EP1095215A1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant

Info

Publication number
EP1095215A1
EP1095215A1 EP99962124A EP99962124A EP1095215A1 EP 1095215 A1 EP1095215 A1 EP 1095215A1 EP 99962124 A EP99962124 A EP 99962124A EP 99962124 A EP99962124 A EP 99962124A EP 1095215 A1 EP1095215 A1 EP 1095215A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
injection valve
actuator
excitation coil
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
EP99962124A
Other languages
German (de)
English (en)
Other versions
EP1095215B1 (fr
Inventor
Wolfgang Ruehle
Juergen Ulm
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 EP1095215A1 publication Critical patent/EP1095215A1/fr
Application granted granted Critical
Publication of EP1095215B1 publication Critical patent/EP1095215B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped

Definitions

  • the invention relates to a fuel injector according to the preamble of claim 1.
  • a fuel injection valve according to the preamble of claim 1 is known from O89 / 10478.
  • the damping device resulting from this document consists of a pot-shaped damping element, a weak compression spring with a low spring coefficient and a strong compression spring with a high spring coefficient.
  • the two compression springs are axially offset from one another and enclose the valve needle in sections.
  • the cup-shaped damping element is located between the two compression springs, the two pressure springs acting in the opposite direction on the cup-shaped damping element and each being supported on the side facing away from the cup-shaped damping element on the valve needle attached to support elements.
  • the weak compression spring counteracts the closing of the fuel injector, the strong compression spring counteracts the opening of the fuel injection valve.
  • the known fuel injector has the following disadvantages: the damping force is predetermined by the spring force and the shear force and can therefore not be adapted to the operating variables of the internal combustion engine, in particular it cannot be adjusted in time. Since the fuel inflow in the direction of the sealing seat is influenced by the damping disk, flow swirls occur in the fuel, whereby the ductility of the fuel outflow is impaired. Am proposed in the O89 / 10478 as an alternative fuel inlet below the damping plate is impractical, since this significantly increases the size of the drain-side valve housing. The additional mechanical components also make the fuel injector more susceptible to wear, particularly since the damping force depends on the width of the between the edge of the damping element and the inner wall. Valve housing trained gap.
  • the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that the fuel injector m is debounced satisfactorily. Furthermore, the electromagnetic damping device does not require any mechanically stressed components such as compression springs and disc springs and does not require any damping fluid. Furthermore, the damping device is temperature stable and enables a variable damping force.
  • the damping device advantageously has an excitation coil for generating a magnetic field and at least one electrically conductive induction loop arranged on the valve needle.
  • the electromagnetic field m required for the damping can thereby be generated in a simple manner.
  • the damping force can act directly on the valve needle.
  • the excitation coil is wound on a valve housing of the fuel injector, the valve housing having a circumferential groove for this. This results in a manufacturing tech iscn simple accommodation of the excitation coil, or the excitation coil is well protected and easy to replace.
  • the electrical conductivity of the induction loop is greater than the electrical conductivity of the valve needle. This creates an m of Induction loop induced ring voltage an electrical induction current carried in the induction loop.
  • the induction loop is electrically insulated from the valve needle.
  • the electromotive force is used particularly well.
  • the induction loop is sleeve-shaped and encloses the valve needle in sections. This results in a shape of the induction loop which is adapted to the geometry of the fuel injection valve and which also enables simple attachment to the valve needle.
  • the axial length of the induction loop along the valve axis is advantageously smaller than the axial length of the excitation coil along the valve axis. This induces a larger ring tension m of the sleeve.
  • a control device for current-controlled control of the excitation coil and / or the actuator advantageously has a current control. This enables precise, quickly reacting control of the damping force acting on the valve needle.
  • the excitation coil is advantageously connected to the actuator in a row in order to utilize the displacement current which arises when the actuator is compressed. As a result, the energy stored in the actuator can be used to vaporize the valve needle.
  • Fig. 1 shows an excerpt axial section through a first gameforementionedsbei one of the invention Fuel injection valve, wherein the fuel injection valve is designed to open inwards;
  • FIG. 2 shows an embodiment of a control of a fuel injection valve according to the invention
  • FIG. 3 shows a schematic diagram to explain the functioning of an exemplary embodiment of a fuel injector according to the invention
  • FIG. 4 shows diagrams for explaining an exemplary embodiment of a fuel injection valve according to the invention
  • FIG. 5 shows a circuit diagram for an exemplary embodiment of a fuel injection valve according to the invention.
  • FIG. 6 diagrams for explaining an embodiment of an inventions
  • FIG. 1 shows a partial axial sectional view of a device according to the invention
  • Fuel injection valve 1 is used in particular for the direct injection of fuel, in particular gasoline, into a combustion chamber of a mixture-compressing, spark-ignited internal combustion engine as a so-called gasoline direct injection valve.
  • the fuel injection valve 1 according to the invention is, however, also suitable for other applications.
  • the fuel injection valve 1 is designed as a men-opening fuel injection valve 1.
  • the fuel injection valve 1 has a valve housing 2 and an end plate 3.
  • a valve needle 4 is located in the valve housing 2 by means of an axially movable valve needle 4 actuatable valve closing body 5, which is formed in one piece with the illustrated embodiment with the valve needle 4.
  • the valve closing body 5 is frustoconical and tapered in the spraying direction.
  • the valve closing body 5 interacts with a valve seat surface 7 formed on a valve seat body 6 to form a sealing seat.
  • the valve seat body 6 is fastened in the front part of the valve housing 2.
  • the contact element 12 On an inner contact surface 10, which is formed on a projection 11 of the valve housing 2, lies on the contact element 12.
  • the contact element 12 can be designed to be plastically or elastically deformable.
  • An intermediate plate 13 is fastened by a screw element 14 in the interior 16 of the fuel injector 1. The intermediate plate 13 is pressed by the screw element 14 against the contact element 12, whereby the contact element 12 is deformed. In order to apply the force required for this, the screw element 14 is screwed in with an internal thread 15, which is formed on the inside of the valve housing 2.
  • a piezoelectric actuator 21 rests on the inflow-side end face 20 of the intermediate plate 13, and a compression spring 23 rests on the sealing face-side end face of the intermediate plate 13.
  • the actuator 21 and the compression spring 23 are enclosed by a tubular housing wall 24, the tubular housing wall 24 having cutouts 25a, 25b through which the intermediate plate 13 projects.
  • the tubular housing wall 24 is connected to a housing plate 25 on the inflow side and a housing plate 26 on the sealing seat side.
  • the tubular housing wall 24, the inflow-side housing plate 25 and the sealing seat-side housing plate 26 together form an inner housing 24, 25, 26.
  • the actuator 21 acts via the inflow-side housing plate 25 on the inner housing 24, 25, 26 and the compression spring 23 acts via the sealing seat side Housing plate 26 on the inner housing 24, 25, 26 em.
  • the valve seat 4 is fastened on the sealing seat side housing plate 26.
  • the fuel is passed through a bore 30 in the end plate 3 into the interior 16 of the fuel injector 1. From there it is passed through at least one bore 31 in the intermediate plate 13 in the direction of the sealing seat formed from valve seat surface 7 and valve closing body 5.
  • the actuator 21 When the actuator 21 is actuated, it expands, as a result of which the inner housing 24, 25, 26 moves in the direction of the end plate 3 and lifts the valve closing member 5 attached to the valve needle 4 from the valve seat surface 7, as a result of which the sealing seat opens.
  • Fuel enters an injection channel 32 via the gap formed between valve seat surface 7 and valve closing element 5, as a result of which fuel emerges from fuel injection valve 1 into a combustion chamber of an internal combustion engine.
  • the fuel injector 1 is closed via the compression spring 23, which acts against the actuator 21 on the inner housing 24, 25, 26, as a result of which the inner housing 24, 25, 26 shifts in the direction of the valve seat body 6 and the valve closing body 5 of the valve needle 4 on the Valve seat surface 7 of the valve seat body 6 is moved. As a result, the sealing seat formed from valve seat surface 7 and valve closing body 5 closes.
  • the electromagnetic damping device according to the invention for damping the movement of the valve needle 4 is formed from sleeves 40a to 40c and an excitation coil 41, which is wound in a circumferential groove 42 on the valve housing 2 of the fuel injection valve 1.
  • the movement of the valve needle 4 is usually limited by a suitable stop.
  • this is Limitation simplified represented by the stop of the inflow-side housing plate 25 on stop elements 43a, 43b.
  • the valve closing body 5 of the valve needle 4 strikes the valve seat surface 7 of the valve seat body 6.
  • the valve needle 4 bounces because of the movement impulse that occurs when opening or closing, as a result of which the sealing seat is not opened with a constant opening cross section or is not closed abruptly.
  • the sleeves 40a to 40c are electrically insulated from the valve needle 4 and from each other. This isolation can e.g. B. done by a paint or an oxide layer. If the space around the sleeves 40a to 40c is filled with fuel, a suitable sealing of the sleeves against the fuel can be provided. Alternatively, it is possible to manufacture the sleeves 40a to 40c from a material which has a higher electrical conductivity than the valve needle 4.
  • FIG. 2 shows a circuit diagram, which represents the wiring of the actuator 21 and the excitation coil 41 in a simplified manner.
  • electrical feed lines 50a, 50b m the fuel injection valve 1 are guided to the actuator 21.
  • electrical feed lines 50c, 50d m lead the fuel injection valve 1 to the excitation coil 41.
  • the electrical feed lines 50a to 50d are connected to the control unit 51. It is advantageous if the control device 51 controls the coil 41 in a current-controlled manner, since this counteracts the coil inductivity 11 when the current intensity I L changes due to a correspondingly high voltage of the control device 51, which is supplied to the coil 41 via the electrical leads 50c, 50d can be.
  • the control device 51 makes it possible, depending on the operating variables of the internal combustion engine, to actuate the actuator 21 and the coil 41 in a coordinated manner in order to prevent the valve needle 4 from bouncing.
  • Fig. 3 is a schematic diagram to explain the functional principle of the damping device of the
  • Excitation coil 41 flowing current I L generates em radially symmetrical magnetic field B, which is proportional to
  • Coil current I L is.
  • the finite length 1 L of the coil 41 m in the axial direction results in an inhomogeneous magnetic field
  • Spulenach.se 55 is present for a change in location m of the order of length 1 L of the coil 41.
  • an induction loop 56 which represents the edge of a surface A which is not necessarily flat.
  • One of the two sides of the area A can be arbitrarily defined as
  • Induction loop 56 changed. According to Faraday's law of induction, a temporal change in the magnetic flux ⁇ flowing through the induction loop 56 creates an electrical m opposite the direction of rotation 58 of the induction loop 56 in the induction loop 56
  • Induction loop 56 an electrical current that at
  • em magnetic field B 1 is generated.
  • the magnetic field B ' is oriented in the opposite (same) direction as the magnetic field B.
  • oppositely directed magnetic fields B, B 1 the induction loop 56 is repelled by the excitation coil 41, with unidirectional magnetic fields B, B ', the induction loop 56 is attracted by the excitation coil 41.
  • the induction loop 56 when the magnetic flux ⁇ increases, the induction loop 56 is repelled by the excitation coil 41 and when the magnetic flux ⁇ decreases, the induction loop 56 is attracted by the excitation coil 41.
  • the associated force K 0 is used according to the invention for damping the valve needle 4.
  • FIG. 4 shows diagrams by means of which the functioning of the damping device of the fuel injector 1 according to the invention is explained.
  • the time t is in each case on the abscissa and the various operating variables of the are in the ordinates
  • Fuel injector 1 applied. For the sake of simplicity, only the closing process of the fuel injection valve 1 is considered below. The mode of operation of the damping device of the fuel injection valve 1 can accordingly be transferred to the opening process.
  • the actuator 21 In the open state of the fuel injector 1, the actuator 21 is acted upon by an electrical actuator voltage U A until the time t a . Since the actuator voltage U A is constant up to the point in time t a , the position of the valve needle 4 also remains unchanged, which corresponds to a constant valve needle stroke h.
  • the actuator 21 is switched off. From time t a to time t ⁇ the fuel injector 1 is closed, whereby the stroke h of the valve needle 4 decreases. In an undamped fuel injector 1, the valve needle 4 bounces, causing the valve needle 4 to come out the sealing seat is lifted, which corresponds to additional lifting movements 60a to 60d.
  • FIG. 5 shows an alternative circuit for wiring the fuel injection valve 1 according to the invention, in which the excitation coil 41 is connected in series with the actuator 21 in order to utilize the displacement current generated when the actuator 21 is compressed.
  • An equivalent circuit diagram consisting of a loss-free inductance L and a loss resistor R L is shown for the excitation coil 41, while an equivalent circuit diagram consisting of a loss-free capacitance C and a loss resistor R A is shown for the actuator 21.
  • the function of the damping device according to the invention is shown on the basis of the diagrams shown in FIG. 6 when it is connected as in FIG. 5.
  • the opening of the fuel injection valve 1 is considered.
  • the functional principle can also be applied to the closing of the fuel injection valve 1.
  • the time t is plotted on the abscissa in the diagrams.
  • the voltage U is increased at time ti to time t 2 .
  • the stroke h of the valve needle 4 increases.
  • the valve needle 4 bounces after opening the fuel injection valve 1, as a result of which additional valve needle strokes 60a to 60c occur.
  • the induction current m of the induction loop 56 ie the sleeves 40a to 40c, is generated.
  • the valve needle 4 is damped by the induction current I ⁇ nc ⁇ .
  • the time course of the stroke h 1 of the valve needle 4 therefore has no additional valve needle lifts 60a to 60c, which are caused by bouncing the valve needle 4. At most, therefore, there is an additional weak valve needle stroke 60e.
  • the invention is not limited to the exemplary embodiments described.
  • the invention is also suitable for an externally opening fuel injection valve 1.
  • the damping device does not necessarily have to act directly on the valve needle 4 and can also be arranged differently in the fuel injection valve 1.
  • At the Valve needle 4 can also be arranged instead of an induction loop 56, a permanent magnet which, together with the excitation coil 41, forms an electromagnetic damping device.
  • the induction loop 56 can also be formed by a wound coil instead of sleeves 40a-40c.

Abstract

L'invention concerne une soupape d'injection de carburant (1), notamment une soupape d'injection destinée à des systèmes d'injection de carburant de moteurs à combustion interne. Cette soupape présente un actionneur piézoélectrique ou magnétostrictif (21) ainsi qu'un obturateur de soupape (5) pouvant être actionné par l'actionneur (21) au moyen d'un pointeau (4) et coopérant avec une surface de siège de soupape (7 ) pour former un siège d'étanchéité. Une unité d'amortissement électromagnétique (40, 41) sert à amortir le mouvement du pointeau (4).
EP99962124A 1999-05-08 1999-12-02 Soupape d'injection de carburant Expired - Lifetime EP1095215B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19921489A DE19921489A1 (de) 1999-05-08 1999-05-08 Brennstoffeinspritzventil
DE19921489 1999-05-08
PCT/DE1999/003869 WO2000068564A1 (fr) 1999-05-08 1999-12-02 Soupape d'injection de carburant

Publications (2)

Publication Number Publication Date
EP1095215A1 true EP1095215A1 (fr) 2001-05-02
EP1095215B1 EP1095215B1 (fr) 2004-08-11

Family

ID=7907576

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99962124A Expired - Lifetime EP1095215B1 (fr) 1999-05-08 1999-12-02 Soupape d'injection de carburant

Country Status (5)

Country Link
US (1) US6612539B1 (fr)
EP (1) EP1095215B1 (fr)
JP (1) JP2002544426A (fr)
DE (2) DE19921489A1 (fr)
WO (1) WO2000068564A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003016707A1 (fr) * 2001-08-08 2003-02-27 Siemens Aktiengesellschaft Dispositif de dosage
DE10153630A1 (de) * 2001-10-31 2003-07-10 Bosch Gmbh Robert Brennstoffeinspritzventil
US7131423B2 (en) * 2004-10-06 2006-11-07 Point-Man Aeronautics, L.L.C. Fuel injection spark ignition system
FR2916810B1 (fr) * 2007-05-31 2009-08-28 Renault Sas Dispositif d'injection de fluide
US20090057438A1 (en) * 2007-08-28 2009-03-05 Advanced Propulsion Technologies, Inc. Ultrasonically activated fuel injector needle
WO2009158147A1 (fr) * 2008-06-27 2009-12-30 Cameron International Corporation Systèmes et dispositifs comprenant des vannes connectées à des dispositifs électriques et procédés pour réaliser, utiliser et faire fonctionner ceux-ci
US8069836B2 (en) * 2009-03-11 2011-12-06 Point-Man Aeronautics, Llc Fuel injection stream parallel opposed multiple electrode spark gap for fuel injector
US20130068200A1 (en) * 2011-09-15 2013-03-21 Paul Reynolds Injector Valve with Miniscule Actuator Displacement
US9115678B2 (en) 2012-08-09 2015-08-25 Ford Global Technologies, Llc Magnetized fuel injector valve and valve seat
EP2860386A1 (fr) * 2013-10-10 2015-04-15 Continental Automotive GmbH Injecteur pour moteur à combustion
US9157349B2 (en) * 2014-03-04 2015-10-13 Ali Farzad Farzaneh High power two cycle engine (without oil and gasoline/benzene mixing)
DE102015219568B4 (de) * 2015-10-09 2017-06-08 Continental Automotive Gmbh Aktuator mit Ventileinheit für piezoservobetriebenen Injektor

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Publication number Priority date Publication date Assignee Title
DE3501077A1 (de) * 1985-01-15 1986-07-17 Kernforschungszentrum Karlsruhe Gmbh, 7500 Karlsruhe Pulsventil
JPS61167364A (ja) * 1985-01-18 1986-07-29 Diesel Kiki Co Ltd 高速電磁弁
DE3533975A1 (de) * 1985-09-24 1987-03-26 Bosch Gmbh Robert Zumessventil zur dosierung von fluessigkeiten oder gasen
JPS63143361A (ja) * 1986-12-04 1988-06-15 Aisan Ind Co Ltd インジエクタ用バルブの制御方法
US4878650A (en) * 1988-04-29 1989-11-07 Allied-Signal Inc. Armature with shear stress damper
DE3833093A1 (de) * 1988-09-29 1990-04-12 Siemens Ag Fuer verbrennungskraftmaschine vorgesehene kraftstoff-einspritzduese mit steuerbarer charakteristik des kraftstoffstrahls
US4994698A (en) * 1990-06-13 1991-02-19 General Electric Company Vibratory linear motor system
DE19546033A1 (de) 1995-12-09 1997-06-12 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19735232A1 (de) * 1997-08-14 1999-02-18 Bosch Gmbh Robert Verfahren zur Dämpfung eines Brennstoffeinspritzventiles und Brennstoffeinspritzventil

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Title
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Also Published As

Publication number Publication date
EP1095215B1 (fr) 2004-08-11
DE59910219D1 (de) 2004-09-16
WO2000068564A1 (fr) 2000-11-16
US6612539B1 (en) 2003-09-02
JP2002544426A (ja) 2002-12-24
DE19921489A1 (de) 2000-11-09

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