EP1407136B1 - Brennstoffeinspritzventil - Google Patents

Brennstoffeinspritzventil Download PDF

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Publication number
EP1407136B1
EP1407136B1 EP02745049A EP02745049A EP1407136B1 EP 1407136 B1 EP1407136 B1 EP 1407136B1 EP 02745049 A EP02745049 A EP 02745049A EP 02745049 A EP02745049 A EP 02745049A EP 1407136 B1 EP1407136 B1 EP 1407136B1
Authority
EP
European Patent Office
Prior art keywords
pressure
coupler
fuel injection
valve
pressure cylinder
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.)
Expired - Lifetime
Application number
EP02745049A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1407136A1 (de
Inventor
Günther HOHL
Michael HÜBEL
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 EP1407136A1 publication Critical patent/EP1407136A1/de
Application granted granted Critical
Publication of EP1407136B1 publication Critical patent/EP1407136B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • 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
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • US 6 142 443 A discloses a hydraulically fixed coupler with a movable piston with an internal inlet bore.
  • a displacement transformer for a piezoelectric actuator in which the actuator transmits a lifting force to a master cylinder, which is closed by a cylinder carrier.
  • a slave piston In this master cylinder, a slave piston is guided, which also closes the master cylinder and thereby forms the hydraulic chamber.
  • a spring In the hydraulic chamber, a spring is arranged, the master cylinder and the slave piston pushes apart.
  • the slave piston mechanically transfers a lifting movement to, for example, a valve needle.
  • DE 195 19 191 A1 discloses a hydraulic travel translating movable coupler having a bore in the pressure cylinder carrier which connects the pressure space in the coupler to the low pressure return of the injector.
  • a disadvantage of this known prior art is that the hydraulic chamber can be filled only slowly. Especially during the cold start with low pressure occur long injection times, so that more hydraulic fluid escapes through the annular gap and then must be replenished in a shorter time at low pressure again. If this does not happen, the injector will lose lift per injection until it completely loses its function.
  • a further disadvantage is that the hydraulic fluid can evaporate if there is no sufficiently high pressure in the hydraulic chamber.
  • a gas is compressible and only builds up a correspondingly high pressure after a strong reduction in volume.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the moving coupler valve seat body lifts off from the Kopplerventilsitz when the moving coupler does not take the possible length as a transmission element between the actuator and the valve needle and thus for the fuel an inflow over the Zulaufbohrung to the pressure chamber releases. Since the cross-sectional area occupied by the Kopplerventlditzitz is smaller than the Quremales Stimbalsky, both the Kopplerfederelement as well as the increased pressure when operating in the coupler space closing on the Kopplerventildichtsitz.
  • the Kopplerventildsitzitz is released when resetting the actuator.
  • the coupler space is filled quickly until it reaches its original position again and closes the Kopplungerveldilditz.
  • the fuel injection valve according to the invention that are automatically compensated by changes in temperature and by changes in the pressure of the fuel expansions of the fuel injection valve on the transmission path between the actuator and valve needle.
  • the stroke of the valve needle can always be the same size.
  • the Kopplerventilsch manyharmonics can be formed as a spherical surface and the corresponding Kopplerventilsitz requirements on the valve needle as a conical surface.
  • the inlet bore are formed in the pressure cylinder carrier and the Coupling valve closing body integrally formed with the pressure cylinder carrier and the pressure cylinder.
  • the Kopplerventilsitz preparation is formed on the valve needle and the pressure piston connected to a guide piston, which is guided in a bore in a cutting disc, which separates the fuel inlet from an actuator chamber. It is also favorable to provide a corrugated tube for sealing this actuator chamber on the guide piston.
  • the stroke of the valve needle can be limited by a stop of an actuator head or alternatively by a stop of the valve needle or alternatively by a stop of the pressure piston or the pressure cylinder.
  • an always the same and defined stroke of the valve needle can be achieved, regardless of expansion and expansion of a valve body of the fuel injection valve when the stroke limited by the stop is always smaller than the minimum stroke of the actuator under all operating conditions.
  • FIG. 1 schematically illustrated fuel injector 1 has a valve needle 2, which is connected to a valve closing body 3 and cooperates via this valve closing body 3 with a formed in a valve body 4 valve seat surface 5 to a valve sealing seat.
  • the fuel injection valve 1 is an outwardly opening fuel injection valve, which has an outwardly opening valve needle 2.
  • the valve needle 2 is guided by a guide section 7, which has a spring system 8 for a valve closing spring 9, in a valve needle guide 10.
  • the valve closing spring 9 is supported against a second spring system 11 on the valve body 4 and biases the valve needle 2 with a force that presses the valve closing body 3 against the valve seat surface 5.
  • a groove 12 arranged in a sealing ring 13 a seal of the annular gap, not shown here between the valve body 4 and a bore, also not shown in a cylinder head of an internal combustion engine.
  • a piezoelectric or magnetostrictive actuator 14 is arranged in a valve body upper part 17, which can be supplied via a bore 15 in the valve body upper part 17 and an electrical supply line 16 with a voltage.
  • the actuator 14 has a greater length to a noticeable stroke when applying a voltage to the actuator 14 to achieve.
  • the largest part of the length of the actuator 14 is in the Fig. 1 not shown.
  • an actuator head 18 connects, which has a spring contact surface 19 to which an actuator clamping spring 20 is applied, which in turn is supported against a cutting disc 21.
  • a bias voltage is applied to the actuator 14, so that upon application of a voltage to the electrical supply line 16, the stroke of the actuator 14 transmits to the actuator head 18.
  • a plunger 22 is formed integrally with the actuator head 18, which transmits the stroke of the actuator 14.
  • the actuator head 18 is guided through an actuator head sleeve 23 in the valve body upper part 17 and this actuator head sleeve 23 strikes after a maximum stroke h on the cutting disk 21 at. As a result, the maximum stroke h of the actuator 14 is limited.
  • the actuator head tappet 22 transmits the lifting movement of the actuator 14 to a pressure piston carrier 24 into which a blind hole 25 is centrally introduced.
  • the pressure piston carrier 24 is guided by a guide bore 27 which penetrates the carrier plate 21.
  • the support plate 21 is sealed by a sealing ring 26 opposite the valve body upper part 17.
  • a corrugated tube 28 concentrically surrounds the pressure piston carrier 24 and is fastened to the pressure piston carrier 24 with a weld seam 29.
  • the corrugated tube 28 is on the other hand fixed to the support plate 21 with a weld 30.
  • the pressure piston carrier 24 integrally acting as a master piston piston piston 33 is formed in a pressure cylinder 34 acting as a slave cylinder is guided.
  • the printing cylinder 34 is formed integrally with a printing cylinder carrier 35.
  • an inlet bore 36 is guided centrally.
  • Pressure piston 33, pressure cylinder 34 and pressure cylinder carrier 35 form the hydraulic coupler 35a.
  • the hydraulic coupler 35a Concentric about the pressure piston 33 and the Druckzlinder 34, the hydraulic coupler 35a has a Kopplerspiralfeder 38 between a spring stop 39 on the pressure cylinder carrier 35 and another spring stop 40 on the pressure piston carrier 24.
  • the inlet bore 36 is separated from the fuel chamber 32 by a Kopplerventilsch basicallyintelligence which is formed as a hemispherical surface on the pressure cylinder carrier 35, and with a Kopplerventilsitz composition 42 which is formed as a conical surface on the guide portion 7 of the valve needle 2, to a Kopplerventldichtsitz.
  • a Kopplerventildsitzitz results in a disc-shaped surface with the diameter d, which is not acted upon by the pressure of the fuel, which is located in the fuel chamber 32.
  • the actuator 14 expands in the longitudinal direction of the fuel injection valve 1 and pushes the actuator head 18 with the molded on this actuator ram 22 in the direction of the valve seat 6.
  • the stroke is by the stop the actuator head sleeve 23 is limited to the cutting disk 21 for a distance h.
  • the movement is transferred to the pressure piston carrier 24 and the pressure piston 33.
  • the fuel contained in the pressure chamber 37 is incompressible as a liquid and therefore transmits the movement further to the pressure cylinder carrier 35.
  • the spring force of the coupler coil spring 38 and the force of the actuator 14 is the Coupling valve closing body 41 on the Coupler valve seat surface 42 is pressed.
  • the Kopplerventildsitzitz 43 sealingly closes and it can escape fuel from the pressure chamber 37.
  • the valve needle 2 opens outwardly from the valve seat 6 lifting. From the pressure chamber 37, only a gap loss amount of fuel can escape through the annular gap between the pressure piston 33 and the pressure cylinder 34 during the stroke.
  • the actuator spring 20 Upon completion of the stroke of the actuator is pushed back by the actuator spring 20 and the valve needle 2 is pressed by the valve needle spring 9 in its valve seat 6. Due to the prestressed corrugated tube 28 of the pressure piston carrier 24 is held adjacent to the Aktorkopfstumbleel 22.
  • the coupler valve seat face 43 now opens because the diameter of the cross-sectional area facing the coupler valve seat face 43 is increased Fuel pressure in the fuel chamber 32 is completed, is smaller than the diameter of the pressure piston 33 and the spring force of the coupler coil spring 38 is overcome. From the fuel chamber 32, pressurized fuel can now pass past the coupler valve seat 43 through the inlet bore 36 into the pressure chamber 37.
  • the coupler coil spring 38 pulls the pressure piston 33 out of the pressure cylinder 34 until the coupler valve closing body 41 sits on the coupler valve seat surface 42 and the coupler valve seat 43 is again closed.
  • the fuel injection valve 1 according to the invention with the described transmission path of the lifting force of the actuator 14 to the valve needle 2 thus automatically adapts to the expansions of the valve body 4 and the valve body shell 17 at pressure fluctuations of the fuel pressure. Likewise, temperature-related expansions are compensated.
  • a failure of the fuel injection valve 1, z. B. can be prevented at a restart after an internal combustion engine has been turned off in the hot condition.
  • the fuel chamber 32 slowly loses fuel pressure. This can lead to evaporation of fuel in the pressure chamber 37.
  • the vaporized fuel in the pressure chamber 37 would be compressed as gas without building up the pressure necessary to open the valve needle 2.
  • the fuel in the fuel chamber 32 is first pressurized by an external pump, not shown here, and thus the coupler valve seat 43 is opened as described above in a fuel injection valve 1 according to the invention and fuel flows through the inlet bore 36 into the pressure chamber 37. As a result, a cooling and the evaporated fuel is condensed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP02745049A 2001-07-09 2002-05-07 Brennstoffeinspritzventil Expired - Lifetime EP1407136B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10133265 2001-07-09
DE10133265A DE10133265A1 (de) 2001-07-09 2001-07-09 Brennstoffeinspritzventil
PCT/DE2002/001640 WO2003006820A1 (de) 2001-07-09 2002-05-07 Brennstoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP1407136A1 EP1407136A1 (de) 2004-04-14
EP1407136B1 true EP1407136B1 (de) 2008-07-02

Family

ID=7691147

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02745049A Expired - Lifetime EP1407136B1 (de) 2001-07-09 2002-05-07 Brennstoffeinspritzventil

Country Status (6)

Country Link
US (1) US6883725B2 (ja)
EP (1) EP1407136B1 (ja)
JP (1) JP4116542B2 (ja)
KR (1) KR100853645B1 (ja)
DE (2) DE10133265A1 (ja)
WO (1) WO2003006820A1 (ja)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10310499A1 (de) * 2003-03-11 2004-09-23 Robert Bosch Gmbh Brennstoffeinspritzventil
DE10310788A1 (de) * 2003-03-12 2004-09-23 Robert Bosch Gmbh Brennstoffeinspritzventil und Verfahren zu dessen Montage
DE10310790A1 (de) 2003-03-12 2004-09-23 Robert Bosch Gmbh Brennstoffeinspritzventil
DE10341810B4 (de) 2003-09-10 2016-04-07 Robert Bosch Gmbh Brennstoffeinspritzventil und Verfahren zum Betrieb eines Brennstoffeinspritzventils
DE10344880A1 (de) * 2003-09-26 2005-04-14 Robert Bosch Gmbh Brennstoffeinspritzventil
DE10353639A1 (de) * 2003-11-17 2005-06-16 Robert Bosch Gmbh Brennstoffeinspritzventil
DE10353641B4 (de) * 2003-11-17 2016-12-01 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102004009460A1 (de) * 2004-02-27 2005-09-15 Robert Bosch Gmbh Ventil
DE102004010183A1 (de) * 2004-03-02 2005-09-29 Siemens Ag Einspritzventil
DE102005025952B4 (de) * 2005-06-06 2009-01-29 Continental Automotive Gmbh Verfahren zum Herstellen eines Ventils
US7665445B2 (en) * 2008-04-18 2010-02-23 Caterpillar Inc. Motion coupler for a piezoelectric actuator
DE102008042850A1 (de) * 2008-10-15 2010-04-22 Robert Bosch Gmbh Einspritzvorrichtung
US8201543B2 (en) * 2009-05-14 2012-06-19 Cummins Intellectual Properties, Inc. Piezoelectric direct acting fuel injector with hydraulic link
DE102013219225A1 (de) * 2013-09-25 2015-03-26 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoff-Direkteinspritzung
US10484598B2 (en) * 2015-08-20 2019-11-19 Sony Corporation System and method for controlling capture of images
DE102015219912B3 (de) * 2015-10-14 2017-04-06 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoffeinspritzung

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0477400B1 (de) * 1990-09-25 2000-04-26 Siemens Aktiengesellschaft Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für den Wegtransformator eines piezoelektrischen Aktors
DE19519191C2 (de) * 1995-05-24 1997-04-10 Siemens Ag Einspritzventil
DE19743640A1 (de) * 1997-10-02 1999-04-08 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19743669A1 (de) * 1997-10-02 1999-04-08 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19746143A1 (de) 1997-10-18 1999-04-22 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
GB9725804D0 (en) * 1997-12-06 1998-02-04 Lucas Ind Plc Fuel injector
DE19817320C1 (de) * 1998-04-18 1999-11-11 Daimler Chrysler Ag Einspritzventil für Kraftstoffeinspritzsysteme
DE19946732B4 (de) * 1999-09-29 2004-07-15 Siemens Ag Vorrichtung zum Übertragen einer Auslenkung eines Aktors auf ein Stellglied und Kraftstoffinjektor mit einer solchen Vorrichtung
DE19950760A1 (de) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19954802A1 (de) * 1999-11-13 2001-05-17 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19958704C2 (de) 1999-12-06 2002-10-02 Siemens Ag Vorrichtung zum Übertragen einer Aktorbewegung und Fluiddosierer mit einer solchen Vorrichtung
LU90684B1 (en) * 2000-11-28 2002-05-29 Delphi Tech Inc Fuel injector with piezoelectric actuator

Also Published As

Publication number Publication date
JP2004521271A (ja) 2004-07-15
DE10133265A1 (de) 2003-01-23
US6883725B2 (en) 2005-04-26
KR100853645B1 (ko) 2008-08-25
KR20030036762A (ko) 2003-05-09
EP1407136A1 (de) 2004-04-14
DE50212447D1 (de) 2008-08-14
JP4116542B2 (ja) 2008-07-09
US20040011892A1 (en) 2004-01-22
WO2003006820A1 (de) 2003-01-23

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