WO2001057383A2 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant Download PDF

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Publication number
WO2001057383A2
WO2001057383A2 PCT/DE2001/000146 DE0100146W WO0157383A2 WO 2001057383 A2 WO2001057383 A2 WO 2001057383A2 DE 0100146 W DE0100146 W DE 0100146W WO 0157383 A2 WO0157383 A2 WO 0157383A2
Authority
WO
WIPO (PCT)
Prior art keywords
fuel injection
injection valve
switching position
fuel
valve
Prior art date
Application number
PCT/DE2001/000146
Other languages
German (de)
English (en)
Other versions
WO2001057383A3 (fr
Inventor
Martin Maier
Guenther Hohl
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 WO2001057383A2 publication Critical patent/WO2001057383A2/fr
Publication of WO2001057383A3 publication Critical patent/WO2001057383A3/fr

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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
    • 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
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/083—Having two or more closing springs acting on injection-valve
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • a disadvantage of the fuel injector known from DE 196 26 576 AI is that small injection quantities can only be implemented with great effort by the electronic control unit due to the fixed, relatively large opening cross section. Due to the short injection time and the steep switching edges, small injection quantities require high electrical actuation power.
  • the fuel injector according to the invention with the features of the main claim has the advantage that small metering quantities and short metering times can be achieved through the two-stage opening stroke with two switch positions that allow different volume flows through the fuel injector.
  • the lower switch position can be reached, at higher speeds and higher fuel consumption the upper switch position.
  • the fuel injector is only up to the first switch position, i.e. H. up to a partial valve stroke. This results in longer metering times compared to the second switching position with a full valve stroke, which places lower demands on the electrical control. This leads to low costs and low thermal stress on the electrical components.
  • the opening process is favored by a lower spring force of the first return spring, which enables lower actuation powers, while an additional acceleration force is available in the closing process from the second switching position by a second return spring in order to quickly close the fuel injector.
  • the spring constant of the first return spring is dimensioned such that the spring force exerted is still sufficient to seal the fuel injector against the pressure in the combustion chamber of the internal combustion engine.
  • Both switch positions can be controlled via the same circuit and therefore do not require the complex installation of a second circuit, since this is achieved the switch positions only require a differently high excitation current.
  • the second return spring is actuated in the opening movement up to the second switching position only after passing through the partial stroke in a relatively small remaining stroke.
  • a stop body biased by the second return spring serves as a stop if only the partial stroke is to be run through and a small metering quantity is to be achieved.
  • FIG. 1 is a sectional view of an embodiment of a fuel injector according to the invention
  • FIG. 2A shows a diagram of the course of the excitation current as a function of time for the exemplary embodiment of the fuel injector according to the invention shown in FIG. 1,
  • FIG. 2B shows a diagram of the course of the stroke as a function of time for the exemplary embodiment of the fuel injector according to the invention shown in FIG. 1
  • 2C shows a diagram of the course of the volume flow through the fuel injection valve as a function of the stroke for the exemplary embodiment of the invention shown in FIG. 1
  • the fuel injection valve 1 shows an axial sectional view of the area of a fuel injection valve 1 on the injection side.
  • the fuel injection valve 1 is used, for. B. for the direct injection of fuel into a combustion chamber, not shown, of a spark-ignition, mixture-compressing internal combustion engine and is designed as an inwardly opening fuel injector 1.
  • the fuel injector 1 comprises a magnet coil 2, which is surrounded by a magnetic reflux body 3, as well as a core 4 and a nozzle body 5, which are surrounded by a valve housing 6.
  • An armature 7 is arranged between the core 4 and the nozzle body 5 and is acted upon by a first return spring 8. The end of the first return spring 8 rests on a support sleeve 9 which prestresses the first return spring 8.
  • the armature 7 is in a non-positive and positive connection with a valve needle 10, at the spray-side end of which a valve closing body 11 is formed.
  • the valve closing body 11 forms a sealing seat with a valve seat surface 12. At least one spray opening 14 is formed in a valve seat body 13.
  • the fuel is supplied centrally and led to the sealing seat via fuel channels 15a, 15b, 15c.
  • a tubular valve needle stop 16 is connected to the valve needle 10.
  • the stop body 18 is acted upon by a second return spring 19 which is preloaded by a spring adjusting ring 20 which is also attached to the inner wall of the nozzle body 5.
  • a total stroke h tot corresponds to the size of a first working gap 21 which is formed between the armature 7 and the core 4.
  • a partial stroke h e ii corresponds to the size of a second working gap 22 which is formed between the valve needle stop 16 and the stop body 18.
  • the first working gap 21 is larger than the second working gap 22.
  • a residual stroke h res t corresponding to the difference h ges -h te ii.
  • the magnetic coil 2 If the magnetic coil 2 is supplied with an electrical excitation current, a magnetic field is built up which accelerates the armature 7 in the direction of the core 4.
  • the armature 7 takes the valve needle 10 connected to it. While the armature 7 and the valve needle 10 pass through the partial stroke h te j_ ⁇ , the magnetic field strength only has to overcome the spring force of the weakly dimensioned first return spring 8 so that the armature 7 can be accelerated in the direction of the core 4.
  • the spring constant of the first return spring 8 is dimensioned such that the spring force is certainly sufficient to seal the fuel injection valve 1 against the combustion chamber (not shown) of the internal combustion engine.
  • the valve needle stop 16 strikes the stop body 18 acted upon by the second return spring 19.
  • the fuel injection valve 1 is only partially opened by energizing it with a first holding current intensity I al t i ⁇ n ; Due to the small opening cross-section, a small amount of fuel can be metered. This is especially true with small ones Speeds of the internal combustion engine are desirable, since very small amounts are required here.
  • valve needle 10 remains in the first switching position reached, since the magnetic field is not further developed and the armature 7 and the valve needle 10 are not further accelerated.
  • a second switching position is activated.
  • the residual stroke h rest must also be covered against the spring forces of the first return spring 8 and the second return spring 19, which is due to a further increase in the excitation current beyond the first holding current strength I h a lt i, which opens the fuel injection valve 1 into the first switching position, happens.
  • the second return spring 19 is compressed by the remaining stroke h rest .
  • the second switching position is reached when the armature 7 strikes the core 4 and the first working gap 21 is closed. Since the opening cross-section is maximum in this switching position, a larger fuel can be metered more narrowly than in the first switching position with the same metering time.
  • 2A-2C show three diagrams to illustrate the two-stage switching of the fuel injection valve 1, in which the relationship between the excitation current I as a function of time t, the stroke h of the armature 7 as a function of time t and the volume flow Q as a function of the valve lift h are represented qualitatively.
  • h ges total stroke hteil partial stroke h rest remaining stroke h ges -h e ii t 0 the beginning of the switching cycle with the first drive t time after which the armature through 7 the partial stroke h te ü has 2 beginning of the second control phase t 3 time after which the armature 7 has passed through the remaining stroke h re ⁇
  • FIG. 2A shows the course of the excitation current I as a function of time t.
  • the excitation current I initially increases to a maximum value I ax, in order then to drop to a first holding current I h a ltl . This is high enough to hold the valve needle stop 16 on the stop body 18, but is not sufficient to move the armature 7 with the valve needle 10 further against the force of the second return spring 19 in the stroke direction.
  • the fuel injector 1 is thus in the first switch position and enables the metering of a small amount of fuel due to the small opening cross section.
  • FIG. 2C shows the volume flow Q of the fuel through the fuel injection valve 1 as a function of the stroke h.
  • the volume flow Q through the Fuel injection valve 1 continuously, since the opening cross section of which increases by the lift-off of the valve seat surface 12 of valve closure member 11 until, at the first switching position with the stroke h e ü a volume flow Q te i l is reached. If the armature 7 is further pulled towards the core 4 by a growing magnetic field against the total spring force of the first return spring 8 and the second return spring 19, the cross-section through which it flows and thus the volume flow Q continue to increase until a maximum value when the armature 7 strikes the core 4 Q max is reached. If the fuel injection valve 1 is held in the first or second switching position, a constant volume flow flows through the fuel injection valve 1 per unit of time.
  • a hydrodynamically optimized spray pattern is aimed for. Since the spray pattern of a fuel injector 1 is dependent on the stroke, the fuel injector 1 can generate different spray patterns in the two switching positions, which reduce the fuel z. B. inject at different angles into the combustion chamber.
  • the invention is not restricted to the exemplary embodiment shown and can also be implemented with a large number of other designs of fuel injection valves 1, in particular with fuel injection valves 1 opening outwards.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une soupape d'injection de carburant (1), notamment une soupape d'injection pour systèmes d'injection de carburant de moteurs à combustion interne. Cette soupape d'injection comprend une bobine d'excitation (2), un induit (7) sollicité en position de fermeture par un premier ressort de rappel (8) et un pointeau de soupape (10) communiquant par liaison de force avec l'induit (7) pour actionner un corps de fermeture de soupape (11) qui forme un siège d'étanchéité conjointement avec une surface de siège de soupape (12). La soupape d'injection de carburant (1) peut être placée dans une première position de commutation avec une première section transversale d'ouverture, en faisant circuler dans la bobine d'excitation (2) un courant de maintien d'une première intensité et dans une seconde position de commutation avec une seconde section transversale d'ouverture, en faisant circuler dans la bobine d'excitation (2) un courant de maintien d'une seconde intensité.
PCT/DE2001/000146 2000-02-04 2001-01-16 Soupape d'injection de carburant WO2001057383A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000105013 DE10005013A1 (de) 2000-02-04 2000-02-04 Brennstoffeinspritzventil
DE10005013.1 2000-02-04

Publications (2)

Publication Number Publication Date
WO2001057383A2 true WO2001057383A2 (fr) 2001-08-09
WO2001057383A3 WO2001057383A3 (fr) 2001-12-27

Family

ID=7629880

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2001/000146 WO2001057383A2 (fr) 2000-02-04 2001-01-16 Soupape d'injection de carburant

Country Status (2)

Country Link
DE (1) DE10005013A1 (fr)
WO (1) WO2001057383A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1258621A3 (fr) * 2001-05-19 2005-01-12 Volkswagen Aktiengesellschaft Méthode de contrôle d'une pompe à carburant commandée par une électrovanne dans un moteur à combustion interne

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016219782A1 (de) 2016-10-12 2018-04-12 Ford Global Technologies, Llc Variabel einstellbares Tellerventil

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19626576A1 (de) 1996-07-02 1998-01-08 Bosch Gmbh Robert Brennstoffeinspritzventil

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60108560A (ja) * 1983-11-16 1985-06-14 Toyota Central Res & Dev Lab Inc 燃料噴射制御法及び装置
US4987887A (en) * 1990-03-28 1991-01-29 Stanadyne Automotive Corp. Fuel injector method and apparatus
AT1622U1 (de) * 1995-02-28 1997-08-25 Avl Verbrennungskraft Messtech Einspritzsystem mit einem einspritzventil für eine selbstzündende brennkraftmaschine
EP0745764B1 (fr) * 1995-06-02 2001-03-21 Ganser-Hydromag Ag Soupape d'injection de combustible pour moteurs à combustion interne

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19626576A1 (de) 1996-07-02 1998-01-08 Bosch Gmbh Robert Brennstoffeinspritzventil

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1258621A3 (fr) * 2001-05-19 2005-01-12 Volkswagen Aktiengesellschaft Méthode de contrôle d'une pompe à carburant commandée par une électrovanne dans un moteur à combustion interne

Also Published As

Publication number Publication date
DE10005013A1 (de) 2001-08-09
WO2001057383A3 (fr) 2001-12-27

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