WO2011069706A1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
WO2011069706A1
WO2011069706A1 PCT/EP2010/064962 EP2010064962W WO2011069706A1 WO 2011069706 A1 WO2011069706 A1 WO 2011069706A1 EP 2010064962 W EP2010064962 W EP 2010064962W WO 2011069706 A1 WO2011069706 A1 WO 2011069706A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve member
injection valve
fuel injector
hydraulic
hydraulic booster
Prior art date
Application number
PCT/EP2010/064962
Other languages
German (de)
English (en)
Inventor
Armin Schuelke
Olaf Ohlhafer
Uwe Iben
Robert Giezendanner-Thoben
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
Priority to EP10768434.2A priority Critical patent/EP2510215B1/fr
Publication of WO2011069706A1 publication Critical patent/WO2011069706A1/fr

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
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic 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 for injecting fuel into a combustion chamber of an internal combustion engine having a magnetic actuator for direct control of a preferably needle-shaped injection valve member, via the lifting movement at least one injection port of the fuel injector is releasable or closable, according to the preamble of claim 1.
  • the control of the injection valve member is as a rule indirect, in that a control pressure present in a control chamber is lowered.
  • a disadvantage of such an injector concept proves that to lower the control chamber pressure, a certain amount of control must be dissipated in a low-pressure fuel return. This in turn requires an increased capacity of the upstream high-pressure pump, which promotes the discharged control amount back to high pressure.
  • indirectly controlled fuel injectors compared to directly controlled fuel injectors inherently a delayed response of the injection valve member on.
  • injector concepts known from the prior art which provide for the use of piezoelectric actuators. Because the use of a Magnetaktors would to open the injection valve member at Rail Treat of over 2000 bar require a large magnetic actuator to realize the necessary force.
  • the object of the present invention is to provide a fuel injector with a solenoid actuator for actuating the injection valve member, which allows a return flow-free di rect control of the injection valve member.
  • the proposed fuel injector should be compact and inexpensive to produce.
  • the proposed fuel injector comprises for direct control of a preferably needle-shaped injection valve member, a magnetic actuator with a liftable anchor element for controlling the control pressure in a control volume.
  • the fuel injector further comprises a hydraulic booster with a control volume limiting hydraulic effective area Ai, which is greater than a control volume limiting hydraulic effective area A 2 of the injection valve member and / or greater than a control volume limiting hydraulic active surface A 3 of the anchor element, said the hydraulic translator with the injection valve member or the anchor member is mechanically coupled such that the hydraulic active surface Ai of the hydraulic booster during a first phase of the lifting movement of the injection valve member causes a force boost and during a second phase of the lifting movement of the injection valve member switching to a path gain.
  • the two-phase sequence of the stroke movement of the injection valve member relates in particular to the opening stroke of the injection valve member for releasing the at least one injection opening.
  • a first phase of the opening stroke of the injection valve member the force which is required to overcome the pressure difference on the closed injection valve member and to lift the injection valve member out of its seat can be realized by means of a power boost while simultaneously reducing the stroke.
  • a pressure equal to the rail pressure builds up below the injection valve member, so that the force required to raise the injection valve member decreases.
  • this second phase of the opening stroke of the injection valve member can be switched to a Wegverstärkung - with simultaneous power reduction - to realize the need for complete seat throttling Düsennadelhub and this maximum injection pressures.
  • the switchover from a force amplification to a boost amplification is effected by a change in the area ratios of the respective hydraulic active surfaces which are relevant in relation to the control volume.
  • the direct control of the injection valve member via a magnetic actuator affects.
  • the direct control is carried out without backflow, which means that the return of a control and / or leakage volume is unnecessary, so that a reduction of the system outlay is possible.
  • a high-pressure pump with a lower flow rate can be used.
  • a directly controlled fuel injector can be made compact with a magnetic actuator, since a magnetic actuator requires less space than, for example, a piezoactuator.
  • magnetic actuators are more cost-effective than piezo actuators, so that a fuel injector according to the invention can furthermore be produced cost-effectively.
  • a stop surface for mechanical coupling of the hydraulic booster is formed on the injection valve member.
  • a stop surface for mechanical coupling of the hydraulic booster is formed at the anchorage ment.
  • a driver function is realized, which causes a change in the area ratios with respect to the respective control volume limiting hydraulic active surfaces and thus switching from a power gain during a first phase to a path gain during a second phase of the stroke of the injection valve member.
  • a stop surface for mechanical coupling of the hydraulic booster is formed on the injection valve member, which causes entrainment of the hydraulic booster only during the second phase of the lifting movement of the injection valve member. In this way, a path gain is realized during the second phase of the lifting movement.
  • an abutment surface for mechanical coupling of the hydraulic booster is formed on the anchor element, which also causes entrainment of the hydraulic booster during the second phase of the lifting movement of the injection valve member and thus a path gain.
  • a stop surface is formed on the injection valve member, which, however, causes entrainment of the injection valve member in a stroke movement of the hydraulic booster.
  • the entrainment takes place in this case during the first phase of the lifting movement of the injection valve member and serves to implement a power boost.
  • a stop is formed on a housing part of the fuel injector, which serves a one-sided effective stroke limitation of the hydraulic booster. If, for example, the hydraulic booster performs a lifting movement during the first phase of the lifting movement of the injection valve member, with which it carries the injection valve member, the changeover from a force amplification to a path reinforcement can be effected by striking the translator on the housing-side stop. Because the impact causes a positional fixation of the hydraulic translator, so that a change in the area ratios and thus switching from a power gain to a path gain during the second phase the lifting movement of the injection valve member takes place.
  • the housing-side stop can also serve to limit the stroke of the hydraulic translator when it is returned.
  • the hydraulic translator is designed as a liftable piston or as a liftable disc.
  • a central bore is formed in the hydraulic booster for partially receiving the injection valve member or the anchor member.
  • the hydraulic translator thus experiences a guide via the outer peripheral surface of the injection valve member or the anchor element.
  • a stop face adjoining the guide area can be realized in a simple manner on the injection valve member or on the anchor element by forming the adjacent area with a larger outer diameter.
  • a spring is particularly suitable a helical compression spring, which is supported on the one hand on the hydraulic booster and on the other hand on a housing part of the fuel injector or on the anchor member.
  • a spring can be used.
  • the arrangement of a spring allows automatic reset of the hydraulic booster without entrainment of the translator must take place in the closing direction of the injection valve member. On the other hand, it can be dispensed with a return spring when carried to return the hydraulic booster entrainment by the injection valve member or the anchor element.
  • the fuel injector preferably opens when the solenoid actuator is energized.
  • the energization of the magnetic actuator triggers first a lifting movement of the anchor element, which causes a pressure drop in the control volume and thus the opening stroke of the injection valve member according to a preferred embodiment.
  • the armature member and the injection valve member move in the same direction upon opening, the armature member "pulls" the injection valve member out of its sealing seat.
  • the lifting movement of the anchor element when the magnetic actuator is energized, causes a pressure change. increased in the control volume and thus the opening stroke of the injection valve member.
  • the direction of movement of the anchor element is opposite to that of the injection valve member.
  • the injection valve member is thus “pushed” out of its sealing seat.
  • a pressure stage with a hydraulic effective area A 2 is formed on the injection valve member, below which the control pressure is applied.
  • the injection valve member, the anchor element and the hydraulic booster are furthermore preferably arranged coaxially.
  • the fuel injector may further be configured such that the hydraulic booster can be coupled to the injection valve member or the anchor element.
  • the housing-side stop can also cause a stroke limitation of the hydraulic booster in the opening direction or closing direction of the injection valve member.
  • Fig. 3 is a schematic longitudinal section through a third embodiment
  • Fig. 4 is a schematic longitudinal section through a fourth embodiment.
  • All embodiments of a fuel injector according to the invention shown in FIGS. 1 to 4 have a magnetic actuator 1 for actuating an injection valve member 2.
  • the magnetic actuator 1 is arranged in each case in an injector body 16 of the fuel injector.
  • the injection valve member 2 is in each case guided in a liftable manner in a nozzle body 17 of the fuel injector, wherein for guiding the injection valve member 2, a guide region 18 may be provided in the nozzle body 17.
  • About the stroke movement of the injection valve member 2 is at least one injection port 3 of the fuel injector can be opened or closed.
  • each of the magnetic actuators 1 of the embodiments of FIGS. 1 to 4 has a liftably mounted anchor element 4.
  • the lifting movement of the armature element 4 causes a control pressure change in a control volume 5, so that a closing pressure applied to the injection valve member 2 is overcome and the injection valve member 2 is lifted out of its sealing seat.
  • the armature element 4 and the injection valve member 2 either the same direction of movement during opening and closing (see embodiments of FIGS. 1 and 2) or an opposite direction of movement ( see embodiments of FIGS. 3 and 4).
  • the latter is effected by the applied below the pressure stage 13 of the injection valve member 2 control volume 5, so that the injection valve member 2 is lifted above the rising control pressure in the control volume 5 from its sealing seat.
  • the pressure stage 13 thus forms a hydraulic effective area A 2 .
  • each fuel injector of the illustrated embodiments has a hydraulic booster 6 in the form of a liftable piston or a liftable disc.
  • the hydraulic booster 6 is mechanically coupled to the injection valve member 2 either via a stop surface 7 formed on the injection valve member 2 (see embodiments of FIGS. 1 and 4) or via an abutment surface 8 formed on the anchor member 4 (see embodiments of Figs. 2 and 3).
  • the components injection valve member 2, anchor member 4 and hydraulic booster 6 are each arranged coaxially.
  • the anchor element 4 in the closed state, the anchor element 4 is pressed against a dial 19 via a compression spring 15.
  • the shim 19 thus forms a stop for the anchor element 4 from here.
  • the anchor element 4 has a hydraulic active surface A 3 , which has a control volume. men 5 limited in an axial direction. In the other axial direction, the control volume 5 is limited by a hydraulic active surface A 2 of an injection valve member 2 and a hydraulic active surface Ai of a hydraulic booster 6.
  • a arranged in the control volume 5 closing spring 14 and the control pressure of the control volume 5 keep the injection valve member 2 pressed against the sealing seat.
  • the hydraulic booster 6 is present disc-shaped and equipped with a central bore 11 for receiving a guide portion of the injection valve member 2.
  • the hydraulic translator 6 is upwardly, that is arranged freely movable in the direction of the electromagnet of the magnetic actuator 1. If now the magnetic actuator 1 is energized, the armature element 4 is moved upward against the pressure force of the compression spring 15, that is to say again in the direction of the electromagnet of the magnetic actuator 1. In this case, the control volume 5 increases and a pressure drop is effected.
  • the selected surface ratios of the hydraulic active surfaces Ai, A 2 and A 3 determine the limit pressure, from which the injection valve member 2 lifts from its seat.
  • control volume 5 via a throttle 21 in hydraulic communication with a high-pressure line 20, via which the high-pressure fuel first formed in the nozzle body 17 pressure chamber and the guide portion 18 and a further annular Pressure chamber is supplied to the injection openings 3.
  • the energization of the solenoid actuator 1 is terminated, so that the armature element 4 is reset by the pressure force of the compression spring 15.
  • the immersed in the control chamber anchor element 4 reduces the control volume 5, which causes a pressure increase.
  • the increasing pressure and the pressing force of the closing spring 14, which is supported on the injection valve member 2 cause the injection valve member 2 is pressed against the sealing seat.
  • the hydraulic translator 6 is returned to its initial position on the stop surface 7 on the injection valve member 2.
  • a stop surface 8 is formed on the anchor element 4, which serves as a driver in the second phase of the lifting movement of the injection valve member 2.
  • the solenoid actuator 1 When the solenoid actuator 1 is energized, a stroke movement of the armature element 4, which increases the control volume 5, and thus a pressure drop, are again caused.
  • the hydraulic active surface A 3 of the anchor member 4 is initially opposite the larger hydraulic effective area A 2 of the injection valve member 2, whereby a force amplification takes place.
  • the injection valve member 2 is lifted from its sealing seat.
  • the hydraulic booster 6 is also mechanically coupled to the anchor element 4.
  • a stop surface 8 is designed as a driver on the anchor element 4. The entrainment takes place again in the second phase of the lifting movement of the injection valve member 2, to switch from a power gain to a path gain.
  • the control volume 5 is reduced by the lifting movement of the armature element 4, which results in a pressure increase.
  • the anchor element 4 is down, that is moved in the direction of the injection valve member 2.
  • control volume 5 in the present case is arranged below a pressure stage 13 on the injection valve member 2, that is, the hydraulic effective area A 2 is acted upon by the control pressure, the injection valve member 2 is lifted from its sealing seat due to the pressure increase.
  • the control volume 5 below the pressure stage 13 is connected via a connecting channel 22 in connection with the control volume 5, which is limited by the hydraulic booster 6 and the anchor element 4.
  • a throttle 21 there is a connection to the high-pressure line 20 via a throttle 21 in order to ensure a rail pressure compensation with a changed rail pressure.
  • the throttle 21 may be omitted with suitable leakage to the guides that lead away from or to a control volume 5 limiting pressure chamber or out.
  • the energization of the magnetic actuator 1 is terminated and the anchor element 4 is reset by the pressure force of the compression spring 15.
  • the spring 12 has the same effect based on the hydraulic booster 6. In this case, the control volume 5 increases and the pressure decreases, so that finally the closing spring 14 causes the closing stroke of the injection valve member 2.
  • the "pushing" actuator principle is likewise realized, ie, when the magnetic actuator 1 is energized by the lifting movement of the armature element 4, the control volume 5 is reduced, so that the pressure rises on a hydraulic active surface Ai of a hydraulic booster 6 and a hydraulic active surface A 2 of a pressure stage 13 at the injection valve member 2 applied pressure, so that they move against the pressure force of the springs 12 and 14 upwards, that is in the direction of the electromagnet of the magnetic actuator 1.
  • the injection valve member 2 and the hydraulic booster 6 are mechanically coupled via an abutment surface 7, so that in a first phase of the lifting movement the hydraulic booster 6 carries the injection valve member 2.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un injecteur de carburant pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion interne, présentant un actionneur magnétique (1) pour la commande directe d'un élément de soupape d'injection (2) de préférence en forme d'aiguille, par le mouvement de levée duquel au moins une ouverture d'injection (3) de l'injecteur de carburant peut être libérée ou fermée, l'actionneur magnétique (1) comprenant un élément d'induit (4) mobile en levée, pour la commande de la pression de commande dans un volume de commande (5). Selon l'invention, l'injecteur de carburant comprend également un dispositif de transmission hydraulique (6) avec une surface active A1 hydraulique limitant le volume de commande (5), qui est supérieure à une surface active A2 hydraulique limitant le volume de commande (5), de l'élément de soupape d'injection (2) et/ou est supérieure à une surface active A3 hydraulique, limitant le volume de commande (5), de l'élément d'induit (4), le dispositif de transmission hydraulique (6) pouvant être couplé mécaniquement avec l'élément de soupape d'injection (2) ou l'élément d'induit (4) de telle sorte que la surface active A1 hydraulique de l'élément de transmission hydraulique (6) entraîne une amplification de force pendant une première phase du mouvement de levée de l'élément de soupape d'injection (2) et une amplification de course pendant une seconde phase du mouvement de levée de l'élément de soupape d'injection (2).
PCT/EP2010/064962 2009-12-07 2010-10-07 Injecteur de carburant WO2011069706A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10768434.2A EP2510215B1 (fr) 2009-12-07 2010-10-07 Injecteur de carburant

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009047559.1 2009-12-07
DE200910047559 DE102009047559A1 (de) 2009-12-07 2009-12-07 Kraftstoffinjektor

Publications (1)

Publication Number Publication Date
WO2011069706A1 true WO2011069706A1 (fr) 2011-06-16

Family

ID=43243687

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/064962 WO2011069706A1 (fr) 2009-12-07 2010-10-07 Injecteur de carburant

Country Status (3)

Country Link
EP (1) EP2510215B1 (fr)
DE (1) DE102009047559A1 (fr)
WO (1) WO2011069706A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012069393A1 (fr) * 2010-11-22 2012-05-31 Robert Bosch Gmbh Injecteur de carburant

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011002422A1 (de) * 2011-01-04 2012-07-05 Robert Bosch Gmbh Einspritzventil zum Einspritzen eines Fluids
DE102012211230A1 (de) 2012-06-29 2014-01-02 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102014206210A1 (de) 2014-04-01 2015-10-01 Robert Bosch Gmbh Kraftstoffinjektor
DE102014225347A1 (de) 2014-12-10 2016-06-16 Robert Bosch Gmbh Kraftstoffinjektor
DE102016202957A1 (de) 2016-02-25 2017-08-31 Robert Bosch Gmbh Kraftstoffinjektor
DE102016214287A1 (de) 2016-08-02 2018-02-08 Robert Bosch Gmbh Kraftstoffeinspritzventil

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006014244A1 (de) * 2006-03-28 2007-10-04 Robert Bosch Gmbh Kraftstoffinjektor mit Servomagnetventil
DE102006015745A1 (de) 2006-04-04 2007-10-11 Robert Bosch Gmbh Kraftstoffinjektor mit direktgesteuertem Einspritzventilglied
WO2007115853A1 (fr) * 2006-04-04 2007-10-18 Robert Bosch Gmbh Injecteur de carburant

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006014244A1 (de) * 2006-03-28 2007-10-04 Robert Bosch Gmbh Kraftstoffinjektor mit Servomagnetventil
DE102006015745A1 (de) 2006-04-04 2007-10-11 Robert Bosch Gmbh Kraftstoffinjektor mit direktgesteuertem Einspritzventilglied
WO2007115853A1 (fr) * 2006-04-04 2007-10-18 Robert Bosch Gmbh Injecteur de carburant

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012069393A1 (fr) * 2010-11-22 2012-05-31 Robert Bosch Gmbh Injecteur de carburant

Also Published As

Publication number Publication date
EP2510215A1 (fr) 2012-10-17
DE102009047559A1 (de) 2011-06-09
EP2510215B1 (fr) 2013-09-11

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