EP3074623A1 - Injecteur de carburant - Google Patents

Injecteur de carburant

Info

Publication number
EP3074623A1
EP3074623A1 EP14781567.4A EP14781567A EP3074623A1 EP 3074623 A1 EP3074623 A1 EP 3074623A1 EP 14781567 A EP14781567 A EP 14781567A EP 3074623 A1 EP3074623 A1 EP 3074623A1
Authority
EP
European Patent Office
Prior art keywords
fuel
fuel injector
injection
chamber
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
EP14781567.4A
Other languages
German (de)
English (en)
Other versions
EP3074623B1 (fr
Inventor
Florian Hoffmann
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 EP3074623A1 publication Critical patent/EP3074623A1/fr
Application granted granted Critical
Publication of EP3074623B1 publication Critical patent/EP3074623B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a fuel injector according to the preamble of
  • Such a fuel injector is known from DE 10 2006 049 830 A1
  • the injector has, within an injector housing, a control chamber in which the end of a nozzle needle opposite an injection opening is inserted.
  • the control chamber is formed via an inlet channel designed as an inflow bore with a
  • the control chamber is used in a known manner to the opening and closing movement of the
  • Nozzle needle is injected into the combustion chamber of the internal combustion engine depends inter alia on different fuel properties.
  • Fuel properties in turn depend on the type of fuel and the environmental conditions. For example, the viscosity of both the type of fuel (winter diesel, summer diesel, mixtures of various
  • the viscosity of the fuel is usually higher than when the engine is at operating temperature. This has the consequence that, without influencing the injection parameters during the cold start, too little fuel is usually injected into the combustion chamber. It is therefore necessary or desirable, during the warm-up phase of the engine or the internal combustion engine, the fuel quantity during an injection process of a relatively high value due to the low
  • inlet bore into the control chamber is shown as an elongated bore, in practice, however, within the diameter / length ratio of approximately 1: 2.5 having inlet bore to influence the flow rate, a flow constriction in the form of a diaphragm is formed. This diaphragm causes the fuel flowing out of the high-pressure chamber into the control chamber to continue to flow turbulently after passing through the diaphragm. From the
  • the present invention seeks to further develop a fuel injector according to the preamble of claim 1 such that during a Einspritztaktes a
  • Injector valve member in particular during the warm-up phase of the internal combustion engine, a target injection amount despite different Viscosities of the fuel at different temperatures in the
  • Combustion chamber of the internal combustion engine can be achieved with the least possible effort. In particular, it should be achieved that even at a relatively high viscosity, i. at a relatively low temperature of the fuel, the desired injection quantity is achieved.
  • Inflow channel via which a post-flow of fuel from the high-pressure chamber takes place in the control chamber of the fuel injector, is formed to form a laminar flow.
  • the invention is based on the finding that in the presence of a laminar flow the
  • Flow rate through the inflow channel is viscosity-dependent.
  • a flow which is reduced compared to a lower viscosity is made possible. This has the consequence that the pressure in the control chamber when opening the Abiaufbohrung falls faster or faster, since the inflowing over the inflow channel fuel with less
  • Flow rate (per unit time) flows through the inflow channel.
  • the at least one inflow channel at least two, preferably a constant diameter having first
  • throttle bores in the element wherein the diameter / length ratio of the at least two throttle bores is less than 1: 5, preferably about 1:10.
  • the diameter / length ratio should be about 1: 15.
  • control chamber is usually formed by an annular circumferential wall portion of a valve piece, or by a voltage applied to a throttle plate in the axial direction control chamber sleeve. Both the minimum wall thickness of the control chamber sleeve and the valve piece is given for pressure or strength reasons and is usually chosen as small as possible. Now to the desired
  • Control chamber sleeve to effect the desired throttle function and on the other hand, for example, in full load operation to take into account that enough fuel can flow into the control chamber, that is, the fuel! Njektor has a desired high dynamics.
  • the at least two throttle bores are arranged at regular angular intervals from one another.
  • the at least one inflow channel comprises at least one groove formed in the injection member between the control chamber and the high-pressure chamber on the lateral surface of the injection member whose width / depth ratio is smaller 1: 10, preferably about 1: 20.
  • Throttle bore dispensed with these and instead of a targeted
  • Fuel causes from the high-pressure chamber in the control room.
  • This solution has a constructive extent in that the strength of the valve piece or the control chamber sleeve is not weakened by throttle bores, and that on the other hand by the usually relatively long in the axial direction of the injection member formed guide a single groove is sufficient to the viscosity-dependent throttling effect of To realize inflow channels.
  • Section passes, which has a smaller diameter compared to the first section.
  • the at least one inflow channel has one in the
  • Injection member formed second throttle bore comprises, wherein the
  • Diameter / length ratio of the throttle bore is less than 1: 5, preferably about 1:10.
  • This variant supplies the fuel via a throttle bore formed, for example, in the longitudinal axis of the injection member (nozzle needle), which is then connected to the high-pressure chamber, for example via a transverse bore.
  • the injection valve member may have a substantially constant diameter or that no mechanical processing is required on the peripheral surface of the injection valve.
  • Fig. 1 shows a portion of a fuel injector according to the invention in
  • FIG. 3 each have a comparison with FIG. 1 modified injection member
  • Fig. 1 is a portion of a fuel according to the invention! shown ejector 10, as it is used as part of a common rail injection system in self-igniting internal combustion engines.
  • the fuel injector 10 has an injector 1 1, in which in an axis 12, an injection member in the form of a nozzle needle 15 is arranged up and down movable. In the illustrated in Fig. 1, lowered position of the nozzle needle 15, the nozzle needle 15 is seated with a seating area on an inner wall of the injector 1 1 to form a sealing seat sixteenth on, at least one, formed in the injector 1 1
  • the at least one injection port 17 is released for injecting fuel into a combustion chamber of the internal combustion engine by 1 befindaji fuel in a high-pressure chamber 18 of the injector 1 1 fuel can be injected via the at least one injection port 17 into the combustion chamber.
  • the high-pressure chamber 18 is connected via a supply bore 19 with a
  • Fuel connection 21 is connected, which in turn is connected via a connection, not shown, in particular with a high-pressure accumulator (rail) for the fuel.
  • a stepped bore 22 is formed, which has two bore sections 23, 24 substantially.
  • a portion of a valve piece 25 into it, which in turn in the transition region between the two bore sections 23, 24 axially on an end face 26 of the Stepped bore 22 is applied.
  • an annular shield member 27, a likewise annular housing part 28 and a clamping ring 29 is arranged, which is formed by means of a threaded connection 30, the
  • an actuator 32 for at least indirect actuation of the nozzle needle 15 is arranged, which has a magnet armature 33.
  • the armature 33 cooperates with a magnetic coil 34 which is inserted in an annular recess of a magnetic core 35.
  • the magnetic core 35 is again arranged with the interposition of a support plate 36 between a step 37 on the housing part 28 and the clamping ring 29.
  • the armature 33 has aligned to the longitudinal axis 12 has a through hole 38 in which a guide pin 39 is arranged.
  • the guide pin 39 serves the axial guidance of the armature 33 and is supported on the side facing away from the valve piece 25 axially against the support plate 36 from.
  • the armature 33 is by means of a compression spring 41 in the direction of an end face
  • valve member 25 is subjected to force and forms in the illustrated in Fig. 1 lowered position of the armature 33 with a sealing surface
  • Section of the valve piece 25 has in the longitudinal axis 12 a formed of a plurality of bore portions through hole, which forms a guide portion 44 on the nozzle needle 15 side facing.
  • a control chamber 45 is formed, which has a
  • Abiaufbohrung 46 with integrated Abströmdrossel 47 in a low pressure chamber 50 can be relieved of pressure.
  • the Abiaufbohrung 46 opens into the end face 42 of the valve member 25 and is radially surrounded by the sealing surface 43 of the armature 33.
  • the control chamber 45 is hydraulically connected to the high-pressure chamber 18 via at least two inflow channels arranged at regular angular intervals in the form of first throttle bores 48, which are formed in the radially encircling wall of the valve member 25 and perpendicular to the longitudinal axis 12.
  • first throttle bores 48, 49 which are preferably produced by a laser-beam device, are designed in such a way that, when fuel flows from the high-pressure chamber 18 into the control chamber 45, a laminar flow is achieved
  • first throttle bores 48, 49 is less than 1: 5, preferably about 1:10. Such a design causes a dependent of the viscosity of the fuel in the high-pressure chamber 18 flow rate of the fuel in the Control room 45. If instead of two throttle holes 48, 49 three
  • Throttle holes are used, so is a preferential
  • Diameter / length ratio of the three throttle bores about 1:15.
  • the actuator 32 by energizing the
  • Magnetic coil 34 is actuated. This raises the armature 33 with his
  • the low-pressure chamber 50 is in turn known per se, and therefore not shown manner with a fuel return of the fuel! njektors 10 hydraulically connected.
  • the pressure drop in the control chamber 45 causes the nozzle needle 15 lifts from its sealing seat 16 and the at least one injection port 17 releases.
  • the fuel flows from the high-pressure chamber 18 via the first two throttle bores 48, 49 as a result of
  • Viscosity-dependent flow rate decelerates towards lower viscosity fuel, resulting in a particularly rapid pressure drop in the air
  • Control chamber 45 is achieved, and thus a particularly rapid lifting of the
  • Fig. 1 operatively connected to the nozzle needle 15 arranged closing spring) is moved. Due to the delayed at high viscosity of the fuel afterflow of the fuel from the high-pressure chamber 18 into the control chamber 45, the pressure in the control chamber 45 is relatively slow
  • FIG. 2 shows a modified embodiment of the invention in which no first throttle bores 48, 49 are formed in the valve piece 25a.
  • the two first throttle bores 48, 49 are in uniform by at least one, preferably more, preferably more than three
  • each other grooves 51 which are formed on the peripheral or lateral surface of the nozzle needle 15 and preferably parallel to the longitudinal axis 12 extend.
  • the nozzle needle 15 in the illustrated embodiment, a first, disposed substantially within the valve piece 25a portion 52 and a second, disposed substantially within the high-pressure chamber 18 section 53. It is essential that the second section 53 has a smaller diameter than the first section 52, so that the at least one groove 51 only in the first
  • Section 52 must be formed to the control chamber 45 with the
  • the width / depth ratio of the at least one groove 51 is less than 1:10, preferably about 1:20, wherein the cross-sectional shape of the groove 51 is preferably rectangular or semicircular (not shown).
  • the depth of the groove 51 is about ⁇ , with an overall length of the groove 51 of about 12mm.
  • FIG. 3 is a further modified embodiment of
  • the second throttle bore 55 has a diameter / length ratio of less than 1: 5, preferably about 1:10.
  • Control chamber 45 formed by a so-called control room sleeve or is limited, which is arranged in analogy to the arranged in the first bore portion 23 portion of the valve member 25, 25 a and then the first throttle bores 48, 49 may have.

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)

Abstract

L'invention concerne un injecteur de carburant (10), comprenant un boîtier (11) dans lequel est ménagé au moins un orifice (17) d'injection de carburant dans la chambre de combustion d'un moteur à combustion interne, l'écoulement par l'au moins un orifice d'injection (17) pouvant être commandé au moyen d'un élément d'injection (15), en particulier d'une aiguille de gicleur, mobile suivant un mouvement de montée et de descente selon un axe longitudinal (12), l'élément d'injection (15) étant disposé dans une chambre à forte pression (18) et plongeant dans un élément (25 ; 25a) (45), délimitant une chambre de commande, par une zone d'extrémité opposée à l'au moins un orifice d'injection (17), et la chambre à forte pression (18) étant reliée hydrauliquement à la chambre à forte pression (18) par au moins un conduit d'amenée (48, 49 ; 51 ; 55) et pouvant se détendre dans une chambre à basse pression (50) par un conduit d'évacuation (46). Selon l'invention, l'au moins conduit d'amenée (48, 49 ; 51 ; 55) est conçu pour conférer au carburant un écoulement laminaire.
EP14781567.4A 2013-11-28 2014-10-09 Injecteur de darburant Active EP3074623B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013224404.5A DE102013224404A1 (de) 2013-11-28 2013-11-28 Kraftstoffinjektor
PCT/EP2014/071594 WO2015078629A1 (fr) 2013-11-28 2014-10-09 Injecteur de carburant

Publications (2)

Publication Number Publication Date
EP3074623A1 true EP3074623A1 (fr) 2016-10-05
EP3074623B1 EP3074623B1 (fr) 2018-08-15

Family

ID=51663199

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14781567.4A Active EP3074623B1 (fr) 2013-11-28 2014-10-09 Injecteur de darburant

Country Status (3)

Country Link
EP (1) EP3074623B1 (fr)
DE (1) DE102013224404A1 (fr)
WO (1) WO2015078629A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201412086D0 (en) 2014-07-08 2014-08-20 Delphi International Operations Luxembourg S.�.R.L. Fuel injector for an internal combustion engine
DE102014215749A1 (de) 2014-08-08 2016-02-11 Continental Automotive Gmbh Drosseleinrichtung zum Steuern einer einer Kraftstoff-Einspritzdüse zuzuführenden Kraftstoffmenge sowie Einspritzeinrichtung
DE102015226326A1 (de) * 2015-12-21 2017-06-22 Robert Bosch Gmbh Hydraulische Kopplereinrichtung und Kraftstoffeinspritzventil mit einer solchen
DE102019200237A1 (de) 2019-01-10 2020-07-16 Robert Bosch Gmbh Kraftstoffinjektor
DE102019203658A1 (de) * 2019-03-19 2020-09-24 Robert Bosch Gmbh Kraftstoffinjektor

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997008452A1 (fr) * 1995-08-29 1997-03-06 Isuzu Motors Limited Dispositif d'injection de carburant du type a accumulation
DE10131631A1 (de) * 2001-06-29 2003-01-16 Bosch Gmbh Robert Kraftstoffinjektor mit hochdruckfestigkeitsoptimiertem Steuerraum
DE10131640A1 (de) * 2001-06-29 2003-01-16 Bosch Gmbh Robert Kraftstoffinjektor mit Einspritzverlaufsformung durch schaltbare Drosselelemente
JP2003113761A (ja) * 2001-08-01 2003-04-18 Denso Corp 燃料噴射弁
EP1296055B1 (fr) * 2001-09-20 2006-01-11 Denso Corporation Injecteur de carburant avec plaque à orifices d'étranglement
JP2004278357A (ja) * 2003-03-13 2004-10-07 Denso Corp インジェクタ
JP2004332545A (ja) * 2003-04-30 2004-11-25 Mitsubishi Heavy Ind Ltd 内燃機関の燃料噴射装置
DE102006009659A1 (de) * 2005-07-25 2007-02-01 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine mit Kraftstoff-Direkteinspritzung
DE102006049830A1 (de) 2006-10-23 2008-04-24 Robert Bosch Gmbh Kraftstoffeinspritzventileinrichtung
JP5120293B2 (ja) * 2009-02-20 2013-01-16 株式会社デンソー 燃料噴射弁
JP5625837B2 (ja) * 2010-03-31 2014-11-19 株式会社デンソー 燃料噴射装置
DE102011086249A1 (de) * 2011-11-14 2013-05-16 Robert Bosch Gmbh Kraftstoffinjektor

Also Published As

Publication number Publication date
DE102013224404A1 (de) 2015-05-28
WO2015078629A1 (fr) 2015-06-04
EP3074623B1 (fr) 2018-08-15

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