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EP0864743B1 - Soupape d'injection de combustible pour moteurs à combustion interne - Google Patents

Soupape d'injection de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP0864743B1
EP0864743B1 EP97120314A EP97120314A EP0864743B1 EP 0864743 B1 EP0864743 B1 EP 0864743B1 EP 97120314 A EP97120314 A EP 97120314A EP 97120314 A EP97120314 A EP 97120314A EP 0864743 B1 EP0864743 B1 EP 0864743B1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
fuel injection
working space
hydraulic working
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.)
Expired - Lifetime
Application number
EP97120314A
Other languages
German (de)
English (en)
Other versions
EP0864743A3 (fr
EP0864743A2 (fr
Inventor
Katsuoki Itoh
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 EP0864743A2 publication Critical patent/EP0864743A2/fr
Publication of EP0864743A3 publication Critical patent/EP0864743A3/fr
Application granted granted Critical
Publication of EP0864743B1 publication Critical patent/EP0864743B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
    • F02M47/046—Fluid pressure acting on injection-valve in the period of injection to open it
    • 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 a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out.
  • Fuel injection valve is a piston-shaped valve member axially slidably disposed in a valve body with its free end in the combustion chamber of the supply Internal combustion engine protrudes.
  • the valve member end on the combustion chamber side with a valve sealing surface which is used to control an injection cross section with a Valve seat surface cooperates on the valve body, one of which Injection opening leads into the combustion chamber of the internal combustion engine.
  • the valve member is operated by an electrical actuator, preferably axially actuated a piezo actuator, wherein the actuating movement of the piezo actuator via a hydraulic Working space is transferred to the valve member.
  • This has the advantage that z. B. temperature-dependent fluctuations of the piezo actuator can be compensated and also the Actuating movement of the piezo actuator in a larger actuating movement of the valve member can be translated.
  • the known fuel injection valve the disadvantage that there are overshoots in dynamic operation and bouncing of the valve member can come result in an unwanted opening of the injection valve.
  • natural vibrations occur in the known fuel injection valve of the piezo actuator via the hydraulic amplifier room transferred to the valve member, so that this too begins to oscillate and thus falsifies the injection process.
  • Another disadvantage of the known fuel injection valve occurs during the reset movement of the piezo actuator on, with the rapid increase in volume of the hydraulic Working space the pressure of the inside Fuel can drop below the vapor pressure and thus cavitation damage may occur.
  • the fuel injection valve according to the invention for internal combustion engines with the characterizing features of the claim 1 has the advantage that the use of a second electrical actuator a very fast and direct valve member actuation is possible with which is the cross section of the injection opening and thus the course of the injection on the fuel injection valve optimally over the Injection time forms.
  • This work space is included divided into two sub-rooms, each by one Pistons of the piezo actuator and the valve member are limited and which are separated from each other by a throttling point, so that vibrations occurring at the piezo actuator do not affect the Valve element are transmitted and an overshoot or Bouncers on the valve member itself are suppressed.
  • Through the Separation of the electric actuator and its adjusting piston will also create a negative pressure at fast Resetting the electrical actuators avoided, whereby then lift them off the adjusting piston.
  • Particularly advantageous is the use of two in the opposite direction the valve actuator acting electrical actuators, because thus in addition to a very fast and controlled opening stroke the closing stroke of the valve member is very quick and controlled can be executed.
  • the electrical actuator can alternatively as a piezoelectric or magnetostrictive actuator.
  • Fuel injection valve as an outward opening injection valve or inward opening injection valve, z. B. hole or tenon nozzle.
  • FIG. 1 shows a first embodiment in a simplified schematic representation, in which the two piezo actuators in the same direction of adjustment via a common hydraulic work area on the Valve member act
  • Figure 2 shows a second embodiment, in which the two electrical actuators in each opposite direction of adjustment via a common hydraulic working space on the valve member of the fuel injector attack
  • Figure 3 a third Embodiment analogous to the representation of Figure 2, at a separate hydraulic one for each electric actuator Working space is assigned to the valve member.
  • Fuel injection valve for internal combustion engines has one Valve body 1 on, with its lower free end in the combustion chamber, not shown, to be supplied Internal combustion engine protrudes.
  • the valve body 1 In the valve body 1 is one axial blind hole 3 is provided, in which a not shown, injection line leading away from a fuel injection pump empties.
  • a piston-shaped is in the valve body 1
  • Valve member 5 is arranged axially displaceable a valve sealing surface 7 at its lower end near the combustion chamber with which it is used to control an injection cross section cooperates with a valve seat surface 9 on the valve body 1, formed at the closed end of the blind hole 3 is. Two lead from the valve seat 9 Injection openings 11 in the combustion chamber to be supplied Internal combustion engine.
  • valve member 5 reduces at its the end facing away from the valve sealing surface 7 has its cross section forming an annular shoulder 13 on which one on the other hand, valve spring 15 which is fixed to the housing attacks such that it engages the valve member 5 in the Valve seat 9 holds.
  • Valve member 5 At its end facing away from the valve sealing surface 7, this has Valve member 5 a valve piston enlarged in cross section 17, which for the axial actuation of the valve member 5 protrudes into a hydraulic working space 19 and this with its lower piston ring end face facing the valve seat 9 21 limited.
  • electrical actuators are also preferably designed as piezo actuators electrical actuators are provided, a first of which Actuator 23 via an axially adjacent first Adjusting piston 25 also in the hydraulic work space 19 protrudes.
  • a too second actuator 27 In addition to the first actuator 23 is a too second actuator 27 arranged offset therefrom, the also with the interposition of a second Adjusting piston 29 projects into the hydraulic working space 19.
  • the hydraulic work space 19 is in three sub-rooms divided, of which a first subspace 31 from the first adjusting piston 25, a second partial space 33 from the second adjusting piston 29 and a third subspace 35 from the valve piston 17 is limited.
  • the third subspace 35 is over each a throttle point 37 with the other two subspaces 31 and 33 connected.
  • the first embodiment shown in Figure 1 of the fuel injection valve according to the invention for internal combustion engines works in the following way.
  • the adjusting pistons 25 and 29 are through the Return springs 41 in contact with the actuators 23 and 27 kept so that only in the hydraulic working space 19 a stand pressure is built up.
  • This on the piston ring face 21 of the valve piston fixedly connected to the valve member 5 17 attacking in the opening direction of the valve member 5 Stand pressure is, however, less than the closing force the valve spring 15, which the valve member 5 with its valve sealing surface 7 sealingly on the valve seat surface 9, so that the injection openings 11 from the valve sealing surface 7 be kept closed.
  • the actuators 23 and 27 are energized and extend in length.
  • the adjusting pistons 25 become more hydraulic in the direction Working space 19 moved so that the hydraulic medium the subspaces 31 and 33 via the throttle points 37 in the third subspace 35 is displaced.
  • There the inflowing takes hold hydraulic pressure medium on the end face 21 of the Valve piston 17 and moves it against the Closing force of the valve spring 15 in that facing away from the valve seat 9 Direction so that the valve member 5 from the valve seat 9th takes off and the flow cross section between that with high pressure fuel filled blind hole 3 to the injection openings 11 releases.
  • This causes vibrations on the valve member 5 by a targeted step-like movement of the electrical Actuators 23 and 27 damped.
  • the axial expansion adjustment movement of the actuators 23 and 27 triggered in stages, with one actuator each short is controlled after the second actuator.
  • the temporal Displacement of the adjustment movements of the actuators 23 and 27 to each other is about a few 10 ⁇ s.
  • the electric actuators 23 and 27 again de-energized so that they are back in very quickly return to their axially shortened starting position. This is done the control of the electric actuators 23 and 27 again with a slight time difference.
  • the respective Adjusting pistons 25 and 29 are driven by the force of Return springs 41 also in the direction of actuators 23, 27 moved back so that the volume in the hydraulic
  • the work area is quickly enlarged and the pressure is quickly reduced the closing pressure of the valve spring 15 drops. Consequently the valve member 5 from the valve spring 15 in again System moved to the valve seat 9, so that the opening cross section closed again on the fuel injector and the injection is finished.
  • This avoidance of cavitation can also be caused by a delay in the reset speed of the electrical Actuators 23 and 27 and by increasing the system pressure in the hydraulic work space 19 well above Vapor pressure of the hydraulic medium are supported.
  • the second embodiment shown in Figure 2 differs from the first one shown in FIG Embodiment in that now two hydraulic Working spaces are provided, which are by the valve piston 17th are so delimited from each other that they are the valve piston 17 of the valve member 5 each in the opposite direction of adjustment apply.
  • the two are hydraulic Workspaces in a common cylindrical Chamber 43 arranged by the slidably guided therein Valve piston 17 in a first upper hydraulic work space 45 and a second lower hydraulic work space 47 is divided.
  • Die hydraulic work spaces 45 and 47 are each in two Sub-rooms divided, of which a sub-room on the adjusting piston 25, 29 of the electric actuator 23, 27 and another sub-space opens onto the valve piston 17 and the again connected to one another via a throttle cross section 37 are.
  • the second embodiment shown in Figure 2 works in the following way.
  • the fuel injector is the first actuator 23 axially extended. This can be done by feeding one Control voltage to be energized axially expanding piezo element or a contracting one under supply of a control voltage Piezo element can be switched off.
  • the first actuator 23 becomes the first Adjusting piston 25 in the direction of the first hydraulic work space 45 moved, this adjustment movement of the first Adjusting piston 25 via the upper valve piston end face 49 of the adjusting piston 17 so transmitted to the valve member 5 is that this with its valve sealing surface 7 sealing in System is pressed against the valve seat surface 9.
  • the second Actuator 27 is when the fuel injector is closed switched so that it has its smallest axial extent having.
  • the second adjusting piston 29 is thereby Return spring 41 held in contact with the actuator 27 and is largely from the second lower hydraulic work space 47 dived.
  • the first actuator 23 is now switched so that it reduces its axial extent.
  • the second actuator 27 switched such that its axial extension increased, so that the second adjusting piston 29 from the second actuator 27 in the direction of the second lower hydraulic working space 47 is moved.
  • This Adjustment movement of the second adjusting piston 29 is hydraulic on the lower piston ring end face 21 of the adjusting piston 17 transmitted so that the valve member 5 from the valve seat 9 is lifted off and the injection cross section in the Releases the combustion chamber of the internal combustion engine.
  • the third exemplary embodiment of the fuel injection valve according to the invention shown in FIG. 3 differs from the second exemplary embodiment shown in FIG. 2 by the design of the valve piston 17, which is now formed in two parts.
  • a first upper piston part 61 delimits the upper hydraulic working chamber 45 with its upper valve piston end face 49, which acts on the valve member 5 in the closing direction.
  • a second lower piston part 63 of the valve piston 17 delimits, with its lower piston ring end face 21, the lower hydraulic working space 47, which acts in the opening direction on the valve member 5 of the fuel injection valve opening inwards.
  • the two piston parts 61 and 63 can be brought into contact with one another at a certain distance from one another by a piston rod 65 which is preferably arranged on the upper piston part 61, with a preliminary stroke h v of the valve member 5 in over the free distance between the piston rod 65 and the lower piston part 63 Can open the opening direction.
  • the fuel injector shown in FIG. 3 without the actuators and the corresponding return springs of the adjusting pistons works analogously to the second exemplary embodiment.
  • the valve member 5 At the beginning of the opening stroke phase when the second actuator 27 is displaced in the direction of the lower hydraulic working space 47, the valve member 5 first runs through a very rapid forward stroke path h v , in which only the force of the valve spring 15, not shown, has to be overpressed.
  • the lower valve piston part 63 comes into contact with the upper valve piston part 61 and now has to overcome a greater restoring force in the course of the further adjustment stroke movement.
  • the opening stroke curve of the valve member 5 following the pre-injection can be adjusted by the corresponding actuation of the first actuator 23 actuating the first adjusting piston 25.
  • the hydraulic working spaces 45 and 47 are preferably separated from one another by the valve piston 17.

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)

Claims (9)

  1. Injecteur de carburant pour moteur à combustion interne comprenant une soupape (5) pouvant coulisser dans l'injecteur (1) et présentant à son extrémité une portée d'étanchéité (7) coopérant pour commander une section d'injection, avec une portée de siège (9) prévue sur l'injecteur (1) et d'où part un orifice (11) assurant l'injection du carburant dans la chambre de combustion du moteur à alimenter, ainsi qu'un organe électrique de commande (23) actionnant axialement la soupape (5) par l'intermédiaire d'une chambre hydraulique de travail (19),
    caractérisé en ce qu'
    il est prévu pour actionner la soupape (5), un second organe électrique de commande (27) pouvant être commandé indépendamment du premier (23).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la chambre hydraulique de travail (19) est délimitée par un piston de soupape (17) relié à la soupape (5) et par des pistons de réglage (25, 29) reliés aux organes électriques de commande (23, 27), les parties de la chambre hydraulique de travail (19) délimitées par les pistons de soupape (25, 29) et le piston de soupape (27) formant des chambres partielles séparées les unes des autres par des sections d'étranglement (37).
  3. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    le piston de soupape (17) est fixé directement sur la soupape (5) et les pistons de commande (25, 29) sont maintenus par des ressorts de rappel (41) en contact par leurs faces frontales éloignées des chambres partielles (31, 33), avec les organes électriques de commande (23, 27) correspondants.
  4. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    les organes électriques de commande (23, 27) sont des actionneurs piézo-électriques.
  5. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    le premier et le second organe de commande (23, 27) agissent dans la même direction de déplacement sur le piston (17) de la soupape (5) par l'intermédiaire de la chambre hydraulique de travail (19).
  6. Injecteur de carburant selon la revendication 2,
    caractérisé en ce qu'
    il est prévu deux chambres hydrauliques de travail (45, 47) délimitées par le piston de soupape (17) de manière que la soupape (5) soit actionnée par ces chambres dans des sens de déplacement opposés.
  7. Injecteur de carburant selon la revendication 6,
    caractérisé en ce que
    les deux chambres hydrauliques de travail (45, 47) sont à l'intérieur d'une chambre cylindrique commune (43) dans laquelle coulisse un piston de soupape (17) divisant la chambre (43) en une première chambre supérieure de travail (45) et une seconde chambre inférieure de travail (47) délimitées, la première (45) par la face frontale supérieure (49) du piston de soupape (17) et la deuxième (47) par la face inférieure (21) de ce piston de soupape.
  8. Injecteur de carburant selon la revendication 7,
    caractérisé en ce que
    les chambres hydrauliques de travail (45, 47) sont divisées chacune en deux chambres partielles dont l'une débouche sur un piston de commande (25 ou 29) de l'organe de réglage (23 ou 27) respectivement et l'autre sur le piston de soupape (17), les chambres de chaque paire étant reliées entre elles par une section d'étranglement.
  9. Injecteur de carburant selon la revendication 6,
    caractérisé en ce que
    le piston de soupape (17) est divisé en deux parties, la première partie supérieure de piston (61) délimitant une première chambre hydraulique supérieure de travail (45) tandis que la seconde partie inférieure de piston (63) délimite une seconde chambre hydraulique de travail (47), les deux parties (61, 63) de piston pouvant avantageusement être amenées en contact par l'intermédiaire d'une tige (65) fixée à une partie de piston.
EP97120314A 1997-03-10 1997-11-20 Soupape d'injection de combustible pour moteurs à combustion interne Expired - Lifetime EP0864743B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19709795A DE19709795A1 (de) 1997-03-10 1997-03-10 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19709795 1997-03-13

Publications (3)

Publication Number Publication Date
EP0864743A2 EP0864743A2 (fr) 1998-09-16
EP0864743A3 EP0864743A3 (fr) 2001-08-08
EP0864743B1 true EP0864743B1 (fr) 2003-06-11

Family

ID=7822845

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97120314A Expired - Lifetime EP0864743B1 (fr) 1997-03-10 1997-11-20 Soupape d'injection de combustible pour moteurs à combustion interne

Country Status (3)

Country Link
EP (1) EP0864743B1 (fr)
JP (1) JPH10252598A (fr)
DE (2) DE19709795A1 (fr)

Cited By (1)

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CN105745832A (zh) * 2013-09-27 2016-07-06 西门子公司 升降系统、用于电气测试的方法、减震器以及机器组件

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DE19843534A1 (de) 1998-09-23 2000-03-30 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19843578A1 (de) * 1998-09-23 2000-03-30 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19950760A1 (de) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
JP4079578B2 (ja) * 2000-06-22 2008-04-23 株式会社日本自動車部品総合研究所 燃料噴射装置
DE10100392C1 (de) * 2001-01-05 2002-06-13 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10333693B3 (de) * 2003-07-24 2004-09-30 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333573B3 (de) * 2003-07-24 2004-11-18 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333427B3 (de) * 2003-07-24 2004-08-26 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE112004001488D2 (de) * 2003-09-10 2006-07-27 Siemens Ag Einspritzventil für die Einspritzung von Kraftstoff in eine Verbrennungskraftmaschine
DE102005024721B4 (de) * 2005-05-30 2017-06-08 Robert Bosch Gmbh Common-Rail-Injektor
JP5024321B2 (ja) * 2009-03-25 2012-09-12 株式会社デンソー 燃料噴射弁
JP5024320B2 (ja) * 2009-03-25 2012-09-12 株式会社デンソー 燃料噴射弁
JP5024322B2 (ja) * 2009-03-25 2012-09-12 株式会社デンソー 燃料噴射弁
EP2500550A1 (fr) * 2011-03-16 2012-09-19 Siemens Aktiengesellschaft Transmetteur de course pour turbine à gaz
DE102011088282A1 (de) * 2011-12-12 2013-06-13 Continental Automotive Gmbh Einspritzventil
KR101314991B1 (ko) * 2012-01-25 2013-10-04 홍종한 차량용 피에조 인젝터
DE102014219604A1 (de) * 2014-09-26 2016-03-31 Siemens Aktiengesellschaft Hubsystem, Verfahren zur elektrischen Prüfung, Schwingungsdämpfer und Maschinenaggregat
US20160377040A1 (en) * 2015-06-24 2016-12-29 Great Plains Diesel Technologies, L.C. Fuel injection rate modulation by magnetostrictive actuator and fluidomechanical coupler
GB2560513A (en) * 2017-03-13 2018-09-19 Ap Moeller Maersk As Fuel injection system
CN110440046A (zh) * 2019-09-06 2019-11-12 厦门赛尔特电子有限公司 一种液体传递行程放大式压电开关阀

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DE3344229A1 (de) * 1983-12-07 1985-06-20 Pierburg Gmbh & Co Kg, 4040 Neuss Elektromagnetisches brennstoffeinspritzventil
DE4306072C2 (de) * 1993-02-26 1994-12-08 Siemens Ag Vorrichtung zum Öffnen und Verschließen einer in einem Gehäuse vorhandenen Durchtrittsöffnung
US5669355A (en) * 1994-07-29 1997-09-23 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
DE19500706C2 (de) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105745832A (zh) * 2013-09-27 2016-07-06 西门子公司 升降系统、用于电气测试的方法、减震器以及机器组件
CN105745832B (zh) * 2013-09-27 2018-09-21 西门子公司 升降系统、用于电气测试的方法、减震器以及机器组件

Also Published As

Publication number Publication date
JPH10252598A (ja) 1998-09-22
EP0864743A3 (fr) 2001-08-08
EP0864743A2 (fr) 1998-09-16
DE59710265D1 (de) 2003-07-17
DE19709795A1 (de) 1998-09-17

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