EP1911966A2 - Injecteur de carburant pour un moteur à combustion interne - Google Patents

Injecteur de carburant pour un moteur à combustion interne Download PDF

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Publication number
EP1911966A2
EP1911966A2 EP07114360A EP07114360A EP1911966A2 EP 1911966 A2 EP1911966 A2 EP 1911966A2 EP 07114360 A EP07114360 A EP 07114360A EP 07114360 A EP07114360 A EP 07114360A EP 1911966 A2 EP1911966 A2 EP 1911966A2
Authority
EP
European Patent Office
Prior art keywords
nozzle needle
coupler
fuel injector
control
injector according
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
EP07114360A
Other languages
German (de)
English (en)
Other versions
EP1911966A3 (fr
EP1911966B1 (fr
Inventor
Hans-Christoph Magel
Dirk Vahle
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 EP1911966A2 publication Critical patent/EP1911966A2/fr
Publication of EP1911966A3 publication Critical patent/EP1911966A3/fr
Application granted granted Critical
Publication of EP1911966B1 publication Critical patent/EP1911966B1/fr
Active 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
    • 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
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for 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
    • 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
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention relates to a fuel injector for an internal combustion engine according to the preamble of claim 1.
  • a control chamber which has a coupler piston with a control surface, is actuated by a control valve.
  • the coupler piston acts on the nozzle needle via a hydraulic coupler space.
  • To open the nozzle needle of the control chamber is connected by means of the control valve with a low pressure / return system, whereby the pressure in the control chamber decreases and the force acting in the opening direction of the nozzle needle pressure forces exceed the force acting on the control surface of the coupler piston pressure force.
  • a fuel injector is for example off DE 101 15 215 A1 known.
  • the coupler piston is guided in a housing.
  • the object of the present invention is to provide a fuel injector in which pressure vibrations are effectively damped and which has an improved wear behavior on the coupler guide. In addition, the production cost is to be reduced.
  • the object of the invention is achieved with the characterizing features of claim 1.
  • a solid guide is provided which exhibits improved wear behavior on the coupler guide.
  • a position separation of the coupler guide is made possible by the injector body. As a result, complex processing for a double guide can be avoided.
  • the guide element with the guide bush for the coupler piston with a nozzle needle with control sleeve for the nozzle needle-side boundary of the coupler space.
  • the nozzle needle can be arranged without guidance on the nozzle needle-side end face of the guide element in the nozzle needle pressure chamber.
  • the control sleeve is biased by a compression spring and is pressed with an annular surface by the biasing force of the compression spring against a nozzle needle-side end face, forming a sealing seat between the annular surface and nozzle needle-side end face, which separates the coupler space from the nozzle needle pressure chamber.
  • the biasing force of the compression spring is designed so that the control sleeve stands at overpressure in the coupler space with respect to the pressure in the nozzle needle pressure chamber from the sealing seat and so can take place a pressure and flow compensation between the rooms.
  • the control sleeve also exerts a switching function, so that an additional check valve for the relaxation of the coupler space can be omitted.
  • the nozzle needle-side end face is in this case of the pointing to the nozzle needle end face of the base plate of Guides formed, so that the sealing surface is also formed on the pointing to the nozzle needle end face of the base plate.
  • the guide element expediently has an opening which connects a first annulus exposed to the nozzle needle and a second annulus exposed to the coupler piston. It is also expedient if connecting channels are formed in the base plate, via which a high-pressure connection between the internal storage space and the nozzle needle pressure chamber takes place. This eliminates a separate high-pressure bore in the injector body.
  • the fuel injector shown in FIGS. 1 and 2 has a housing with an injector body 10 and a nozzle body 11.
  • a control valve 12 with an electromagnetic actuator 13 and a valve element 14 is arranged in the injector body 10.
  • the adjusting element 13 is connected to a connection part 15, which is clamped hydraulically tight with a first clamping nut 16, with the injector body 10.
  • a guide element 20 is further arranged.
  • the nozzle body 11 and the guide member 20 are clamped hydraulically tight with the injector body 10 by means of another clamping nut 19.
  • an injection valve member with an axially displaceable in the nozzle body 11 guided nozzle needle 21 is arranged.
  • injection openings 22 are introduced, which is preceded by a nozzle needle seat 23 on the nozzle body 11, on which the nozzle needle 21 rests with a sealing surface.
  • the nozzle needle seat 23 is preceded by a nozzle needle pressure chamber 24 in the nozzle body 11, to which the nozzle needle 21 is exposed with an upper pressure shoulder 25 and a lower pressure shoulder 26.
  • the nozzle needle 21 further has a nozzle needle piston 27 with a kopplerraum practicalen end face 28.
  • a control sleeve 30 is guided axially biased with a compression spring 31.
  • the control sleeve 30 further comprises an annular surface 32 which is pressed by means of the biasing force of the compression spring 31 against a later explained in more detail surface and thus forms a sealing seat.
  • the nozzle needle piston 27 and the control sleeve 30 is surrounded by an annular space 29 which is hydraulically connected via a formed on the nozzle needle 21 flattening with the nozzle needle pressure chamber 24.
  • the annular space 29 and the nozzle needle pressure chamber 24 form a common hydraulic space in which rail or system pressure is present as the injection pressure.
  • a through hole 35 is formed, which forms an internal storage space 36 for the fuel.
  • the storage space 36 performs a transverse bore 37 which is provided with a connection 38 which is connected to a high pressure line of a common rail system, not shown. Via the connection 38 and the transverse bore 37, the fuel is supplied to the internal storage space 36 with the rail or system pressure applied in the common rail system.
  • a coupler rod 40 is arranged so that the coupler rod 40 is surrounded by the system pressure.
  • the coupler rod 40 includes a needle piston side coupler piston 41 and solenoid valve side, a control piston 42.
  • the coupler rod 40 is biased by a compression spring 43 in the direction of the nozzle needle 21.
  • the control piston 42 is guided in a valve piece 44, so that a control chamber 45 is formed within the valve piece 44, to which the control piston 42 is exposed with a control surface 46.
  • the valve piece 44 On the opposite side of the control chamber 45, the valve piece 44 has a valve seat for a valve ball.
  • the valve element 14 further comprises a valve piston 47, which communicates with a magnet armature 48, which in turn is actuated by the electromagnetic actuator 13.
  • the Valve element 14 separates via the valve seat the control chamber 45 from a low pressure chamber 50 in which the actuator 12 is arranged and which is connected via hydraulic channels, not shown, with the hydraulic port 18, which leads to a low pressure / return system.
  • the compression spring 43 of the coupler piston 40 is supported via an annular disc on the valve piece 44.
  • From the control chamber 45 performs a hydraulic discharge line 49 with an outlet throttle, not shown in the low pressure chamber 50 via the valve seat of the valve member 14 from the internal storage space 36 performs another hydraulic supply line 52 with an inlet throttle also not shown in the control chamber 45.
  • the outlet throttle and the inlet throttle are dimensioned so that more fuel can flow out via the drain line 49 with the outlet throttle when the valve element 14 is open than can flow via the inlet line 52 with the inlet throttle.
  • the guide element 20 comprises a flange-like base plate 61 and a guide bushing 62 formed thereon with a guide bore 63.
  • an opening 64 is formed in alignment with the guide bore 63 and leads into the guide bore 63.
  • a nozzle needle side annular space 71 and a coupler piston side annular space 72 is formed, wherein the opening 64 and the two annular spaces 71, 72 form a coupler space 70.
  • the base plate 61 is designed on the side facing the nozzle needle 21 side with an end face 65. Against the end face 65 presses the annular surface 32 of the control sleeve 30 by means of the biasing force of the compression spring 31, so that forms between the annular surface and the end face 65 of the sealing seat with which the control sleeve 30 surrounds the nozzle needle side annular space 71 and thereby the coupler space 70 to the nozzle needle pressure chamber 24th essentially hydraulically seals.
  • the biasing force of the compression spring 31 is designed so that the control sleeve 30 additionally performs a switching function, wherein the control sleeve 30 lifts at overpressure in the coupler chamber 70 against the pressure in the nozzle needle pressure chamber 24 from the sealing seat and so a pressure and flow compensation between the coupler chamber 70 and the Nozzle needle pressure chamber 24 can take place.
  • the end face 65 can be designed as a stroke stop for the end face 28 of the nozzle needle 27 which is on the coupler-space-side.
  • the guide element 20 On the side facing the coupler rod 40, the guide element 20 has a further annular end face 66, which runs radially around the guide bushing 62.
  • a guide collar 67 which serves to center the guide element 20, is formed on the further annular end face 66.
  • a plurality of connecting channels 68 are guided through the base plate 61, which lead at the annular end face 66 by the guide collar 67 so that they surround the guide bush 63 radially. Via the connecting channels 68, a hydraulic connection of the internal storage space 36 with the nozzle needle pressure chamber 24 takes place.
  • a Hubeinstell Domain 75 is arranged in the coupler space 70, for example, which is dimensioned in diameter so that the annular spaces formed on the nozzle needle piston 27 and the coupler piston 41 via the opening 64 are hydraulically connected.
  • the base plate 61 on the side of the nozzle needle side sealing surface 65 to be provided with a stop surface, while the coupler rod 40 can move freely and thus ensures a constant pressure level in the coupler chamber 70 .
  • the advantages of a Hubanschlages lie in the mutual sealing of the two annular spaces 71, 72 from each other.
  • the fuel injector operates as follows: If the electromagnetic actuator 13 of the control valve 12 is energized, the armature 48 is pulled against the actuator 13 and thus lifts the valve element 14 from the valve seat. This results in a hydraulic connection of the control chamber 45 via the connection 49 with the low-pressure chamber 50, which in turn via the hydraulic port 18 with the low-pressure return system is connected. As a result, the pressure in the control chamber 45 drops and the opening force acting in the opening direction of the nozzle needle 21 on the pressure shoulders 25, 26 exceeds the closing force acting on the control surface 46 in the control chamber 45. The nozzle needle 21 is thereby lifted from the nozzle needle seat 23 and the injectors 22 are released.
  • the fuel present in the nozzle needle pressure chamber 24 is injected at the system pressure of the common rail. If the electromagnetic actuator 13 is de-energized again, the armature 48 drops and the armature 48 presses the valve member 14 by means of a closing spring not shown in the valve seat. Thus, the control chamber 45 is decoupled again from the low pressure / return system. The control chamber 45 is now filled via the further hydraulic connection 52 again with system pressure from the internal storage space 36.
  • the coupler rod 40 moves back in the direction of the nozzle needle 21, wherein the movement is transmitted via the coupler chamber 70 to the nozzle needle 21, so that the nozzle needle 21 again is placed in the nozzle needle seat 23.
  • the control sleeve 30 exerts a switching function and lifts off with the annular surface 32 from the nozzle needle-side sealing surface 65. Over the gap between the annular surface 32 and the nozzle needle side sealing surface 65 excess leakage from the coupler chamber 70 is discharged into the nozzle needle pressure chamber 24. As a result, the injection nozzles 22 are decoupled from the system pressure at the nozzle needle pressure chamber 24 and the injection process is ended.

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)
EP07114360A 2006-10-10 2007-08-15 Injecteur de carburant pour un moteur à combustion interne Active EP1911966B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006047935A DE102006047935A1 (de) 2006-10-10 2006-10-10 Kraftstoffinjektor für eine Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP1911966A2 true EP1911966A2 (fr) 2008-04-16
EP1911966A3 EP1911966A3 (fr) 2009-07-01
EP1911966B1 EP1911966B1 (fr) 2011-10-19

Family

ID=38924759

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07114360A Active EP1911966B1 (fr) 2006-10-10 2007-08-15 Injecteur de carburant pour un moteur à combustion interne

Country Status (3)

Country Link
EP (1) EP1911966B1 (fr)
AT (1) ATE529625T1 (fr)
DE (1) DE102006047935A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010086284A1 (fr) * 2009-02-02 2010-08-05 Continental Automotive Gmbh Soupape d'injection
WO2011160900A1 (fr) * 2010-06-23 2011-12-29 Robert Bosch Gmbh Dispositif d'injection de carburant à coupleur hydraulique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008044093A1 (de) 2008-11-26 2010-05-27 Robert Bosch Gmbh Kraftstoffinjektor für Brennkraftmaschinen

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10115215A1 (de) 2001-03-28 2002-10-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1989436A1 (fr) 2006-02-24 2008-11-12 Robert Bosch GmbH Dispositif d'injection de carburant pour moteur a combustion interne

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10115215A1 (de) 2001-03-28 2002-10-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1989436A1 (fr) 2006-02-24 2008-11-12 Robert Bosch GmbH Dispositif d'injection de carburant pour moteur a combustion interne

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010086284A1 (fr) * 2009-02-02 2010-08-05 Continental Automotive Gmbh Soupape d'injection
WO2011160900A1 (fr) * 2010-06-23 2011-12-29 Robert Bosch Gmbh Dispositif d'injection de carburant à coupleur hydraulique

Also Published As

Publication number Publication date
DE102006047935A1 (de) 2008-04-17
EP1911966A3 (fr) 2009-07-01
ATE529625T1 (de) 2011-11-15
EP1911966B1 (fr) 2011-10-19

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