EP2511514B1 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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Publication number
EP2511514B1
EP2511514B1 EP20120158513 EP12158513A EP2511514B1 EP 2511514 B1 EP2511514 B1 EP 2511514B1 EP 20120158513 EP20120158513 EP 20120158513 EP 12158513 A EP12158513 A EP 12158513A EP 2511514 B1 EP2511514 B1 EP 2511514B1
Authority
EP
European Patent Office
Prior art keywords
sleeve
valve
bore
annular gap
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.)
Not-in-force
Application number
EP20120158513
Other languages
German (de)
English (en)
Other versions
EP2511514A3 (fr
EP2511514A2 (fr
Inventor
Karsten-Sepp Ramsauer
Holger Rapp
Daniel Schrader
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 EP2511514A2 publication Critical patent/EP2511514A2/fr
Publication of EP2511514A3 publication Critical patent/EP2511514A3/fr
Application granted granted Critical
Publication of EP2511514B1 publication Critical patent/EP2511514B1/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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • 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
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • 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

Definitions

  • a double-switching control valve in which a valve body is guided in the housing of the control valve, so that the wear on a valve cone of the valve body and a first valve seat in the housing of the control valve is reduced.
  • the control valve has a spring chamber into which a bypass and an outlet throttle lead.
  • the bypass establishes a hydraulic connection between an inlet channel and an inlet of the control valve.
  • the switching valve includes the valve pin sleeve (guide sleeve) which can seal the space under the valve pin from high pressure fuel and provide communication therewith to fuel under reflux.
  • a stroke stop for the valve pin can still be performed and it can still be provided a valve spring, which acts on the valve pin in the pressureless state of the system with a closing force.
  • the switching valve is switched back to its idle state, then takes place in an advantageous manner on the then re-opened sealing seat between the valve and the sleeve an inflow from the high-pressure passage in the valve chamber and from there also against their actual flow direction via an outlet throttle in a control room ,
  • the control chamber can be filled not only via an inlet throttle, but also via the seat between the sleeve and the valve pin and the outlet throttle, which in this case flows backwards. This makes it possible to achieve an increased closing speed of the nozzle needle.
  • Another disadvantage of a throttled high-pressure channel is that at each switching operation of the switching valve, the pressure in the annular space surrounding the sleeve drops significantly below the rail pressure as a result of the now existing throttling in front of this annulus. As a result, in turn, an increased slip between the sleeve and the throttle plate and thus increased wear on this contact point arises. In this case, the sealing effect of the contact point between the sleeve and the throttle plate can be lost.
  • the sleeve has at least one bore which leads from an outer side of a sleeve to an annular gap between an inner side of the sleeve and the valve pin, and in that the valve chamber can be connected to the high-pressure channel via the annular gap and the bore in the sleeve.
  • the bore is designed as a throttle bore.
  • the bore thereby forms a throttled passage for the fuel.
  • at least one throttle bore is provided. However, it can also be provided several throttle bores.
  • valve pin and / or the sleeve are configured so that the annular gap between the inside of the sleeve and the valve pin along an axis of the valve pin at least substantially from the sealing seat between the sleeve and the valve pin to the Mouth opening extends and that the annular gap, at least in the region of the mouth opening has a certain radial annular gap height.
  • a throttle point can be formed at the deflection point at the mouth opening.
  • the throttle may advantageously be formed at the deflection of the mouth of the bore, wherein the cross-sectional area of the throttle at least approximately by a product having a multiplier which is equal to the outlet circumference of the mouth of the bore, and a multiplicand equal to the radial annular gap height of the annular gap in the region of the mouth opening is given.
  • the throttle effect can be adjusted specifically.
  • the bore can be designed as a continuous bore with a uniform diameter or as a stepped bore with variable over the length diameter.
  • Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view.
  • the fuel injection valve 1 can be used in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail that stores diesel fuel under high pressure and divides it into several fuel injection valves 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a seat plate 2, a valve plate 3 and a throttle plate 4.
  • a switching valve 5 is configured in the region of the valve plate 3.
  • the switching valve 5 has a space 6 which is configured in the valve plate 3.
  • the space 6 may in this case be configured by a bore in the valve plate 3.
  • a sleeve 7 and a valve pin 8 are arranged in the space 6, .
  • the valve pin 8 is guided in this case in the sleeve 7.
  • a throttle 23 is provided, which is formed in this embodiment by a throttle bore 23.
  • the throttle bore 23 extends in this case with respect to an axis 24 of the valve pin 8 radially through the sleeve 7.
  • the throttle bore 23 leads from the outer side 20 of the sleeve 7 to an annular gap 25 between an inner side 26 of the sleeve 7 and the valve pin 8.
  • the valve chamber 9 is connected via the annular gap 25 and the throttle bore 23 and the annular space 17 with the high pressure passage 16.
  • the high-pressure passage 16 does not necessarily have to extend through the throttle plate 4.
  • the high-pressure passage 16 can also be configured in the valve plate 3.
  • the sealing seat 11 Upon actuation of the switching valve 5 by means of the actuator 14, the sealing seat 11 is opened and at the same time the sealing seat 15 is closed. Thus flows in the valve chamber 9 under high pressure fuel. Since the throttle 23 is arranged relative to the fluidic distance between the sealing seat 15 and the high-pressure passage 16 relatively close to the sealing seat 15, when switching back the switching valve 5 in the in the Fig. 1 illustrated starting position, the control amount largely limited to the necessary extent and the occurrence of a strong Ab Kunststoffcies avoided during the switching process.
  • the fuel injection valve 1 has a nozzle needle 27, which is enclosed at its end by a sealing sleeve 28.
  • the sealing sleeve 28 is supported here on the throttle plate 4, so that a control chamber 29 between the nozzle needle 27, the sealing sleeve 28 and the throttle plate 4 is formed.
  • the control chamber 29 is connected to the valve space 9 via an outlet throttle 30, which is configured in the throttle plate 4, and a connecting channel 31, which is configured in the valve plate 3, and a recess 32, which is configured in the seat plate 2.
  • the recess 32 in the seat plate 2 can, as in Fig.
  • the recess 32 in the seat plate 2 may alternatively not be configured circumferentially around the valve seat, so that the sleeve 7 between the seat plate 2 and the throttle plate 4 mechanically clamped and so axially is fixed.
  • the pressure in the control chamber 29 is thus influenced by the pressure in the valve chamber 9. If the sealing seat 11 is opened, then the pressure in the control chamber 29 also drops.
  • the pressure in the control chamber 29 increases due to the subsequent flow of fuel via an inlet throttle 33.
  • the inlet throttle 33 is shown schematically as a bore in the sealing sleeve 38 for ease of illustration.
  • the closing speed of the nozzle needle 27 is here, however, further increased because under high pressure fuel also flows backwards through the outlet throttle 30, as at the same time standing under high pressure fuel from the high pressure passage 16 into the valve chamber 9 passes.
  • At least one passage bore 23 is provided through the sleeve 7, which is designed as a throttle 23.
  • the fuel volume between the throttle point 23 and the sealing seat 15 can be kept very small, so that the control amount is largely limited to the necessary extent.
  • the high-pressure passage 16 can be configured by a simple bore, through which the fuel is conducted without significant throttle effect. That is, the throttle effect of the high-pressure passage 16 is small in comparison with the throttling action of the throttle bore 23.
  • the throttling takes place only downstream seen from the annular space 17, so that in the annular space 17 always the high pressure, in particular the rail pressure, or the pressure prevails at the inlet to a nozzle of the fuel injection valve 1.
  • a throttle bore 23 and a plurality of throttle bores 23 may be provided in the sleeve 7, which produce a plurality of connections between the annular space 17 and the sealing seat 15 of the switching valve 5.
  • the throttle bores 23, which are designed in particular as transverse bores, can be distributed over the height, that is to say along the axis 24, as well as with respect to the axis 24 over the circumference of the sleeve 7, that is to say azimuthally.
  • the throttle bore 23 is designed to extend radially in this embodiment. But the throttle bore 23 and the plurality of throttle bores 23 may also run as desired obliquely in the sleeve 7.
  • the high-pressure passage 16 can also open further upstream of the throttle plate 4 from open into the annular space 17.
  • Fig. 2 shows a fuel injection valve 1 in a partial, schematic sectional view according to a second embodiment of the invention.
  • a bore 23 ' is provided in the sleeve 7, as unthrottled bore 23 'is configured.
  • the bore 23 ' has an orifice 40, on which the bore 23' has a defined outlet cross-section.
  • the bore 23 ' opens into an annular gap 25, which has defined predetermined dimensions.
  • valve pin 8 and / or the sleeve 7 are designed so that the annular gap 25 between the inner side 26 of the sleeve 7 and the valve pin 8 along the axis 24 of the valve pin 8 of the sealing seat 15 between the sleeve 7 and the valve pin 8 to extends to the orifice 40 and preferably slightly further with a certain, radial annular gap height h B.
  • the radial annular gap height h B is in this case measured or determined radially with respect to the axis 24 of the valve pin 8.
  • At the mouth opening 40 results in a fluidic deflection point 41 of the bore 23 'in the annular gap 25.
  • the cross-sectional area of the throttle 42 formed thereby which is composed of the bore 23' with the orifice 40 and the annular gap 25, at least approximately by a product having a multiplier equal to the exit circumference of the orifice 40 of the bore 23 'and a multiplicand equal to the radial annular gap height h B of the annular gap 25. If the orifice 40 has a diameter d, then the outlet cross-section results according to the exit circumference given by the diameter d and the gap height h B.
  • the bore 23 ' can be designed as a continuous bore with a uniform diameter or as a stepped bore with variable over the length diameter.
  • these transverse bores are distributed uniformly over the circumference, mutual compensation can be achieved with respect to the resulting transverse force acting on the sleeve 7. Also a distribution over the height is possible.
  • annular gap 25 is configured by reducing a diameter 45 of the valve pin 8 in sections.
  • an inner diameter 45 of the sleeve 7 can also be made larger in sections in order to form the annular gap 25 in sections.

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)

Claims (10)

  1. Soupape d'injection de combustible (1), en particulier injecteur pour des installations d'injection de combustible de moteurs à combustion interne à auto-allumage et compression d'air, comprenant une soupape de commutation (5), un canal de liaison (31) qui conduit d'un espace de commande (29) dans une chambre de soupape (9) de la soupape de commutation (5) et un canal haute pression (16), l'espace de soupape (9) pouvant être connecté en fonction de la position de commutation de la soupape de commutation (5) à une région basse pression (12) ou au moins de manière indirecte au canal haute pression (16), la soupape de commutation (5) présentant une douille (7) et un boulon de soupape (8) guidé dans la douille (7), et un siège d'étanchéité (15) étant formé entre la douille (7) et le boulon de soupape (8), par le biais duquel siège d'étanchéité la connexion de l'espace de soupape (9) au canal haute pression (16) peut être commandée, le boulon de soupape (8) étant guidé dans la douille (7),
    caractérisée en ce que dans la région du guide entre le boulon de soupape (8) et la douille (7) est configuré au moins un étranglement (23, 42) par le biais duquel l'espace de soupape (9) peut être connecté au canal haute pression (16), en ce que le canal haute pression (16) par comparaison à un effet d'étranglement de l'étranglement (23, 42) est configuré sous forme de canal haute pression sans étranglement (16) et la douille (7) présente au moins un alésage (23, 23') qui conduit depuis un côté extérieur (20) de la douille (7) jusqu'à une fente annulaire (25) entre un côté intérieur (26) de la douille (7) et le boulon de soupape (8), et en ce que l'espace de soupape (9) peut être connecté par le biais de la fente annulaire (25) et de l'alésage (23, 23') dans la douille (7) au canal haute pression (16), l'alésage (23) étant configuré sous forme d'alésage étranglé (23).
  2. Soupape d'injection de combustible selon la revendication 1,
    caractérisée en ce
    qu'une ouverture débouchante (40) de l'alésage (23'), au niveau de laquelle l'alésage (23') débouche dans la fente annulaire (25) entre le côté intérieur (26) de la douille (7) et le boulon de soupape (8), présente un diamètre de sortie défini (d).
  3. Soupape d'injection de combustible selon la revendication 2,
    caractérisée en ce que
    le boulon de soupape (8) et/ou la douille (7) sont configurés de telle sorte que la fente annulaire (25), entre le côté intérieur (26) de la douille (7) et le boulon de soupape (8), s'étende au moins essentiellement le long d'un axe (24) du boulon de soupape (8) depuis le siège d'étanchéité (15) entre la douille (7) et le boulon de soupape (8) jusqu'à l'ouverture débouchante (40) et en ce que la fente annulaire (25) présente au moins dans la région de l'ouverture débouchante (40) une certaine hauteur de fente annulaire radiale (hB).
  4. Soupape d'injection de combustible selon la revendication 3,
    caractérisée en ce que
    l'étranglement (42) est formé au niveau d'un point de renvoi (41) de l'ouverture débouchante (40) de l'alésage (23'), la surface en section transversale de l'étranglement (42) étant au moins approximativement obtenue par un produit avec un multiplicateur qui est égal à la périphérie de sortie de l'ouverture débouchante (40) de l'alésage (23'), et un multiplicande qui est égal à la hauteur de fente annulaire radiale (hB) de la fente annulaire (25) dans la région de l'ouverture débouchante (40).
  5. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que
    l'alésage (23, 23') dans la douille (7) est configuré sous forme d'alésage orienté radialement (23, 23').
  6. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que
    l'alésage (23, 23') dans la douille (7) est configuré obliquement dans la douille (7).
  7. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce que
    la douille (7) présente plusieurs alésages (23, 23') qui conduisent depuis un côté extérieur (20) de la douille (7) jusqu'à une fente annulaire (25) entre le côté intérieur (26) de la douille (7) et le boulon de soupape (8), et en ce que l'espace de soupape (9) peut être connecté par le biais de la fente annulaire (25) et des alésages (23, 23') dans la douille (7) au canal haute pression (16).
  8. Soupape d'injection de combustible selon la revendication 7,
    caractérisée en ce
    qu'au moins une partie des alésages (23, 23') est configurée de manière répartie sur la périphérie dans la douille (7) par rapport à un axe (24) du boulon de soupape (8).
  9. Soupape d'injection de combustible selon la revendication 7 ou 8,
    caractérisée en ce
    qu'au moins une partie des alésages (23, 23') est configurée de manière répartie axialement dans la douille (7) par rapport à un axe (24) du boulon de soupape (8).
  10. Soupape d'injection de combustible selon l'une quelconque des revendications 7 à 9,
    caractérisée en ce que
    des ouvertures débouchantes (40) des alésages (23'), au niveau desquelles les alésages (23') débouchent dans une fente annulaire (25) entre le côté intérieur (26) de la douille (7) et le boulon de soupape (8), présentent au moins approximativement le même diamètre de sortie (d).
EP20120158513 2011-04-11 2012-03-08 Soupape d'injection de combustible Not-in-force EP2511514B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201110007106 DE102011007106A1 (de) 2011-04-11 2011-04-11 Brennstoffeinspritzventil

Publications (3)

Publication Number Publication Date
EP2511514A2 EP2511514A2 (fr) 2012-10-17
EP2511514A3 EP2511514A3 (fr) 2013-11-13
EP2511514B1 true EP2511514B1 (fr) 2014-11-19

Family

ID=45833180

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20120158513 Not-in-force EP2511514B1 (fr) 2011-04-11 2012-03-08 Soupape d'injection de combustible

Country Status (2)

Country Link
EP (1) EP2511514B1 (fr)
DE (1) DE102011007106A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012212614A1 (de) 2012-07-18 2014-01-23 Continental Automotive Gmbh Piezoinjektor mit hydraulisch gekoppelter Düsennadelbewegung
DE102012222509A1 (de) 2012-12-07 2014-06-12 Continental Automotive Gmbh Piezoinjektor
DE102012223934B4 (de) 2012-12-20 2015-10-15 Continental Automotive Gmbh Piezoinjektor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004061800A1 (de) 2004-12-22 2006-07-06 Robert Bosch Gmbh Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine
DE102007042466B3 (de) * 2007-09-06 2009-04-09 Continental Automotive Gmbh Einspritzsystem mit reduzierter Schaltleckage und Verfahren zum Herstellen eines Einspritzsystems
DE102009026564A1 (de) * 2009-05-29 2010-12-02 Robert Bosch Gmbh Kraftstoff-Injektor mit druckausgeglichenem Steuerventil
DE102009027494A1 (de) * 2009-07-07 2011-01-13 Robert Bosch Gmbh Kraftstoff-Injektor mit druckausgeglichenem Steuerventil
DE102009055267A1 (de) * 2009-12-23 2011-06-30 Robert Bosch GmbH, 70469 Druckausgeglichener Kraftstoffinjektor mit Bypass und minimiertem Ventilraumvolumen

Also Published As

Publication number Publication date
DE102011007106A1 (de) 2012-10-11
EP2511514A3 (fr) 2013-11-13
EP2511514A2 (fr) 2012-10-17

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