EP1654453A1 - Injecteur pour systemes d'injection de carburant de moteurs a combustion interne, notamment de moteurs diesel a injection directe - Google Patents

Injecteur pour systemes d'injection de carburant de moteurs a combustion interne, notamment de moteurs diesel a injection directe

Info

Publication number
EP1654453A1
EP1654453A1 EP04738750A EP04738750A EP1654453A1 EP 1654453 A1 EP1654453 A1 EP 1654453A1 EP 04738750 A EP04738750 A EP 04738750A EP 04738750 A EP04738750 A EP 04738750A EP 1654453 A1 EP1654453 A1 EP 1654453A1
Authority
EP
European Patent Office
Prior art keywords
nozzle
nozzle needle
injector
piezo actuator
needle
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.)
Withdrawn
Application number
EP04738750A
Other languages
German (de)
English (en)
Inventor
Sebastian Kanne
Godehard Nentwig
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 EP1654453A1 publication Critical patent/EP1654453A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • F02M2200/215—Piezoelectric or magnetostrictive elements being able to tilt in its housing
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to an injector according to the preamble of patent claim 1.
  • An injector of the aforementioned type is the subject of (not previously published) DE ... (R.305 558). Advantages of this known injector are in its comp. uncomplicated construction (few individual parts) and direct control of the nozzle needle by the piezo actuator. The speed of the nozzle needle movement can be set via the voltage curve of the piezo actuator. In addition, the known injector is characterized in that it does not require a fuel return.
  • the object of the present invention is to comp. simple means to create a way to gradually control and actuate the nozzle outlet.
  • the invention advantageously makes it possible to actuate the nozzle outlet in stages by driving the two nozzle needles one after the other - by correspondingly applying voltage to the piezo actuator.
  • the system according to the invention also has the advantage of not requiring a return.
  • FIG. 1 shows an embodiment of a directly controlled common rail injector with a piezo actuator, in a vertical longitudinal section
  • FIG. 2 shows a lower part of the injector according to Mg. 1, in an enlarged view compared to FIG. 1, and
  • 10 denotes a cylindrical injector body with a continuous recess 11, which is cylindrical over the major part of its longitudinal extent. At its upper end, the recess 11 initially has a conically tapering section 12, which merges into a section 13, 14 which is bent at a right angle and finally opens outwards.
  • a likewise cylindrical piezo actuator 16 is arranged with a comparatively large longitudinal extent, the diameter of which is smaller than the inside diameter of the recess section 15.
  • the upper, angled section 13, 14 of the recess 11 functions as a cable duct for the power supply of the piezo actuator 16.
  • a fuel supply 18 e.g. High-pressure connection of a common rail system is provided, which is in hydraulic connection with the annular space 17 via a pressure channel 19.
  • a nozzle body 20 which receives a first nozzle needle 21.
  • the nozzle body 20 is fastened to the injector body 10 by means of a union nut (clamping nut) 22 in such a way that it comes into sealing contact with a rear end face 23 on a lower end face 24 of the injector body 10.
  • the nozzle body 20 In order to receive the first nozzle needle 21, the nozzle body 20 has an interior 25 that is open at the top and has multiple steps, the one below j nm forms several nozzle outlet bores 26 to 29 opening out of the conical valve seat 30.
  • the first nozzle needle 21 has a section 31 of larger diameter, which is fitted into a cylindrical interior 32 of a sleeve-shaped, downwardly open booster piston 33.
  • the upper end of the booster piston 33 is formed by a collar 34.
  • a helical compression spring 35 which is arranged in the annular space 17 - here enclosing the booster piston 33 - is supported on the one hand on the end face 23 of the nozzle body 20 and on the other hand on the collar 34 of the booster piston 33 the piezo actuator on the front.
  • the top side 37 of the piezo actuator 16 is sealed against the injector body 10, and the electrical connection (not shown) can thus be made through the angled bores 13, 14 be led out of the injector body 10.
  • a special feature - particularly evident from FIG. 2 - consists in the fact that the first nozzle needle 21 has a continuous, concentric axial recess 39 which is stepped by a shoulder 38 and in which a second nozzle needle 41, which is likewise stepped by a shoulder 40, is axially displaceably fitted.
  • a cylindrical pressure chamber 42 concentrically surrounding the first nozzle needle 21 is formed, which has holes 43, 44 in the nozzle body 20 and one between the nozzle body 20 and the nozzle body
  • Clamping nut 22 formed annular space 45 is hydraulically connected to the annular space 17 of the injector body 10.
  • the interior 25 of the nozzle body 20 has a stepped diameter widening 46 at the top, in which the booster piston 33 is guided such that a first control chamber 47 formed in the widened interior part 46 below the booster piston 33 has a leakage gap 48 (see in particular FIG. 2). is in hydraulic connection with the annular space 17 of the injector body 10.
  • a section 49 of the nozzle body interior 25 with a comparatively small diameter serves to guide the first nozzle needle 21 within the nozzle body 20. This guide fit 49 is also designed in such a way that a leakage gap results.
  • the first control chamber 47 is thus hydraulically connected to the cylindrical chamber 42 via the second leakage gap 49, which in turn is subjected to high pressure from the annular chamber 17 of the injector body 10 via the recesses 43 to 45.
  • the interior 32 of the booster piston 33 which extends above the nozzle needle 21, is also hydraulically connected to the high-pressure annular space 17 of the injector body 10, specifically via a lateral bore 50 in the booster piston 33.
  • the upper (thickened) section 31 of the first nozzle needle 21 is thus in the Translator piston 33 guided that there is a (further) leakage gap 51 (see FIG. 2).
  • a hydraulic connection between the first control chamber 47 and the pressurized annular chamber 17 of the injector body 10 is thus also established via this (third) leakage gap 51.
  • the second (inner) control space 52 has a smaller volume than the first (outer) control space 47.
  • Control rooms are provided through a bore 53 which penetrates the first nozzle needle 21 obliquely in the region of its shoulder 38.
  • a (second) helical compression spring 54 is arranged in the interior 32 of the booster piston 33 and exerts a force directed in the closing direction (arrow 55) on the first nozzle needle 21.
  • the (second) compression spring 54 keeps the first nozzle needle 21 closed during the breaks between the injection processes and when the vehicle is at a standstill. 1 and 2, the opening position of the two nozzle needles 21 and 41 is shown. In this position, an injection process takes place, in which all the outlet openings - in the example shown, the bores 26 to 29 - are involved.
  • fuel passes from the cylindrical pressure chamber 42 through the outlet bores 26 to 29 into the cylinder combustion chamber (not shown) of the internal combustion engine.
  • the first control chamber 47 formed at the lower end of the booster piston 33 serves for hydraulic length compensation and as a hydraulic booster for the expansion movement of the piezo actuator 16 with respect to the first nozzle needle 21.
  • a shoulder 57 is formed at the (upper) end of the second nozzle needle 41 on the piezo actuator side, to which a pin part 58 with a smaller diameter is connected, on which the helical compression spring 56 is arranged.
  • the axial recess 39 of the first nozzle needle 21 penetrated by the second nozzle needle 41 has a diameter widening in its (lower) region on the nozzle outlet side.
  • annular cylindrical cavity 59 surrounding the (lower) area of the second nozzle needle 41 on the nozzle outlet side.
  • a radial bore 60 is machined into the first nozzle needle 21 and hydraulically connects the cylindrical pressure chamber 42 to the annular cylindrical cavity 59.
  • a further special feature is that the (lower) end region 61 of the nozzle body 20 containing the nozzle outlet openings 26 to 29 and the end sections 62, 63 of the two nozzle needles 21 and 41, each functioning as a closing body, are conical, so that complete the end sections 62, 63 of the nozzle needles 21 and 41 in the common closed or open position (FIGS. 1 and 2) to form a uniform conical surface.
  • the nozzle outlet openings 26 to 29 and the conical end sections 62, 63 of the two nozzle needles 21 and 41 are matched to one another in terms of their dimensions and their position so that the two radially inner nozzle outlet openings 26, 27 extend from the conical end section 63 second nozzle needle 41 are actuated and the two radially outer nozzle outlet openings 28, 29 with the conical end portion 62 of the first
  • the injector described above works as follows: The piezo actuator 16 is deenergized during spray breaks. If the piezo actuator 16 is now electrically controlled, it expands and moves it
  • the second (inner) nozzle needle 41 As soon as the second (inner) nozzle needle 41 opens, the pressure in the control rooms 47, 52 does not decrease further. After a short stroke (approx. 0.1 mm, depending on the hydraulic flow), the second nozzle needle 41 strikes its upper stop, the pin part 58 coming into contact with the inner (upper) end face of the booster piston 33. In order to now also move the first (outer) nozzle needle 21 into its open position (FIGS. 1 and 2), a (further) increase in the electrical voltage applied to the piezo actuator 16 is required. As a result, the piezo actuator 16 expands again in the axial direction (arrow 55) to such an extent that the first nozzle needle 21 now also moves into the open position (FIGS. 1 and 2) and opens the nozzle outlet openings 28, 29.
  • the first nozzle needle 21 is able to carry out a maximum stroke which is clearly above the stroke of the piezo actuator 16. (Since the first nozzle needle 21 is supplied with fuel from the inside and outside, the stroke can be significantly less than 200 ⁇ m.) As soon as the nozzle needles 21, 41 have left the stroke region of the seat throttle, they are pressure-balanced. The piezo actuator 16 then has to keep the pressure in the control chambers 47, 52 only above the high pressure (rail pressure) of the fuel supplied at 18 (FIG. 1) via the booster piston 33 so that the resistances of the springs 35, 54 and 56 can be overcome. The longest possible activation period is determined by the leakage from the control rooms 47, 52.
  • the nozzle needles 21, 41 close.
  • the electrical voltage applied to the piezo actuator 16 must be reduced to zero.
  • the piezo actuator 16 then contracts, and the pressure in the control rooms 47, 52 drops below the rail pressure.
  • the first (outer) compression spring 35 prevents the piezo actuator 16 from separating from the booster piston 33.
  • the volumes of the control chambers 47, 52 and the surfaces of the nozzle needles 21, 41 acted upon by the control chamber pressures or by the pressure of the fuel supply 18, 19 or by the spring medium pressure are coordinated such that the two nozzle needles 21, 41 open in succession by changing the electrical voltage applied to the piezo actuator 16 and can be closed simultaneously by removing the voltage from the piezo actuator 16.
  • 64 designated force-distance-KutNe fulfilled can be used. If the seat angle is increased and the necessary strokes of the first and second nozzle needles (21 and 41) are made somewhat narrower, significantly lower values for maximum force and stroke can also be achieved. For example, with a seat angle of 90 ° (in the embodiment shown in FIGS. 1 and 2, the seat angles are somewhat smaller than 90 °), the second (inner) nozzle needle 41 would only have a stroke of 60 ⁇ m and the first (outer) nozzle needle 21 only need a stroke of 100 ⁇ m. This would result in a significantly smaller maximum stroke of the piezo actuator 16 of only 80 ⁇ m (s curve 65 in FIG. 3) with the same transmission ratios and the same surcharge for leakage.

Abstract

L'invention concerne un injecteur pour systèmes d'injection de carburant de moteurs à combustion interne, notamment de moteurs diesel à injection directe. Cet injecteur présente un piézo-actionneur (16) qui est monté dans un corps d'injecteur (10) et qui est maintenu en contact, par l'intermédiaire de premiers moyens ressorts (35), d'une part avec l'injecteur (10) et d'autre part avec un piston multiplicateur (33) de type douille. Cet injecteur présente, en outre, un corps de buse (20) qui est raccordé au corps d'injecteur (10), est pourvu d'au moins un orifice de sortie de buse (26, 27) et dans lequel une (première) aiguille de buse (21) à gradins est guidée de manière à pouvoir coulisser axialement. Des (deuxièmes) moyens ressorts, placés à l'intérieur du piston multiplicateur (33), maintiennent la (première) aiguille de buse (21) en position fermée, en association avec la pression d'injection agissant, côté arrière, sur la (première) aiguille de buse (21). Cet injecteur présente également une chambre de commande (extérieure) (47) qui est formée à l'extrémité, côté aiguille de buse, du piston multiplicateur (33) et qui communique, par l'intermédiaire d'au moins une fente de fuite, avec une conduite d'alimentation en carburant (18) soumise à la pression d'injection. La (première) aiguille de buse (21) est sollicitée dans le sens d'ouverture (36) par le carburant se trouvant dans la chambre de commande (47).
EP04738750A 2003-08-07 2004-06-22 Injecteur pour systemes d'injection de carburant de moteurs a combustion interne, notamment de moteurs diesel a injection directe Withdrawn EP1654453A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10336327.0A DE10336327B4 (de) 2003-08-07 2003-08-07 Injektor für Kraftstoff-Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren
PCT/DE2004/001301 WO2005014995A1 (fr) 2003-08-07 2004-06-22 Injecteur pour systemes d'injection de carburant de moteurs a combustion interne, notamment de moteurs diesel a injection directe

Publications (1)

Publication Number Publication Date
EP1654453A1 true EP1654453A1 (fr) 2006-05-10

Family

ID=34112016

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04738750A Withdrawn EP1654453A1 (fr) 2003-08-07 2004-06-22 Injecteur pour systemes d'injection de carburant de moteurs a combustion interne, notamment de moteurs diesel a injection directe

Country Status (6)

Country Link
US (1) US20080163852A1 (fr)
EP (1) EP1654453A1 (fr)
JP (1) JP2007506897A (fr)
KR (1) KR20060060675A (fr)
DE (1) DE10336327B4 (fr)
WO (1) WO2005014995A1 (fr)

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DE102004010183A1 (de) * 2004-03-02 2005-09-29 Siemens Ag Einspritzventil
DE102004031790A1 (de) * 2004-07-01 2006-01-26 Robert Bosch Gmbh Common-Rail-Injektor
DE102004060550A1 (de) * 2004-12-16 2006-07-06 Robert Bosch Gmbh Kraftstoffeinspritzdüse
DE102005015731A1 (de) * 2005-04-06 2006-10-12 Robert Bosch Gmbh Kraftstoffinjektor mit Piezoaktor
DE102005039551A1 (de) * 2005-08-22 2007-03-01 Robert Bosch Gmbh Piezoaktor mit zweiteiligem Haltekörper
DE102005050784A1 (de) * 2005-10-24 2007-04-26 Robert Bosch Gmbh Kraftstoffeinspritzventile für Brennkraftmaschinen
JP4535037B2 (ja) * 2006-02-08 2010-09-01 株式会社デンソー インジェクタおよび燃料噴射装置
DE102006012242A1 (de) * 2006-03-15 2007-09-20 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
JP4333757B2 (ja) 2007-03-13 2009-09-16 株式会社デンソー 燃料噴射弁
KR100891962B1 (ko) * 2007-05-29 2009-04-08 인하대학교 산학협력단 중공 압전작동기를 이용한 비접촉 방식의 디스펜서 헤드
CN101649797B (zh) * 2008-08-16 2013-05-29 柳州福尔曼汽车电子有限公司 一种磁致伸缩元件驱动的无背压电控柴油喷油器
DE102008042171A1 (de) 2008-09-17 2010-03-18 Robert Bosch Gmbh Brennstoffeinspritzventil
JP4911435B2 (ja) * 2008-10-03 2012-04-04 株式会社デンソー 燃料噴射弁
DE102009027727A1 (de) * 2009-07-15 2011-01-20 Robert Bosch Gmbh Ventilanordnung
DE102009046093A1 (de) 2009-10-28 2011-05-05 Robert Bosch Gmbh Piezoelektrischer Aktor
DE102009046309A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Piezoelektrischer Aktor
DE102009046306A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Piezoelektrischer Aktor
DE102009046312A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Piezoelektrischer Aktor
DE102009046311A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Piezoelektrischer Aktor
DE102009046320A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Einspritzventil
DE102009046314A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Piezoelektrischer Aktor
DE102009046356A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Aktormodul und Brennstoffeinspritzventil
DE102009046308A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Piezoelektrischer Aktor
DE102009046989A1 (de) 2009-11-23 2011-05-26 Robert Bosch Gmbh Brennstoffeinspritzventil
KR101137614B1 (ko) * 2010-10-28 2012-04-19 현대중공업 주식회사 내연기관용 연료분사밸브
DE102011078423A1 (de) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Komponente eines Brennstoffeinspritzsystems
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WO2016097463A1 (fr) 2014-12-19 2016-06-23 Wärtsilä Finland Oy Injecteur de carburant pour moteur à combustion interne
CN104612876B (zh) * 2015-02-10 2017-03-01 长城汽车股份有限公司 喷油器和具有其的汽车

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Also Published As

Publication number Publication date
JP2007506897A (ja) 2007-03-22
US20080163852A1 (en) 2008-07-10
DE10336327B4 (de) 2016-03-17
DE10336327A1 (de) 2005-03-03
KR20060060675A (ko) 2006-06-05
WO2005014995A1 (fr) 2005-02-17

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