EP1693564A2 - Injecteur de carburant à commande de pointeau directe pour un moteur à combustion interne - Google Patents

Injecteur de carburant à commande de pointeau directe pour un moteur à combustion interne Download PDF

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Publication number
EP1693564A2
EP1693564A2 EP05112526A EP05112526A EP1693564A2 EP 1693564 A2 EP1693564 A2 EP 1693564A2 EP 05112526 A EP05112526 A EP 05112526A EP 05112526 A EP05112526 A EP 05112526A EP 1693564 A2 EP1693564 A2 EP 1693564A2
Authority
EP
European Patent Office
Prior art keywords
actuator
nozzle needle
control
piston
fuel injector
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
EP05112526A
Other languages
German (de)
English (en)
Other versions
EP1693564A3 (fr
EP1693564B1 (fr
Inventor
Rudolf Heinz
Andreas Rau
Andreas Bartsch
Christian Kuhnert
Stefan Schuerg
Wolfgang Stoecklein
Michael Mennicken
Holger Rapp
Thomas Kuegler
Hans-Christoph Magel
Andreas Wengert
Thomas Pauer
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 EP1693564A2 publication Critical patent/EP1693564A2/fr
Publication of EP1693564A3 publication Critical patent/EP1693564A3/fr
Application granted granted Critical
Publication of EP1693564B1 publication Critical patent/EP1693564B1/fr
Not-in-force 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
    • 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

Definitions

  • the invention relates to a fuel injector with direct needle control for an internal combustion engine according to the preamble of claim 1.
  • Fuel injectors with a so-called direct needle control are known. Such fuel injectors come without an intermediate control valve between an electrically actuated actuator and a nozzle needle. The power transmission between the actuator and the nozzle needle is realized by means of a hydraulic coupler or hydraulic translator.
  • piezoelectric actuators are suitable as actuators, which, depending on the energization in the closed state, have a direct or inverse control. In a direct control of the piezoelectric actuator is energized to open the nozzle needle, so that a linear expansion of the piezoelectric actuator realized by a pressing movement opening the injectors, which is amplified by the translator. In the closed state, the piezoelectric actuator has a smaller linear expansion.
  • the piezo actuator In the case of inverse activation, the piezo actuator is charged in the closed state of the nozzle needle, so that the piezo actuator keeps the nozzle needle closed in the state of its longitudinal expansion.
  • the piezoactuator When the piezoactuator is actuated, the piezoactuator is discharged to initiate the injection process, so that a pressure relief takes place by a pulling movement of the piezoactuator in a control space of the hydraulic booster. As a result, the lifting movement of the piezo actuator is hydraulically translated to open the nozzle needle.
  • a fuel injector with direct needle control is already proposed in DE patent application 10 2004 037 125.3.
  • the fuel injector in this case has an actuator-side booster piston and a nozzle needle-side booster piston, wherein the actuator-side booster piston is assigned to an actuator-side coupler space and the nozzle needle-side booster piston is assigned to a nozzle needle-side coupler space.
  • a hydraulic throttle device is provided, which has different flow cross-sections for the inflow or outflow of fuel into and out of the nozzle needle-side control chamber.
  • a first slide sleeve for limiting the actuator-side coupler space and the nozzle needle-side booster piston, a further slide sleeve for limiting the nozzle needle-side coupler space is guided axially.
  • the pusher sleeves are biased by a compression spring so that they press with one end face against a sealing surface. The use of the pusher sleeves allows axial decoupling of the actuator-side and the nozzle needle-side booster piston, whereby the booster piston can be mounted with an axial offset.
  • the object of the present invention is to provide a fuel injector with two-stage transmission with different transmission ratios.
  • the object of the invention is achieved with the characterizing features of claim 1.
  • a fuel injector with direct needle control with compact and small size can be realized, which manages with few moving components to realize the required ratios for a two-stage translation.
  • a two-stage gear ratio of the Aktorhubs with different ratios can be realized particularly useful if in a first opening phase of the nozzle needle, the control is applied by the voltage applied to its control surfaces pressures in a starting position and at the beginning of a second opening phase of the nozzle needle due to the changing pressure conditions on the control surfaces of the control, the control lifts from the starting position, so that increases the volume in the actuator-side coupler space, whereby the translation between aktor discoveredem and nozzle-side booster piston is changed.
  • the control chamber acts as a pressure or energy storage, so that formed to initiate the second opening phase, a pressure threshold in the control room.
  • an axially displaceably guided control sleeve is arranged as a control element on the actuator-side booster piston whose first end face is hydraulically coupled as first control surface to the actuator-side coupler space and whose second end face is assigned to the control chamber as second control surface.
  • the first end face is in relation to a first opening phase of the nozzle needle in an initial position.
  • the first end face lifts off from the starting position, so that with respect to the second opening phase of the nozzle needle an effective surface is exposed to the actuator-side coupler space, which is composed of the pressure surface of the booster piston and the first end face.
  • the actuator-side booster piston is a stepped piston, with which the first pressure surface and the second pressure surface are formed.
  • An expedient embodiment of the fuel injector also consists in that the coupler space assigned to the actuator-side pressure booster piston is connected via a hydraulic connection to a nozzle needle-side coupler space assigned to the nozzle needle-side booster piston.
  • a slide sleeve is guided on the actuator-side booster piston.
  • the fuel injector shown in Figure 1 has an injector 10 with a nozzle body 11 which projects with its lower end into a combustion chamber of an internal combustion engine.
  • a nozzle needle guide 12 is formed, in which a nozzle needle 13 is guided with a guide portion 14 axially displaceable.
  • a sealing seat 15 is formed, which are arranged downstream of the injection nozzle 16 formed in the nozzle body 11 and projecting into the combustion chamber.
  • the injector housing 10 has a receiving space 18 which is connected to a fuel feed, not shown, which is connected to a high-pressure system, for example to a common-rail system of a diesel injection device.
  • an intermediate body 19 with an actuator-side surface 23 and a nozzle needle-side surface 24 is arranged, which is designed with connecting bores 21 and with a hydraulic connection acting as a throttle 22.
  • the connecting bores 21 serve to forward the fuel introduced into the receiving space 18 via the fuel supply at high pressure into a high-pressure space 25 assigned to the nozzle needle 13.
  • a piezoelectric actuator 20 is arranged, which acts on a hydraulic booster 30.
  • the hydraulic booster 30 has an actuator-side booster piston 31 which is drive-coupled to the piezo-actuator 20 and which is also housed in the receiving space 18.
  • the actuator-side booster piston 31 is designed as a stepped piston with a first piston portion 32 with a diameter d1 and with a second piston portion 33 with a diameter d2, where d2> d1.
  • the hydraulic booster 30 further comprises a second piston portion 33 axially guided sliding sleeve 34, an axially between the sleeve 34 and the first piston portion 32 axially guided control sleeve 35, an actuator-side coupler 36 and a control chamber 37.
  • a coupling surface-side pressure surface 38 is formed in accordance with Figure 2, which faces into the actuator-side coupler space 36. Due to the diameter ratio d1 ⁇ d2 between the first piston section 32 and the second piston section 33, there is an annular surface with a second pressure surface 48 on the second piston section 33 which points into the control chamber 37 as a further control surface.
  • the control sleeve 35 has the function of a control element 40, which is generally described in connection with Figure 3.
  • the control sleeve 35 has a first end face 44 and a second end face 45 and is biased by a compression spring 43 on the actuator-side booster piston 31.
  • the compression spring 43 causes the control sleeve 35 is held until the initiation of the second opening phase of the nozzle needle 13 in an initial position.
  • the control sleeve 35 is pressed with the first end face 44 against the actuator-side surface 23 of the intermediate body 19, so that the control sleeve 35 limits the actuator-side coupler space 36 in this position.
  • the first end face 44 forms a hydraulically coupled first control surface 47 with the actuator-side coupler space 36.
  • the second end face 45 which is formed opposite the end face 44 on the control sleeve 35, points into the control space 37 and forms a second control surface 46 with respect to the control space 37 the control sleeve 35.
  • the slide sleeve 34 is also biased by a further compression spring 49 on the actuator-side booster piston 31. As a result, the sliding sleeve 34 according to FIG. 2 is pressed against the actuator-side surface 23 of the intermediate body 19 with an end face 42, so that a sealing surface forms on the surface 23.
  • To the hydraulic translator 30 further includes a connected to the nozzle needle 13 nozzle needle-side booster piston 51 having a diameter d3, which has a nozzle needle-side pressure surface 52 in a nozzle needle-side coupler 53.
  • a further slide sleeve 54 is guided axially, which is pressed by means of a closing spring 56 against the nozzle needle-side surface 24 of the intermediate body 19 and so the nozzle needle-side coupler space 53 limited.
  • the nozzle needle-side coupler space 53 is connected to the actuator-side coupler space 36 via the hydraulic connection 22.
  • the hydraulic connection 22 can act as a throttle.
  • the sealing seat 15 of the nozzle needle 13 is closed.
  • the system pressure which has reached the receiving space 18 and the pressure space 25 via the fuel supply, equally rests in all pressure chambers.
  • 35 leakage gaps are present on the slide sleeves 34, 54 and the control sleeve, such that the system pressure is present in the actuator-side coupler space 36, in the control space 37 and in the nozzle needle-side coupler space 53 via the leakage gaps.
  • the hydraulic booster 30 is pressure compensated.
  • the piezoelectric actuator 20 is supplied with a voltage, whereby the piezoelectric actuator 20 is elongated in its loaded state in the vertical direction.
  • the system pressure applied in the nozzle needle-side coupler chamber 53 acts in the closing direction on the nozzle needle-side booster piston 51.
  • the sealing seat 15 of the nozzle needle 13 is closed in this state of the piezoelectric actuator 20.
  • the closing spring 56 acts on the nozzle needle, the closing spring 56 which holds the nozzle needle 13 closed in the idle state.
  • the length of the piezoelectric actuator 20 in the vertical direction is likewise reduced.
  • the piezo actuator 20 is thus operated inversely. Due to the biased by the compression spring 49 in the direction of the piezoelectric actuator 20 actuator-side booster piston 31 this is also moved in the vertical direction due to the reduced vertical length of the piezo-actuator 20.
  • the opening pressure is transmitted via the hydraulic connection 22 into the nozzle needle-side coupler space 53, so that the opening pressure also bears against the nozzle needle-side pressure surface 52.
  • a first gear ratio for opening the nozzle needle 13 is introduced, which is effective due to the area ratios of the pressure surfaces 38 and 52, wherein the gear ratio of the first opening phase by the area ratio d1 2 / d3 2 is determined.
  • the volume in the control chamber 37 is increased by the second piston portion 33 and pointing in the control chamber 37 upward movement of the second pressure surface 48, whereby the pressure drops in the control chamber 37.
  • the control chamber 37 acts as a pressure accumulator or energy storage in the form of a hydraulic spring.
  • the actuator-side coupler space 36 is thus exposed to an effective pressure surface, which is composed of the actuator-side pressure surface 38 of the first piston portion 32 and the first end surface 44 of the control sleeve 35.
  • an effective pressure surface which is composed of the actuator-side pressure surface 38 of the first piston portion 32 and the first end surface 44 of the control sleeve 35.
  • the inner diameter of the slide sleeve 34 is guided on the diameter d2 of the second piston portion 33 and the control sleeve 35 between the slide sleeve 34 and the first piston portion 32 is arranged, wherein the outer diameter of the control sleeve 35 is guided on the inner diameter of the slide sleeve 34, the composite effective pressure surface determined by the outer diameter of the control sleeve 35, which corresponds to the diameter d2.
  • the composite effective pressure surface causes a translation jump, which acts as a second gear ratio on the nozzle needle side pressure surface 52 of the nozzle needle side booster piston 51.
  • the stroke of the piezoactuator 20 is transmitted to the nozzle needle 13 with a larger ratio, which results from the area ratios of the composite effective pressure surface to the pressure surface 52, wherein the second transmission ratio is determined by the area ratios d2 2 / d3 2 .
  • the nozzle needle 13 is moved at a greater speed and with a larger stroke.
  • control element 40 which is shown as a piston remains due to the pressure prevailing in the control chamber 37 initially in one starting position.
  • the compression spring 43 acts only supportive.
  • the pressure in the control chamber 37 is further reduced by means of the second piston section 33 until the pressure applied in the space 36 'is fallen below.
  • the control element 40 with the area A1 which corresponds to the first control surface 47, emotional.
  • the pulling movement of the surface A1 creates an additional volume in the space 36 ', which also becomes effective via the connection 22' in the actuator-side coupler space 36.
  • the additional volume is transmitted via the connection 22 to the nozzle needle-side coupler space 53, so that the surface A4 of the nozzle needle-side booster piston 51 now faces the sum of the areas A1 and A3 as the ratio for realizing the second opening phase.
  • the gear ratio of the second opening phase (A1 + A3) to A4 is thus greater than the ratio of the first opening phase resulting from the ratio of A3 to A4. Due to the larger transmission ratio of the second opening phase, a larger opening speed is realized with a larger stroke when opening the nozzle needle 13.
  • the first piston portion 32 with the pressure surface 38 increases the pressure in the actuator-side coupler space 36, which is transmitted via the hydraulic connection 22 to the nozzle needle-side coupler space 53, wherein the nozzle needle 13 on the sealing seat due to the pressure increase in the nozzle needle-side coupler space 53 by means of the nozzle needle side booster piston 51 15 is pressed and thereby the injection nozzles 16 are separated from the pressure chamber 25.
  • a pressure-balanced state is again formed in the pressure chambers of the hydraulic booster 30.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
EP05112526A 2005-02-18 2005-12-20 Injecteur de carburant à commande de pointeau directe pour un moteur à combustion interne Not-in-force EP1693564B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005007543A DE102005007543A1 (de) 2005-02-18 2005-02-18 Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP1693564A2 true EP1693564A2 (fr) 2006-08-23
EP1693564A3 EP1693564A3 (fr) 2007-01-10
EP1693564B1 EP1693564B1 (fr) 2008-07-23

Family

ID=36337484

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05112526A Not-in-force EP1693564B1 (fr) 2005-02-18 2005-12-20 Injecteur de carburant à commande de pointeau directe pour un moteur à combustion interne

Country Status (4)

Country Link
US (1) US7258283B2 (fr)
EP (1) EP1693564B1 (fr)
AT (1) ATE402337T1 (fr)
DE (2) DE102005007543A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008086941A1 (fr) * 2007-01-16 2008-07-24 Robert Bosch Gmbh Injecteur de carburant à coupleur
WO2009086997A1 (fr) * 2008-01-10 2009-07-16 Robert Bosch Gmbh Injecteur de combustible
EP2949918A1 (fr) * 2014-05-27 2015-12-02 Robert Bosch Gmbh Injecteur de carburant

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10352736A1 (de) * 2003-11-12 2005-07-07 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadeleinspritzung
DE102005015735A1 (de) * 2005-04-06 2006-10-12 Robert Bosch Gmbh Brennstoffeinspritzventil
JP4459183B2 (ja) * 2006-03-16 2010-04-28 株式会社デンソー インジェクタ
ATE511014T1 (de) * 2006-03-20 2011-06-15 Delphi Tech Holding Sarl Dämpfungsanordnung für ein einspritzventil
EP1837515A1 (fr) * 2006-03-20 2007-09-26 Delphi Technologies, Inc. Dispositif d'amortissement pour un injecteur de carburant
DE102006048979B8 (de) * 2006-10-17 2017-02-23 Continental Automotive Gmbh Verfahren und Einspritzsystem zum Einspritzen eines Fluids
DE102007002278A1 (de) * 2007-01-16 2008-07-17 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff
US8201543B2 (en) * 2009-05-14 2012-06-19 Cummins Intellectual Properties, Inc. Piezoelectric direct acting fuel injector with hydraulic link
WO2010144559A2 (fr) * 2009-06-10 2010-12-16 Cummins Intellectual Properties, Inc. Injecteur de carburant par action directe piézoélectrique avec liaison hydraulique
US8500036B2 (en) 2010-05-07 2013-08-06 Caterpillar Inc. Hydraulically amplified mechanical coupling
US9284930B2 (en) 2011-06-03 2016-03-15 Michael R. Harwood High pressure piezoelectric fuel injector
DE102012212614A1 (de) 2012-07-18 2014-01-23 Continental Automotive Gmbh Piezoinjektor mit hydraulisch gekoppelter Düsennadelbewegung
DE102012222509A1 (de) 2012-12-07 2014-06-12 Continental Automotive Gmbh Piezoinjektor
DE102012223934B4 (de) * 2012-12-20 2015-10-15 Continental Automotive Gmbh Piezoinjektor
DE102013210843A1 (de) * 2013-06-11 2014-12-11 Continental Automotive Gmbh Injektor
US10006429B2 (en) * 2016-03-31 2018-06-26 GM Global Technology Operations LLC Variable-area poppet nozzle actuator

Citations (1)

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DE102004037125A1 (de) 2004-07-30 2006-03-23 Robert Bosch Gmbh Common-Rail-Injektor

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US5505384A (en) * 1994-06-28 1996-04-09 Caterpillar Inc. Rate shaping control valve for fuel injection nozzle
US6520423B1 (en) * 2000-03-21 2003-02-18 Delphi Technologies, Inc. Hydraulic intensifier assembly for a piezoelectric actuated fuel injector
EP1174615B1 (fr) * 2000-07-18 2007-01-31 Delphi Technologies, Inc. Injecteur de combustible
DE10148594A1 (de) * 2001-10-02 2003-04-10 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10160263A1 (de) * 2001-12-07 2003-06-18 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10251679A1 (de) * 2002-11-07 2004-05-19 Robert Bosch Gmbh Druckverstärker mit hubabhängiger Bedämpfung
DE10326259A1 (de) * 2003-06-11 2005-01-05 Robert Bosch Gmbh Injektor für Kraftstoff-Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren
DE10333696A1 (de) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE102004062006A1 (de) * 2004-12-23 2006-07-13 Robert Bosch Gmbh Kraftstoffinjektor mit direkt angesteuertem Einspritzventilglied

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004037125A1 (de) 2004-07-30 2006-03-23 Robert Bosch Gmbh Common-Rail-Injektor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008086941A1 (fr) * 2007-01-16 2008-07-24 Robert Bosch Gmbh Injecteur de carburant à coupleur
US7992810B2 (en) 2007-01-16 2011-08-09 Robert Bosch Gmbh Fuel injector with coupler
WO2009086997A1 (fr) * 2008-01-10 2009-07-16 Robert Bosch Gmbh Injecteur de combustible
EP2949918A1 (fr) * 2014-05-27 2015-12-02 Robert Bosch Gmbh Injecteur de carburant

Also Published As

Publication number Publication date
DE102005007543A1 (de) 2006-08-24
US20060186221A1 (en) 2006-08-24
EP1693564A3 (fr) 2007-01-10
EP1693564B1 (fr) 2008-07-23
US7258283B2 (en) 2007-08-21
DE502005004797D1 (de) 2008-09-04
ATE402337T1 (de) 2008-08-15

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