EP2267295A2 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2267295A2
EP2267295A2 EP10160976A EP10160976A EP2267295A2 EP 2267295 A2 EP2267295 A2 EP 2267295A2 EP 10160976 A EP10160976 A EP 10160976A EP 10160976 A EP10160976 A EP 10160976A EP 2267295 A2 EP2267295 A2 EP 2267295A2
Authority
EP
European Patent Office
Prior art keywords
valve
piston
stop
chamber
fuel injector
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.)
Withdrawn
Application number
EP10160976A
Other languages
German (de)
English (en)
Other versions
EP2267295A3 (fr
Inventor
Joerg Hahn
Peter Schweidler
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 EP2267295A2 publication Critical patent/EP2267295A2/fr
Publication of EP2267295A3 publication Critical patent/EP2267295A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • F02M2200/70—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 injector according to the preamble of claim 1.
  • a fuel injector of the aforementioned type is for example made DE 103 22 672 A1 known.
  • the stroke of the piezo actuator is transmitted via a hydraulic coupler to a valve element of a control valve which controls a control chamber of the nozzle needle by the control chamber is connected to open the nozzle needle with a relatively pressureless low pressure / return system.
  • the control valve When the control valve is closed, the control chamber is filled via an inlet throttle with the system pressure of the common rail and the nozzle needle is placed in the nozzle needle seat.
  • the piezo actuator To open the valve seat of the control valve, the piezo actuator must press against the pressure prevailing in the valve chamber a valve pin of the control valve from the valve seat.
  • valve element comprises a valve pin and a valve pin axially guided valve sleeve, which are arranged in a valve chamber.
  • the valve sleeve separates with a sealing surface a low-pressure space, which is exposed to the valve pin with an end face, against the highly pressurized valve chamber hydraulically.
  • the valve chamber is connected to a control chamber to which the nozzle needle is exposed.
  • the control chamber is connected via the valve seat of the control valve to the low-pressure / return system, so that an outflow volume can flow out of the control chamber into the low-pressure / return system via an outlet throttle.
  • the effluent from the control chamber outflow volume flows through the valve chamber in the direction of the hydraulic coupler surrounding low pressure space, past the valve seat of the valve element.
  • the invention has the advantage that with a defined stroke stop of the valve piston of the hydraulic coupler unit acting on the valve element of the control valve Aktorhub is delimited. As a result, a defined outlet geometry is realized at the valve seat between a valve chamber of the valve element and a low-pressure chamber of the hydraulic coupler unit, whereby a defined throttling of the outflow volume from the valve chamber is made possible. In addition, an improvement of the control and regulation behavior of the fuel injector is achieved because the Aktorschwingisme occurring in the controlled state are minimized.
  • a defined outflow of Abströmvolumens from the valve chamber in the low-pressure space is achieved by at least one overflow connection between the valve chamber and the low-pressure space is present, which is effective in the stop position and at a valve pin seated by the valve seat.
  • the defined throttling of the outflow volume from the valve space leads to the avoidance or reduction of cavitating flows, which occur in particular in the vicinity of the valve seat.
  • annular surface is formed on the control valve side end of the valve piston, which forms a counter surface for the stop.
  • the stop is formed by a valve body formed on the plane stop surface, such that in the stop position, the annular surface of the valve piston rests substantially on the planar stop surface.
  • a conical circumferential surface is formed on the control valve-side end of the valve piston, which forms a counter surface for the stop.
  • the stop is formed by a valve body formed on the conical abutment surface, such that in a stop position, the conical Outer surface of the valve piston rests substantially on the conical abutment surface of the valve body.
  • the overflow connection is formed by slot-shaped or gap-shaped overflow channels on an end face of the valve piston and / or on the stop face of the valve body. Expediently, four slot-shaped or gap-shaped overflow channels arranged at right angles and directed radially to the center are provided.
  • FIG. 1 shows a part of a fuel injector in longitudinal section with an actuator element 10, a hydraulic coupler unit 11, a control valve 12 and an injection valve 13.
  • the actuator element 10 may be, for example, a piezo actuator, but also an electromagnetic actuator.
  • the actuator element 10 and the hydraulic coupler unit 11 are accommodated in an injector body 14.
  • a valve body 15, a throttle plate 16 and a nozzle body 17 adjoin the injector body 14.
  • the said bodies are clamped by means of a hydraulic nozzle nut 18 hydraulically tight.
  • a nozzle needle pressure chamber 19 is formed, which is supplied via a high pressure line 21 to the system pressure of a common rail.
  • a nozzle needle 20 is arranged, at one end of a control chamber 22 a control chamber 23 separates from the nozzle needle pressure chamber 19.
  • the hydraulic coupler unit 11 comprises a coupler body 25, in which a coupler piston 26 and a valve piston 27 are axially guided. Between the coupler piston 26 and the valve piston 27, a coupler gap 28 is formed, which is filled with fuel.
  • the valve piston 27 is designed with a conical pressure piece 29 which engages in a cone-shaped overflow opening 31 formed on the valve body 15. Between the pressure piece 29 and the overflow 31, a flow gap 32 is present. Axially in alignment with the overflow opening 31, a passage 33 is arranged in the valve body 15 and leads into a valve space 34 for the control valve 12.
  • the control valve 12 comprises a valve pin 40, on which a valve sleeve 41 is biased by means of a valve spring 42.
  • the valve pin 40 has a mushroom-shaped or valve-shaped element 44, which cooperates with a valve seat 45 formed adjacent to the passage 33.
  • the valve sleeve 41 encloses a low pressure chamber 47, which is constantly connected via a hydraulic connecting channel 48 to the low pressure / return system. Outside the valve sleeve 41, the valve chamber 34 is connected via a drain line 51 to the control chamber 23 of the nozzle needle 20.
  • the control valve 12 is shown in FIG FIG. 1 shown in the closed state, in which the valve seat member 44 rests against the valve seat 45.
  • a gap is present between the pressure piece 29 of the valve piston 27 and a support bolt of the valve seat element 44, so that the closing pressure of the valve spring 33 acts both on the valve sleeve 41 and on the valve seat element 44.
  • An additional closing force acts on the valve seat element 44 by the pressure prevailing in the valve chamber 34 of the control chamber 23 in the closed state of the nozzle needle 20.
  • the actuator element 12 is actuated and the stroke of the actuator element 12 via the coupler piston 26, the coupler gap 28 and the valve piston 27 transmitted to the valve pin 40, whereby the valve seat member 44 lifts off from the valve seat 45 and the valve chamber 34 with a hydraulic Coupler unit 11 surrounding low pressure space 30 connects.
  • the low pressure space 30 is connected to the low pressure / return system.
  • the pressure in the control chamber 23 is lowered and the nozzle needle 20 is lifted from the nozzle needle seat, not shown, and the fuel with the in the Pin pressure chamber 19 prevailing rail pressure (system pressure) injected into the combustion chamber of an internal combustion engine.
  • a mating surface 61 formed on the valve piston 27 of the hydraulic coupling unit 11 acts on a stop 64 formed on the valve body 15, whereby the stroke of the valve piston 27 and thus the stroke of the actuator element 10 acting on the valve pin 40 is limited becomes.
  • the pressure piece 29 of the valve piston 27 in this case has an end face 63 which presses against an adjacent further end face 66 of the valve pin 40.
  • overflow connections 65 are formed, which form a defined hydraulic throttle of the outflow volume between the valve space 34 and the low pressure space 30.
  • the abutment 64 is carried out by a planar abutment surface 64.1 arranged on the valve body 15 and formed by a plane surface running perpendicular to the center line of the valve piston 27 on the valve body 15.
  • a planar abutment surface 64.1 arranged on the valve body 15 and formed by a plane surface running perpendicular to the center line of the valve piston 27 on the valve body 15.
  • annular surface 61.1 designed as a mating surface 61 for the stop surface 64.1.
  • the valve seat member 44 is lifted from the valve seat 45.
  • slot-shaped or gap-shaped overflow channels 65.1 are formed, which are open on the annular surface 61.1 and on the outer circumferential surface of the valve piston 27.
  • FIG. 2a In the opened state of the control valve 12, the overflow channels 65. 1 ensure a defined throttling of the outflow volume between the valve space 34 and the low-pressure space 30
  • FIG. 2a illustrated embodiment of the slot or slit-shaped overflow channels 65, it is also conceivable, the annular Run counter-surface 61.1 continuously and incorporate the transfer channels 65.1 in the stop surface 64.1 of the valve body 15.
  • the stop 64 is formed by a conical abutment surface 64.2 formed by the conical section 31 of the valve body 15.
  • the mating surface 61 for this purpose forms a conical mantle surface 61.2 formed on the pressure piece 29.
  • slot-shaped or slot-shaped transfer channels 65.2 are incorporated in the conical jacket surface 61.2.
  • FIG. 3a in which, for example, four slot-shaped or gap-shaped transfer channels 65.2 are shown.
  • the transfer channels 65.2 in the conical abutment surface 64.2 of the valve body 15.

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)
EP10160976A 2009-06-25 2010-04-26 Injecteur de carburant Withdrawn EP2267295A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910027187 DE102009027187A1 (de) 2009-06-25 2009-06-25 Kraftstoffinjektor

Publications (2)

Publication Number Publication Date
EP2267295A2 true EP2267295A2 (fr) 2010-12-29
EP2267295A3 EP2267295A3 (fr) 2013-03-06

Family

ID=42937240

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10160976A Withdrawn EP2267295A3 (fr) 2009-06-25 2010-04-26 Injecteur de carburant

Country Status (2)

Country Link
EP (1) EP2267295A3 (fr)
DE (1) DE102009027187A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011086297A1 (de) 2011-11-14 2013-05-16 Robert Bosch Gmbh Kraftstoffinjektor zum Einspritzen von Kraftstoff
DE102011086335A1 (de) 2011-11-15 2013-05-16 Robert Bosch Gmbh Brennstoffeinspritzventil

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10322672A1 (de) 2003-05-20 2004-12-09 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10019767A1 (de) * 2000-04-20 2001-10-31 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE102006027484A1 (de) * 2006-06-14 2007-12-20 Robert Bosch Gmbh Kraftstoffinjektor mit kraftausgeglichenem Steuerventil
DE102007042466B3 (de) * 2007-09-06 2009-04-09 Continental Automotive Gmbh Einspritzsystem mit reduzierter Schaltleckage und Verfahren zum Herstellen eines Einspritzsystems
DE102008040637A1 (de) 2008-07-23 2010-01-28 Robert Bosch Gmbh Kraftstoffeinspritzventileinrichtung

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10322672A1 (de) 2003-05-20 2004-12-09 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten

Also Published As

Publication number Publication date
EP2267295A3 (fr) 2013-03-06
DE102009027187A1 (de) 2010-12-30

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