EP2090771A1 - Injecteur de carburant doté d'un pointeau de soupape commandé directement - Google Patents

Injecteur de carburant doté d'un pointeau de soupape commandé directement Download PDF

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Publication number
EP2090771A1
EP2090771A1 EP09100004A EP09100004A EP2090771A1 EP 2090771 A1 EP2090771 A1 EP 2090771A1 EP 09100004 A EP09100004 A EP 09100004A EP 09100004 A EP09100004 A EP 09100004A EP 2090771 A1 EP2090771 A1 EP 2090771A1
Authority
EP
European Patent Office
Prior art keywords
actuator
sleeve
fuel injector
elastomer
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
EP09100004A
Other languages
German (de)
English (en)
Other versions
EP2090771B1 (fr
Inventor
Martin Kiontke
Rudolf Heinz
Udo Schaich
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 EP2090771A1 publication Critical patent/EP2090771A1/fr
Application granted granted Critical
Publication of EP2090771B1 publication Critical patent/EP2090771B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms

Definitions

  • the invention is based on a fuel injector with a directly controlled valve needle according to the preamble of patent claim 1.
  • Such a fuel injector is for example by the DE 10 2005 004 738 A1 known.
  • a hydraulic coupler is provided between the piezo actuator and the nozzle needle, and the needle movement follows directly the actuator movement.
  • the piezo actuator is arranged in an actuator receiving space, which is connected to a high-pressure accumulator of the fuel.
  • DE 10 2005 004 738 A1 Nothing is said about the sealing of the piezo actuator with respect to the fuel.
  • the object of the invention is to protect the piezo actuators, which are located in the injector, from moisture (diesel, H 2 O, RME, other electrically conductive substances), particles and suspended solids and the high pressures, pressure and temperature fluctuations.
  • the compensating element which may be designed as a sleeve, annular piston or piston, is pushed axially in the direction of the actuator head until the elastomer has reached its maximum volume expansion.
  • the elastomer contracts and thereby reduces its volume, and the compensation element is now pushed back over the applied high pressure of the fuel and tracked the elastomer.
  • the compensation element thus ensures the necessary lifting and temperature compensation on the actuator module (-40 to +160 ° C).
  • the permeation of moisture (diesel, H 2 O, RME, other electrically conductive substances) via suitable high-pressure sealing elements, coatings or coating geometries must be reduced to a minimum.
  • the design with a separation of temperature compensation and functional movement allows a considerable gain in space and thus allows a more robust structural design.
  • the components can, for example, increase the radial forces with additional geometric adjustments and thus achieve a support of the sealing force.
  • the in Fig. 1 shown fuel injector 1 has an injector 2 with a nozzle body 3 , which projects with its lower end into a combustion chamber of an internal combustion engine. Between injector housing 2 and nozzle body 3, an intermediate plate 4 is arranged with a guide bore 5 , in which a valve or nozzle needle 6 is guided axially displaceable. Between the tip of the nozzle needle 6 and the nozzle body 3, a sealing seat 7 is formed, which are arranged downstream of the injection nozzle 8 formed in the nozzle body 3 and projecting into the combustion chamber. In the nozzle body 3, the sealing seat 7 is preceded by a high-pressure chamber 9 is formed.
  • the injector housing 2 has an actuator receiving space 10 in an upper area, to which a fuel inlet 11 is connected.
  • the fuel inlet 11 is connected to a high pressure system, for example to a common rail system a diesel injector, connected.
  • a connecting bore 12 leads through the intermediate plate 4 , so that the fuel introduced via the fuel feed 11 into the actuator receiving space 10 is conducted at high pressure into the high-pressure space 9 assigned to the nozzle needle 6.
  • a piezoelectric actuator 13 is arranged, which comprises a fixedly connected to the injector 2 actuator base 14, an actuator head 15 and between the actual piezoelectric element (piezo stack) 16 , wherein the actuator head 15 and the piezo stack 16 relative to the actuator 14 in the Diameter are reduced.
  • the actuator head 15 is also guided in the guide bore 5 and defined therein together with the nozzle needle 6 a coupler space 17, whereby the nozzle needle 6 is hydraulically coupled with the piezoelectric actuator 13. Furthermore, engages the nozzle needle 6 a supported on the intermediate plate 4 closing spring 18 , which presses the nozzle needle 6 in the closing direction.
  • the sealing seat 7 is closed by the nozzle needle 6.
  • the fuel pressure reached via the fuel inlet 11 into the actuator accommodating space 10 is in the high-pressure chamber 9 and in the coupler chamber 17 equally.
  • acting in the coupler chamber 17 on the nozzle needle 6 hydraulic closing force is equal to acting in the high pressure chamber 9 on the nozzle needle 6 hydraulic opening force, so that the nozzle needle 6 is pressed by the closing spring 18 in its closed position. If the voltage at the piezoelectric actuator 13 is reduced or the piezoactuator 13 is de-energized, the length of the piezoelectric actuator 13 is reduced in the vertical direction and the actuator head 15 moves upwards.
  • the volume increases in the coupler space 17, whereby there takes place a pressure reduction and acting on the nozzle needle 6 closing force of the closing spring 18 is overcome.
  • the nozzle needle 6 lifts off from the sealing seat 7 and releases the injection openings 8 for fuel injection.
  • an extension of the piezoelectric actuator 13 is again introduced, which generates a pressure increase in the coupler chamber 17, which leads to the closing of the nozzle needle 6.
  • the closing spring 18 acting on the nozzle needle 6 then holds the nozzle needle 6 on the sealing seat 7, ie in the closed state.
  • the piezo stack 16 is surrounded by a sleeve 20 made of metal floating on the piezoelectric actuator 13, ie axially displaceable, is stored and the piezo stack 16 seals against the Aktorfactraum 10 and thus protects against fuel and water ingress.
  • a bottom seal (sliding seal) 21 is integrated, on which the sleeve 20 is mounted axially displaceable.
  • a ring 22 is welded on the inside high pressure tight, in which a head gasket (sliding seal) 23 is integrated, which is mounted axially displaceably on the actuator head 15.
  • the annular space between the sleeve 20 and piezoelectric actuator 13 is filled with an elastomer 24 (eg fluoroelastomers), the heat dissipation from the piezo stack 16 to the sleeve 20, for electrical insulation and as a support member relative to the sleeve 20 under the prevailing system pressures of up to 2500 bar serves.
  • elastomer 24 eg fluoroelastomers
  • seals 21, 23 metallic and elastomeric high-pressure sealing elements can be used.
  • paired elements on the actuator base 14 and the actuator head 15 in strength and coefficient of thermal expansion should be chosen so that a close tolerance with low radial expansion is possible. In this way, a suitable high pressure seal is possible.
  • the floating sleeve 20 can compensate for the volume change of the elastomer 24 abutting its one annular end surface 25a by being axially displaceable along the base gasket 21.
  • the actuator head 15 can slide along the head gasket 23 and at this point converts its functional movement.
  • the sleeve 20 Upon thermal expansion of the elastomer 24 supported on the actuator foot 14, the sleeve 20 is pushed axially in the direction of the actuator head 15 and slides with its sealing elements 21, 23 along the actuator foot 14 and actuator head 15 until the elastomer 24 has reached its maximum volume expansion.
  • the elastomer 24 contracts and thereby reduces its volume.
  • the sleeve 20 is now pushed back over the applied at its other annular end face 25b high pressure of the fuel and the elastomer 24 tracked.
  • the sleeve 20 is subjected to a higher force in the head area due to the annular end face 25b in the head area than in the foot area.
  • the sleeve 20 thus always ensures a pressure equalization inside and outside the sleeve 20, so that they are at high Pressing and possible suppression is not deformed.
  • Due to the additional annular end face 25, the sleeve 20 thus forms a movable differential piston, the necessary lifting and temperature compensation on Piezo actuator 13 in the temperature range of -40 to +160 ° C ensures.
  • the permeation of moisture (diesel, water, RME) or other electrically conductive substances via suitable coatings, coating geometries or suitable high-pressure sealing elements 21, 23 on the ring 22 and the actuator base 14 to a minimum.
  • the material pairings of sleeve 20, actuator base 14, actuator head 15 and ring 22 must be selected in terms of strength and thermal expansion coefficient so that the sealing elements 21, 23 can be designed as small as possible and no geometric overdetermination between the movable sealing points takes place.
  • the ring 22 and the actuator base 14 can be adapted and designed in their geometry and shape according to the selected type of seal.
  • an additional radial contact pressure of the foot and head gaskets 21, 23 can be achieved.
  • the sleeve 20 can apply an additional radial force by appropriate geometric design and thus achieve a support of the sealing force.
  • the undercut of the sleeve 20 allows an additional radial force on the head gasket 23. In this way, wear and temperature differences can be compensated.
  • the radial contact pressure can still be increased by springs 27 , which radially spread apart the legs 28 of the H-shaped cross section.
  • the ring 22 may have a U-shaped cross-section only on its end face facing the actuator receiving space 10.
  • an additional radial contact pressure can be achieved by reducing the wall of the sleeve 20.
  • the sleeve 20 is welded at one end to the actuator base 14 in a high pressure-tight manner and closed at the other end by an annular piston 40 , which is mounted so as to be axially displaceable by sliding seals 41, 42 in the sleeve 20 and on the actuator head 15.
  • the coupler space 17 is formed within a coupler sleeve 43 , in which the actuator head 15 and optionally also the nozzle needle 6 are guided displaceably.
  • the two sliding seals 41, 42 are on Ring piston 40 is provided and allow the sliding and high pressure-tight sealing of the annular piston 40 relative to the sleeve 20 (temperature compensation) and relative to the actuator head 15 (Brushubterrorism).
  • the material pairings of actuator head 15, sleeve 20 and annular piston 40 should be chosen in terms of strength and thermal expansion coefficient so that the sliding seals 41, 42 can be designed as small as possible.
  • seals 41, 42 metallic and elastomeric high-pressure sealing elements can be used.
  • the annular piston 40 can be designed in length and shape according to the selected type of seal.
  • the annular piston 40 can compensate for the change in volume of the elastomer 24 resting against its one annular end surface 44a by axially displacing itself with its outer sliding seal 41 within the sleeve 20.
  • the actuator head 15 can slide along the inner sliding seal 42 and at this point reverses its functional movement.
  • the annular piston 40 In a thermal expansion of the supported on the actuator base 14 elastomer 24, the annular piston 40 is pushed to increase the volume axially in the direction of the free actuator head end and slides with its sliding seals 41, 42 high pressure within the sleeve 20 and the actuator head 15 along until the elastomer 24 its maximum Volume expansion has reached. Upon cooling, the elastomer 24 contracts and thereby reduces its volume. The annular piston 40 is now pushed back over the applied at its other annular end face 44b high pressure of the fuel and the elastomer 24 tracked. The annular piston 40 thus always ensures a pressure equalization with respect to the sleeve 20, so that it is not deformed at high pressure. To assist the ring piston 40 may be biased with a supported on the coupler sleeve 43 spring 45 in contact with the elastomer 24.
  • Fig. 5a can be achieved by two annular grooves 46, so an H-shaped cross-section of the annular piston 40, an additional radial contact force of the sliding seal 41, 42.
  • the radial contact force can still by analog springs as in Fig. 3a increase.
  • a bellows 47 can be formed or embossed on the sleeve 20, which - in particular in the case of a geometric overdetermination in the tolerance chain (actuator foot 14, sleeve 20, annular piston 40, actuator head 15) - a radial tolerance compensation on the piezoelectric actuator 13th allows.
  • the bellows 46 can reduce jamming or increased wear on the annular piston 40, the sleeve 20 and the actuator head 15 due to its radially and axially flexible properties. In addition to a classic Blagpatented other compensation stampings on the sleeve 20 are possible.
  • the sleeve 20 is welded to the actuator base 14 and the actuator head 15 in a high-pressure-tight manner and is formed as a bellows 47 therebetween.
  • a piston 60 is guided in a guide bore 61 of the actuator head 15 by means of a sliding seal or coating 62 axially displaceable and high pressure- tight and limited in the guide bore 61 has two piston chambers 63a, 63b .
  • Upper piston chamber 63a is connected via elastomer inlet bores 64 with the annulus filled by the elastomer 24 and the lower piston chamber 63b via high-pressure inlet bores 65 with the Aktorfactraum 10.
  • springs 66 can be used to compensate for any existing differences in power between elastomer 24 and fuel and friction forces.
  • the guide bore 61 is formed in the actuator head 15 blind bore, which is closed with a closure element 67 .
  • the sleeve 20 takes on their bellows structure or other Wegausreterete geometry, the lifting movement of the actuator function in the axial direction.
  • the piston 60 compensates only for the thermal expansion of the elastomer 24 and the other components and thus prevents radial expansion or possible overuse of the sleeve 20.
  • pressure fluctuations in the Aktorfactraum 10 are compensated by the piston 60 so that the sleeve 20 is pressure balanced at all times and not deformed unduly.
  • the piston 60 Upon thermal expansion of the elastomer 24 supported on the actuator root 14, the piston 60 is pushed so far in the direction of the free actuator head end by the elastomer 24 resting on its one piston surface 68a until the elastomer 24 has reached its maximum volume expansion.
  • the elastomer 24 is ideally connected without stiffness, pressure and flow losses to the piston 60, with the appropriate vote on the number, bore diameter and shape of the inlet holes 64 takes place.
  • the elastomer 24 contracts and thereby reduces its volume.
  • the piston 60 is now pushed back over the prevailing in the lower piston chamber 63b and acting on its other piston surface 68b high pressure of the fuel and the elastomer 24th tracked.
  • the piston 60 thus always ensures a pressure equalization inside and outside the sleeve 20, so that it is not deformed at high pressures and possible suppression.
  • the material pairings of sleeve 20, piston 60, actuator base 14 and actuator head 15 should be chosen in terms of strength and thermal expansion coefficient so that the sliding seal 62 on the piston 60 can be designed as small as possible.
  • metallic and elastomeric high-pressure sealing elements can be used.
  • the piston 60 can be adapted and designed in its geometry and shape according to the selected type of seal.
  • an additional radial contact pressure of the sliding seal 62 can be achieved in each case by two annular grooves 69, that is, by a double-H-shaped cross-section of the piston 60.
  • an additional radial contact pressure of the sliding seal 62 can also be achieved in each case by an annular groove 69, that is, by an H-shaped cross section of the piston 60.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP20090100004 2008-02-13 2009-01-05 Injecteur de carburant doté d'un pointeau de soupape commandé directement Expired - Fee Related EP2090771B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810008847 DE102008008847A1 (de) 2008-02-13 2008-02-13 Kraftstoffinjektor mit einer direkt gesteuerten Ventilnadel

Publications (2)

Publication Number Publication Date
EP2090771A1 true EP2090771A1 (fr) 2009-08-19
EP2090771B1 EP2090771B1 (fr) 2011-08-17

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Application Number Title Priority Date Filing Date
EP20090100004 Expired - Fee Related EP2090771B1 (fr) 2008-02-13 2009-01-05 Injecteur de carburant doté d'un pointeau de soupape commandé directement

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EP (1) EP2090771B1 (fr)
DE (1) DE102008008847A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3112661A1 (fr) * 2015-06-29 2017-01-04 Delphi International Operations Luxembourg S.à r.l. Dispositif de scellement

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1424492A2 (fr) * 2002-11-26 2004-06-02 Robert Bosch Gmbh Vanne de commande de liquides avec une buse et une valve de commande
EP1452729A1 (fr) * 2003-02-28 2004-09-01 Robert Bosch Gmbh Injecteur de carburant
DE10310789A1 (de) * 2003-03-12 2004-09-23 Robert Bosch Gmbh Brennstoffeinspritzventil
EP1561942A1 (fr) * 2004-01-29 2005-08-10 Siemens VDO Automotive S.p.A. Unjecteur de liquide et son procédé de fabrication
DE102005004738A1 (de) 2005-02-02 2006-08-10 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine
EP1741922A1 (fr) * 2005-06-28 2007-01-10 Robert Bosch Gmbh Injecteur de carburant
WO2009059862A1 (fr) * 2007-11-09 2009-05-14 Robert Bosch Gmbh Module d'actionnement piézo-électrique

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1424492A2 (fr) * 2002-11-26 2004-06-02 Robert Bosch Gmbh Vanne de commande de liquides avec une buse et une valve de commande
EP1452729A1 (fr) * 2003-02-28 2004-09-01 Robert Bosch Gmbh Injecteur de carburant
DE10310789A1 (de) * 2003-03-12 2004-09-23 Robert Bosch Gmbh Brennstoffeinspritzventil
EP1561942A1 (fr) * 2004-01-29 2005-08-10 Siemens VDO Automotive S.p.A. Unjecteur de liquide et son procédé de fabrication
DE102005004738A1 (de) 2005-02-02 2006-08-10 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine
EP1741922A1 (fr) * 2005-06-28 2007-01-10 Robert Bosch Gmbh Injecteur de carburant
WO2009059862A1 (fr) * 2007-11-09 2009-05-14 Robert Bosch Gmbh Module d'actionnement piézo-électrique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3112661A1 (fr) * 2015-06-29 2017-01-04 Delphi International Operations Luxembourg S.à r.l. Dispositif de scellement

Also Published As

Publication number Publication date
EP2090771B1 (fr) 2011-08-17
DE102008008847A1 (de) 2009-08-27

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