EP2082127B1 - Injecteur pour injecter du carburant dans des chambres à combustion de moteurs à combustion interne - Google Patents

Injecteur pour injecter du carburant dans des chambres à combustion de moteurs à combustion interne Download PDF

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Publication number
EP2082127B1
EP2082127B1 EP07820155A EP07820155A EP2082127B1 EP 2082127 B1 EP2082127 B1 EP 2082127B1 EP 07820155 A EP07820155 A EP 07820155A EP 07820155 A EP07820155 A EP 07820155A EP 2082127 B1 EP2082127 B1 EP 2082127B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
valve sleeve
valve seat
fuel
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.)
Not-in-force
Application number
EP07820155A
Other languages
German (de)
English (en)
Other versions
EP2082127A1 (fr
Inventor
Andreas Rettich
Friedrich Boecking
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 EP2082127A1 publication Critical patent/EP2082127A1/fr
Application granted granted Critical
Publication of EP2082127B1 publication Critical patent/EP2082127B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injector according to the preamble of claim 1.
  • the EP 1 612 403 A1 describes a common rail injector with a pressure compensated in the axial direction control valve for locking and opening a Kraftstoffablaufweges from a control chamber.
  • the fuel pressure can be influenced within the control chamber.
  • the control chamber is supplied via a pressure channel with fuel from a hydraulically connected to a high-pressure fuel pressure chamber.
  • a nozzle needle is moved between an open position and a closed position, wherein the nozzle needle in its open position releases the fuel flow into the combustion chamber of an internal combustion engine.
  • the control valve has an adjustable in the axial direction by means of an electromagnetic actuator valve sleeve, which cooperates sealingly with a stationary, conical valve seat surface.
  • the invention is therefore based on the object to propose an injector with a control valve, the opening characteristic remains at least substantially constant over its lifetime.
  • the invention is based on the idea, instead of a raised, for example conical valve seat provided as a flat seat valve seat with a flat valve seat surface, wherein the flat valve seat surface sealingly cooperates with a frontal peripheral edge of the valve sleeve of the control valve.
  • the peripheral edge extends from the valve sleeve in the axial direction.
  • the peripheral edge so the bearing edge, with which the valve sleeve rests on the flat valve seat surface, must be formed by the inner circumference of the valve sleeve.
  • the diameter of the peripheral edge is equal to the inner diameter of the valve sleeve in its guide portion on the axial pressure forces receiving guide pin in a pressure compensated in the axial direction control valve.
  • angles between the valve seat surface and the annular surface are suitable in a range between approximately 0.5 ° and 20 °.
  • the angle is approximately between 1 ° and 10 °; optimum results are achieved at an angle of about 5 °.
  • a defined pressure application surface can be provided in development of the invention at the expense of the axial pressure balance, which ensures that when a maximum fuel pressure within the valve sleeve is exceeded, it lifts from the flat valve seat and thus the fuel under an impermissible overpressure into a low-pressure space can drain away.
  • the pressure application surface is dimensioned such that the valve sleeve lifts at fuel pressures from 2100 bar, in particular from 2200 bar against the force of a valve spring from the valve seat.
  • the pressure application surface is designed as a circumferential pressure level. Such a pressure application surface is easy to produce with high accuracy.
  • the peripheral edge with which the valve sleeve rests on the flat valve seat surface, arranged at a radial distance from the guided on the guide pin inner surface of the valve sleeve.
  • this inner surface and the peripheral edge is preferably formed as a circumferential pressure step pressure application surface.
  • the guide pin extends from an area radially inside the flat valve seat surface in the axial direction into the valve sleeve.
  • valve sleeve is formed in an embodiment of the invention in one piece with an anchor plate of the actuator designed as an actuator.
  • the Kraftstoffablaufweg runs through the valve seat having the component in the axial direction in the guide pin and from there in the radial direction from this into an annular space within the valve sleeve. From there, the fuel can flow in the radial direction in a low-pressure chamber with valve sleeve lifted from the valve seat.
  • Fig. 1 are shown schematically the essential parts for the control of a common rail injector 1.
  • a common rail injector 1 Within a nozzle body 2, an elongated nozzle needle 3 is movably guided in the axial direction.
  • the nozzle needle 3 has at its needle tip, not shown, a closing surface with which it can be brought into tight contact with a needle body within the nozzle body 3, also not shown.
  • the fuel outlet When the nozzle needle 3 rests against the needle seat, the fuel outlet is blocked from a nozzle hole arrangement, not shown. If, on the other hand, it is raised from the needle seat, fuel can flow from a pressure chamber 4 in the axial direction along the nozzle needle 3 through the nozzle hole arrangement and be sprayed into a combustion chamber substantially under high pressure (rail pressure).
  • the basic structure of an injector 1 is known. In this regard is on the DE 100 24 703 A1 directed.
  • the injector 1 has a throttle plate 5, which extends sleeve-shaped in the plane of the drawing down into the nozzle body 2 inside.
  • a control chamber 7 is limited.
  • the control chamber 7 is connected via a pressure channel 8 with inlet throttle 9 to the pressure chamber 4, which in turn is connected via a supply line, not shown, with a high-pressure fuel storage. High-pressure fuel can thus flow into the control chamber 7 via the pressure channel 8.
  • From the control chamber 7 leads out in the axial direction of a fuel drain 10 with outlet throttle 11. About the fuel drain 10, fuel from the control chamber 7 with open control valve 12 can flow into a low-pressure chamber 13.
  • the flow cross-sections of the inlet throttle 9 and the outlet throttle 11 are coordinated so that the inflow through the pressure channel 8 is weaker than the outflow through the fuel drain 10 and thus with open control valve 12, a net outflow of fuel from the control chamber 7 results.
  • the resulting pressure drop in the control chamber 7 causes the amount of closing force falls below the amount of the opening force and lifts the nozzle needle 3 from its needle seat.
  • the fuel drainage path 10 leads through the throttle plate 5 with outlet throttle 11 in a plane arranged in the drawing plane component 14.
  • the component 14 has a valve seat 22 (flat seat) with a flat valve seat surface 15 of the control valve 12, wherein a valve sleeve 16 of the control valve 12 in the closed Control valve sealingly rests on the valve seat surface 15.
  • the valve sleeve 16 is spring-loaded by a valve spring 17 in the axial direction on the valve seat surface 15.
  • the valve spring 17 is supported in the plane of the drawing on top of an injector body 18 and at the opposite end on a spring guide part 19, which in turn rests on the valve sleeve 16.
  • the valve sleeve 15 is penetrated in the axial direction by a guide pin 25, on whose outer surface it is guided.
  • the guide pin 25 is formed integrally with a cylindrical portion of the component 14.
  • the valve spring 17 is disposed within an electromagnet 20.
  • an armature plate 21 formed integrally with the valve sleeve 16 is moved axially in the direction of the electromagnet 20, whereby the valve sleeve 16 lifts against the spring force of the valve spring 17 of the valve seat surface 15, which in turn the fuel flow from the control chamber 7 is made possible via the Kraftstoffablaufweg 10 in the low-pressure chamber 13. From there, the fuel can flow via a return line, not shown, to a reservoir.
  • the pressure within the low-pressure chamber is approximately between 0 and 10 bar, whereas the fuel pressure within the pressure chamber is approximately between 1800 and 2000 bar.
  • valve seat surface 15 of the valve seat 22 is formed flat, wherein the valve seat surface 15 extends transversely to the longitudinal central axis 23 of the valve sleeve 16.
  • the valve sleeve 16 rests against the valve seat surface 15 with a frontal peripheral edge 24 extending in the axial direction when the control valve 12 is closed.
  • the peripheral edge 24 is formed on the inner diameter d1 of the valve sleeve 16.
  • the diameter d2 of the valve sleeve 16 at the peripheral edge 24 corresponds to the diameter d1 of the valve sleeve 16 in the guide section on the guide pin 25. Because the diameter d2 corresponds to the diameter d1, the control valve 12 is according to FIG Fig. 2 pressure balanced in the axial direction. This means that act on the valve sleeve 16 in the axial direction no or minimal pressure forces.
  • At the peripheral edge 24 includes in the radial direction outwardly a conical annular surface 27 at. This includes with the flat valve seat surface 15 in the embodiment shown an angle ⁇ of about 5 °.
  • the injector 1 according to Fig. 1 can also be like in Fig. 3 be formed represented. Also in this embodiment, a flat valve seat surface 15 is provided.
  • a flat valve seat surface 15 is provided.
  • the diameter d2 is slightly larger than the diameter d1, thereby forming a pressure step, annular pressure application surface 28 at the Valve sleeve 16 is formed.
  • This pressure application surface 28 prevents damage or destruction of the injector when exceeding a maximum allowable fuel pressure within the control valve 12.
  • the pressure application surface 28 is dimensioned such that the valve sleeve 16 lifts on reaching an impermissible pressure level, for example, about 2200 bar from the valve seat 22 and thus fuel can flow into the low pressure chamber 13.

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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)

Claims (10)

  1. Injecteur pour injecter du carburant dans des chambres de combustion de moteurs à combustion interne, en particulier injecteur à rampe commune, comprenant une douille de soupape (16) d'une soupape de commande (12) entourant un boulon de guidage (25), qui est disposée de manière déplaçable axialement par rapport à un siège de soupape (22), une voie d'écoulement de carburant (10) hors d'une chambre de commande (7), qui est en liaison hydraulique avec un canal de pression (8) servant à l'alimentation en carburant pouvant être bloquée ou libérée au moyen de la soupape de commande (12), de sorte que la pression dans la chambre de commande (7) puisse être commandée, de sorte qu'un pointeau de buse (3) en liaison fonctionnelle avec la chambre de commande (7) puisse être déplacé entre une position d'ouverture libérant le flux de carburant et une position de fermeture, caractérisé en ce que le siège de soupape (22) est réalisé sous forme de siège plat avec une surface de siège de soupape plane (15) et en ce que la douille de soupape (16) s'applique sur la surface de siège de soupape (15) avec une arête périphérique frontale (24) lorsque la soupape de commande (12) est fermée.
  2. Injecteur selon la revendication 1, caractérisé en ce qu'une surface annulaire (27) s'étendant radialement vers l'extérieur depuis l'arête périphérique (24) forme avec la surface de siège de soupape (22) un angle (α).
  3. Injecteur selon la revendication 2, caractérisé en ce que l'angle (α) est compris entre environ 0,5° et 20°, de préférence entre environ 1° et 10°, de préférence est d'environ 5°.
  4. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'on prévoit sur la douille de soupape (16) une surface d'application de pression (28) pour la pression de carburant dans la direction d'ouverture de la douille de soupape (16).
  5. Injecteur selon la revendication 4, caractérisé en ce que la surface d'application de pression (28) est réalisée sous forme d'un étage de pression périphérique s'étendant dans la direction radiale.
  6. Injecteur selon l'une quelconque des revendications 4 ou 5, caractérisé en ce que la surface d'application de pression (28) est dimensionnée de telle sorte que la douille de soupape (16) se soulève du siège de soupape (22) à partir de pressions de carburant de 2100 bar, notamment de 2200 bar.
  7. Injecteur selon l'une quelconque des revendications 2 à 5, caractérisé en ce que l'arête périphérique (24) est disposée à distance radiale de la surface interne de la douille de soupape (16) guidée sur le boulon de guidage.
  8. Injecteur selon l'une quelconque des revendications 1 à 7, caractérisé en ce que le boulon de guidage (25) est réalisé d'une seule pièce avec un composant (14) présentant le siège de soupape (22), et s'étend dans la direction axiale depuis une région radialement à l'intérieur de la surface du siège de soupape (15).
  9. Injecteur selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la douille de soupape (16) est réalisée d'une seule pièce avec une plaque d'armature (21) d'un actionneur réalisé sous forme d'entraînement par électroaimant, qui déplace la douille de soupape (16).
  10. Injecteur selon l'une quelconque des revendications 1 à 9, caractérisé en ce que la voie d'écoulement de carburant (10) s'étend axialement dans le boulon de guidage (25) et dans la direction radiale hors de celui-ci, dans un espace annulaire (26) limité par la douille de soupape (16) lorsque la soupape de commande (12) est fermée.
EP07820155A 2006-10-23 2007-09-12 Injecteur pour injecter du carburant dans des chambres à combustion de moteurs à combustion interne Not-in-force EP2082127B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006049885A DE102006049885A1 (de) 2006-10-23 2006-10-23 Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen
PCT/EP2007/059593 WO2008049691A1 (fr) 2006-10-23 2007-09-12 Injecteur pour injecter du carburant dans des chambres à combustion de moteurs à combustion interne

Publications (2)

Publication Number Publication Date
EP2082127A1 EP2082127A1 (fr) 2009-07-29
EP2082127B1 true EP2082127B1 (fr) 2010-11-24

Family

ID=38686539

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07820155A Not-in-force EP2082127B1 (fr) 2006-10-23 2007-09-12 Injecteur pour injecter du carburant dans des chambres à combustion de moteurs à combustion interne

Country Status (6)

Country Link
US (1) US8573186B2 (fr)
EP (1) EP2082127B1 (fr)
CN (1) CN101529080B (fr)
AT (1) ATE489550T1 (fr)
DE (2) DE102006049885A1 (fr)
WO (1) WO2008049691A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2202403B1 (fr) 2008-06-27 2013-07-31 C.R.F. Società Consortile per Azioni Injecteur de carburant doté d'une servocommande de mesure pour moteur à combustion interne
US9464613B2 (en) 2008-06-27 2016-10-11 C.R.F. Societa Consortile Per Azioni Fuel injector equipped with a metering servovalve for an internal combustion engine
ATE503106T1 (de) 2008-06-27 2011-04-15 Fiat Ricerche Brennstoffeinspritzvorrichtung mit balanciertem mess-servoventil für einen verbrennungsmotor
EP2674608B1 (fr) * 2012-06-13 2015-08-12 Delphi International Operations Luxembourg S.à r.l. Injecteur à carburant
CN104314722A (zh) * 2014-10-17 2015-01-28 中国重汽集团重庆燃油喷射***有限公司 压力平衡式电控喷油器
DE102014225323A1 (de) * 2014-12-09 2016-06-09 Robert Bosch Gmbh Schalt- oder Druckregelventil für ein Karftstoffeinspritzsystem
US10077748B2 (en) 2014-12-23 2018-09-18 Cummins Inc. Fuel injector for common rail
DE102015203515A1 (de) * 2015-02-27 2016-09-01 Robert Bosch Gmbh Teildruckausgeglichenes Druckregelventil für einen Hochdruckspeicher

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6257499B1 (en) * 1994-06-06 2001-07-10 Oded E. Sturman High speed fuel injector
DE19640826B4 (de) * 1995-10-03 2004-11-25 Nippon Soken, Inc., Nishio Speicherkraftstoffeinspritzvorrichtung und Druckregelvorrichtung hierfür
US5947380A (en) * 1997-11-03 1999-09-07 Caterpillar Inc. Fuel injector utilizing flat-seat poppet valves
EP0970305B1 (fr) * 1997-12-23 2003-05-21 Siemens Aktiengesellschaft Soupape d'injection a vanne de controle
US6109542A (en) * 1998-09-21 2000-08-29 Cummins Engine Company, Inc. Servo-controlled fuel injector with leakage limiting device
ES2280318T3 (es) * 2000-07-18 2007-09-16 Delphi Technologies, Inc. Inyector de combustible.
FI119120B (fi) * 2004-01-23 2008-07-31 Waertsilae Finland Oy Laitteisto ja menetelmä polttoaineen ruiskutuspaineen muokkaamiseksi
ES2277229T3 (es) * 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni Servovalvula para controlar el inyector de combustible de un motor de combustion interna.
DE602004003928T2 (de) * 2004-06-30 2007-10-18 C.R.F. S.C.P.A. Einspritzventil für Verbrennungskraftmaschine
DE602004017593D1 (de) * 2004-06-30 2008-12-18 Fiat Ricerche Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
EP1621764B1 (fr) * 2004-06-30 2007-11-07 C.R.F. Società Consortile per Azioni Injecteur d'un moteur à combustion interne
DE102004031790A1 (de) * 2004-07-01 2006-01-26 Robert Bosch Gmbh Common-Rail-Injektor
DE102004041172B3 (de) 2004-08-25 2006-01-05 Siemens Ag Einspritzventil
DE102005040912A1 (de) 2005-08-30 2007-03-08 Robert Bosch Gmbh Einspritzdüse
DE102007009165A1 (de) * 2007-02-26 2008-08-28 Robert Bosch Gmbh Kraftstoffinjektor mit einer zusätzlichen Ablaufdrossel oder mit einer verbesserten Anordnung derselben im Steuerventil

Also Published As

Publication number Publication date
WO2008049691A1 (fr) 2008-05-02
CN101529080A (zh) 2009-09-09
US20100294240A1 (en) 2010-11-25
ATE489550T1 (de) 2010-12-15
DE502007005792D1 (de) 2011-01-05
EP2082127A1 (fr) 2009-07-29
US8573186B2 (en) 2013-11-05
CN101529080B (zh) 2011-08-03
DE102006049885A1 (de) 2008-04-24

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