EP1045983B1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

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

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Publication number
EP1045983B1
EP1045983B1 EP99969769A EP99969769A EP1045983B1 EP 1045983 B1 EP1045983 B1 EP 1045983B1 EP 99969769 A EP99969769 A EP 99969769A EP 99969769 A EP99969769 A EP 99969769A EP 1045983 B1 EP1045983 B1 EP 1045983B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
space
fuel
spring
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
EP99969769A
Other languages
German (de)
English (en)
Other versions
EP1045983A1 (fr
Inventor
Maximilian Kronberger
Herbert Strahberger
Raphael Combe
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 EP1045983A1 publication Critical patent/EP1045983A1/fr
Application granted granted Critical
Publication of EP1045983B1 publication Critical patent/EP1045983B1/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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to a combination of a Fuel injection valve and a high pressure pump for Internal combustion engine according to the preamble of claim 1.
  • Such a combination of a fuel injection valve and a high-pressure pump is known from EP 0 844 384 A.
  • the fuel injection valve axially displaceable valve member, which with his combustion chamber side end to a flow area at least an injection port opens or heads.
  • the Valve member protrudes with its combustion chamber remote end at least indirectly in a fuel-filled spring chamber in which a valve member clamped in the closing direction valve spring is clamped.
  • the Valve spring is supported at one end with its end remote from the valve Evasive piston, which during the supply of high pressure standing fuel to the fuel injection valve by one certain stroke is hineinverschiebbar in the spring chamber and the while increasing the biasing force of the valve spring.
  • the high pressure pump has a Pumping room is on and to control the high-pressure pumping an electric control valve disposed on the high-pressure pump. Due to the throttle as a connection between the spring chamber and the Fuel low pressure chamber will be the outflow of fuel from the Restricted spring space, which in addition to increasing the Preload force of the valve spring by the movement of the bypass piston in the spring chamber into a hydraulic closing force increase is effected on the valve member.
  • the inventive combination of a fuel injection valve and a high-pressure pump has the advantage that the Leadership of the bypass piston is improved and this sure his full stroke in the spring chamber and thus performs a defined Increasing the preload force of the valve spring is achieved.
  • FIG. 1 shows a longitudinal section through the essential part of the invention described Fuel injection valve for internal combustion engines.
  • the illustrated in the figure 1 embodiment of The combination of a fuel injection valve and a high-pressure pump according to the invention shows this Fuel injection valve 1 in a structural unit with the High-pressure fuel pump 3, at which an electric Control valve 5 is arranged and as a unit in a Housing 7 used to be supplied internal combustion engine is.
  • the fuel injection valve 1 has a Valve body 9 on, with its one end in a not closer to the combustion chamber to be supplied Internal combustion engine sticks out and the one with its other end with the interposition of a washer 11 axially against a valve holding body 13 is braced. This takes place this axial clamping means of a clamping nut 15, the a paragraph on the valve body 9 surrounds and in a Thread of a housing 17 of the high-pressure fuel pump 3rd is screwed.
  • the valve body 9 of Fuel injection valve 1 also has a Guide bore 19, in which a piston-shaped Valve member 21 is guided axially displaceable.
  • the Valve member 21 has in a known manner at his combustion chamber-side end of a valve sealing surface 23, with it for controlling an injection opening cross-section with a Valve seat surface 25 at the closed end of Guide bore 19 cooperates. Leading downstream the sealing cross-section between the sealing surface 23 and Valve seat surface 25 injection openings 27 of the Valve seat surface 25 from, in the combustion chamber of Internal combustion engine.
  • the valve member 21 has furthermore a pressure shoulder pointing in opening stroke direction 29 on its shaft, with it into a pressure chamber 31st projects through a cross-sectional extension of the Guide bore 19 is formed. This extends Pressure chamber to the valve seat surface 25 and is by a High-pressure fuel channel 33 with high pressure Fuel fillable.
  • valve member 21 continues to have his combustion chamber remote end on a pressure pin 35, the the intermediate disc 11 extends through and into a cross-section extended spring chamber 37 in the valve holding body 13 opens. It is at the spring-side end of the pressure pin 35 a lower spring plate 39 provided, on the other hand, a in the spring chamber 37 clamped valve spring 41 is applied, the while the valve member 21 in the closing direction for Valve seat surface 25 is acted upon.
  • This valve spring 41 supported on the other hand on an upper spring plate 43, the on his side facing away from the spring on a bypass piston 45 is present.
  • the valve member 21 dives with its thrust pin 35 in a fuel-filled damping chamber 47, by a through the end face of the intermediate disc 11 formed stationary Paragraph 49 is limited to a stroke stop for a Ring shoulder 51 on the valve member 21 forms. It is between the wall of the damping chamber 47 and the pressure pin 35 a Thru-shaped cross-section formed as a mecanicnanschliff 53rd is formed and over which the damping chamber 47 with the Spring chamber 37 is connected.
  • the consultancynanschliff 53 on the pressure pin 35 an axial distance from the annular shoulder 51 on the valve member 21, in the region of the pressure pin 35 the diameter of the receiving opening in the Washer 11 corresponds, so that a control edge 55th is formed, whose crossing over the paragraph 49 the Controlling the hydraulic damping chamber 47 controls.
  • the housing 17 of the high-pressure fuel pump 3 is connected via a Spacer 57 by means of the clamping nut 15 axially against the Valve holding body 13 clamped.
  • the High-pressure fuel pump 3 in a cylinder bore 59th axially displaceable pump piston 61, which with his immersed end face a pump working space 63 in the Cylinder bore 59 limited.
  • the pump piston 61 is the High-pressure fuel delivery from a not closer shown motor-driven cam drive via a Push rod 65 driven axially reciprocatingly.
  • this Intake space 73 leads to a first control line 75 electrical control valve 5, in a known manner as Solenoid valve is formed and not closer illustrated manner the fuel passing into a second Control line 77 depending on the operating parameters the to be supplied internal combustion engine by means of a controls electrical control unit.
  • This second Control line 77 also penetrates the housing 17 the high-pressure fuel pump 3 and opens into the Pump working space 63.
  • the hydraulic working space 81 has two different ones Diameter up, with a first smaller one Diameter range 85 constantly through the bore 79 with the Pump working space 63 of the high-pressure fuel pump 3 connected is.
  • a second, larger diameter area 87 of the hydraulic working space 81 is only after Auf interviewedn a flow area through the Lifting movement of the bypass piston 45 with the pump working space 63 connectable.
  • the bypass piston 45 has two different hydraulic force application surfaces, of which a first smaller force introduction surface 89 the first, smaller in diameter hydraulic Working space part 85 limited.
  • a second bigger one Force introduction surface 91 is on a collar 93 on Evasive piston 45 is formed and limits the larger Diameter range 87 of the hydraulic working space 81.
  • the fuel injection valve according to the invention Internal combustion engine operates in the following way.
  • During the Suction stroke of the high-pressure fuel pump 3, is at up moved pump piston 61 fuel from the suction 73rd via the first control line 75, the opened electric Control valve 5 and the second control line 77 in the Pump workspace 63 sucked.
  • the valve member 21 of the Fuel injection valve 1 is doing by the Valve spring 41 held in the closed position on the valve seat 25.
  • Beginning of the downward conveying stroke of the Pump piston 61 of the high-pressure fuel pump 3 is First, a part of the fuel from the same way the pump working space 63 in the suction 73 back promoted.
  • the electrical Control valve controls the electrical Control valve the time of the beginning and also the end the high-pressure delivery of the high-pressure fuel pump. 3 to the fuel injection valve 1.
  • the Fuel high pressure conveying and in consequence the Fuel injection at the fuel injection valve 1 through the closing of the flow cross-section between the Control lines 75 and 77 on the electric control valve. 5 initiated.
  • a high fuel pressure in Pump workspace 63 constructed, which extends over the bore 79, the channel 83 and the high-pressure fuel channel 33 to in the pressure chamber 31 continues on the fuel injection valve 1.
  • the fuel injection on the invention Fuel injection valve in a pre and a Main injection quantity divided, wherein the valve member 21st initially only a limited one during the pre-injection phase Run through the opening stroke, by passing over the Control edge 55 on the valve member 21 via the shoulder surface 49th the intermediate disc 11 is limited, as a result of the Damper chamber 47 controlled at the fuel injection valve 1 is, so that the closing force on the valve member 21st elevated.
  • the bypass piston 45 starts in the to lift off upcoming injection high pressure from its seat and by the on the first and after taking off the Ausweichkolbens 45 from the seat on the second Force introduction surface 89 and 91 now attacking High fuel pressure shifted in the direction of the spring chamber 37.
  • the size of the additional hydraulic closing force in the Spring chamber 37 and the pressure reduction can be in Dependence on the total stroke of the bypass piston 45 and the Shaft diameter of the valve member 21 through the Set the dimensioning of the throttle bore 99, wherein the Diameter of this throttle bore 99 at a stroke of Ausweichkolbens 45 from about 0.5 to imm preferably between 0.4 to 1.2mm.

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 (6)

  1. Combinaison formée d'un injecteur de carburant et d'une pompe à haute pression pour des moteurs à combustion interne, dans laquelle
    l'injecteur de carburant (1) a une aiguille d'injecteur (21) coulissante axialement dont l'extrémité située du côté de la chambre de combustion commande la section de passage vers au moins un orifice d'éjection (27) pour l'ouvrir ou le fermer et dont l'extrémité éloignée de la chambre de combustion pénètre au moins indirectement dans une chambre à ressorts (37) remplie de carburant et dans laquelle est serré un ressort d'injection (41) agissant sur l'aiguille d'injecteur (21) dans le sens de la fermeture, ce ressort s'appuyant contre un piston d'échappement (45) par son extrémité opposée à celle s'appuyant sur l'aiguille,
    pendant l'alimentation en carburant à haute pression, au niveau de l'injecteur (1), ce piston coulisse d'une certaine course dans la chambre à ressort (37) et augmente la force de précontrainte du ressort d'injecteur (41), et un canal de liaison en forme d'organe d'étranglement (99) relie la chambre à ressorts (37) à une chambre basse pression de carburant (73), la chambre basse pression de carburant (73) entourant un organe de retenue d'injecteur (13) qui entoure l'injecteur de carburant (1),
    la pompe haute pression (3) qui fournit le carburant à haute pression forme avec l'injecteur de carburant (1) une unité constructive logée dans un boítier (7) du moteur thermique à alimenter, et
    une soupape de commande électrique (5) équipe la pompe haute pression (3) pour commander le débit à haute pression de la pompe haute pression (3),
    caractérisée en ce que
    le piston d'échappement (45) est guidé dans une chambre hydraulique active (81) ayant deux diamètres différents, une première zone de petit diamètre (85) communique en permanence avec la chambre active (63) de la pompe haute pression (3) alors qu'une seconde zone de diamètre plus grand (87) ne communique avec la chambre active (63) de la pompe qu'après la commande d'ouverture d'une section de passage par un mouvement de déplacement du piston d'échappement (45), et
    le piston d'échappement (45) présente deux surfaces hydrauliques différentes, dont une première surface d'application de force (89), petite, délimite la première zone de petit diamètre de la chambre active hydraulique (81), et dont une seconde surface d'application de force (91) plus grande se situe dans la seconde zone de grand diamètre (87) de la chambre active hydraulique (81).
  2. Combinaison selon la revendication 1,
    caractérisée en ce que
    l'organe d'étranglement (99) est en forme de perçage d'étranglement dont le diamètre est compris de préférence dans une plage entre 0,4 et 1,2 mm.
  3. Combinaison selon la revendication 2,
    caractérisée en ce que
    le perçage d'étranglement (99) débouche à partir de la chambre à ressorts (37) dans une chambre d'aspiration (73) formant la chambre basse pression et entourant le support d'injecteur (13) de l'injecteur de carburant.
  4. Combinaison selon la revendication 1,
    caractérisée en ce que
    l'aiguille (21) comporte, à son extrémité éloignée de la chambre de combustion, un bouton d'appui (35) qui pénètre dans la chambre d'amortissement (47) remplie de carburant, et qui est délimité par un décrochement (49) fixe, formant une butée de déplacement pour un épaulement annulaire (51) de l'aiguille d'injecteur (21), et
    entre la paroi de la chambre d'amortissement (47) et le bouton de pression (35) il se forme une section d'étranglement dans laquelle débouche la chambre à ressorts (37) et qui peut être commandée pendant le mouvement de soulèvement de l'aiguille d'injecteur (21).
  5. Combinaison selon la revendication 1,
    caractérisée en ce que
    le piston d'échappement (45) comporte une collerette annulaire (93) délimitant la chambre active hydraulique (81), la surface frontale annulaire de cette collerette, tournée vers la chambre active (63) de la pompe, constituant la seconde plus grande surface d'application de force (91) et la surface frontale annulaire opposée à la chambre active de pompe (63) forme une surface d'appui coopérant avec une surface de butée de course, fixe, pour limiter le mouvement du piston d'échappement (45).
  6. Combinaison selon la revendication 1,
    caractérisée en ce que
    le piston d'échappement comporte, à son extrémité opposée à celle de la chambre active (63), un plateau à ressort (43), supérieur, arrivant jusque dans la chambre à ressorts (37), ce plateau à ressort fixe formant un appui réglable pour le ressort d'injecteur (41).
EP99969769A 1998-09-30 1999-09-29 Soupape d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP1045983B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19844891A DE19844891A1 (de) 1998-09-30 1998-09-30 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19844891 1998-09-30
PCT/DE1999/003140 WO2000019089A1 (fr) 1998-09-30 1999-09-29 Soupape d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1045983A1 EP1045983A1 (fr) 2000-10-25
EP1045983B1 true EP1045983B1 (fr) 2005-02-23

Family

ID=7882830

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99969769A Expired - Lifetime EP1045983B1 (fr) 1998-09-30 1999-09-29 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (6)

Country Link
US (1) US6305359B1 (fr)
EP (1) EP1045983B1 (fr)
JP (1) JP4443051B2 (fr)
KR (1) KR100642172B1 (fr)
DE (2) DE19844891A1 (fr)
WO (1) WO2000019089A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10062896B4 (de) * 2000-12-16 2009-12-17 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10203264A1 (de) * 2001-02-20 2002-11-07 Volkswagen Ag Kraftstoffeinspritzdüse mit Ausweichkolben
DE10119602A1 (de) * 2001-04-21 2002-10-24 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE20110130U1 (de) * 2001-06-19 2002-10-24 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
US6595188B2 (en) * 2001-12-04 2003-07-22 Caterpillar Inc Compact valve assembly and fuel injector using same
DE10160080A1 (de) * 2001-12-07 2003-06-26 Siemens Ag Pumpe-Düse-Einheit
DE10201529A1 (de) * 2002-01-17 2003-07-31 Volkswagen Ag Pumpe-Düse-Element für eine Brennkraftmaschine
DE10207974A1 (de) * 2002-02-25 2003-09-18 Bosch Gmbh Robert Geräuschoptimierte Einrichtung zum Einspritzen von Kraftstoff
WO2004057176A1 (fr) 2002-12-20 2004-07-08 Volkswagen Mechatronic Gmbh & Co. Kg Unite d'injecteur-pompe
DE10311522A1 (de) * 2003-03-17 2004-09-30 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE102004034672A1 (de) 2004-07-17 2006-02-16 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
AT501668B1 (de) * 2004-08-24 2007-03-15 Bosch Gmbh Robert Steuerventil für eine einspritzdüse
DE102004047143A1 (de) * 2004-09-29 2006-04-06 Robert Bosch Gmbh Piezoelektrischer Brennraum-Drucksensor mit einem Druckübertragungsstift
DE102005004069A1 (de) 2005-01-28 2006-08-03 Volkswagen Mechatronic Gmbh & Co. Kg Einspritzvorrichtung mit einer Dichtungsanordnung
JP4227965B2 (ja) * 2005-02-28 2009-02-18 三菱重工業株式会社 電磁制御燃料噴射装置
JP5308477B2 (ja) * 2011-05-24 2013-10-09 ヤマハ発動機株式会社 ４サイクルエンジン

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6036772A (ja) * 1983-08-10 1985-02-25 Diesel Kiki Co Ltd 燃料噴射弁
JP2523759B2 (ja) * 1987-02-04 1996-08-14 フエスト − アルピネ オウトモチブ ゲゼルシャフト ミットベシュレンクテル ハフツンク 燃料噴射ノズル
DE3900763C2 (de) * 1989-01-12 1994-05-19 Robert Bosch Ag Wien Kraftstoffeinspritzdüse, insbesondere Pumpedüse, für eine Brennkraftmaschine
JPH03504035A (ja) * 1989-01-12 1991-09-05 フエスト　‐　アルピネ　オウトモチブ　ゲゼルシャフト　ミット　ベシュレンクテル　ハフツンク 燃料噴射ノズル
DE19641824A1 (de) * 1996-10-10 1998-04-16 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
GB9624513D0 (en) * 1996-11-26 1997-01-15 Lucas Ind Plc Injector
DE19706469A1 (de) * 1997-02-19 1998-08-27 Daimler Benz Ag Speichereinspritzsystem für eine mehrzylindrige Brennkraftmaschine mit magnetventilgesteuerten Kraftstoffeinspritzventilen
US5947382A (en) * 1997-06-11 1999-09-07 Stanadyne Automotive Corp. Servo controlled common rail injector

Also Published As

Publication number Publication date
US6305359B1 (en) 2001-10-23
JP2002525496A (ja) 2002-08-13
KR100642172B1 (ko) 2006-11-03
JP4443051B2 (ja) 2010-03-31
DE19844891A1 (de) 2000-04-06
EP1045983A1 (fr) 2000-10-25
DE59911660D1 (de) 2005-03-31
WO2000019089A1 (fr) 2000-04-06
KR20010024670A (ko) 2001-03-26

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