EP2438288B1 - Soupape de commande - Google Patents

Soupape de commande Download PDF

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Publication number
EP2438288B1
EP2438288B1 EP10713929.7A EP10713929A EP2438288B1 EP 2438288 B1 EP2438288 B1 EP 2438288B1 EP 10713929 A EP10713929 A EP 10713929A EP 2438288 B1 EP2438288 B1 EP 2438288B1
Authority
EP
European Patent Office
Prior art keywords
valve
guide
seat
guide section
seat surface
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
EP10713929.7A
Other languages
German (de)
English (en)
Other versions
EP2438288A1 (fr
Inventor
Wolfgang Stoecklein
Andreas Rettich
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 EP2438288A1 publication Critical patent/EP2438288A1/fr
Application granted granted Critical
Publication of EP2438288B1 publication Critical patent/EP2438288B1/fr
Active 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
    • 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
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0019—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of electromagnets or fixed armatures
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a switching valve, in particular a solenoid valve for fuel injection valves, and a fuel injection valve with such a switching valve.
  • the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
  • a fuel injector with a pressure compensated control valve is known.
  • an injection valve member which opens or closes an injection port, is driven by a control valve, the control valve releasing or closing a connection from a control chamber into a fuel return by placing or releasing a closing element in a seat.
  • the hydraulic forces are minimized via a pressure compensation.
  • the spring force can be reduced with less stroke and larger cross-sectional area. As a result, short switching times and advantageous dynamics are possible.
  • the from the DE 10 2006 021 741 A1 known fuel injector has the disadvantage that it may come to a seat leakage due to a misalignment of an anchor and a lack of centering due to a formed flat seat. Furthermore, the control valve is relatively sensitive to particles, since the support effect is limited. In addition, the seat limitation can only be done via the anchor, with very small seat lengths with two functional edges, which also adversely affects the coating and particle impacts.
  • a switching valve according to the preamble of claim 1 is known from DE 102 007 009 165 known.
  • the switching valve according to the invention with the features of claim 1 and the fuel injection valve according to the invention with the features of claim 12 have the advantage that an operation is improved. Specifically, there is the advantage that a robust switching valve can be created, which is also suitable for high pressures.
  • the space into which the channel of the valve piece opens between the guide section and the sealing seat is formed at least partially in the guide opening.
  • a puncture is provided on the valve piece between the guide portion and the valve seat surface, and that the space into which opens the channel of the valve piece between the guide portion and the sealing seat, at least substantially predetermined by the puncture, wherein an inner wall of the guide opening bounded by the recess space.
  • the guide opening is designed as a guide bore, in particular as a continuous guide bore, and that at least the guide section of the valve piece is configured axially symmetrical to an axis of the guide bore.
  • a guide between the valve piece and the valve closing body is ensured, so that a leak on the sealing seat is prevented by misalignment of the valve closing body.
  • a relatively large guide play is predetermined between the guide section and the guide bore. In this way, a tensile load between the guide portion and the rest of the valve piece can be reduced. About the relatively large leadership game targeted leakage is possible.
  • a lateral bevel is provided on the guide section, on which a leakage gap is formed between the guide section and the guide bore.
  • About the leakage gap can also be a tensile load between the guide portion and the rest of the valve piece can be reduced.
  • the channel which opens into the space between the guide portion and the sealing seat, designed as a throttled channel.
  • the channel can be realized through the channel, in particular an outlet throttle.
  • valve closing body has a sealing edge which faces the valve seat surface, that the sealing seat between the sealing edge and the valve seat surface is formed and that a predetermined by the sealing edge seat diameter of the sealing seat is at least approximately equal to a diameter of the guide portion of the valve piece.
  • valve seat surface is designed as a conical valve seat surface and that an opening angle of the conical valve seat surface is selected from a range of about 80 ° to about 120 °.
  • sealing edge is configured on a conical end face of the valve closing body and that an opening angle of the conical end face is greater than the opening angle of the conical valve seat surface. This allows an advantageous centering effect of the valve closing body with respect to the valve seat surface of the valve piece. Thus, leakage at the sealing seat by misalignment or the like can be prevented.
  • a seat limitation may be mounted in or on the valve piece.
  • the seat diameter of the sealing seat is not greater than 2 mm, in particular approximately equal to 1.8 mm.
  • a relatively large leakage which may occur, for example, with a seat diameter of 2.5 mm, be prevented and a high pressure resistance for very high pressures, especially for pressures of more than 160 MPa (1600 bar), created.
  • Fig. 1 shows an embodiment of a fuel injection valve 1 with a switching valve 2 in a schematic, excerpt, axial sectional view.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the fuel injector 1 is for a fuel injection system having a fuel rail which supplies diesel fuel under high pressure to a plurality of fuel injectors 1.
  • the fuel injection valve according to the invention 1 and the switching valve 2 according to the invention are also suitable for other applications.
  • the switching valve 2 has a valve piece 3, on which a valve seat surface 4 is formed. Furthermore, the switching valve 2 has a valve closing body 5, which cooperates with the valve seat surface 4 to a sealing seat.
  • the valve closing body 5 is a part of an armature 6. In this case, the valve closing body 5 is formed integrally with the armature 6. However, the valve closing body 5 can also be connected to the armature 6.
  • a solenoid 8 is arranged, which serves to generate a magnetic field for actuating the valve closing body 5 of the armature 6 by means of the magnetic core 7. As a result, the sealing seat formed between the valve closing body 5 and the valve seat surface 4 can be opened and closed.
  • the armature 6 is in this case guided on a pressure pin 9, which is supported on a support element 10. Further, a valve spring 11 is provided, which is arranged between the support member 10 and the armature 6, to bias the armature 6 against a magnetic attraction of the magnetic core 7, which is controllable by a current through the magnetic coil 8. In this case, the force of the valve spring 11 influences the contact force of an edge 12 of the valve closing body 5 against the valve seat surface 4 when the sealing seat is closed.
  • valve piece 3 is inserted into a further housing part 13 of the fuel injection valve 1.
  • the valve member 3 is supported on a shoulder 14 of the housing part 13.
  • the valve piece 3 has a bore 15 in which a control chamber 16 is delimited by a valve piston 17.
  • In the control chamber 16 performs an inlet throttle 18, which connects the control chamber 16 with a high-pressure chamber 19 in the interior of the housing part 13.
  • the switching valve 2 has an axis 25, on which the armature 6 and the valve piece 3 are aligned.
  • the armature 6 is designed axially symmetrical to the axis 25.
  • the valve piece 3 is designed substantially axially symmetrical to the axis 25.
  • the valve piece 3 has a guide portion 26 which is guided in a guide bore 27 of the armature 6.
  • the guide bore 27 is configured here as a continuous guide bore 27.
  • In the guide bore 27 also extends the pressure pin 9 to guide the armature 6 on the pressure pin 9.
  • a recess 28 is provided on the valve piece 3.
  • a fuel chamber 29 is formed, which is bounded by an inner wall 30 of the guide bore 27 of the armature 6. The fuel room 29 is thus formed between the guide portion 26 and the valve seat surface 4.
  • the valve piece 3 has an axial blind bore 31, from which a channel 32 and a channel 33 branch off. About the blind bore 31 and the channels 32, 33 of the control chamber 16 is connected to the fuel chamber 29.
  • the channels 32, 33 are designed as throttled channels 32, 33.
  • the channels 32, 33 both open into the fuel chamber 29 between the guide portion 26 and the sealing seat, which is formed at the edge 12 between the valve closing body 5 and the valve seat surface 4.
  • the fuel space 29 is formed in the guide bore 27.
  • the edge 12 of the valve closing body 5 is designed as a sealing edge on which the sealing seat between the valve closing body 5 and the valve seat surface 4 comes about.
  • the sealing edge 12 faces the valve seat surface 4.
  • a diameter 34 of the sealing edge 12 is at least approximately the same size as a diameter 35 of the guide portion 26. This is in relation to the fuel chamber 29, a pressure equalization allows.
  • the diameter 34 is very small, so that a seat diameter of the sealing seat is also very small.
  • the diameter 34 and thus the seat diameter at the sealing edge 12 can not be greater than 2 mm, in particular approximately equal to 1.8 mm.
  • the armature 6 has an end face 36 which faces the valve seat surface 4 of the valve piece 3.
  • the sealing edge 12 is formed between the end face 36 and the inner wall 30 of the guide bore 27.
  • the conical valve seat surface 4 for example, has an opening angle which is equal to 90 °.
  • An opening angle of the conical end face 36 of the valve closing body 5 is greater than the opening angle of the conical valve seat surface 4, that is, in this embodiment, greater than 90 ° selected.
  • the opening angle of the conical valve seat surface 4 is determined by the required centering and may be in a range of less than 120 °. It is particularly advantageous if it is in a range of about 80 ° to about 120 °.
  • the opening angle the conical end face 36 of the valve closing body 5 is then selected to be greater than the opening angle of the conical valve seat surface 4.
  • the valve seat surface 4 is limited by a step 37. In this way, a maximum diameter 38 of the valve seat surface 4 can be predetermined for seat limitation.
  • the seat limitation can be attached to the valve member 3 through the step 37 or in other ways.
  • the guide section 26 is preferably made relatively short along the axis 25. This short guide section 26 essentially serves for centering during assembly. The leadership of the armature 6 via the pressure pin 9. The pressure forces from the seat diameter are preferably absorbed by the pressure pin 9. About the support member 10 thus takes place a support to a magnet group. In this case, the guide section 26 does not seal against the high pressure in the fuel chamber 29. This ensures that the valve member 3 in the region of the recess 28 and in particular at the mouths of the channels 32, 33 is not loaded on train and thus in this area no or only very small tensile stresses in the valve piece 3 occur. Here it is possible to provide a further strain relief.
  • a bevel 39 may be provided on one side of the guide section 26, which forms a leakage gap between the guide section 26 and the inner wall 30 of the guide bore 27.
  • the guide portion 26 in which no bevel 39 or the like is provided.
  • the guide portion 26 is thereby configured axially symmetrical to the axis 25. In this way, a certain amount of guidance can be achieved in order to achieve a reliable closing of the sealing seat between the sealing edge 12 and the valve seat surface 4. Specifically, a tilting between the valve closing body 5 and the valve member 3 is prevented or at least reduced, whereby a self-centering of the sealing edge 12 is supported on the conical valve seat surface 4.

Claims (11)

  1. Soupape de commutation (2), en particulier soupape magnétique pour des soupapes d'injection de carburant de moteurs à combustion interne à auto-allumage et compression d'air, comprenant une pièce de soupape (3) sur laquelle est réalisée une surface de siège de soupape (4), et un corps de fermeture de soupape (5) qui fait partie d'une armature (6) et qui coopère avec la surface de siège de soupape (4) pour produire un siège d'étanchéité, la pièce de soupape (3) présentant une portion de guidage (26) sur laquelle le corps de fermeture de soupape (5) est guidé avec une ouverture de guidage (27), et la pièce de soupape (3) présentant au moins un canal (32, 33) qui débouche dans une chambre à combustible (29) entre la portion de guidage (26) et le siège d'étanchéité,
    caractérisée en ce que
    l'armature (6) est guidée au niveau d'un boulon de pression (9) qui s'appuie contre un élément de support (10) et en ce qu'entre la portion de guidage (26) et l'alésage de guidage (27) est réalisée une fente de fuite de sorte qu'il se produise une égalisation de la pression dans l'alésage de guidage (27) entre la portion de guidage (26) et le boulon de pression (9) avec la pression dans la chambre à combustible (29).
  2. Soupape de commutation selon la revendication 1, caractérisée en ce que la chambre (29) dans laquelle débouche le canal (32, 33) de la pièce de soupape (3) entre la portion de guidage (26) et le siège d'étanchéité est réalisée au moins en partie dans l'ouverture de guidage (27).
  3. Soupape de commutation selon la revendication 1 ou 2, caractérisée en ce qu'une encoche (28) est prévue au niveau de la pièce de soupape (3) entre la portion de guidage (26) et la surface de siège de soupape (4) et en ce que la chambre (29) dans laquelle débouche le canal (32, 33) de la pièce de soupape (3) entre la portion de guidage (26) et le siège d'étanchéité est au moins essentiellement prédéfinie par l'encoche (28), une paroi interne (30) de l'ouverture de guidage (27) limitant la chambre (29) prédéfinie par l'encoche (28).
  4. Soupape de commutation selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'ouverture de guidage (27) est configurée sous forme d'alésage de guidage (27), en particulier sous forme d'alésage de guidage traversant (27), et en ce qu'au moins la portion de guidage (26) de la pièce de soupape (3) est configurée sous forme axialement symétrique par rapport à un axe (25) de l'alésage de guidage (27).
  5. Soupape de commutation selon l'une quelconque des revendications 1 à 3, caractérisée en ce qu'un biseau latéral (39) est prévu sur la portion de guidage (26).
  6. Soupape de commutation selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le canal (32, 33) qui débouche dans la chambre (29) entre la portion de guidage (26) et le siège d'étanchéité est réalisé sous forme de canal étranglé (32, 33).
  7. Soupape de commutation selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le corps de fermeture de soupape (5) présente une arête d'étanchéité (12) qui est tournée vers la surface de siège de soupape (4), en ce que le siège d'étanchéité est formé entre l'arête d'étanchéité (12) et la surface de siège de soupape (4) et en ce qu'un diamètre de siège (34) du siège d'étanchéité, prédéfini par l'arête d'étanchéité (12), est au moins approximativement égal à un diamètre (35) de la portion de guidage (26) de la pièce de soupape (3).
  8. Soupape de commutation selon la revendication 7, caractérisée en ce que la surface de siège de soupape (4) est configurée sous forme de surface de siège de soupape conique (4) et en ce qu'un angle d'ouverture de la surface de siège de soupape conique (4) est choisi dans une plage d'environ 80° à environ 120°.
  9. Soupape de commutation selon la revendication 8, caractérisée en ce que l'arête d'étanchéité (12) est configurée au niveau d'une surface frontale conique (36) du corps de fermeture de soupape (5) et en ce qu'un angle d'ouverture de la surface frontale conique (36) est supérieur à l'angle d'ouverture de la surface de siège de soupape conique (4).
  10. Soupape de commutation selon l'une quelconque des revendications 7 à 9, caractérisée en ce que le diamètre de siège (34) du siège d'étanchéité n'est pas supérieur à 2 mm, en particulier vaut au moins approximativement 1,8 mm.
  11. Soupape d'injection de carburant (1), en particulier injecteur pour installations d'injection de carburant de moteurs à combustion interne à auto-allumage et compression d'air, comprenant une soupape de commutation (2) selon l'une quelconque des revendications 1 à 10.
EP10713929.7A 2009-06-05 2010-04-13 Soupape de commande Active EP2438288B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910026774 DE102009026774A1 (de) 2009-06-05 2009-06-05 Schaltventil
PCT/EP2010/054810 WO2010139501A1 (fr) 2009-06-05 2010-04-13 Soupape de commande

Publications (2)

Publication Number Publication Date
EP2438288A1 EP2438288A1 (fr) 2012-04-11
EP2438288B1 true EP2438288B1 (fr) 2014-11-12

Family

ID=42313859

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10713929.7A Active EP2438288B1 (fr) 2009-06-05 2010-04-13 Soupape de commande

Country Status (4)

Country Link
EP (1) EP2438288B1 (fr)
CN (1) CN102803704B (fr)
DE (1) DE102009026774A1 (fr)
WO (1) WO2010139501A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201600070056A1 (it) * 2016-07-06 2018-01-06 Magneti Marelli Spa Pompa carburante con una valvola di massima pressione perfezionata per un sistema di iniezione diretta
CN106014740B (zh) * 2016-07-25 2018-12-11 成都威特电喷有限责任公司 消除阀杆轴向力的控制阀

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1707798B1 (fr) * 2005-03-14 2010-05-19 C.R.F. Società Consortile per Azioni Soupape de dosage asservie réglable pour un injecteur de carburant ainsi que sa méthode de réglage
DE102006021741A1 (de) 2006-05-10 2007-11-15 Robert Bosch Gmbh Kraftstoffinjektor mit druckausgeglichenem Steuerventil
DE102007009165A1 (de) * 2007-02-26 2008-08-28 Robert Bosch Gmbh Kraftstoffinjektor mit einer zusätzlichen Ablaufdrossel oder mit einer verbesserten Anordnung derselben im Steuerventil
DE102007013248A1 (de) * 2007-03-20 2008-09-25 Robert Bosch Gmbh Druckausgeglichenes Schaltventil
DE102007018005A1 (de) * 2007-04-17 2008-10-23 Robert Bosch Gmbh Injektor
DE102007044361A1 (de) * 2007-09-17 2009-03-19 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor

Also Published As

Publication number Publication date
CN102803704A (zh) 2012-11-28
WO2010139501A1 (fr) 2010-12-09
EP2438288A1 (fr) 2012-04-11
DE102009026774A1 (de) 2010-12-09
CN102803704B (zh) 2015-08-12

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