EP2103802A1 - Injecteur - Google Patents

Injecteur Download PDF

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Publication number
EP2103802A1
EP2103802A1 EP09100059A EP09100059A EP2103802A1 EP 2103802 A1 EP2103802 A1 EP 2103802A1 EP 09100059 A EP09100059 A EP 09100059A EP 09100059 A EP09100059 A EP 09100059A EP 2103802 A1 EP2103802 A1 EP 2103802A1
Authority
EP
European Patent Office
Prior art keywords
pressure
nozzle needle
nozzle
valve
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
EP09100059A
Other languages
German (de)
English (en)
Other versions
EP2103802B1 (fr
Inventor
Olaf Ohlhafer
Sebastian Jansen
Sergey Solovyev
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 EP2103802A1 publication Critical patent/EP2103802A1/fr
Application granted granted Critical
Publication of EP2103802B1 publication Critical patent/EP2103802B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0614—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature
    • F02M51/0617—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature having two or more electromagnets

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • injectors in addition to a high pressure port of the injector, a low pressure port must be provided, can run back through the fuel in a substantially pressure-free tank when the control chamber to open the nozzle needle is to be relieved of pressure.
  • Injectors of this type therefore inherently have a required for the realization of the Düsennadelhubs control flow and optionally a leakage volume flow, which on the one hand, additional system overhead for return lines and on the other hand, an increased flow of the high pressure pump for the fuel are necessary.
  • the object of the invention is therefore to reduce the forces required to open an injector, so that the nozzle needle can be actuated directly with the help of comparatively weak actuators.
  • the invention is based on the general idea to provide the nozzle needle for a switchable pressure equalization, such that the hydraulically generated forces on the nozzle needle cancel each other with the appropriate circuit of the pressure compensation valve order of magnitude and dosed the nozzle needle from its nozzle blocking the closing position with correspondingly small forces can be to inject fuel into the respective combustion chamber.
  • the opening stroke of the nozzle needle can then be effected with weak and only a small volume requiring actuators. Due to the pressure equalization effected with appropriate switching of the pressure compensation valve, the opening stroke of the valve needle is thus "prepared".
  • the opening stroke or the termination of the open position of the nozzle needle is effected by appropriate control of the actuator.
  • the additional space the pressure of which is controlled by means of the pressure compensation valve, arranged on the input side of the nozzle and in the closed position located nozzle needle or the like via a remaining between the nozzle needle and inlet side of the nozzle throttle gap is vented into the combustion chamber ,
  • the fact is exploited that between the injectors a comparatively large cross-section of the nozzle needle can be acted upon opening of the pressure compensation valve with high fuel pressure.
  • the pressure relief valve ensures that a discharge of very small amounts of fuel through the throttle gap and the nozzles in the combustion chamber is sufficient to relieve the additional space from the pressure.
  • the nozzle needle can be configured as a hollow needle with an axial bore communicating with the high-pressure source (common rail) and the pressure compensation valve can be arranged at the nozzle-near end of the axial bore, wherein the valve body of the pressure-compensating valve then expediently controls an outlet which continues the axial bore, which opens into the additional space arranged between the nozzles.
  • the high-pressure source common rail
  • the pressure compensation valve can be arranged at the nozzle-near end of the axial bore, wherein the valve body of the pressure-compensating valve then expediently controls an outlet which continues the axial bore, which opens into the additional space arranged between the nozzles.
  • an electromagnet arrangement is preferably provided which cooperates magnetically with an armature arrangement associated with the nozzle needle and with an armature arrangement assigned to the valve body of the pressure compensation valve.
  • the armature arrangements of the nozzle needle and the pressure compensating valve can be combined with separate electromagnet arrangements, with the possibility in principle of energizing the electromagnet arrangements independently of one another electrically. This increases the flexibility of the injection system. In addition, if necessary, small amounts can be injected in special injection phases by opening only the pressure compensation valve.
  • the electromagnet arrangements can be arranged electrically in series.
  • the injector has an injector body 1, the interior of which is constantly connected to a high-pressure source (common rail) for fuel.
  • the injector body 1 continues downward into a nozzle body 2, the interior of which communicates with the interior of the injector body 1.
  • the nozzle body 2 has substantially the shape of a tube whose free end is formed by a nozzle tip 3 provided with a cone. These nozzles open into a combustion chamber, not shown, of an internal combustion engine.
  • a nozzle needle 4 which is designed here as a hollow needle and similar to the nozzle body has the shape of a tube whose lower end in the drawing is formed by a conical tip.
  • the seat 5 is arranged radially outside the entrance sides of the nozzles 3. Accordingly, the input sides of the nozzles 3 are shut off from the annular space between the outside of the nozzle needle 4 and the inner periphery of the nozzle body 2 when the nozzle needle 4 is seated on the seat 5.
  • the seat 5 may also be formed as an annular bead, which cooperates sealingly with the apex of the nozzle needle 4.
  • This additional space 6 communicates with the interior of the nozzle needle 4 via a bore 7 which continues the axial bore of the nozzle needle 4 and is controlled by a small, spherical valve body 8 of a pressure compensation valve 7, 8 in the illustrated example.
  • the nozzle needle 4 controlling solenoid assembly 10 cooperates with a arranged at the opposite end of the nozzle needle 4 armature assembly 12, i. the armature assembly 12 is acted upon electrical energization of the solenoid assembly 10 with a force that seeks to lift the nozzle needle 4 from the seat 5.
  • valve body 8 is connected to its associated armature assembly 13 via a central bore of the solenoid assembly 10 passing through rod 14, which is formed by a trained example as a helical compression spring closing spring 15 which is clamped between a flange on the rod 14 and an abutment surface on the solenoid assembly 10, after is biased downward, such that the valve body 8 is brought into the closed position on the associated seat on the bore 7.
  • rod 14 is formed by a trained example as a helical compression spring closing spring 15 which is clamped between a flange on the rod 14 and an abutment surface on the solenoid assembly 10, after is biased downward, such that the valve body 8 is brought into the closed position on the associated seat on the bore 7.
  • the injector shown Fig. 1 works as follows:
  • the electromagnet assemblies 10 and 11 are electrically connected in series and can accordingly be energized together by means of an electrical voltage source 16 when a switch 17 is closed.
  • this switch should be open according to picture A, ie the solenoid assemblies 10 and 11 are without electric current, and the nozzle needle 4 and the valve body 8 of the pressure compensating valve 7, 8 are actuated by the hydraulic pressure in the injector body 1 and in the nozzle body 2, respectively crowded.
  • the additional space 6 is in the combustion chamber connected to the nozzle outlet vented, according to Fig. 2 between the outside of the cone of the nozzle needle 4 and the annular bulge-shaped input side of the nozzle 3, a narrow throttle gap 18 remains open.
  • the electromagnet assemblies 10 and 11 are electrically energized by closing the switch 17. Due to its small cross section, the valve body 8 of the pressure compensating valve 7,8 can be immediately lifted out of its seat by the magnetic forces acting between the electromagnet assembly 11 and the armature assembly 13. Thus, the additional space 6 is charged via the bore 7 at high pressure, such that the forces acting between the armature assembly 12 and the solenoid assembly 10 magnetic forces in conjunction with the hydraulic pressure forces in the additional space 6 sufficient to lift the nozzle needle 4 from its seat 5. This condition is shown in Figure C. Thus, the input side of the nozzles 3 communicates with the interior of the injector body 1 via the interior of the nozzle body 2, and fuel is injected via the nozzles 3 into the connected combustion chamber.
  • the remaining in the closed position of the nozzle needle 4 throttle gap 18 at the input side of the nozzle 3 has, as shown above, on the one hand the function that the additional space 6 can vent with closed pressure compensation valve 9 in the combustion chamber. Furthermore, this throttle gap 18 at the opening pressure compensation valve 7.8 the effect that in the additional space 6 can follow a rapid increase in pressure, because initially due to the throttling effect of the throttle gap 18, only a small proportion of the flowing through the bore 7 and high pressure fuel on the Nozzles 3 flows out. As a result, therefore, a fast opening of the nozzle needle 4 at the beginning of the injection phase is achieved by a very narrow throttle gap 18.
  • the armature assemblies 12 and 13 according to Fig. 3 be actuated by a single solenoid assembly 19.
  • the armature assemblies 12 and 13 according to Fig. 3 arranged coaxially with each other.
  • the closing spring 15 of the pressure compensating valve 7, 8 above the solenoid assembly 19 between a bottom of the injector body 1 and a flange on the rod 14, which passes through a central bore of the solenoid assembly 19, be clamped.
  • the armature assembly 13 of the pressure compensation valve 7.8 in the upper end position (open position) of the nozzle needle 4 and the associated armature assembly 12 has a sufficient axial mobility to open the pressure compensation valve 7.8 or close.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP09100059A 2008-03-17 2009-01-22 Injecteur Not-in-force EP2103802B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008000702A DE102008000702A1 (de) 2008-03-17 2008-03-17 Injektor

Publications (2)

Publication Number Publication Date
EP2103802A1 true EP2103802A1 (fr) 2009-09-23
EP2103802B1 EP2103802B1 (fr) 2011-01-19

Family

ID=40822395

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09100059A Not-in-force EP2103802B1 (fr) 2008-03-17 2009-01-22 Injecteur

Country Status (4)

Country Link
EP (1) EP2103802B1 (fr)
AT (1) ATE496216T1 (fr)
DE (2) DE102008000702A1 (fr)
ES (1) ES2358869T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3111078B1 (fr) * 2014-02-28 2020-04-22 Robert Bosch GmbH Injecteur de fluide

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008042227A1 (de) 2008-09-19 2010-04-01 Robert Bosch Gmbh Kraftstoff-Injektor
DE102010030037A1 (de) 2010-06-14 2011-12-15 Robert Bosch Gmbh Einspritzventil
DE102010030385A1 (de) 2010-06-23 2011-12-29 Robert Bosch Gmbh Einspritzventil
DE102018219311A1 (de) 2018-11-13 2020-05-14 Robert Bosch Gmbh Injektor mit Hohlnadel

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2150978A (en) * 1983-12-07 1985-07-10 Pierburg Gmbh & Co Kg Electromagnetic fuel injection valve
WO1999030029A1 (fr) 1997-12-05 1999-06-17 L'orange Gmbh Injecteur pour injection de carburant intermittente
EP1612401A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Società Consortile per Azioni Système d'injection de carburant pour moteur à combustion interne
EP1925812A1 (fr) * 2006-11-27 2008-05-28 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs à combustion interne

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2150978A (en) * 1983-12-07 1985-07-10 Pierburg Gmbh & Co Kg Electromagnetic fuel injection valve
WO1999030029A1 (fr) 1997-12-05 1999-06-17 L'orange Gmbh Injecteur pour injection de carburant intermittente
EP1612401A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Società Consortile per Azioni Système d'injection de carburant pour moteur à combustion interne
EP1925812A1 (fr) * 2006-11-27 2008-05-28 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs à combustion interne

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3111078B1 (fr) * 2014-02-28 2020-04-22 Robert Bosch GmbH Injecteur de fluide

Also Published As

Publication number Publication date
DE102008000702A1 (de) 2009-09-24
ATE496216T1 (de) 2011-02-15
DE502009000293D1 (de) 2011-03-03
ES2358869T3 (es) 2011-05-16
EP2103802B1 (fr) 2011-01-19

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