EP2246553A1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2246553A1
EP2246553A1 EP10154614A EP10154614A EP2246553A1 EP 2246553 A1 EP2246553 A1 EP 2246553A1 EP 10154614 A EP10154614 A EP 10154614A EP 10154614 A EP10154614 A EP 10154614A EP 2246553 A1 EP2246553 A1 EP 2246553A1
Authority
EP
European Patent Office
Prior art keywords
servo
nozzle
needle
fuel injector
actuator
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.)
Granted
Application number
EP10154614A
Other languages
German (de)
English (en)
Other versions
EP2246553B1 (fr
Inventor
Matthias Burger
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 EP2246553A1 publication Critical patent/EP2246553A1/fr
Application granted granted Critical
Publication of EP2246553B1 publication Critical patent/EP2246553B1/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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • 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
    • 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
    • F02M2547/005—Fuel injectors without fuel return, i.e. the pressure in the control chamber is released into the combustion chamber with fluid flow only in one direction

Definitions

  • the invention relates to a fuel injector with a arranged in the injector body high-pressure chamber, which communicates constantly in operation with a high pressure fuel source and via nozzles, which are controlled by a servo-controlled nozzle needle or the like, for injecting fuel with a combustion chamber is connectable, and with an actuator which controls the actuation of the nozzle needle, the pressure in a servo workspace of a servo piston forcibly coupled to the nozzle needle.
  • Fuel injectors are used as standard in the internal combustion engines of motor vehicles.
  • the problem is given in a fuel injector, on the one hand perform the opening and closing movements of the nozzle needle with the least possible delay against Aktorh; on the other hand, the power requirement of the actuator should be kept low. It is therefore an object of the invention to provide an actuator with servo-controlled nozzle needle according to the type specified a particularly rapid response of the nozzle needle to Aktorhübe.
  • This object is achieved in that a partial cross section of the servo piston acted upon by the pressure in the high-pressure chamber against the pressure in the servo workspace and the actuator is positively coupled to a valve body, one of the operating positions of the nozzle needle independent connection between the input side of the nozzle and the constantly throttled with controls the servo workspace communicating with the high pressure space.
  • the invention is based on the general idea of hydraulically arranging the servo work space such that the pressure in the servo work room can be raised to the pressure in the high-pressure space and lowered to the comparatively negligible pressure in the combustion space, that is to say on the outlet side of the nozzles.
  • the actuator brings the aforementioned valve body in its open position, the connection between the servo workspace and the inlet side of the nozzle is opened, with the result that the pressure in the servo work chamber is lowered below the pressure in the high-pressure chamber and the nozzle needle is opened by the high pressure acting on a partial cross-section of the servo piston.
  • the invention is based on the finding that the comparatively low pressure in the combustion chamber can be used instead of the vanishing pressure in a fuel tank, which is generally far away from the fuel injector, as the low-pressure level for the servo workspace.
  • a particular advantage of the invention is the fact that no line to a far away low pressure area, such. Eg fuel tank, required.
  • the fuel injector therefore only has to be connected to a high-pressure source for fuel, generally a common rail.
  • the nozzle needle can be configured as a hollow needle with an axial passage connecting the servo work space to the input side of the nozzles and the valve body controlled by the actuator as a valve needle controlling the axial passage.
  • valve needle is displaceably guided in the axial channel and cooperates with a seat arranged at the nozzle-side end of the axial channel.
  • nozzle needle can be arranged between the high-pressure chamber and the inlet side of the nozzle effective when the nozzle needle throttle.
  • this throttle is designed as a gap throttle between the outer circumference of the nozzle needle or a plate or the like arranged thereon and the inner circumference of a subsequent to the high-pressure chamber of the injector nozzle body, communicates through the interior of the high-pressure chamber with the input side of the nozzle.
  • a throttle is preferably provided between the high-pressure chamber and the servo working chamber, with which the speed of the pressure increase in the servo work space is determined when the connection of the servo work chamber to the input side of the nozzles is blocked.
  • the illustrated fuel injector has a built-up injector body 1, with two high-pressure chambers 2 and 3.
  • the first high-pressure chamber 2 is continuously connected to a high-pressure source 4 for fuel via a bore passing through the injector body 1, this high-pressure source typically being designed as a so-called common rail.
  • the second high-pressure chamber 3 communicates with the first high-pressure chamber 2 via a bore 7 passing through the intermediate bodies 5 and 6, so that pressure equality exists in the two chambers 2 and 3.
  • the high-pressure chamber 3 is connected via the interior of a nozzle body 7 with the input side of injection nozzles 8, the output side open into a combustion chamber, not shown, of an engine or the like.
  • the injection nozzles 8 are controlled by means of a nozzle needle 9, which is guided displaceably in the nozzle body 7 and with its in the drawing lower end with a within the Nozzle body 7 arranged, the inlet openings of the injectors 8 enclosing seat 10 cooperates.
  • the outer circumference of the nozzle needle 9 and the inner circumference of the nozzle body 7 are shaped such that on the one hand a relatively play-free axial guidance of the nozzle needle 9 is ensured in the nozzle body 7 and on the other hand communicate the input sides of the injectors 8 with the second high-pressure chamber 3, when the nozzle needle 9 from the Seat 10 takes off open position.
  • an annular disc 11 is formed, the outer periphery of the inner periphery of the leading from the high-pressure chamber 3 to the injectors 8 bore in the injector body 1 is closely adjacent, such that a ring gap choke 12 is formed.
  • the purpose of the annular gap choke 12 will be explained below.
  • a piston 13 is arranged with respect to the cross section of the nozzle needle 9 enlarged cross-section.
  • a sealing sleeve 14 is slidably guided, which is clamped by a concentric to the piston 13 helical compression spring which is clamped between an annular step at the lower end of the high-pressure chamber 3 and the facing end face of the sealing sleeve 14, sealingly against the facing end face of the intermediate body. 6 is tense.
  • the top edge of the sealing sleeve 14 in the drawing is tapered wedge-shaped, so that the sealing sleeve is sealingly seated on the intermediate body 6 at an annular contact zone.
  • the sealing sleeve 14 separates above the piston 13 a servo chamber 15, which continues in a coaxial to the nozzle needle 9 hole in the intermediate body 6, from the high-pressure chamber 3.
  • the servo chamber 15 is connected via an intermediate body 6 passing through throttle channel 16 with an annular groove 17 on the intermediate body 5 facing end face of the intermediate body 6 connected.
  • the diameter of this annular groove 17 is dimensioned so that the annular groove without throttle communicates with the high-pressure chambers 2 and 3 connecting the bore, which passes through the intermediate body 5 and 6.
  • the nozzle needle 9 is formed as a hollow needle with an open at the lower end of the nozzle needle 9 axial channel, the upper end opens into the servo chamber 15.
  • a valve needle 18 is guided axially displaceable, the lower end cooperates with a seat at the lower end of the aforementioned axial channel in the nozzle needle 9 and controls the axial channel.
  • In the illustrated closed position of the valve needle 8 of the axial channel is shut off in the nozzle needle 9.
  • the valve needle 8 lifts from its seat at the lower end of the nozzle needle 9, the servo space 15 is connected to the input side of the injectors 8.
  • the valve needle 18 is constantly clamped by a helical compression spring 19, which is clamped between an annular flange on the valve needle 18 and the lower end face of the intermediate body 5, in the seated on the seat 10 closed position.
  • a piezoelectric actuator 20 is provided, which is hydraulically coupled to the valve needle 18 in a manner shown below.
  • the actuator 20 is housed in the high pressure chamber 2 and formed in a basically known manner so that it elongates in the vertical direction when it is electrically charged, that is connected to an electrical voltage source (not shown). As soon as the actuator 20 is electrically discharged, it shortens in the vertical direction.
  • a plungertellr master piston 21 is arranged on the outer circumference of a sealing sleeve 22 is slidably guided, which is tensioned by a concentric to the master piston 21 helical compression spring 23 against the upper end side of the intermediate body 5, wherein the intermediate body facing end edge of the sealing sleeve 22 has a wedge-shaped profile, so that the sealing sleeve 22 is seated with a ring-shaped sealing edge on the intermediate body 5.
  • the sealing sleeve 22 downwardly exciting helical compression spring 23 simultaneously urges the actuator 20 upwards, such that its upper front end is constantly seated on an upper bottom of the injector body 1 and the ceramic of the piezoelectric actuator 20 is subjected to pressure only.
  • the sealing sleeve 22 separates from the high-pressure chamber 2 from a transmitter chamber 24, which communicates with a slave chamber 25, which remains free in an upper plunger-like end of the valve needle 18 slidably receiving axial bore in the intermediate body 5 above the valve needle 18.
  • the transmitter chamber increases, so that hydraulic fluid from the slave chamber 25 flows into the transmitter chamber 24 and the valve needle 18 can perform an upward stroke.
  • the servo chamber 15 is shut off in the direction of the input side of the injection nozzles 8.
  • the servo chamber 15, which communicates via the throttle bore 16 and the annular groove 17 with the high-pressure chamber 2 is charged to the high system pressure of the high-pressure chamber 2.
  • the nozzle needle 9 is held in its closed position.
  • valve needle 18 moves away from its seat at the lower end of the axial bore in the nozzle needle 9, and the servo chamber 15 is in communication with the input side of the injectors 8.
  • the inlet side of the nozzles 8 has the same pressure as when the nozzle needle 9 is in the closed position the output side of the nozzles 8 arranged combustion chamber. Since the combustion chamber pressure is considerably lower than the pressure in the high-pressure chambers 2 and 3, the pressure in the servo chamber 15 drops correspondingly, whereby the throttle channel 16 prevents an inflow of high-pressure fluid which compensates for the pressure drop from occurring due to inflowing fluid from the high-pressure chamber 2.
  • the high pressure in the High pressure chamber 3 is present and acts on the annular step between the nozzle needle 9 and servo piston 13 and on the partial cross section of the nozzle needle 9 outside the seat 10, that the nozzle needle 9 lifts off from the seat 10. This starts the injection phase, that is from the high-pressure chamber 3 flows under high pressure fluid to the input side of the injectors 8 and thus into the combustion chamber.
  • a particular advantage of the invention is the fact that the nozzle needle 8 follows exactly the movement of the valve needle 18.
  • valve needle 18 assume a position between its end positions in the course of a movement stroke. If the nozzle needle 9 in this case has a position in which the nozzle needle 9 passing axial channel is shut off, a high pressure will build up in the servo chamber 15, with the result that the nozzle needle 9 moves relative to the valve needle 18 slightly downward and the aforementioned axial channel is opened. Thus, the pressure in the servo chamber 15 drops below the pressure in the high pressure chambers 2 and 3, because at the input side of the injectors 8 due to unavoidable throttle losses in the flow path from the high pressure chamber 2 to the injectors 8, a lower pressure than in the high pressure chambers 2 and 3 is present.
  • the stroke of the valve needle 18 caused by the actuator 20 is thus executed in a reproducible manner by the nozzle needle 9.
  • the actuator 20 must However, only apply the necessary forces for the movements of the valve needle 19. Since the valve needle 18 in the slave chamber 25 and the master piston in the encoder chamber 24 are displaceable with different cross-sections, a corresponding Hubüber acid is effected, that is, the stroke of the valve needle 18 is greater by a predetermined by the quotient of the effective Verdrängerquerroughe factor than the stroke of the actuator 20th or the master piston 21. In this case, a corresponding translation of the actuating speeds, that is, the valve needle 18 moves together with the nozzle needle 9 significantly faster than the master piston 21st
  • the construction shown in the drawing of the injector body 1 is shown only schematically.
  • the nozzle body 7 can be held on a lower part body of the injector body 1, wherein the lower part body can be connected with the interposition of the intermediate body 5 and 6 with an upper body part of the injector body 1 by means of a sleeve-shaped nut.

Landscapes

  • 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)
EP20100154614 2009-04-24 2010-02-25 Injecteur de carburant Not-in-force EP2246553B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910002621 DE102009002621A1 (de) 2009-04-24 2009-04-24 Kraftstoffinjektor

Publications (2)

Publication Number Publication Date
EP2246553A1 true EP2246553A1 (fr) 2010-11-03
EP2246553B1 EP2246553B1 (fr) 2013-04-10

Family

ID=42167501

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100154614 Not-in-force EP2246553B1 (fr) 2009-04-24 2010-02-25 Injecteur de carburant

Country Status (2)

Country Link
EP (1) EP2246553B1 (fr)
DE (1) DE102009002621A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10348925A1 (de) * 2003-10-18 2005-05-12 Bosch Gmbh Robert Kraftstoffinjektor mit mehrteiligem, direktgesteuertem Einspritzventilglied
DE102006019736A1 (de) * 2006-04-28 2007-10-31 Robert Bosch Gmbh Kraftstoffinjektor
DE102006035983A1 (de) * 2006-08-02 2008-02-07 Robert Bosch Gmbh Injektor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10348925A1 (de) * 2003-10-18 2005-05-12 Bosch Gmbh Robert Kraftstoffinjektor mit mehrteiligem, direktgesteuertem Einspritzventilglied
DE102006019736A1 (de) * 2006-04-28 2007-10-31 Robert Bosch Gmbh Kraftstoffinjektor
DE102006035983A1 (de) * 2006-08-02 2008-02-07 Robert Bosch Gmbh Injektor

Also Published As

Publication number Publication date
DE102009002621A1 (de) 2010-10-28
EP2246553B1 (fr) 2013-04-10

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