WO2001014717A1 - Dispositif d'injection de carburant pour moteurs a combustion interne - Google Patents

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

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Publication number
WO2001014717A1
WO2001014717A1 PCT/DE2000/002678 DE0002678W WO0114717A1 WO 2001014717 A1 WO2001014717 A1 WO 2001014717A1 DE 0002678 W DE0002678 W DE 0002678W WO 0114717 A1 WO0114717 A1 WO 0114717A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel injection
injection device
valve member
fuel
piezo
Prior art date
Application number
PCT/DE2000/002678
Other languages
German (de)
English (en)
Inventor
Patrick Mattes
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
Priority to JP2001518566A priority Critical patent/JP2003507642A/ja
Priority to EP00956130A priority patent/EP1210511A1/fr
Publication of WO2001014717A1 publication Critical patent/WO2001014717A1/fr

Links

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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0063—Two or more actuators acting on a single valve body
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1, as is known from DE 196 24 001 AI.
  • the opening stroke required to open the valve member that relieves a control chamber is generated by means of a piezo actuator. So that the useful stroke of the valve member is constant at all temperatures, one is required
  • Valve member is arranged.
  • the hydraulic coupler has the additional advantage of translating a piezo actuator into a stroke, which leads to a significant increase in the valve speed.
  • the amount of fuel can be controlled very precisely and the stroke-to-stroke scatter of a fuel injector decreases.
  • the problem with the use of a hydraulic coupler is that, due to the system, in the hydraulic coupler very high pressures must be generated so that the valve member lifts off its valve seat and opens. It is therefore necessary, on the one hand, to design the piston gap dimensions to be very small in order to limit the leakage from the hydraulic coupler, and on the other hand the piezo actuator must be significantly oversized in order to compensate for the stroke losses due to the leakage.
  • the fuel injection device for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that the piezo device requires a reduced volume overall. This can be explained by the fact that, due to the lower pressure required in the hydraulic coupler, this has less leakage and thus less stroke losses. This in turn results in a correspondingly smaller-sized piezo actuator that interacts with the hydraulic coupler.
  • the smaller-sized piezo actuator also requires lower currents to control the piezo actuator and a smaller and simpler control device for the piezo actuator.
  • the reduced pressure prevailing in the hydraulic coupler it is possible to provide for an increase in the tolerance of the piston gap dimensions, so that production is simplified.
  • FIG. 1 shows a schematic illustration of a fuel injection device and FIG. 2 shows part of a fuel injection valve together
  • FIG. 1 shows a fuel injection valve 10 m in a simplified representation, which has an injection valve housing 12 with a stepped bore 13, in which a valve needle is guided as an injection valve member 15. This has at one end a conical sealing surface 16 which cooperates with a conical valve seat 17 at the end of the stepped bore 13. Fuel injection openings 18 are arranged downstream of the valve seat 17 and are separated from a pressure chamber 19 when the sealing surface 16 is placed on the valve seat 17. The pressure chamber 19 extends over an annular space 22 which is formed around the part 21 of the injection valve member 15 which adjoins the sealing surface 16 upstream and has a smaller diameter as far as the valve seat 17.
  • the pressure chamber 19 is connected via a pressure line 23 to a high-pressure fuel source in the form of a high-pressure fuel reservoir 24, which is supplied, for example, by a high-pressure pump 25, which delivers a variable delivery rate, from a reservoir 27 with fuel which is brought to the injection pressure.
  • the high-pressure fuel accumulator 24 supplies several of the fuel injection valves 10 shown Fuel injection system is referred to as a “common rail system”.
  • the part 21 of the injection valve member 15 with a smaller diameter goes with a pressure shoulder 28 m pointing towards the valve seat 17 and a part 29 of the larger diameter
  • Injector valve member 15 over. This is tightly guided in the stepped bore 13 and continues on the side facing away from the pressure shoulder 28 in an intermediate part 30 to hm to a piston-shaped end 31 of the injection valve member 15. In the area of the intermediate part 30, the latter has a spring plate 32, between which and the injection valve housing 12 a compression spring 33 is clamped, which acts on the injection valve member 15 in the closed position.
  • the piston-shaped end 31 of the injection valve member 15 delimits an end face 34, the area of which is larger than that of the pressure shoulder 28 in the injection valve housing 12, a control chamber 35.
  • the control chamber 35 is connected via a supply throttle 36 m to the
  • control chamber 35 is connected to a relief chamber 39, which can also be the reservoir 27, for example, via an outlet channel 38 and an outlet throttle 37.
  • the passage of the drain channel 38 is controlled by a control valve 40, which is designed as a 2/2 way valve.
  • control valve 40 The structure of the control valve 40 is shown in more detail in FIG.
  • the cylindrical control valve 40 is connected to the
  • the control valve 40 has an essentially sleeve-shaped outer housing 42, the end 43 facing away from the injection valve housing 12 is closed by a flanging process or the like.
  • Inside the outer case 42 is on the Injection valve housing 12 facing away from a first, simplified piezo actuator 45 integrated, which is axially delimited by two fixed bearing plates 46, 47.
  • the lower fixed bearing plate 47 is coupled to a first plunger 48, which is sealed on its circumference by means of a sealing element 49 to the outer housing 42.
  • a section 51, enlarged in diameter, of the first plunger 48 projects into a first bore 52 of a hydraulic translator 55 or hydraulic coupler having a cylindrical housing 53.
  • a second bore 56 of smaller diameter is formed in the housing 53, in which a second plunger 57 is immersed from the side facing the injection valve housing 12.
  • the underside 58 of the housing 53 facing the injection valve housing 12 lies flat on the upper end face 59 of the injection valve housing 12.
  • the injection valve housing 12 has a threefold stepped through hole 61 opening into the control chamber 35.
  • the section 62 of the through hole 61 facing the housing 53 has the largest diameter, the section 63 opening into the control chamber 35 has the smallest diameter.
  • the drain channel 38 also branches off from the section 63 to the relief chamber 39.
  • a second piezo actuator 65 likewise shown in simplified form, is arranged in section 62.
  • the second piezo actuator 65 which is significantly smaller than the first piezo actuator 45, has a centrally arranged through hole 66 which is penetrated by the second plunger 57 with radial play. With regard to its axial movement path, the second piezo actuator 65 is arranged in a form-fitting manner between the underside 58 of the housing 53 and a collar 67 of the second plunger 57 which is enlarged in diameter. The collar 67 is slidably guided in the central section 64 of the through hole 61. The reason 68 of the middle section 64 serves as an axial stroke limiter for the second plunger 57.
  • a plunger section 69 adjoins the collar 67, which is guided in section 63 with radial play and which interacts with a valve member 70 designed as a ball.
  • a seat edge 72 is formed which, together with the valve member 70, forms a sealing seat, so that no fuel can flow out of the control chamber 35 via the section 63 and the drain channel 38 to the relief chamber 39.
  • the control of the fuel injection valve 10 takes place via the control valve 40 or the two piezo actuators 45, 65 via a control device 73, which controls the control valves 40 of the individual fuel injection valves 10 as a function of operating parameters, and the pressure in the high-pressure fuel accumulator with a pressure sensor 74 24 detects and controls the variable delivery high pressure pump 25 in accordance with the deviation from a desired setpoint.
  • a pressure limiting valve 75 can be provided, which can also be controlled as a pressure control valve depending on operating parameters, depending on the design of the high-pressure fuel supply.
  • the high-pressure pump 25 can also continuously deliver in the same quantity and the pressure in the high-pressure fuel accumulator 24 can be regulated via the pressure limiting valve 75, which is to be regarded here explicitly as a pressure control valve.
  • the fuel injection device described above which is in particular a component of a diesel internal combustion engine, works as follows: When the control valve 40 is closed, ie the piezoactuators 45, 65 are not actuated, the valve member 70 bears against the seat edge 72 and seals the control chamber 35 to the relief chamber 39.
  • the sealing seat is due to the constant connection of the control room 35 with the
  • High-pressure fuel accumulator 24 is formed because the pressure prevailing in the control chamber 35 is at a high level. Because the area of the end face 34 is larger than the area of the pressure shoulder 28 and the pressure acting on both areas is the same at the moment, a resultant force results which holds the injection valve member 15 in the closed position with respect to the injection openings 18.
  • first only the second piezo actuator 65 is controlled by the control unit 73. The second piezo actuator 65 is therefore only for lifting the
  • Valve member 70 responsible from the seat edge 72 i.e. that it has a relatively small stroke.
  • the relatively small stroke of the second piezo actuator 65 is sufficient to overcome an increase in the opening force of the valve member 70 due to the seat angle difference.
  • the second piezo actuator 65 expands, it is supported against the underside 58 of the housing 53 and presses it via the collar 67 of the second plunger 57 in the direction of the relief chamber 35
  • Actual opening of the valve member 70 by means of the first piezo actuator 45 which has a greater stroke than the second piezo actuator 65.
  • a relatively low lifting force of the first piezo actuator 45 is sufficient to move the second plunger 57 further.
  • the stroke of the first piezo actuator 45 is increased by the hydraulic translator 55.
  • the maximum stroke of the second plunger 57 is determined by the bottom 68 of the through bore 61 acting as a stroke stop is limited.
  • the lifting of the valve member 70 or the opening stroke by the first piezo actuator 45 causes fuel to flow out of the control chamber 35 to the relief chamber 39, so that, decoupled from

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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)

Abstract

L'invention concerne un dispositif d'injection de carburant pour moteurs à combustion interne, qui comporte plusieurs soupapes d'injection de carburant (10) qui sont alimentées en carburant par un accumulateur haute pression de carburant (24). Chaque soupape d'injection de carburant (10) comporte un obturateur d'injection (15) sous forme de pointeau, dont le déplacement peut être commandé par l'intermédiaire de la pression de carburant régnant dans une chambre de commande (35). Selon l'invention, il est proposé que le déplacement d'un obturateur (70) déchargeant la chambre de commande (35) en direction d'une chambre de décharge (39), lequel est couplé à un poussoir (57), soit commandé au moyen de deux actionneurs piézo (45, 65). Ces deux actionneurs piézo (45, 65) sont montés l'un derrière l'autre de telle sorte que leurs levées agissent dans le même sens.
PCT/DE2000/002678 1999-08-20 2000-08-10 Dispositif d'injection de carburant pour moteurs a combustion interne WO2001014717A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2001518566A JP2003507642A (ja) 1999-08-20 2000-08-10 内燃機関用の燃料噴射装置
EP00956130A EP1210511A1 (fr) 1999-08-20 2000-08-10 Dispositif d'injection de carburant pour moteurs a combustion interne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19939446A DE19939446A1 (de) 1999-08-20 1999-08-20 Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19939446.6 1999-08-20

Publications (1)

Publication Number Publication Date
WO2001014717A1 true WO2001014717A1 (fr) 2001-03-01

Family

ID=7918972

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2000/002678 WO2001014717A1 (fr) 1999-08-20 2000-08-10 Dispositif d'injection de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
EP (1) EP1210511A1 (fr)
JP (1) JP2003507642A (fr)
CZ (1) CZ2002606A3 (fr)
DE (1) DE19939446A1 (fr)
WO (1) WO2001014717A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10129375B4 (de) * 2001-06-20 2005-10-06 Mtu Friedrichshafen Gmbh Injektor mit Piezo-Aktuator
JP4167230B2 (ja) 2004-01-13 2008-10-15 デルファイ・テクノロジーズ・インコーポレイテッド 燃料噴射装置
DE102009026554A1 (de) * 2009-05-28 2010-12-02 Robert Bosch Gmbh Drosselventil für flüssige und/oder gasförmige Stoffe
DE102011103262A1 (de) 2011-06-01 2012-12-06 Golle Motor Gmbh Einspritzinjektor für Verbrennungsmotoren

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01147143A (ja) * 1987-12-01 1989-06-08 Toyota Motor Corp 内燃機関の燃料噴射装置
EP0789142A1 (fr) * 1995-08-29 1997-08-13 Isuzu Motors Limited Dispositif d'injection de carburant du type a accumulation
DE19624001A1 (de) 1996-06-15 1997-12-18 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19654782C1 (de) * 1996-12-31 1998-05-20 Dualon International S A Einspritzinjektor für Dieselmotoren
DE19732802A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01147143A (ja) * 1987-12-01 1989-06-08 Toyota Motor Corp 内燃機関の燃料噴射装置
EP0789142A1 (fr) * 1995-08-29 1997-08-13 Isuzu Motors Limited Dispositif d'injection de carburant du type a accumulation
DE19624001A1 (de) 1996-06-15 1997-12-18 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19654782C1 (de) * 1996-12-31 1998-05-20 Dualon International S A Einspritzinjektor für Dieselmotoren
DE19732802A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 013, no. 405 (M - 868) 7 September 1989 (1989-09-07) *

Also Published As

Publication number Publication date
CZ2002606A3 (cs) 2003-06-18
JP2003507642A (ja) 2003-02-25
EP1210511A1 (fr) 2002-06-05
DE19939446A1 (de) 2001-03-01

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