EP1601868A1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant

Info

Publication number
EP1601868A1
EP1601868A1 EP04711299A EP04711299A EP1601868A1 EP 1601868 A1 EP1601868 A1 EP 1601868A1 EP 04711299 A EP04711299 A EP 04711299A EP 04711299 A EP04711299 A EP 04711299A EP 1601868 A1 EP1601868 A1 EP 1601868A1
Authority
EP
European Patent Office
Prior art keywords
injection valve
fuel injection
valve according
section
slave
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
EP04711299A
Other languages
German (de)
English (en)
Other versions
EP1601868B1 (fr
Inventor
Werner Kammerer
Klaus Noller
Michael Huebel
Thomas Gerschwitz
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 EP1601868A1 publication Critical patent/EP1601868A1/fr
Application granted granted Critical
Publication of EP1601868B1 publication Critical patent/EP1601868B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

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
    • F02M51/0603—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

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • a slave piston is guided in the master cylinder, which also closes the master cylinder and thereby forms the hydraulic chamber.
  • a spring is arranged in the hydraulic chamber, which presses the master cylinder and the slave piston apart.
  • this stroke movement is caused by the pressure of a hydraulic fluid in the hydraulic chamber Transfer slave piston, since the hydraulic fluid in the hydraulic chamber can not be compressed and only a small proportion of the hydraulic fluid can escape through the annular gap during the short period of a stroke.
  • the spring pushes the slave piston out of the cylinder and the resulting negative pressure causes the hydraulic fluid to enter the hydraulic space through the annular gap and refill it.
  • the hydraulic coupler automatically adjusts to the linear expansion and pressure-related expansion of a fuel injector.
  • the hydraulic medium is sealed using sealing rings.
  • Fuel injection valves are also known from the prior art, which seal the hydraulic medium with corrugated-tube or bellows-shaped seals.
  • a disadvantage of this known prior art is that the restoring force is applied solely by the spring. Changes in the behavior of the spring, for example due to aging, have a greater impact on the restoring force and thus on the behavior of the coupler. The size of the spring is also increased.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that the coupler is simple and inexpensive to manufacture, less expensive to build, reliable durability and its behavior is less dependent on the operating time.
  • the compensation space is connected to the throttle via a transverse bore and / or the compression spring is of spiral design. This makes the coupler particularly easy to set up. 5
  • the coupler can be constructed in a particularly compact, simple and inexpensive manner.
  • the throttle comprises a throttle ball which is guided in an opening with a throttle gap.
  • the perforated disk and sleeve-shaped design by the axial section and the radial section permits compact and simple fastening of the flexible section.
  • a simple, secure and, in particular, hermetically sealed fastening of the flexible section is also advantageous
  • the ends of the flexible section are turned inwards, whereby they are one Form trough.
  • the ends advantageously engage hermetically in the recesses.
  • the internal pressure of the compensation chamber can thus be used advantageously to press the ends of the flexible section in a hydraulically sealing manner against the recesses by means of a pressure transmission via the hydraulic medium and thus to seal them reliably and permanently.
  • FIG. 1 shows a schematic section through a fuel injection valve according to the prior art
  • FIG. 2 shows a schematic section of a fuel injection valve in the area of the coupler according to the prior art, similar to the fuel injection valve shown in FIG. 1,
  • Fig. 3 shows an embodiment of a fuel injector according to the invention in the area of the coupler
  • Fig. 4 is a ⁇ further embodiment of a fuel injector according to the invention in the region of the flexible portion of the coupler.
  • the fuel injector 1 shown in FIG. 1 is in the form of a fuel injector 1 for fuel injection systems of mixture-compressing, spark-ignited internal combustion engines.
  • the fuel injection valve 1 is particularly suitable for injecting fuel directly into a combustion chamber (not shown) of an internal combustion engine.
  • the fuel injector 1 comprises a housing 2, in which a piezoelectric or magnetos ' trictive actuator 4 provided with an actuator coating 3 is arranged. An electrical voltage can be supplied to the actuator 4 by means of an electrical line 5, on which an electrical connection 6 protruding from the housing 2 can be formed.
  • the actuator 4 is supported on the upstream side on a master piston 9 of a hydraulic coupler 7 and on the downstream side on an actuator head 8.
  • the hydraulic coupler 7 further comprises a slave piston 10, a compression spring 11 which acts on the hydraulic coupler 7 with a ' preload, and an equalizing chamber 12 which is filled with a hydraulic medium.
  • the fuel is fed centrally via an inlet 14.
  • An actuating body 15, which acts on a valve needle 16 is arranged on the downstream side of the actuator head 8.
  • the valve needle 16 has a valve closing body 17 at its downstream end. This cooperates with a valve seat surface 18, which is formed on a nozzle body 19, to form a sealing seat.
  • a return spring 20 acts on the valve needle 16 so that the fuel injector 1 in the de-energized state of the Actuator 4 remains in the closed state. It also provides for the resetting of the valve needle 16 after the injection phase.
  • the nozzle body 19 is fixed by means of a weld seam 21 in an inner housing 22 which seals the actuator 4 against the fuel.
  • the fuel flows; from the inlet 14 between the housing 2 and the inner housing 22 to the sealing seat.
  • FIG. 2 shows a coupler 7 constructed similarly to the coupler shown in FIG. 1.
  • Hydraulic couplers 7 in fuel injection valves 1 are usually designed on the one hand to convert or translate the stroke of the actuator 4 to the valve needle 16 and / or on the other hand to compensate for temperature-related changes in length of the actuator 4 and the housing 2.
  • the latter as shown in the exemplary embodiment, is realized by means of the coupler 7 designed as a second medium coupler, which contains a hydraulic medium that does not come into contact with the fuel.
  • the hydraulic medium fills the compensation chamber 12 and a coupler volume 23 formed between the master piston 9 and the slave piston 10, which is connected to the compensation chamber 12 via a throttle 24.
  • the compensation chamber 12 is arranged inside and outside of the slave piston 10, the two parts being connected to one another by a transverse bore 31 and the outside part of the compensation chamber 12 being sealed against the fuel flowing through the fuel injection valve 1 by means of a flexible section 13 designed as a corrugated pipe seal.
  • the coupler 7, for example during manufacture, is filled with hydraulic medium through a channel 29, which can be closed, for example, by means of a pressed-in locking ball 30.
  • FIG. 3 shows an exemplary embodiment of a coupler 7 for a fuel injection valve 1 designed according to the invention.
  • the slave piston 10 engages with a cup-shaped first slave section 34 into the hollow-cylindrical master piston 9, which is closed on one side.
  • the slave piston 10 or the first slave section 34 is guided in the master piston 9 so as to be axially movable with a guide gap 38.
  • the guide gap 38 is relatively small, the amount of hydraulic medium flowing through the guide gap 38 being very small. In other exemplary embodiments, the guide gap 38 can perform a throttling function.
  • the slave piston 10 consists of the first slave section 34, a second slave section 35 and a connecting section 33.
  • the first slave section 34 with its closed end together with the base of the master piston 9, delimits the coupler volume 23, the closed end of the first slave section 34 centered the throttle 24 is arranged.
  • the throttle 24 consists of an opening 36 centered in the bottom of the cup-shaped first slave section 24 and a throttle ball 39 guided therein with a throttle gap 37.
  • the open end of the first slave section 34 facing away from the coupler volume 23 is closed by the connecting section 33.
  • the connecting section 33 partially engages in the first slave section 34 and is for example by pressing or welding with it joined motionless.
  • the compression spring 11 is arranged with a prestress in a spring chamber 45 arranged in the first slave section 34.
  • the compression spring 11 is spiral-shaped and presses on the throttle ball 39 under the interposition of a spring plate 40, the throttle ball 39 being supported on the bottom of the master piston 9 in the coupler volume 23.
  • the upper ends of the first slave section 34 and the master piston 9 facing away from the coupler volume 23 lie approximately at the same height, the connecting section 33 with a flange 44 resting on the upper end of the first slave section 34 and partially protruding from the first slave section 34.
  • the flange 44 has approximately the diameter of the first slave section 34.
  • the compensation chamber 12 is delimited by the flexible section 13, the connecting section 33 or the flange 44, the master piston 9 and the first slave section 34, the compensation chamber 12 being connected to the throttle 24 via the transverse bore 31 and the spring chamber 45.
  • the flexible section 13 is elastic and consists, for example, of an elastomer or of steel.
  • the flexible section 13 is divided into an axial section 46 that extends axially to the direction of movement of the slave piston 10 and a radial section 47 that extends radially to the direction of movement of the slave piston 10.
  • the plate-shaped and sleeve-shaped flexible section 13 is thickened at its ends.
  • the flexible section 13 lies with the end formed on the radial section 47 in a second recess 43, which is formed on the side of the flange 44 facing away from the coupler volume 23, and with its end formed on the axial section 46 in a first recess 42, which in the region of the upper end of the 'Master piston 9 is arranged on its outer surface.
  • the recesses 42, 43 are trough-shaped.
  • the thickened end formed on the radial section 47 is hermetically pressed and fixed in the second recess 43 by the second slave section 35, which rests on the top of the connecting section 33 and partially engages in it.
  • the end of the flexible section 13 formed on the axial section 46 is pressed hermetically sealingly into the first recess 42 by a sleeve 41 which partially surrounds the master piston 9 and is thereby fixed.
  • the sleeve comprises the axial section 46 and the transition to the radial section 47 with a precise fit, the sleeve 41 thus serving as a limitation of expansion.
  • the sleeve continues to taper upwards and in this case comprises the second slave section 35 at least partially radially and with an accurate fit with little play.
  • the compression spring 11 can also be arranged outside the spring chamber 45.
  • the dynamic rigidity of the coupler 7 is determined in particular by the size and shape of the throttle gap 37 and, if appropriate, by the size and shape of the guide gap 38.
  • FIG. 4 shows a further exemplary embodiment of a fuel injection valve 1 according to the invention in the region of the flexible section 13 of the coupler 7, similar to the exemplary embodiment from FIG. 3.
  • both ends of the flexible section 13 are turned inwards, so that troughs 48 form on the sides of the ends of the flexible section 13 facing the compensation space.
  • the ends of the ends lie hermetically in the recesses 42, 43.
  • the shape of the troughs 48 can be semicircular, triangular, oval or polygonal, for example.
  • the invention is not limited to the exemplary embodiments shown and is suitable for any designs of fuel injection valves 1, in particular also for fuel injection valves 1 for self-igniting internal combustion engines and / or fuel injectors opening inwards. All of the described features can be combined with one another as desired.

Landscapes

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

Abstract

L'invention concerne une soupape d'injection de carburant comprenant un actionneur piézo-électrique ou magnétostrictif (4) qui actionne un obturateur de soupape (17), lequel coopère avec une surface siège de soupape (18) pour former un siège hermétique. Un coupleur hydraulique (7) comprend un piston émetteur (9), un piston récepteur (10) et, entre les deux, un volume de couplage (23). Ce volume de couplage (23) est relié par un dispositif d'étranglement (24) à un compartiment de compensation (12). Une section flexible élastique (13) limite au moins partiellement le compartiment de compensation (12) et le volume de couplage (23), le dispositif d'étranglement (24) et le compartiment de compensation (12) étant remplis d'un agent hydraulique. La section flexible (13) exerce sur l'agent hydraulique une pression par une précontrainte. La force d'un ressort de pression (11) exercée sur le piston récepteur (10) et le piston émetteur (9) directement et/ou par l'intermédiaire de composants solides (40, 39) est dirigée par une précontrainte de telle façon qu'elle augmente le volume de coupleur (23).
EP04711299A 2003-02-27 2004-02-14 Soupape d'injection de carburant Expired - Fee Related EP1601868B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10308635 2003-02-27
DE10308635 2003-02-27
PCT/DE2004/000280 WO2004076845A1 (fr) 2003-02-27 2004-02-14 Soupape d'injection de carburant

Publications (2)

Publication Number Publication Date
EP1601868A1 true EP1601868A1 (fr) 2005-12-07
EP1601868B1 EP1601868B1 (fr) 2007-04-04

Family

ID=32841991

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04711299A Expired - Fee Related EP1601868B1 (fr) 2003-02-27 2004-02-14 Soupape d'injection de carburant

Country Status (4)

Country Link
EP (1) EP1601868B1 (fr)
JP (1) JP4072172B2 (fr)
DE (4) DE10360449A1 (fr)
WO (1) WO2004076845A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10310790A1 (de) * 2003-03-12 2004-09-23 Robert Bosch Gmbh Brennstoffeinspritzventil
US7726625B2 (en) 2003-12-05 2010-06-01 Continental Automotive Gmbh Device, method for producing the device, chamber device and transfer device
DE10357189A1 (de) * 2003-12-08 2005-07-07 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102004021920A1 (de) 2004-05-04 2005-12-01 Robert Bosch Gmbh Brennstoffeinspritzventil
CN1830495B (zh) * 2005-03-11 2010-12-15 广东天普生化医药股份有限公司 基于亲和吸附的血液净化方法及系统
DE102005025953A1 (de) 2005-06-06 2006-12-07 Siemens Ag Einspritzventil und Ausgleichselement für ein Einspritzventil
FI121719B (fi) * 2009-05-28 2011-03-15 Waertsilae Finland Oy Polttoaineen ruiskutusventtiili
DE102015219912B3 (de) * 2015-10-14 2017-04-06 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoffeinspritzung

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2829154A1 (de) * 1978-07-03 1980-01-17 Bbc Brown Boveri & Cie Einrichtung zur temperaturmessung an insbesondere elektrischen maschinen, bauelementen o.dgl.
DE3742241A1 (de) * 1987-02-14 1988-08-25 Daimler Benz Ag Piezosteuerventil zur steuerung der kraftstoffeinspritzung ueber ein einspritzventil bei brennkraftmaschinen
JPH0656162B2 (ja) * 1987-03-03 1994-07-27 トヨタ自動車株式会社 ストロ−ク可変装置
DE59010904D1 (de) * 1990-09-25 2000-05-31 Siemens Ag Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für den Wegtransformator eines piezoelektrischen Aktors
DE19708304C2 (de) * 1997-02-28 1999-09-30 Siemens Ag Vorrichtung zur Übertragung einer Bewegung und Einspritzventil mit einer Vorrichtung zur Übertragung einer Bewegung
DE19856185A1 (de) * 1998-12-05 2000-06-15 Bosch Gmbh Robert Piezoelektrischer Antrieb
DE19912666A1 (de) * 1999-03-20 2000-09-21 Bosch Gmbh Robert Brennstoffeinspritzentil
DE19950760A1 (de) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10046323B4 (de) * 2000-09-19 2004-02-12 Siemens Ag Hydraulisches Spielausgleichssystem
DE10048430A1 (de) * 2000-09-29 2002-04-25 Bosch Gmbh Robert Piezoelektrischer Aktor
DE10148594A1 (de) * 2001-10-02 2003-04-10 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10162045B4 (de) * 2001-12-17 2005-06-23 Siemens Ag Vorrichtung zum Übersetzen einer Auslenkung eines Aktors, insbesondere für ein Einspritzventil
DE10230089A1 (de) * 2002-07-04 2004-01-15 Robert Bosch Gmbh Brennstoffeinspritzventil

Non-Patent Citations (1)

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Title
See references of WO2004076845A1 *

Also Published As

Publication number Publication date
DE502004003400D1 (de) 2007-05-16
EP1601868B1 (fr) 2007-04-04
DE10360451A1 (de) 2004-09-09
WO2004076845A1 (fr) 2004-09-10
DE10360450A1 (de) 2004-09-09
DE10360451B4 (de) 2014-01-09
JP4072172B2 (ja) 2008-04-09
JP2006512536A (ja) 2006-04-13
DE10360449A1 (de) 2004-09-09

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