EP2872768A1 - Injecteur de fluide - Google Patents

Injecteur de fluide

Info

Publication number
EP2872768A1
EP2872768A1 EP13736849.4A EP13736849A EP2872768A1 EP 2872768 A1 EP2872768 A1 EP 2872768A1 EP 13736849 A EP13736849 A EP 13736849A EP 2872768 A1 EP2872768 A1 EP 2872768A1
Authority
EP
European Patent Office
Prior art keywords
control
control piston
transmission pin
fluid
piston unit
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
EP13736849.4A
Other languages
German (de)
English (en)
Other versions
EP2872768B1 (fr
Inventor
Willibald SCHÜRZ
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive 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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP2872768A1 publication Critical patent/EP2872768A1/fr
Application granted granted Critical
Publication of EP2872768B1 publication Critical patent/EP2872768B1/fr
Not-in-force 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
    • 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
    • F02M61/04—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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M2200/70—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
    • 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
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve

Definitions

  • Fluid injector The invention relates to a fluid injector with a solid state actuator, which may be, for example, a piezoelectric actuator.
  • a fluid injector with a solid state actuator which may be, for example, a piezoelectric actuator.
  • Such fluid injectors are used, for example, in internal combustion engines for metering fuel.
  • a precise metering of the fluid by means of the per ⁇ pillar Fluidinj is ector important.
  • fluid injectors with solid state actuators are used, in particular also in diesel internal combustion engines.
  • the fluid to be metered is frequently supplied to the injector at a feed pressure of up to approximately 2500 bar and then metered into the respective combustion chamber of the internal combustion engine by means of the fluid injector.
  • the invention is characterized by a fluid injector with a solid body actuator and with an injector body.
  • the injector body has an actuator recess in which the solid state actuator is arranged.
  • a control piston unit which is arranged in a control piston unit recess of the injector body.
  • a transfer pin is provided which is arranged to penetrate a transfer pin recess in the injector body and mechanically couple the solid state actuator to the control piston unit.
  • the fluid injector comprises a nozzle body which has a nozzle body recess, of which in one region of a nozzle tip one or more injection holes are formed penetrating the nozzle body to the outside.
  • a nozzle needle is arranged, which limits the second control chamber with an end face facing away from the nozzle tip.
  • the nozzle needle is arranged axially movable in the DüsenAvemaus predominantlyung. It stops in one
  • the spool assembly includes a spool having an end surface at an axial end facing the transmission pin which is coupled to the transmission pin and defines the first control space.
  • control piston unit has a control sleeve, which is arranged coaxially to the control piston and has a radially inwardly directed projection, via which a driving coupling between the control piston and the control sleeve takes place after overcoming a predetermined first control piston stroke of the control piston caused by an elongation of the solid.
  • peraktuators which is conditioned by supplying electrical energy.
  • the control sleeve is arranged and designed so that it influences a free volume of the first control chamber during an axial movement of the control piston with existing entrainment coupling.
  • the moving out of the nozzle needle from its closed position requires a particularly high reduction of the force which is introduced by means of the fluid pressure on the nozzle needle tip facing away from the end face of the nozzle needle in this, namely, in the closed position of the nozzle needle on a range of "
  • Nozzle needle tip which is located radially within a seat of the nozzle needle, only a small force acts, since in this area the fluid pressure corresponds approximately to the ambient pressure.
  • the seat of the nozzle needle is located radially outside the injection holes.
  • this is also advantageous if very small amounts of fluid have to be measured one behind the other in very short time intervals, as is the case, for example, with multiple injections.
  • a smaller amount of charge is thus supplied to the solid body actuator and it can thus be withdrawn faster, which leads to The consequence is that even very short distances between the individual meterings of fluid can be realized.
  • the first and also the second control chamber are subjected in a stationary manner to a feed pressure of the fluid which is supplied to the fluid injector for metering the fluid.
  • control piston of the control piston unit is coupled at its end facing away from the transfer pin axial end with a compensation chamber which is subjected to a stationary feed pressure of the fluid and in which a spring element is arranged such that one towards the
  • Transfer pin directed force is exerted on the control piston. This contributes in particular to a hydraulic clearance ⁇ compensation.
  • the fluid injector is also strongly thermally influenced by self-heating as a result of electrical losses in the region of the solid-state actuator.
  • the temperature due to the relaxation of fluid from feed pressure to ambient pressure plays an essential role.
  • the idle stroke of the solid-body actuator required without hydraulic play compensation.
  • the idle stroke in such cases changes during operation of the fluid injector by changing the length of the solid state actuator due to polarization changes and component wear.
  • control sleeve comprises a first part and a second part.
  • the second part has the radially inward projection.
  • the first part is arranged in the axial direction closer to the transmission pin than the second part.
  • the first part and the second part are hydraulically coupled in the axial direction via a coupling space. Furthermore, they are mechanically coupled by means of a spring element arranged in the coupling space.
  • control piston is associated with a pressure piece, which is arranged axially in the region of the radially inwardly directed projection of the control sleeve and having a collar member having a larger cross-section than the radially inwardly directed projection of the control sleeve and axially thereafter the end of the control sleeve facing away from the transfer pin is arranged.
  • control sleeve comprises the corresponding first and second part and also the collar is acted upon by the feed pressure in the expansion chamber and also the force exerted by the spring element located in the compensation chamber force ent ⁇ speaking over the collar and the pressure element is introduced to the control piston.
  • the collar element is formed as a separate part of the pressure piece.
  • FIG. 2 shows a first partial section in a sectional view of the fluid injector according to FIG. 1 and FIG.
  • Figure 3 shows a second partial section based on the first
  • a fluid injector 1 has an injector body, which is basically formed in one piece, but preferably in several pieces.
  • the injector body in a multi-part design comprises an injector body part 3, an intermediate plate 9, a control plate 11 and an end plate 13.
  • the Injektor Congress 3 has an AktuatorausEnglishung 5, in which a solid-state actuator 7 is introduced.
  • the solid-state actuator 7 is designed, for example, as a piezoelectric actuator and is an electromechanical converter.
  • the injector particularly the injector body 3, which may not necessarily need a compensation function Temperaturaus ⁇ meet and can be made of a material, which may be in terms timiert high compressive strength ⁇ op.
  • Adding or removing electrical charge contributes, so in particular in the case of a piezoelectric actuator of the piezo stack, for example, by means of a membrane or a corrugated tube of the fluid hermetically separated.
  • control piston unit recess is formed, in which a control piston unit is arranged.
  • Transmission pin recess 14 penetrates and the Festkör- peraktuator 7 mechanically coupled to the control piston unit.
  • a first control chamber 17 is limited.
  • the first control chamber 17 is hydraulically coupled to a second control chamber 19 via a connecting bore 21.
  • the control piston unit has a control piston 23 which has an end face 25 at an axial end facing the transmission pin 15, which communicates with the transmission pin 15 is coupled and the first control room 17 limited.
  • control piston unit has a control sleeve which is arranged coaxially with the control piston 23.
  • the control sleeve has a first part 27 and a second part 29.
  • the second part 29 of the control sleeve has a radially inwardly directed projection 35, via which a driving coupling between the control piston 23 and the control sleeve takes place after overcoming a predetermined first Steuerkolbenhubs the control piston 23rd caused by an elongation of the Fest stressesaktuators 7, which is due to supply of electrical energy.
  • the control sleeve is arranged and designed such that it influences during axial movement of the control piston 23 to be ⁇ standing entrainment coupling a free volume of the first control chamber 17th
  • the first part 27 of the control sleeve is arranged in the axial direction closer to the transmission pin 15 than the second part 29 of the control sleeve.
  • the first part 27 and the second part 29 are hydraulically coupled in the axial direction via a coupling space 31 and are mechanically coupled by means of a spring element 33 arranged in the coupling space 31.
  • the control piston 23 is associated with a pressure piece 37 which is arranged axially in the region of the radially inwardly directed projection 35 of the control sleeve and which has a collar element 39 with a larger cross-section than the radially inwardly directed projection 35 of the control sleeve and the axial ⁇ closing the end of the control sleeve facing away from the transfer pin 15 is arranged.
  • the collar member 39 may be formed as a separate part of the pressure piece 37, but it may also be integrally or integrally formed therewith.
  • a compensation space is formed, which is subjected to a supply pressure of the fluid stationary and in which a spring element 41 is arranged such that it exerts a directed toward the transfer pin 15 force on the control piston.
  • the spring element 41 is arranged in this context so that it transmits a force via the collar element 39 to the control piston unit and thus in particular via the pressure piece 37 on the control piston 23.
  • acting on the in the direction of the transfer pin 15 hyd ⁇ raulische force on the control piston 23 via the collar member 39 a. This is how it is essential for a reliable coupling between the
  • a nozzle body 45 which has a nozzle body recess 47.
  • the nozzle body recess 47 one or more injection holes are formed in a region 49 of a nozzle tip, namely the nozzle body 45 starting from the nozzle body recess 47 penetrating outwards.
  • a nozzle needle 53 is arranged, which limits the second control chamber 19 with an end face 55 facing away from the nozzle tip.
  • the nozzle needle 53 is axially movable in the Düsen stresses ⁇ recess 47 is arranged in such a manner that it prevents in a closed position, fluid flow through the one or more injection holes and otherwise releases it.
  • a feed bore 56 is in the
  • Control plate 11 and the end plate 13 is provided which is hydraulically coupled to a fluid port 61 which is hydraulically coupled to a fluid supply during operation, by means of which the fluid to be metered during operation of the fluid injector 1 is supplied to this under the feed pressure.
  • the transfer pin 15 is fitted with a very small clearance in the ellessbuildausEnglishung 14 in such a way that the smallest possible leakage of fluid from the first control chamber 17 through the effetsstructausappelung 14 and so a practical hydraulic tightness with respect to the highly ⁇ dynamic processes in given the control room 17.
  • a mating clearance for the control piston 23 in the control sleeve, ie in the first and second part 27, 29, so small chosen that for the highly dynamic processes in the first control chamber 17 a practical tightness can be ensured. This also applies to the coupling space 31 and also for the compensation chamber 43.
  • Drift processes caused by different tempera ⁇ turausdehnungskostoryen the components involved or different temperatures in the components at different locations, can be done according to a pressure equalization, such as between the first control chamber 17 and / or the coupling space 31 and / or the compensation chamber 43 and so on hydraulic clearance compensation done.
  • the pairing games to be provided are approximately 2 to 6 ym, the transfer pin 15 in the transfer pin recess is the pairing game at less than 2 ym.
  • Both the first control chamber and the second control chamber, as well as the coupling chamber 31, and the compensation chamber 43 are subjected to the feed pressure stationarily.
  • the nozzle body 45 is coupled via a nozzle retaining nut 59 with the injector body.
  • the second control chamber 19 is further delimited by means of a nozzle needle sleeve 47, which is arranged coaxially with the nozzle needle 53.
  • the operation of the Fluidinj ector will be explained in more detail below.
  • a pressure drop is generated in the first control chamber 17, which is transmitted via the connecting bore 21 to the second control chamber 19. If the pressure then drops in the second control chamber 21 below a respectively predetermined threshold value, a resultant force acts on the nozzle needle 53 in the direction away from the nozzle tip, with the result that the nozzle needle 53 lifts off its seat and thus its Closing position leaves.
  • the first Steuerkolbenhub is the difference between L2 and LI (see Figure 3). He is so predetermined that preferably the driving coupling takes place approximately when the force acting on the nozzle needle 53 acting force just changes its sign, so that the nozzle needle 53 their
  • this transmission ratio is particularly large, for example, set to a value of about 2.0.
  • this transmission ratio is particularly large, for example, set to a value of about 2.0.
  • the spring element 33 which is formed in particular as a spring washer, a contribution is made that in a starting position, that is, when the nozzle needle is in its closed position, the first part 27 of the control sleeve to stop on the intermediate plate 9 and the second part 29 of the control sleeve is always on stop on the collar element 39.
  • the force exerted by the spring element 41 force consistently leads to a direct coupling of the control piston 23 with the leakage pin 15. In this way a backlash-free drive is ensured.
  • Characteristic power jumps occur when you lift the Dü ⁇ nozzle needle 53 from its seat, the transition from the first to the second gear stage and closing of the nozzle needle 53rd In the case of a needle stop (limitation of the needle stroke), an evaluable force jump occurs even when the stop is reached.
  • Time of opening the nozzle needle 53 must be supplied when the nozzle needle 53 leaves its closed position.

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 un injecteur de fluide qui présente un actionneur monolithique et un corps d'injecteur. Une unité de piston de commande est disposée dans un évidement pour unité de piston de commande du corps d'injecteur. Une tige de transmission (15) est disposée de manière à traverser un évidement pour tige de transmission dans le corps d'injecteur et à accoupler mécaniquement l'actionneur monolithique à l'unité de piston de commande. L'unité de piston de commande et le corps d'injecteur délimitent une première chambre de commande (17) qui est couplée hydrauliquement à une deuxième chambre de commande. L'unité de piston de commande présente un piston de commande (23) qui présente, à une extrémité axiale orientée vers la tige de transmission (15), une surface frontale (25) qui est accouplée à la tige de transmission (15) et délimite la première chambre de commande (17). L'unité de piston de commande présente également une douille de commande qui est disposée coaxialement au piston de commande (23) et présente une saillie (35) qui est orientée radialement vers l'intérieur et par l'intermédiaire de laquelle un accouplement d'entraînement a lieu entre le piston de commande (23) et la douille de commande après avoir surmonté une première course prédéfinie du piston de commande (23) provoquée par un allongement de l'actionneur monolithique (7) qui dû à la fourniture d'énergie électrique. La douille de commande est disposée et conçue de manière à influencer un volume libre de la première chambre de commande (17) pendant un mouvement axial du piston de commande (23) avec lequel la douille est en accouplement d'entraînement.
EP13736849.4A 2012-07-13 2013-07-04 Injecteur de fluide Not-in-force EP2872768B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012212266.4A DE102012212266B4 (de) 2012-07-13 2012-07-13 Fluidinjektor
PCT/EP2013/064106 WO2014009237A1 (fr) 2012-07-13 2013-07-04 Injecteur de fluide

Publications (2)

Publication Number Publication Date
EP2872768A1 true EP2872768A1 (fr) 2015-05-20
EP2872768B1 EP2872768B1 (fr) 2016-09-28

Family

ID=48790404

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13736849.4A Not-in-force EP2872768B1 (fr) 2012-07-13 2013-07-04 Injecteur de fluide

Country Status (6)

Country Link
US (1) US9856843B2 (fr)
EP (1) EP2872768B1 (fr)
CN (1) CN105247199B (fr)
DE (1) DE102012212266B4 (fr)
IN (1) IN2014DN10942A (fr)
WO (1) WO2014009237A1 (fr)

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Also Published As

Publication number Publication date
US9856843B2 (en) 2018-01-02
WO2014009237A1 (fr) 2014-01-16
EP2872768B1 (fr) 2016-09-28
IN2014DN10942A (fr) 2015-09-18
DE102012212266A1 (de) 2014-05-22
US20150211456A1 (en) 2015-07-30
CN105247199A (zh) 2016-01-13
DE102012212266B4 (de) 2015-01-22
CN105247199B (zh) 2018-03-30

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