en ce que la paroi latérale (465) de la chambre de commande (450, 460) est réalisée arrondie, au moins en partie, et
    en ce que le canal d'arrivée (420) débouche sensiblement perpendiculairement dans la partie de forme arrondie de la paroi latérale.
  8. Soupape d'injection de carburant suivant l'une des revendications précédentes, caractérisée
    en ce que le premier corps partiel est réalisé comme corps de soupape (300), qui présente un canal de carburant (320) et une servo-soupape (340) pour réguler la pression de carburant dans la chambre de commande (540, 450, 460), et
    en ce que le deuxième corps partiel est réalisé comme corps intermédiaire (500), qui est installé entre la plaque d'étranglement (400) et le corps de buse (510).
  9. Soupape d'injection de carburant suivant l'une des revendications précédentes, caractérisée
    en ce qu'un alésage central de guidage est prévu pour guider le piston (590).
    en ce que la plaque d'étranglement (400) présente un évidement de piston (450) qui se raccorde à l'alésage de guidage (550) et présente essentiellement la même section que l'alésage de guidage (550).
  10. Soupape d'injection de carburant suivant l'une des revendications précédentes, caractérisée
    en ce qu'une servo-soupape (340) est prévue, qui commande l'écoulement du carburant depuis une chambre de soupape (345) du premier corps partiel,
    en ce que la plaque d'étranglement (400) présente un évidement de soupape (430), qui présenta essentiellement la même section que la chambre de soupape (345), l'évidement de soupape (430) étant ouvert vers la chambre de soupape (345) dans laquelle est disposé un corps de fermeture (370) de la servo-soupape (340).
  11. Soupape d'injection de carburant suivant l'une des revendications précédentes, caractérisée
    en ce qu'un ressort de soupape (390), qui exerce un serrage préalable contre un siège de soupape (350), est installé en partie dans l'évidement de soupape (430) et dans la chambre de soupape (345).
EP99950475A 1998-07-31 1999-07-30 Soupape d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP1101033B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19834668 1998-07-31
DE19834668 1998-07-31
PCT/DE1999/002352 WO2000006892A2 (fr) 1998-07-31 1999-07-30 Soupape d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1101033A2 EP1101033A2 (fr) 2001-05-23
EP1101033B1 true EP1101033B1 (fr) 2002-10-02

Family

ID=7876058

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99950475A Expired - Lifetime EP1101033B1 (fr) 1998-07-31 1999-07-30 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (3)

Country Link
EP (1) EP1101033B1 (fr)
DE (1) DE59902966D1 (fr)
WO (1) WO2000006892A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10019810A1 (de) * 2000-04-20 2002-01-31 Siemens Ag Einspritzventil mit optimierten Dichtflächen
DE10220931C1 (de) * 2002-05-10 2003-11-27 Siemens Ag Injektor zur Kraftstoffeinspritzung
CN108547717B (zh) * 2018-02-08 2020-09-29 龙口龙泵燃油喷射有限公司 电控柴油喷射器

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4129255A (en) * 1977-09-12 1978-12-12 General Motors Corporation Electromagnetic unit fuel injector
JPH01224454A (ja) * 1988-03-04 1989-09-07 Yamaha Motor Co Ltd エンジンの高圧燃料噴射装置
EP0363142A1 (fr) * 1988-10-04 1990-04-11 LUCAS INDUSTRIES public limited company Injecteurs de combustible pour moteurs à combustion interne
GB9320798D0 (en) * 1993-10-08 1993-12-01 Lucas Ind Plc Fuel injection nozzle
GB9520243D0 (en) * 1995-10-04 1995-12-06 Lucas Ind Plc Injector

Also Published As

Publication number Publication date
WO2000006892A2 (fr) 2000-02-10
WO2000006892A3 (fr) 2000-06-02
EP1101033A2 (fr) 2001-05-23
DE59902966D1 (de) 2002-11-07

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