EP2314860A1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2314860A1
EP2314860A1 EP10178124A EP10178124A EP2314860A1 EP 2314860 A1 EP2314860 A1 EP 2314860A1 EP 10178124 A EP10178124 A EP 10178124A EP 10178124 A EP10178124 A EP 10178124A EP 2314860 A1 EP2314860 A1 EP 2314860A1
Authority
EP
European Patent Office
Prior art keywords
armature
valve needle
fuel injector
fuel
injector according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10178124A
Other languages
German (de)
English (en)
Other versions
EP2314860B1 (fr
Inventor
Matthias Burger
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 EP2314860A1 publication Critical patent/EP2314860A1/fr
Application granted granted Critical
Publication of EP2314860B1 publication Critical patent/EP2314860B1/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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to a fuel injector, in particular a common rail injector, for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • control valve element bounce appears in a hard stop (metal to metal) in conjunction with a very fast control valve element (valve needle).
  • Straight bounces have a particularly negative impact on the function of the fuel injector and generally lead to large Hub / Hub scattering.
  • no squish gap can be realized to minimize the impact momentum.
  • the Applicant has indicated some mechanical approaches to minimizing closing bounces in fuel injectors.
  • the armature plate relative to the valve needle to arrange adjustable, so that the armature plate can continue their axial movement down after the valve needle is already taken on her valve seat.
  • the movement of the armature plate is braked by a nip, which forms between the armature plate and a separate from the valve needle ring part, which is held on the valve needle.
  • the invention has for its object to provide a fuel injector, which is characterized on the one hand by a simple structure and on the other hand by a minimized closing bounce.
  • the composite anchor and valve needle should be mounted in the simplest way.
  • the invention is based on the idea to minimize the bounce due to the fact that the armature plate designed as an anchor on the side facing away from the electromagnetic actuator a stop or overstroke stop is assigned, which is formed directly from the valve needle, ie the axially closable control valve element.
  • a nip for braking the armature movement can form directly between the armature and the valve needle, thereby dispensing with a separate ring element used in the prior art and thereby simplifying the structure of the fuel injector.
  • At one after the concept of Invention formed fuel injector acts on the control valve seat only the pulse of the valve needle while the armature swinging in the direction of overstroke.
  • fuel injector overstroke stop which is formed directly from the valve needle, limits the swinging of the armature, whereby short injection intervals can be realized. It is thus ensured that the resonant anchor is transferred back to its initial position within a very short time. Because the overstroke stop is limited directly by the valve needle, the overstroke stop results from the thickness extension of the preferably plate-shaped armature and the armature guide length, which is ground into an advantageously provided armature guide part, which will be explained later. These two dimensions can be very precisely measured, ground or manufactured due to the parallelism of the contact surfaces. The overtravel stop can thus be measured before assembly and, if necessary, adjusted precisely by selection groups. An elaborate setting process, in which the overstroke stop must be determined and corrected in the assembled state, is not required due to the component-independent manufacturing dimensions.
  • valve needle is sleeve-shaped and the nip between the armature and valve needle of a, preferably upper, annular surface of the sleeve-shaped valve needle is limited.
  • the formation of the preferably a stepped bore having valve needle as a sleeve makes it possible in a comparatively simple manner that the control valve is pressure balanced in the closed state in the axial direction, with the aim to be able to use smaller and less powerful electromagnetic actuators.
  • a hydraulic coupler which causes the valve needle is adjusted when energized the electromagnetic actuator together with the preferably plate-shaped armature in the axial direction towards the electromagnetic actuator. It is particularly preferred if a coupler volume of the hydraulic coupler is arranged such that the leaking from this leak (fuel leakage) is that leakage that flushes the nip, so ensures that the damping function of the nip is maintained. It is particularly expedient that the coupler volume is checked to ensure the coupler function of a high pressure leakage from a limiting of the sleeve-shaped valve needle valve chamber.
  • the coupler volume of the hydraulic coupler is axially sealed by a guide gap
  • said guide gap is preferably arranged radially between the valve needle designed as a sleeve and a bolt projecting axially into the valve needle wherein the bolt preferably has the function of sealing a valve chamber of the control valve in an axial upward direction.
  • the bolt is supported for example on an injector cover or the magnet assembly. It is particularly useful if the coupler volume, in particular in the axial direction is sealed down by a guide gap which is formed between an armature guide member and the sleeve formed as a valve needle.
  • armature guide part which is even more preferably inserted into a stepped bore of the valve needle and, on the one hand, has the function of guiding the armature and, on the other hand, a moving component of the hydraulic coupler forms, which sucks the valve needle when energizing the electromagnetic actuator, ie entraining.
  • the armature guide member is relatively adjustable to the valve needle to suck the valve needle in an upward movement and thereby be able to move upward.
  • the armature, the armature guide member and the valve needle can be mounted and axially adjusted by nesting are arranged.
  • additional fastening means are dispensed with.
  • a closing spring is preferably provided, which is even more preferably supported axially on the armature guide part. It is now particularly useful to provide in addition to the closing spring acting in the opposite direction closing spring, which is supported axially, preferably from below, to the anchor. At the moment of Anker simplyschwingens the valve needle is thereby pushed back exclusively by the closing spring, while the closing force results from the difference of closing spring and positioning spring. As a result, a greater spring force acts during the rebound than before the valve impact, whereby the locking bounce is further reduced.
  • the armature is formed of a material that is different from the valve needle forming material. It is therefore possible due to the multi-part design, the anchor from a special, the magnetic flux optimizing, i. to produce reinforcing magnetic material, for example, a sintered material, in particular having a high ohmic resistance. Overall, can be reduced by a choice of different materials, the total weight and the magnetic force can be increased.
  • this nip can be realized for example between armature and magnet assembly, in particular between the armature and an inner yoke of the magnet assembly.
  • FIG. 1 shows in the only one Fig. 1 partially one Fuel injector for injecting fuel in a combustion chamber of an internal combustion engine.
  • Fig. 1 is a section of a trained as a common-rail injector fuel injector 1 for injecting fuel in a combustion chamber of an internal combustion engine shown.
  • the fuel injector 1 is a so-called leakage-free injector, ie an injector without a permanent low-pressure stage on the injection valve element - leakage in the servo valve is inevitable in the embodiment shown.
  • a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail).
  • this fuel especially diesel, is stored under high pressure of over 2000bar in this embodiment.
  • the fuel injector 1 is connected via other, not shown, fuel injectors via a supply line.
  • the supply line 5 opens into a pressure chamber 6, in which a one-piece, only partially illustrated injection valve element 7 is guided axially adjustable.
  • the fuel flows from the pressure chamber 6 in the axial direction past the injection valve element 7 to nozzle bores of a nozzle hole arrangement, not shown, into the combustion chamber of the internal combustion engine.
  • the fuel injector 1 is connected via an injector return port 8 to a return line 9. About this return line 9, a later to be explained control amount of fuel flow from the fuel injector 1 to the reservoir 3 and are fed back from there from the high pressure circuit.
  • a control chamber 10 (servo chamber) is limited, which is supplied via an introduced in a lower sleeve-shaped portion 11 of a throttle plate 12 inlet throttle 13 with high-pressure fuel from the pressure chamber 6.
  • the sleeve-shaped portion 11 bounds the control chamber 10 radially outwardly, which is connected via a discharge throttle 14, which is also incorporated in the throttle plate 12, with a valve chamber 15 of a control valve 16 (servo valve).
  • the valve chamber 15 is bounded radially on the outside by a sleeve-shaped valve needle 17 (control valve element), which is equipped with a stepped bore 18.
  • the valve needle 17 is formed with an anchor plate An armature 19 operatively connected via a later to be explained hydraulic coupler 20, so that the valve needle is lifted when energized an electromagnetic actuator 21 from the control valve seat 22 and adjusted in the direction of the actuator 21, which in turn hydraulically the valve chamber 15 with a low pressure region 23 of the fuel injector. 1 is connected.
  • the control valve When the control valve is open, the fuel flowing out of the valve chamber 22 flows via radial bores 27 in the annular extension 25 into an armature chamber 28 belonging to the low-pressure region 23.
  • the flow cross-sections of the inlet throttle 13 and the outlet throttle 14 are matched to one another such that when the control valve 16 is open there is a net outflow of fuel resulting from the control chamber 10, whereby the pressure in the control chamber 10 drops rapidly, which in turn causes the injection valve element 7 lifts from its injector element seat, not shown, and can flow as a result, fuel from the pressure chamber 6 into the combustion chamber.
  • the energization of the electromagnetic actuator 21 is interrupted, whereby the valve needle 17 is pressed by a closing spring 24 axially downward on the control valve seat 22.
  • FIG. 1 can be seen that in the valve needle 17, a bolt 26 protrudes in the axial direction from top to bottom and the valve chamber 15 seals in the axial direction upwards. Since act on the valve needle 17 in the closed state, no axial forces, the control valve 16 is referred to as pressure-balanced valve in the axial direction.
  • the plate-shaped armature 19 is formed as a separate component from the valve needle 17.
  • the armature 19 is not arranged stationary to the valve needle 17, but arranged relative to the valve needle 17 adjustable.
  • the plate-shaped armature 19 is not guided on the valve needle 17 but with its inner circumference on the outer circumference of a sleeve-shaped armature guide member 29, which is inserted axially into the stepped bore 18, more precisely in the upper, ie larger diameter portion of the stepped bore 18 of the valve needle 17 is.
  • the armature guide member 29 projects beyond a central anchor hole in the radial direction, so that the armature 19, the armature guide member 29 and thus, as will be explained later, via the hydraulic coupler 20, the valve needle 17 moves in its upward movement.
  • the hydraulic coupler 20, more precisely a coupler volume of the coupler 20, is bounded axially upwardly from a lower end face of the armature guide member 29 and axially downwardly from a step or annular shoulder of the valve needle 17.
  • the coupler volume is sealed in an upward axial direction by one the first guide gap 33, which is limited in the radial direction of the valve needle 17 and the outer periphery of the armature guide member 29.
  • a second guide gap 34 radially between the pin 26 and the inner circumference of the valve needle 17, more precisely is limited by the bore portion of smaller diameter.
  • the function of the coupler 20 can only be guaranteed if it is always filled with fuel.
  • the first guide gap 33 and a third guide gap 36 radially between the inner circumference of the armature guide part 29 and the bolt 26 are low pressure-sealing guides and are preferably characterized by a
  • the gap between the armature guide part 29 and the valve needle 17 which results during the upward movement of the armature 19 and thus of the armature guide part 29 ensures that the latter is lifted from its control valve seat 22 when the electromagnetic actuator 21 is energized, from which the opening movement of the control valve 16 results.
  • the armature 19 is associated with a positioning spring 35 which has a larger diameter, but a lower spring constant than the closing spring 24.
  • the positioning spring 35 is supported at one end on the underside of the armature 19 and the other end on an upper side of the throttle plate 12.
  • an upper nip 38 is realized, which is located in the embodiment shown between a chromium layer on the armature and an inner pole 39 of the electromagnetic actuator, more precisely the magnet group.

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)
EP10178124A 2009-10-13 2010-09-22 Injecteur de carburant Not-in-force EP2314860B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009045623A DE102009045623A1 (de) 2009-10-13 2009-10-13 Kraftstoff-Injektor

Publications (2)

Publication Number Publication Date
EP2314860A1 true EP2314860A1 (fr) 2011-04-27
EP2314860B1 EP2314860B1 (fr) 2012-03-28

Family

ID=43334413

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10178124A Not-in-force EP2314860B1 (fr) 2009-10-13 2010-09-22 Injecteur de carburant

Country Status (3)

Country Link
EP (1) EP2314860B1 (fr)
AT (1) ATE551519T1 (fr)
DE (1) DE102009045623A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012201413A1 (de) 2012-02-01 2013-08-01 Robert Bosch Gmbh Magnetventil für einen Kraftstoffinjektor
DE102013225376A1 (de) 2013-12-10 2015-06-11 Robert Bosch Gmbh Magnetventil für einen Kraftstoffinjektor
DE102021133233A1 (de) 2021-12-15 2023-06-15 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Lagerungsvorrichtung zur Lagerung eines Ankerkörpers einer elektromagnetischen Schalt- oder Ventilvorrichtung sowie elektromagnetische Schalt- oder Ventilvorrichtung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19708104A1 (de) * 1997-02-28 1998-09-03 Bosch Gmbh Robert Magnetventil
DE102007060396A1 (de) 2007-12-03 2009-06-04 Robert Bosch Gmbh Mechanische Löschung von Schließprellern bei Einspritzdüsen
DE102007059263A1 (de) * 2007-12-10 2009-06-18 Robert Bosch Gmbh Schaltventil für Injektoren
DE102008000697A1 (de) * 2008-03-17 2009-09-24 Robert Bosch Gmbh Schaltventil für Injektoren
EP2211046A1 (fr) * 2008-12-29 2010-07-28 C.R.F. Società Consortile per Azioni Système d'injection de carburant doté d'une répétabilité et d'une stabilité élevées pour le fonctionnement d'un moteur à combustion interne

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19708104A1 (de) * 1997-02-28 1998-09-03 Bosch Gmbh Robert Magnetventil
DE102007060396A1 (de) 2007-12-03 2009-06-04 Robert Bosch Gmbh Mechanische Löschung von Schließprellern bei Einspritzdüsen
DE102007060395A1 (de) * 2007-12-03 2009-06-04 Robert Bosch Gmbh Schaltventil für Injektoren
DE102007059263A1 (de) * 2007-12-10 2009-06-18 Robert Bosch Gmbh Schaltventil für Injektoren
DE102008000697A1 (de) * 2008-03-17 2009-09-24 Robert Bosch Gmbh Schaltventil für Injektoren
EP2211046A1 (fr) * 2008-12-29 2010-07-28 C.R.F. Società Consortile per Azioni Système d'injection de carburant doté d'une répétabilité et d'une stabilité élevées pour le fonctionnement d'un moteur à combustion interne

Also Published As

Publication number Publication date
DE102009045623A1 (de) 2011-04-14
EP2314860B1 (fr) 2012-03-28
ATE551519T1 (de) 2012-04-15

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