EP2275666B1 - Injecteur de carburant doté d'une soupape de distribution à pression compensée - Google Patents

Injecteur de carburant doté d'une soupape de distribution à pression compensée Download PDF

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Publication number
EP2275666B1
EP2275666B1 EP10162230A EP10162230A EP2275666B1 EP 2275666 B1 EP2275666 B1 EP 2275666B1 EP 10162230 A EP10162230 A EP 10162230A EP 10162230 A EP10162230 A EP 10162230A EP 2275666 B1 EP2275666 B1 EP 2275666B1
Authority
EP
European Patent Office
Prior art keywords
control valve
valve element
chamber
fuel injector
hydraulic connection
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.)
Not-in-force
Application number
EP10162230A
Other languages
German (de)
English (en)
Other versions
EP2275666A1 (fr
Inventor
Andreas Rau
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 EP2275666A1 publication Critical patent/EP2275666A1/fr
Application granted granted Critical
Publication of EP2275666B1 publication Critical patent/EP2275666B1/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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/0045—Three-way valves

Definitions

  • the invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
  • a fuel injector which has a control valve (servo valve).
  • the control valve is designed as a so-called 3/2-way valve and controls the connection between a directly from an injection valve element control space and a low pressure area (leakage oil space) of the fuel injector.
  • the control valve has a control valve element, which can be adjusted axially by means of an actuator, for example an electromagnetic or piezoelectric actuator, within a control valve chamber and thus cooperates with a first control valve seat and with a second control valve seat. If the control valve element is in contact with the first (upper) control valve seat, the connection between the control space bounded by the injection valve element and the low-pressure region of the fuel injector is blocked.
  • a bypass throttle is opened, via which the control chamber is refilled.
  • the bypass throttle is closed and the hydraulic connection between the control chamber and the low pressure region of the fuel injector is established, whereby the pressure in the control valve chamber drops, which in turn causes the injection valve element to move from its position Injector valve seat lifts and thus releases the flow of fuel through a nozzle hole arrangement in the combustion chamber of the internal combustion engine.
  • a disadvantage of the axially not pressure balanced control valve is that the load of the actuator with increasing rail pressure continues to increase. As a result, given a known actuator with the known principle, there is no potential for a further system pressure increase.
  • the control valve member of the control valve is disposed in a control valve space which is bounded radially outwardly by a single plate member, to the axially below a throttle plate and axially above an actuator space limited component abuts.
  • the new injector seems to be optimized in terms of shortened remindbehellles the control room.
  • the invention has for its object to provide a fuel injector, on the one hand has sufficient potential for system pressure increases and in the other hand, a minimized stuntbehellzeit is realized for refilling the control chamber.
  • the invention is based on the idea, a second, in particular lower control valve seat on which the control valve element of the control valve (servo valve) sealingly abuts in the second switching position to the immediate hydraulic Interrupt connection between the high-pressure region of the fuel injector and the control valve chamber on a guide sleeve for the control valve, which leads, preferably not sleeve-shaped, in particular bolt-shaped, control valve element on its outer circumference.
  • the control valve element bears directly against the guide sleeve in a sealing manner.
  • the fuel injector preferably designed as a throttle connection hydraulic connection between the high-pressure region of the fuel injector and the control valve chamber through the second, preferably lower, control valve seat can be separated.
  • the minimized control valve volume results in a significantly lower characteristic slope, which makes it possible to use nozzles that rapidly decompress, whereby the engine output can be increased without impairing the fuel injector's small-capacity capability.
  • the fuel injector according to the invention has particularly good hydraulic properties by the simultaneous presence of a bypass (hydraulic connection between the high-pressure region and the control valve chamber) and a minimum control valve chamber volume, which in combination to an extreme quick refilling the control valve chamber and thus the control chamber and thus in turn leads to a very quick reversal of the injection valve element with said flat map.
  • the refilling time which is required to refill the control chamber, can be reduced in the invention by a minimum, in which instead of a helical compression spring, a plate spring is used as a valve spring for the control valve.
  • the plate spring is arranged such that the control valve element in the direction of the first switching position, i. Federkraftbeaufschlagt in the direction of the first control valve seat, so that the control valve member against the spring force of the spring plate must be moved from the first switching position to the second switching position. Due to the design of the spring as a plate spring, the control valve volume can be reduced to a minimum, resulting in the first switching position of the control valve, an accelerated pressure increase in the control valve chamber and thus also in the control room.
  • the hydraulic connection between the high-pressure region, for example, a pressure chamber surrounding the control chamber radially outside and the control valve chamber is designed as a throttle connection.
  • a throttle bore is integrated, which is particularly preferably, as will be explained later, is arranged in a throttle plate, which bears axially against the guide sleeve for the control valve element.
  • the spring in particular the plate spring, against the spring force
  • the control valve element must be adjusted on its way from the first switching position to the second switching position one end axially on the control valve element, in particular on a peripheral collar of the control valve element and the other end is supported on the guide sleeve for the control valve element.
  • P refers the spring is arranged such that it is not completely flattened even in the second switching position of the control valve.
  • the hydraulic connection comprises a gap, which is bounded radially outwardly directly from the guide sleeve and radially inwardly directly from the control valve member.
  • the space formed as an annular space is preferably contoured and arranged such that resulting from the fuel under high pressure in the space no resulting axial forces on the control valve element.
  • the aforementioned gap is at least one introduced into the guide sleeve sleeve bore hydraulically permanently connected to an annular space which is bounded radially inwardly of the guide sleeve and preferably radially outwardly from the inner periphery of an end-side recess in a throttle plate is limited.
  • annular space arranged radially outside the guide sleeve is connected via a channel in a throttle plate on which the guide sleeve rests in the axial direction to the high-pressure region, preferably to a pressure chamber surrounding the control chamber radially on the outside.
  • this channel is designed as a throttle bore.
  • control valve element on the outer circumference leading guide sleeve, in particular on a, in particular piezoelectric actuator facing Side has a biting edge for sealing cooperation with the control valve element in the second switching position.
  • the fuel can be actuated with an electromagnetic actuator.
  • an embodiment variant with a piezoelectric actuator is particularly preferred, wherein a coupler is preferably provided between the piezoelectric actuator and the control valve element, with which a force path transmission can be realized and compensated for with the expansion effects due to heat.
  • the hydraulic connection between the control chamber and the control valve chamber so the hydraulic connection through which in the second switching position of the control valve fuel from the limited by the injection valve element control chamber can flow into the low pressure region, at least two, Having in different injector components extending sections.
  • a section extends in a previously explained throttle plate and another section in a control valve space radially outwardly bounding plate.
  • Fig. 1 is a designed as a common rail injector fuel injector 1 for injecting fuel in a combustion chamber, not shown, of a likewise not shown internal combustion engine of a motor vehicle in a schematic Illustration shown.
  • a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel or gasoline, under high pressure, stored in this embodiment about 2000 bar.
  • the fuel injector is connected via other, not shown, injectors via a supply line 5.
  • the supply line 5 opens into a supply channel 6 within the fuel injector 1, which in turn opens into a pressure chamber 7, which, like the supply channel 6, belongs to the high-pressure region 8 of the fuel injector 1.
  • the fuel injector 1, more precisely a low-pressure region 10 of the fuel injector 1, is connected to a return line 11 via an injector return port (not shown). Via the return line 11, a control quantity of fuel, which will be explained later, can flow into the fuel injector 1 to the storage container 3 and be fed back from there to the high-pressure circuit.
  • a one-piece injection valve element 12 designed as a nozzle needle is arranged axially adjustable. This can also be made in several parts instead of the one-piece training and, for example, consist of a control rod and a coupled with this nozzle needle.
  • the preferred one-piece injection valve element 12 protrudes in the drawing plane down to an injection valve element seat 13, with which it cooperates in a sealing manner in a conventional manner.
  • the injection valve member 12 abuts its injection valve member seat 13, i. is in a closed position, the fuel outlet from a plurality of injection openings comprehensive nozzle hole assembly 14 is locked. If, on the other hand, it is lifted from its injection valve element seat 13, fuel can be injected from the pressure chamber 7 into a region below the injection valve element 12 and from there through the nozzle hole arrangement 14, substantially under high pressure (rail pressure) into the combustion chamber.
  • a control chamber 17th limited which is supplied via a in a throttle plate 18, on which the sleeve 16 is supported in the axial direction, introduced inlet throttle 19 with high-pressure fuel from the high-pressure region 8, here the supply channel 6.
  • the inlet throttle 19 may also be provided as a radial bore in the sleeve 16.
  • the sleeve 16 with the control chamber 17 enclosed therein is enclosed radially on the outside by fuel under high pressure, so that an annular guide gap between the sleeve 16 and the injection valve element 12 is comparatively fuel-tight.
  • the sleeve 16 is supported in the axial direction from below on the aforementioned throttle plate 18, in which in addition to the inlet throttle 19, a flow restrictor 20 exhibiting flow channel 21 is introduced.
  • the drainage channel 21 as well as an aligned in the flow direction with this channel 22, which is introduced in an axially adjacent to the throttle plate 18 plates 23 to a hydraulic connection between the control chamber 17 and a radially outwardly of the plate 23 limited control valve chamber 24.
  • the control valve chamber 24 is inserted in a lower portion of a stepped bore 25 in the plate 23.
  • Axially adjustable within the control valve chamber 24 is a bolt-shaped control valve element 26 of a control valve 27 which is connected by means of a piezoelectric actuator 29 via a hydraulic coupler 29 between an upper first switching position, i. between an upper first control valve seat 30 and a lower, i. second switching position, ie a second control valve seat 31 is adjustable.
  • the control valve 27 is a 3/2-way valve.
  • the hydraulic connection between the high pressure region 8 and the control valve chamber 24 includes a throttle bore 35 in the throttle plate 18, wherein the throttle bore 35 hydraulically connects the pressure chamber 7 with an annular space 36, wherein the annular space 36 radially outward from the inner periphery of a frontal bore in the throttle plate 18 and is bounded radially inwardly from the outer periphery of the guide sleeve 32 for the control valve element 26.
  • the annular space 36 is connected via a sleeve bore 37 in permanent hydraulic connection with a gap 38, which is bounded radially outwardly from the inner circumference of a central bore in the guide sleeve 32 and radially inwardly from the outer periphery of the control valve element 26.
  • the second (lower) switching position of the control valve 27 of the intermediate space 38 is separated from the control valve chamber 24 via a formed on the guide sleeve 32 biting edge 39 which cooperates sealingly with the underside of a peripheral collar 40 of the control valve element 26.
  • the biting edge 39 is located on the front side of an axial,
  • the extension 41 creates axial space for accommodating a plate spring 42 (control valve spring), against the spring force, the control valve member 26 must be moved in energizing the piezoelectric actuator 28 in the drawing plane down to the second switching position.
  • a plate spring 42 as a control valve spring, the volume of the control valve chamber 24 can be minimized as shown.
  • the plate spring 42 is supported in the axial direction on an upper end side of the guide sleeve 32 and in the other axial direction from below on the peripheral collar 40 of the control valve element 26.
  • the control valve element 26 is an at least approximately pressure-balanced control valve element 26 in the axial direction; this means that when the control valve element 26 is in the upper (first) switching position, no (or possibly only small) resulting hydraulic forces act in the axial direction. This is achieved in that the control valve element 26 is acted upon at a lower end face 43 with low pressure.
  • the lower end face 43 bounded in the axial direction upwards a compensation chamber 44, which belongs to the low pressure region 10 of the fuel injector 1 and is hydraulically connected via a low pressure passage 45 to the injector return port.
  • the compensation chamber 44 is bounded radially on the outside by the guide sleeve 32, which limits the control valve chamber 24 in the axial direction downwards.
  • the guide sleeve 32 is received over a majority of its axial extent in a frontal bore in the throttle plate 18 and is sealingly connected to an upper portion of its outer periphery to a lower portion of the inner periphery of the stepped bore 25, so that the annular space 36 is sealed relative to the control valve chamber 24.

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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 l'injection de carburant dans une chambre de combustion d'un moteur à combustion interne, en particulier injecteur à rampe commune, comprenant un élément de soupape d'injection en une ou plusieurs parties (12), pour l'ouverture et la fermeture d'au moins une ouverture d'injection, une soupape de commande (27) étant associée à l'élément de soupape d'injection (12), laquelle présente un élément de soupape de commande (26) réglable entre une première et une deuxième position de commutation, disposé dans un espace de soupape de commande (24), une liaison hydraulique entre un espace de commande (17) en liaison fonctionnelle avec l'élément de soupape d'injection (12) et une plage de basse pression (10) de l'injecteur de carburant (1) étant bloquée et une liaison hydraulique (33) entre une plage de haute pression de l'injecteur de carburant (1) et l'espace de soupape de commande (24) étant ouverte dans la première position de commutation, et dans la deuxième position de commutation, la liaison hydraulique entre l'espace de commande (17) et la plage de basse pression (10) étant ouverte et la liaison hydraulique entre la plage de haute pression (8) et l'espace de soupape de commande (24) étant interrompue,
    caractérisé en ce que
    l'élément de soupape de commande (26) est réalisé et disposé de telle sorte que du fait de la pression dans l'espace de soupape de commande (24), aucune ou seulement une faible force hydraulique résultante soit exercée dans la direction axiale sur l'élément de soupape de commande (26), lorsque la liaison hydraulique (33) entre l'espace de soupape de commande (24) et la plage de basse pression (10) est interrompue dans la première position de commutation de l'élément de soupape de commande (26), et en ce que l'élément de soupape de commande (26) dans la deuxième position de commutation, pour assurer l'étanchéité de la liaison hydraulique (33) entre la plage de haute pression (8) et l'espace de soupape de commande (24), s'applique hermétiquement contre une douille de guidage (32) guidant l'élément de soupape de commande (26) au niveau de sa périphérie extérieure.
  2. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un ressort est disposé d'une part de manière supportée axialement contre un épaulement périphérique (40) de l'élément de soupape de commande (26) et d'autre part de manière supportée axialement contre la douille de guidage (32) pour l'élément de soupape de commande (26).
  3. Injecteur de carburant selon l'une quelconque des revendications 1 ou 2,
    caractérisé en ce que
    la liaison hydraulique (33) entre la plage de haute pression (8) et l'espace de soupape de commande (24) est réalisée sous forme de liaison étranglée, de préférence en pratiquant un alésage étranglé (35).
  4. Injecteur de carburant selon la revendication 2, caractérisé en ce que
    le ressort est réalisé sous forme de rondelle Belleville (42).
  5. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la liaison hydraulique (33) comprend un espace intermédiaire limité radialement à l'extérieur par la douille de guidage (32) et radialement à l'intérieur par l'élément de soupape de commande (26).
  6. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que
    l'espace intermédiaire est connecté par le biais d'au moins un alésage de douille (37) dans la douille de guidage (32) à un espace annulaire (36) limité radialement à l'intérieur par la douille de guidage (32).
  7. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la douille de guidage (32) est axialement adjacente à une plaque d'étranglement (18) dans laquelle est pratiqué un alésage, réalisé de préférence sous forme d'alésage étranglé (35), sous forme de portion partielle de la liaison hydraulique (33) entre la région de haute pression (8) et l'espace de soupape de commande (24).
  8. Injecteur de carburant selon la revendication 7,
    caractérisé en ce que
    la douille de guidage (32) présente une arête d'attaque pour coopérer de manière hermétique avec l'élément de soupape de commande (26) dans la deuxième position de commutation.
  9. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    pour l'actionnement de la soupape de commande (27) est prévu un actionneur piézoélectrique (28).
  10. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la liaison hydraulique (20, 21, 22) entre l'espace de commande (17) et l'espace de soupape de commande (24) s'étend à travers deux composants axialement adjacents l'un à l'autre.
EP10162230A 2009-07-07 2010-05-07 Injecteur de carburant doté d'une soupape de distribution à pression compensée Not-in-force EP2275666B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009027494A DE102009027494A1 (de) 2009-07-07 2009-07-07 Kraftstoff-Injektor mit druckausgeglichenem Steuerventil

Publications (2)

Publication Number Publication Date
EP2275666A1 EP2275666A1 (fr) 2011-01-19
EP2275666B1 true EP2275666B1 (fr) 2012-01-18

Family

ID=42767939

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10162230A Not-in-force EP2275666B1 (fr) 2009-07-07 2010-05-07 Injecteur de carburant doté d'une soupape de distribution à pression compensée

Country Status (3)

Country Link
EP (1) EP2275666B1 (fr)
AT (1) ATE542042T1 (fr)
DE (1) DE102009027494A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011002955A1 (de) * 2011-01-21 2012-07-26 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102011007106A1 (de) * 2011-04-11 2012-10-11 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102011081643A1 (de) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Kraftstoffinjektor

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004030445A1 (de) 2004-06-24 2006-01-12 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE102004046191B3 (de) * 2004-09-23 2006-04-13 Siemens Ag Servoventil und Einspritzventil
DE102004049702B3 (de) * 2004-10-12 2006-03-09 Siemens Ag Servoventil und Einspritzventil
DE102006009070A1 (de) * 2006-02-28 2007-08-30 Robert Bosch Gmbh Brennstoffeinspritzventil
JP4582061B2 (ja) * 2006-07-04 2010-11-17 株式会社デンソー ピエゾインジェクタ及びインジェクタ駆動システム
DE102007047426A1 (de) * 2007-05-15 2008-11-20 Robert Bosch Gmbh Injektor mit Piezoaktor
US20090165749A1 (en) * 2007-12-27 2009-07-02 Caterpillar Inc. Engine and control valve assembly having reduced variability in operation over time
DE102008001330A1 (de) 2008-04-23 2009-10-29 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen

Also Published As

Publication number Publication date
EP2275666A1 (fr) 2011-01-19
ATE542042T1 (de) 2012-02-15
DE102009027494A1 (de) 2011-01-13

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