EP2743493B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2743493B1
EP2743493B1 EP13189766.2A EP13189766A EP2743493B1 EP 2743493 B1 EP2743493 B1 EP 2743493B1 EP 13189766 A EP13189766 A EP 13189766A EP 2743493 B1 EP2743493 B1 EP 2743493B1
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EP
European Patent Office
Prior art keywords
pressure
valve
valve element
control
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.)
Active
Application number
EP13189766.2A
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German (de)
English (en)
Other versions
EP2743493A3 (fr
EP2743493A2 (fr
Inventor
Henning Kreschel
Christian Grimminger
Holger Rapp
Marco Beier
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
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Filing date
Publication date
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Publication of EP2743493A2 publication Critical patent/EP2743493A2/fr
Publication of EP2743493A3 publication Critical patent/EP2743493A3/fr
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Publication of EP2743493B1 publication Critical patent/EP2743493B1/fr
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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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid 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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/008—Means for influencing the flow rate out of or into a control chamber, e.g. depending on the position of the needle

Definitions

  • the invention relates to a fuel injector for a fuel injection system, in particular a common rail injection system, having the features of the preamble of claim 1.
  • an injector for injecting fuel into a combustion chamber of an internal combustion engine which has an injector housing in which a control valve for actuating an injection valve member which opens or closes at least one injection opening, is accommodated.
  • the fuel injector is supplied at its fuel inlet from a pressure accumulator with fuel under high pressure.
  • the pressure at this injector input will be referred to as "high pressure" below.
  • the control valve comprises a control valve element, by means of which a connection from a control chamber into a fuel return can be opened or closed. If the connection is released, the control chamber is relieved and the concomitant pressure drop in the control chamber causes an opening of the nozzle needle.
  • the connection to the fuel return is closed again.
  • fuel flows from at least one throttle element from a high-pressure fuel volume in the control chamber, with the result that the nozzle needle is displaced again in the direction of its rest position and closes.
  • a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine which has a control device for controlling an axial movement of the injection valve member for releasing or blocking of at least one injection port, wherein the injection opening facing away from the side of the injection valve member delimits a control chamber, which Can be filled with fuel via an inlet throttle and can be relieved via an outlet throttle.
  • a control chamber which Can be filled with fuel via an inlet throttle and can be relieved via an outlet throttle.
  • the JP 2011 208554 A describes a similar device for blocking or releasing a control chamber with a high pressure area.
  • a device is described which can open and close the hydraulic connection between the control chamber and a high pressure area.
  • Object of the present invention is to provide a fuel injector of the aforementioned type, in which also to reduce the fuel return supplied amount of fuel from the inflow from the high-pressure fuel volume is interrupted in the control room.
  • the proposed fuel injector comprises a control valve for controlling the lifting movement of a liftable nozzle needle for releasing and closing at least one injection opening, wherein the end of the nozzle needle facing away from the injection opening delimits a control space.
  • the control chamber can be filled to influence a control chamber pressure acting on the nozzle needle via an inlet throttle with high-pressure fuel and can be relieved in the open position of the control valve via an outlet throttle.
  • Upstream of the inlet throttle is a pressure-actuatable further valve with a displaceable valve element for releasing and closing a hydraulic connection of the inlet throttle formed with a high-pressure region. Due to the further valve formed upstream of the inlet throttle, the inflow from a high-pressure fuel volume into the control chamber can be interrupted.
  • the control valve is opened and the control chamber is relieved via the outlet throttle.
  • the control chamber is relieved faster because no additional amount of fuel flows into the control chamber, on the other hand, the return flow reduces and thus increases the efficiency of the fuel injection system.
  • the outlet throttle can be designed with a considerably reduced throttle cross-section.
  • the valve element has a radially or obliquely to a longitudinal axis A of the valve element extending inlet bore, which connects the control chamber with a pressure chamber.
  • the inlet throttle is formed in the inlet bore.
  • the radially or obliquely extending inlet bore opens on the one hand into the control chamber upstream of the outlet throttle, on the other hand into a pressure chamber, which is connectable in dependence on the switching position of the other valve with the high-pressure region of the fuel injector.
  • the sealing seat of the further valve, via which the connection is switched to the high-pressure region of the injector, is located upstream of the inlet throttle.
  • the valve element of the pressure-actuated further valve has a first control surface, which abuts the pressure prevailing in the control chamber, and at least one further control surface, at which the downstream of the outlet throttle between the outlet throttle and a valve seat of the control valve and / or the upstream of the inlet throttle between the other valve and the inlet throttle ruling pressure prevails.
  • the first control surface therefore preferably limits - together with the nozzle needle - the control chamber in the axial direction.
  • the at least one further control surface preferably defines a further pressure chamber, which is formed downstream of the outlet throttle in front of the valve seat of the control valve and / or upstream, preferably immediately upstream, of the inlet throttle.
  • the further valve Since in the outlet channel downstream of the outlet throttle and / or immediately upstream of the inlet throttle prevails at least temporarily different from the control chamber pressure pressure or prevail, can on the pressure difference or the pressure differences between the control chamber pressure and the pressure or the pressures in at least one further pressure chamber, the further valve are actuated.
  • the control chamber pressure preferably causes a force acting on the valve element in the closing direction, while the pressure in at least one further pressure chamber causes a force acting on the valve element in the opening direction. If, for example, the control valve is opened, the pressure drops sharply in at least one further pressure space, preferably between the outlet throttle and the valve seat of the control valve. The pressure difference causes the other valve closes and there is no connection of the control chamber via the inlet throttle with the high-pressure region of the fuel injector. This means that no fuel can flow into the control chamber via the inlet throttle. As a result, the amount of fuel flowing out via the outlet throttle is significantly reduced. Only the amount of fuel displaced from the control chamber by the nozzle needle in the course of its opening movement must still escape via the outlet throttle from the control chamber.
  • the outlet throttle can be designed in the episode with a much smaller throttle cross-section, without thereby reducing the opening speed of the nozzle needle or delayed the beginning of the injection.
  • valve element of the pressure-actuatable further valve is acted upon in the closing direction by the spring force of a spring.
  • the spring serves to return the valve element of the further valve after the end of an injection.
  • the spring is supported either directly or indirectly on the one hand on the valve element and on the other hand on the nozzle needle. In this way, the spring can be used in addition to the loading of the nozzle needle with a force independent of the high pressure closing force.
  • the valve element limits the control chamber in the axial and / or radial direction. This simplifies the formation of a first control surface to which control chamber pressure is applied.
  • the valve element may be designed to be piston-shaped and / or have a section designed as a hollow piston.
  • the valve element has a preferably axially extending bore in which the outlet throttle is formed.
  • the bore preferably opens on the one hand into the control chamber and on the other hand into a further pressure chamber, which is delimited by a further control surface of the valve element.
  • the bore thus connects the control room with the further pressure chamber.
  • This further pressure chamber is preferably formed between the outlet throttle and the valve seat of the control valve.
  • the valve element is at least partially axially slidably received in a guide bore of a valve member, wherein the guide bore is designed to form at least one pressure chamber and / or cooperating with the valve element annular sealing edge stepped.
  • the annular sealing edge seals the at least one further pressure chamber with respect to the high-pressure region of the fuel injector when the valve element bears against the sealing edge.
  • the annular sealing edge can also be arranged on the valve element and interact with a sealing surface on the valve piece.
  • valve element delimit the at least one pressure chamber formed in the guide bore in the radial and / or axial direction.
  • the surfaces defining a pressure chamber in the axial direction preferably also serve as control surfaces, via which the valve element of the further valve can be acted upon by a pressure force.
  • the valve element defines at least two pressure chambers, which are arranged at an axial distance from one another and are hydraulically connected via the inlet throttle.
  • the inlet throttle is preferably formed in the valve piece and not in the valve element.
  • the valve element is acted upon in the opening direction of the spring force of a spring - alternatively or in addition to acting in the closing direction spring force of the aforementioned spring.
  • the spring force of the further, acting in the opening direction spring is preferably selected to be greater than the spring force of the spring acting in the closing direction. This applies in particular when the spring acting in the closing direction also serves to return the nozzle needle.
  • the spring force of the other spring causes the other valve in the idle state assumes an open position.
  • the valve element has a cooperating with a stroke stop radially extending stop surface.
  • the opening stroke of the valve element is limited in this way.
  • the stroke stop can be formed by a body of the fuel injector, in particular a nozzle body or a holding body, or by a separate, preferably disk-shaped component.
  • the disc-shaped component is used in the high-pressure region of the fuel injector and preferably has at least one through-flow opening in order to ensure a connection of the pressure chambers located on this side and beyond the disk-shaped component.
  • the injection opening facing away from the end of the nozzle needle is surrounded by a sealing sleeve.
  • the sealing sleeve defines the control space formed between the nozzle needle and the valve element of the further valve in the radial direction.
  • the sealing sleeve is preferably supported on the valve element and / or axially prestressed in the direction of the valve element for sealing the control chamber with respect to the high-pressure region via the spring force of the spring.
  • the sealing sleeve allows the compensation of any axial offset between the nozzle needle and the valve element. At the same time, the formation of the valve element is simplified.
  • the Indian FIG. 1 schematically illustrated fuel injector according to the invention comprises a liftable nozzle needle 2 for releasing and closing a plurality of injection openings 3.
  • the movement of the nozzle needle 2 is controlled by a control valve 1, which in the present case designed as a ball valve and a solenoid actuator 27 can be actuated.
  • a spherical control valve element 28 of the control valve 1 When the solenoid actuator 27 is deactivated, a spherical control valve element 28 of the control valve 1 is pressed against a valve seat 30 by the pressure force of a spring 29.
  • pressure transmitting member is an anchor member 31 which is disposed between the spring 29 and the control valve member 28.
  • the armature element 31 When activated solenoid actuator 27, the armature element 31 is pulled against the spring force of the spring 29 in the direction of the magnetic actuator 27, wherein the control valve 1 opens.
  • the control valve 1 When the control valve 1 is open, there is a connection of a control chamber 4 via an outlet throttle 7 with a return 32, so that a relief of the control chamber 4 is effected.
  • the pressure drop in the control chamber 4 has the consequence that the nozzle needle 2, which limits the control chamber 4 with one end, opens and the injection openings 3 releases. High-pressure fuel from a high-pressure region 11 is then injected into the combustion chamber of an internal combustion engine (not shown) via the injection openings 3. To close the nozzle needle 2, the activation of the solenoid actuator 27 is terminated, so that the spring force of the spring 29 causes the return of the anchor member 31, wherein the spherical control valve member 28 is placed back in the valve seat 30 and the control valve 1 closes.
  • the fuel flowing through an inlet throttle 8 from a volume of high-pressure fuel into the control chamber 4 causes a reversal of direction of the nozzle needle movement and, consequently, a continuous closing movement of the nozzle needle 2.
  • the nozzle needle 2 returns to its original position spent and the injection ends.
  • a pressure-actuatable further valve 9 is arranged upstream of the inlet throttle 8, which interrupts the supply of high-pressure fuel to the inlet throttle 8 and then into the control chamber 4 in the closed position.
  • the pressure-actuable further valve 9 has a displaceable valve element 10 with a first control surface 12 and a second control surface 13.
  • the first control surface 12 limits the control chamber 4, so that here control chamber pressure is applied.
  • the pressure prevails downstream of the outlet throttle 7 between the outlet throttle 7 and the valve seat 30 of the control valve 1. With the opening of the control valve 1, the pressure drops downstream of the outlet throttle 7 more than in the control chamber 4.
  • the pressure difference causes the valve element 10 of the further valve 9 is acted upon by a force acting on the first control surface 12 closing force which is greater than a force acting on the second control surface 13 opening force resulting from the hydraulic pressure applied thereto and the spring force of a spring 14.
  • This has the consequence that the further valve 9 closes and, for lack of connection to a high-pressure accumulator 33, no fuel flows via the inlet throttle 8 into the control chamber 4.
  • the pressure conditions on the valve element 10 of the other valve 9 are equalized, which has an opening of the other valve 9 and thus a rapid refilling of the control chamber 4 via the inlet throttle 8 result.
  • FIG. 2 an alternative embodiment of a fuel injector according to the invention is shown, wherein the representation has been limited to the hydraulic circuit diagram.
  • the downstream of the outlet throttle 7 between outlet throttle 7 and the valve seat 30 of the control valve 1 prevailing pressure on the second control surface 13 of the valve element 10 of the other valve, but also the pressure immediately upstream of the inlet throttle. 8 between the other valve 9 and the inlet throttle 8 prevails.
  • the switching movement of the valve element 10 can be significantly accelerated in this way.
  • the high-pressure fuel from a high-pressure volume 11 of the injector in front of the sealing seat of the other valve 9 may act on a part of the second control surface 13, which favors the immediate initiation of the opening operation of the further valve 9 after closing the control valve 1.
  • FIGS. 3 to 5 is an embodiment of a fuel injector, not part of the invention, can be seen, wherein the representation is limited to the range of the other valve 9.
  • the further valve 9 has a displaceable valve element 10, which is designed as a stepped hollow piston for forming the control chamber 4.
  • the injection openings 3 facing away from the end of the nozzle needle 2 is added, which thus limits the control chamber 4 axially.
  • the outlet throttle 7 is formed, via which the control chamber 4 - with the control valve 1 open - with the return 32 (see FIG. 1 ) is connectable.
  • the second section is used here at the same time as a guide portion which is received in a guide bore 15 of a valve member 16.
  • the guide bore 15 has sections with different inner diameters, so that a plurality of pressure chambers 17, 18, 19 are formed in the guide region between the valve piece 16 and the valve element 10.
  • a first pressure chamber 17 is formed between a radially extending shoulder of the guide bore 15 and an end face of the valve element 10, which is part of the second control surface 13.
  • This first pressure chamber 17 thus comprises the fuel volume between the outlet throttle 7 and the valve seat 30 of the control valve 1.
  • An annular second pressure chamber 18 is formed by a circumferential groove in the guide bore 15.
  • This second pressure chamber 18 is connected via a radially or obliquely through the valve element 10 leading inlet bore 5 with the control chamber 4. Consequently, in this second pressure chamber 18 there is the control chamber pressure or a pressure which differs negligibly from the control chamber pressure, so that the second pressure chamber 18 represents an extension or a component of the control chamber 4 from a functional point of view. Furthermore, the second pressure chamber 18 and thus the control chamber 4 via a throttle bore, which forms the inlet throttle 8, connected to a third pressure chamber 19 which is limited both in the radial direction and in the axial direction of the valve element 10.
  • the third pressure chamber 19 limiting surfaces on the valve element 10 are also part of the second control surface 13, wherein the pressure applied here corresponds to the pressure immediately upstream of the inlet throttle 8 between the other valve 9 and the inlet throttle 8.
  • the third pressure chamber 19 is sealed off from the high-pressure region 11.
  • the high-pressure fuel in the high-pressure region 11 causes an axial force on the valve element 10 by acting on the annular surface between the sealing edge 20 and the guide diameter, in which the nozzle needle 2 is guided in the valve element 10.
  • This guide diameter will be referred to in the following as "control chamber diameter”.
  • this axial force is directed in the opening or in the closing direction of the valve element 10.
  • the area with which the valve element 10 adjoins the high-pressure region 11 thus also represents a part of the second pressure surface 13.
  • the valve element 10 is acted upon in the closing direction, holds the valve element 10 in contact with the annular sealing edge 20, as long as the hydraulic pressure conditions on the valve element 10 are largely balanced. In this position of the valve element 10, there is no connection of the control chamber 4 and the pressure chambers 18 and 19 to the external high-pressure accumulator 33 or to the high-pressure region 11 of the fuel injector ( FIG. 3 ).
  • control valve 1 If the control valve 1 opens, the pressure in the pressure chamber 17 drops rapidly downstream of the outlet throttle 7, as a result of which the valve element 10 is subjected to an additional pressure force acting in the closing direction ( FIG. 4 ). With closing of the control valve 1, the flow through the outlet throttle 7 is suppressed and there is pressure equalization between the control chamber 4 and the first pressure chamber 17. The initially still present opening movement of the nozzle needle 2 now leads to a compression of the fuel in the control chamber 4 and thus to a brief Increase in the control room pressure. For a short time, the control chamber pressure may exceed the high pressure in the high-pressure region 11 of the injector.
  • the nozzle needle 2 Due to the increase in the control chamber pressure, the nozzle needle 2 is braked and reverses its direction of movement, so that the fuel in the control chamber 4 relaxes again and the control chamber pressure decreases again. If the sealing diameter 20 selected larger than the control chamber diameter, so the short-term exceeding the pressure level in the high pressure chamber 11 by the pressure in the control chamber 4 and in the pressure chambers 17, 18 and 19 results in a resulting opening force on the valve element 10 and thus to open at the Sealing edge 20 formed sealing seat.
  • the sealing diameter 20 is smaller than the control chamber diameter
  • the pressure level in the high-pressure chamber 11 by the pressure in the control chamber 4 and in the pressure chambers 17, 18 and 19 causes an additional closing force on the valve element 10 and the other valve 9 initially remains closed.
  • the opening time of the further valve 9 is independent of the height of the short pressure pulse in the control chamber 4th during the nozzle needle reversal. Therefore, this embodiment is particularly advantageous.
  • the opening operation of the valve element 10 causes a further increase in the force in the opening direction on the valve element 10 and thus a positive feedback on the opening movement, which stabilizes the opening operation of the other valve 9.
  • a received between the valve member 16 and a body 24 disc-shaped member 25 forms a stroke stop 22, which cooperates with a radially extending stop surface 23 on the valve element 10 to limit limiting.
  • FIGS. 6 to 8 An alternative concrete embodiment of a fuel injector according to the invention is in the FIGS. 6 to 8 shown.
  • the inlet throttle 8 is formed directly in the radially or obliquely extending inlet bore 5 in the valve element 10. Consequently, it connects the control chamber 4 in this embodiment directly to the third pressure chamber 19, which is bounded in both the radial and axial direction of the valve element 10.
  • the arrangement of the inlet throttle 8 in the valve element 10 eliminates the formation of the second pressure chamber 18.
  • the operation of the in the FIGS. 6 to 8 illustrated embodiment corresponds to in the FIGS. 3 to 5 shown embodiment, so that reference is made thereto.
  • FIG. 6 to 8 illustrated embodiment corresponds to in the FIGS. 3 to 5 shown embodiment, so that reference is made thereto.
  • FIG. 6 shows the position of the valve element 10 of the further valve 9 when the control valve 1 is closed, in which the spring force of the spring 14 presses the valve element 10 against the annular sealing edge 20.
  • the control valve 1 With opening of the control valve 1 acts on the valve element 10 an additional force acting in the closing direction compressive force ( FIG. 7 ).
  • the further valve 9 opens as a result of the increase in pressure in the first pressure chamber 17 and consequently also in the third pressure chamber 19 (FIG. FIG. 8 ).
  • FIG. 9 A modification of the in the FIGS. 6 to 8 illustrated embodiment is the FIG. 9 refer to.
  • the valve element 10 is acted upon in the opening direction by the spring force of a spring 21, wherein the spring force of the spring 21 is greater than that of the spring 14, so that when the control valve 1 is closed, the other Valve 9 is opened and a connection of the control chamber 4 via the inlet throttle 8, the pressure chamber 19 and the open seat of the other valve 9 with the high-pressure region 11 is.
  • the connection is only then separated when the control valve 1 opens and the pressure in the first pressure chamber 17 drops.
  • the spring 14 which at the same time serves as a nozzle needle closing spring in the present case, is not supported on the valve element 10 but, for example, on the body 24, it is not necessary for the spring force of the spring 21 to be greater than that of the spring 14.
  • An additional spring 21, whose spring force acts on the valve element 10 in the opening direction, can also in the in the FIGS. 3 to 5 used embodiment shown.
  • FIG. 10 out A further preferred specific embodiment of a fuel injector according to the invention is based on FIG. 10 out.
  • the control chamber 4 limiting end of the nozzle needle 2 is not performed in the valve element 10, but in a sealing sleeve 26 which is axially biased by the spring force of the spring 14 against the valve member 10.
  • the sealing sleeve 26 allows the compensation of any axial offset between the nozzle needle 2 and the valve element 10. Further, it simplifies the design of the valve element 10.
  • the sealing sleeve 26 can also in an injector according to the FIGS. 3 to 5 be used.

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (10)

  1. Injecteur de carburant pour un système d'injection de carburant, en particulier un système d'injection à rampe commune, comprenant une soupape de commande (1) pour commander le mouvement de course d'un pointeau de buse (2) effectuant un mouvement de course pour libérer et fermer au moins une ouverture d'injection (3), l'extrémité du pointeau de buse (2) opposée à l'ouverture d'injection (3) limitant un espace de commande (4) qui, pour influencer une pression dans l'espace de commande agissant sur le pointeau de buse (2), peut être rempli de carburant soumis à une haute pression par le biais d'un étranglement d'alimentation (8) et qui, dans la position d'ouverture de la soupape de commande (1), peut être déchargé par le biais d'un étranglement de sortie (7), une soupape supplémentaire (9) pouvant être commandée par la pression, avec un élément de soupape déplaçable (10) pour libérer et fermer une connexion hydraulique de l'étranglement d'alimentation (8) à une région haute pression (11), étant réalisée en amont de l'étranglement d'alimentation (8),
    caractérisé en ce que l'élément de soupape (10) possède un alésage d'alimentation (5) s'étendant radialement ou obliquement par rapport à un axe longitudinal (A) de l'élément de soupape (10), lequel alésage d'alimentation relie l'espace de commande (4) à un espace de pression (18, 19) et en ce que l'étranglement d'alimentation (8) est réalisé dans l'alésage d'alimentation (5).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que l'élément de soupape (10) de la soupape supplémentaire (9) pouvant être commandée par la pression possède une première surface de commande (12) contre laquelle s'applique la pression régnant dans l'espace de commande (4), et au moins une surface de commande supplémentaire (13), au niveau de laquelle s'applique la pression régnant en aval de l'étranglement de sortie (7) entre l'étranglement de sortie (7) et un siège de soupape (30) de la soupape de commande (1) et/ou la pression régnant en amont de l'étranglement d'alimentation (8) entre la soupape supplémentaire (9) et l'étranglement d'alimentation (8).
  3. Injecteur de carburant selon la revendication 1 ou 2,
    caractérisé en ce que l'élément de soupape (10) de la soupape supplémentaire (9) pouvant être commandée par la pression peut être sollicité dans la direction de fermeture par la force de ressort d'un ressort (14) qui est à chaque fois supporté directement ou indirectement de préférence d'une part au niveau de l'élément de soupape (10) et d'autre part au niveau du pointeau de buse (2).
  4. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément de soupape (10) limite l'espace de commande (4) dans la direction axiale et/ou radiale et possède un alésage s'étendant de préférence axialement, dans lequel est réalisé l'étranglement de sortie (7).
  5. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément de soupape (10) est reçu de manière déplaçable axialement au moins en partie dans un alésage de guidage (15) d'une pièce de soupape (16), l'alésage de guidage (15) étant réalisé sous forme étagée pour réaliser au moins un espace de pression (17, 18, 19) et/ou une arête d'étanchéité (20) de forme annulaire coopérant avec l'élément de soupape (10).
  6. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que l'élément de soupape (10) limite l'au moins un espace de pression (17, 18, 19) réalisé à l'intérieur de l'alésage de guidage (15) dans la direction radiale et/ou axiale, au moins deux espaces de pression (18, 19) étant de préférence disposés à distance axiale l'un de l'autre et étant connectés hydrauliquement par le biais de l'étranglement d'alimentation (8).
  7. Injecteur de carburant selon la revendication 1 ou 5,
    caractérisé en ce que l'étranglement d'alimentation (8) relie l'espace de commande (4) à l'espace de pression (19).
  8. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément de soupape (10) est sollicité dans la direction d'ouverture par la force de ressort d'un ressort (21), la force de ressort du ressort (21) étant de préférence supérieure à la force de ressort du ressort (14).
  9. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément de soupape (10) possède une surface de butée (23) s'étendant radialement et coopérant avec une butée de course (22), la butée de course (22) étant réalisée par un corps (24) de l'injecteur de carburant ou par un composant séparé (25), de préférence en forme de disque.
  10. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'extrémité du pointeau de buse (2) opposée à l'ouverture d'injection (3) est entourée par une douille d'étanchéité (26) qui est supportée de préférence au niveau de l'élément de soupape (10) et/ou qui est précontrainte axialement pour réaliser l'étanchéité de l'espace de commande (4) par rapport à la région haute pression (11) par le biais de la force de ressort du ressort (14) dans la direction de l'élément de soupape (10).
EP13189766.2A 2012-12-14 2013-10-22 Injecteur de carburant Active EP2743493B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012223166.8A DE102012223166A1 (de) 2012-12-14 2012-12-14 Kraftstoffinjektor

Publications (3)

Publication Number Publication Date
EP2743493A2 EP2743493A2 (fr) 2014-06-18
EP2743493A3 EP2743493A3 (fr) 2015-07-29
EP2743493B1 true EP2743493B1 (fr) 2017-02-08

Family

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Application Number Title Priority Date Filing Date
EP13189766.2A Active EP2743493B1 (fr) 2012-12-14 2013-10-22 Injecteur de carburant

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EP (1) EP2743493B1 (fr)
DE (1) DE102012223166A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015205582A1 (de) * 2015-03-27 2016-09-29 Robert Bosch Gmbh Kraftstoffinjektor für ein Kraftstoffeinspritzsystem
DE102015226070A1 (de) * 2015-12-18 2017-06-22 Robert Bosch Gmbh Kraftstoffinjektor
DE102017205772A1 (de) 2017-04-05 2018-10-11 Robert Bosch Gmbh Kugelventil
EP3990770A1 (fr) * 2019-06-25 2022-05-04 Ganser-Hydromag AG Soupape d'injection de carburant pour des moteurs à combustion interne

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4428357B2 (ja) * 2006-04-03 2010-03-10 株式会社デンソー 燃料噴射弁
DE102006049050A1 (de) 2006-10-18 2008-04-30 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff
CH700396A1 (de) * 2009-02-09 2010-08-13 Ganser Hydromag Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
JP5531713B2 (ja) * 2010-03-29 2014-06-25 株式会社デンソー 燃料噴射装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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Also Published As

Publication number Publication date
EP2743493A3 (fr) 2015-07-29
EP2743493A2 (fr) 2014-06-18
DE102012223166A1 (de) 2014-06-18

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