EP2185807B1 - Vanne de commande pour un injecteur - Google Patents

Vanne de commande pour un injecteur Download PDF

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Publication number
EP2185807B1
EP2185807B1 EP08787092A EP08787092A EP2185807B1 EP 2185807 B1 EP2185807 B1 EP 2185807B1 EP 08787092 A EP08787092 A EP 08787092A EP 08787092 A EP08787092 A EP 08787092A EP 2185807 B1 EP2185807 B1 EP 2185807B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
guide
valve sleeve
region
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
EP08787092A
Other languages
German (de)
English (en)
Other versions
EP2185807A1 (fr
Inventor
Friedrich Boecking
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 EP2185807A1 publication Critical patent/EP2185807A1/fr
Application granted granted Critical
Publication of EP2185807B1 publication Critical patent/EP2185807B1/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
    • 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
    • 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
    • F02M63/007—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
    • 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

Definitions

  • the invention relates to a control valve for a fuel injector with the features of the preamble of claim 1.
  • Out EP 1 612 403 A1 is a force-balanced control valve is known in which a valve sleeve is guided axially movable on a valve body.
  • the valve sleeve defines an annular space to the outside, which is connected to a control chamber of a nozzle needle of the fuel injector via an outlet throttle.
  • a closing spring By a closing spring, the valve sleeve is pressed against a valve seat formed on the valve body and thereby closes the annular space to the outside.
  • the valve sleeve is moved by an electromagnetic actuator and thereby operated force-free, ie, that no force is exerted in the direction of movement of the valve sleeve by the fuel pressure in the annulus.
  • valve sleeve is pulled away via an electromagnet of the electromagnetic actuator from the valve seat, which can be done very quickly by the lack of hydraulic force component and overcoming the relatively small closing force of the closing spring.
  • the control chamber of the nozzle needle is connected to a low-pressure / return system and as a result depressurized.
  • a disadvantage of such a technical solution is that over the system pressure, the dynamics of the fuel injector on the control valve remains constant and the control valve does not open automatically at massive excess of the maximum pressure in order to have a safety function.
  • the control valve according to the invention with the characterizing features of claim 1 has the advantage that the control valve opens faster. This is achieved by the formation of a dynamic pressure stage in the guide gap between the valve sleeve and guide pin.
  • the dynamic pressure level is created by a targeted widening of the guide clearance on the valve sleeve by the valve sleeve in the region of the valve seat portion is stiff and relatively soft in the remaining area of the guide portion.
  • the valve sleeve in the region of the valve seat portion has a higher rigidity than in the region of the guide portion, so that the guide clearance of the guide diameter of the valve sleeve widens relative to the valve seat diameter with increasing pressure in the annular space.
  • the minimum, self-forming dynamic pressure stage generates, for example, at an increase in pressure from 200 to 1800 bar an opening force of, for example, 8 - 10N.
  • this dynamic pressure stage causes the control valve to open automatically when the closing force of the closing spring is exceeded, thereby reducing the pressure in the uncritical low-pressure / return region.
  • the force-balanced function of the control valve is maintained in that the valve seat has the same diameter as the guide portion of the valve sleeve.
  • the dynamic pressure stage which forms relative to the diameter of the valve seat, arises because within the valve sleeve of the annulus is pressurized with system pressure of the common rail and the valve sleeve from the outside surrounded by the leak oil pressure, which corresponds to the pressure of the low pressure / return system, for example, 10 bar.
  • valve sleeve in the form that in the region of the guide portion, the valve sleeve is made relatively soft compared to the region of the valve seat portion is advantageously formed by the outer diameter D1 in the region of the guide portion is smaller than the outer diameter D2 in the region of the valve seat portion.
  • a fuel injector for a common rail system of a diesel injection device is shown in partial section, with an injector housing 10, a base body 11, a nozzle needle 12, a control valve 13 and an actuating element 14.
  • the main body 11, a guide member 15 for the nozzle needle 12 and a valve member 16 for the control valve 13 is inserted hydraulically tight in the injector 10 and separates a high-pressure chamber 17 of a low-pressure chamber 37.
  • annular high-pressure chamber 17 opens a high-pressure bore 18 which is connected to the unillustrated Commom Rail system.
  • a control chamber 20 is formed, to which the nozzle needle 12 is exposed to a control surface 21. From the high-pressure chamber 17, an inlet bore 22 with an inlet throttle 23 leads into the control chamber 20.
  • the valve piece 16 has a guide pin 31, on which a valve sleeve 32 is arranged to be axially displaceable.
  • the valve sleeve 32 is designed with a guide cylinder 34 and a plate-shaped magnet armature 35.
  • the valve sleeve 32 is guided axially displaceably with the guide cylinder 34 with a guide diameter d on the guide pin 31, wherein a guide gap 39 is present in the region of the guide diameter d between the guide pin 31 and the valve sleeve 32.
  • the valve sleeve 32 has a control chamber remote end portion 45 and a control near the end portion 47.
  • a sealing surface 43 is further formed, with which the valve sleeve 32 rests with a valve seat diameter on a valve seat 33 formed on the valve seat 33.
  • the sealing surface 43 and the valve seat 33 can, as the embodiments in FIG. 1 . 3 and 4 or FIG. 2 and 4 show, be formed at different locations on the valve member 16 and on the valve sleeve 32.
  • valve sleeve 32 Between guide pin 31 and valve sleeve 32, an annular space 36 is further formed.
  • the valve sleeve 32 is further surrounded by the low pressure chamber 37, which is connected to a pressurized with leak oil pressure, not shown, low pressure / return system.
  • a closing spring 38 acts on the valve sleeve 32, so that the valve sleeve 32 is held with the sealing surface 43 against the valve seat 33 in the closed position.
  • a riser 25 with an outlet throttle 26 and, for example, two oblique holes 27 are arranged, which lead from the riser hole 25 into the annular space 36.
  • About the riser 25 with the outlet throttle 26 and the oblique holes 27 of the control chamber 20 is hydraulically connected to the annular space 36.
  • the adjusting element 14 which is for example a magnetic actuator, comprises a magnetic coil 41, which is fixed in a magnetic core 42 and acts on the armature 35 of the valve sleeve 32.
  • the electromagnetic actuator 14 forms together with the control valve 13, a servo-valve for controlling the control chamber 20th
  • the valve sleeve 32 has a guide portion 48 and a valve seat portion 49.
  • the guide portion 48 is formed with an outer diameter D1 and the valve seat portion 49 with an outer diameter D2, where D1 ⁇ D2.
  • the annular space 36 is incorporated in the valve sleeve 32.
  • the valve seat 33 is formed there on an actuating element-side section of the guide pin 31.
  • the valve seat portion 49 with the outer diameter D2 and with the sealing surface 43 located at the control room remote end portion 45 of the valve sleeve 32.
  • the larger outer diameter D2 of the valve seat portion 49 is realized by the wall of the valve sleeve 32 at the control room remote end portion 45 through the plate-shaped armature 35 is stronger than in the underlying guide section 48.
  • the annular space 36 is incorporated in the guide pin 31.
  • the valve seat portion 33 is located at a control-room-side end portion of the guide pin 31.
  • the valve seat portion 49 with the outer diameter D2 and the sealing surface 43 is located at the control chamber near end portion 47 of the valve sleeve 32.
  • the larger outer diameter D2 of the valve seat portion 49 is realized by the wall of the Valve sleeve 32 is thickened at the control chamber near end portion 47.
  • the valve sleeve 32 on the valve seat portion 49 is relatively stiff and the rest of the guide portion 48 relative soft. This measure has the effect that the guide diameter d of the valve sleeve 32 in the region of the guide section 48 can widen relative to the valve seat diameter of the valve seat 33. In the region of the valve seat portion 49, the valve sleeve 32 remains rigid, so that there the guide diameter d does not expand or significantly less expands than in the region of the guide portion 48, so that there the guide diameter d corresponds substantially to the valve seat diameter. As a result arises according to FIGS.
  • valve sleeve 32 The rigidity of the valve sleeve 32 should be designed so that the pressure stage 51 acts in the opening direction of the valve seat 33 of the valve sleeve 32.
  • the widening 50 arises due to the high pressure of, for example, 1800 bar of the common rail pressure, which acts via the riser bore 25, the oblique bore 27 and via the annular space 36 in the guide gap 39 from the inside to the valve sleeve 32. Because only the pressure in the low-pressure chamber 37 leak oil pressure of less than 10 bar acts on the outside of the valve sleeve 32, said expansion 50 is formed with the dynamically acting compression stage 51st
  • the emergence of the expansion 50 is exploited by the present invention to produce relative to the valve seat diameter of the valve seat 33, the dynamic pressure acting stage 51 in the guide gap 39 in the opening direction of the valve sleeve 32. This ensures that the valve sleeve 32 opens quickly when actuated by the actuator 14 and / or that at a rail pressure exceeding the valve sleeve 32 lifts off the valve seat 33 without activation by the actuator 14.

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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 (7)

  1. Vanne de commande servant à piloter un espace de commande (20) d'un injecteur de carburant, avec un manchon de vanne (32) guidé de façon mobile, avec un diamètre de guidage d au niveau d'un tenon de guidage (31), avec un cylindre de guidage (34), et avec une force de fermeture appuyant contre un siège de vanne (33) réalisé au niveau du tenon de guidage (31), le manchon de vanne (32) pouvant être actionné par un élément de réglage (14) et comportant une section de guidage (48) ainsi qu'une section de siège de vanne (49), une fente de guidage (39) étant présente entre le manchon de vanne (32) et le tenon de guidage (31) et un espace annulaire (36) étant réalisé, ledit espace annulaire (36) étant délimité par le manchon de vanne (32) en interaction avec le siège de vanne (33) et l'espace annulaire (36) et l'espace de commande (20) étant reliés par le biais d'une liaison hydraulique (25, 26, 27), caractérisée en ce que le manchon de vanne (32) présente une rigidité supérieure dans la zone de la section de siège de vanne (49) à celle régnant dans la zone de la section de guidage (48), de telle sorte qu'un élargissement (50) de la fente de guidage (39) se produit au niveau du manchon de vanne (32) en présence d'une haute pression s'exerçant dans l'espace annulaire (36), ledit manchon étant pour l'essentiel limité sur la zone de la section de guidage (48) et formant à cet endroit un étage de pression (51) dynamique au niveau du diamètre de guidage d du manchon de vanne (32), l'étage de pression (51) dynamique agissant sur le manchon de vanne (32) dans la direction d'ouverture.
  2. Vanne de commande selon la revendication 1, caractérisée en ce que le manchon de vanne (32) présente un diamètre extérieur D1 dans la zone de la section de guidage (48) et un diamètre extérieur D2 dans la zone de la section de siège de vanne (49) et que pour obtenir des rigidités différentes du manchon de vanne (32) dans la zone de la section de guidage (48) et dans la zone de la section de siège de vanne (49), le diamètre extérieur D1 observé dans la zone de la section de guidage (48) est inférieur au diamètre extérieur D2 observé dans la zone de la section de siège de vanne (49).
  3. Vanne de commande selon la revendication 1 ou 2, caractérisée en ce que le manchon de vanne (32) comporte une section d'extrémité (45) située à distance de l'espace de commande et une section d'extrémité (47) située à proximité de l'espace de commande et que la section de siège de vanne (49) est réalisée au niveau de la section d'extrémité (45) située à distance de l'espace de commande.
  4. Vanne de commande selon la revendication 1 ou 2, caractérisée en ce que le manchon de vanne (32) comporte une section d'extrémité (45) située à distance de l'espace de commande et une section d'extrémité (47) située à proximité de l'espace de commande et que la section de siège de vanne (49) est réalisée au niveau de la section d'extrémité (47) située à proximité de l'espace de commande.
  5. Vanne de commande selon l'une quelconque des revendications précédentes, caractérisée en ce que l'espace annulaire (36) est réalisé au niveau du manchon de vanne (32).
  6. Vanne de commande selon l'une quelconque des revendications précédentes, caractérisée en ce que l'espace annulaire (36) est réalisé au niveau de l'élément de vanne (31).
  7. Vanne de commande selon l'une quelconque des revendications précédentes, caractérisée en ce que la haute pression correspond à la pression du système d'une rampe commune d'un dispositif d'injection de Diesel.
EP08787092A 2007-08-27 2008-08-11 Vanne de commande pour un injecteur Not-in-force EP2185807B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710040248 DE102007040248A1 (de) 2007-08-27 2007-08-27 Steuerventil für einen Kraftstoffinjektor
PCT/EP2008/060518 WO2009027215A1 (fr) 2007-08-27 2008-08-11 Vanne de commande pour un injecteur

Publications (2)

Publication Number Publication Date
EP2185807A1 EP2185807A1 (fr) 2010-05-19
EP2185807B1 true EP2185807B1 (fr) 2012-10-31

Family

ID=39951479

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08787092A Not-in-force EP2185807B1 (fr) 2007-08-27 2008-08-11 Vanne de commande pour un injecteur

Country Status (3)

Country Link
EP (1) EP2185807B1 (fr)
DE (1) DE102007040248A1 (fr)
WO (1) WO2009027215A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009046563A1 (de) * 2009-11-10 2011-05-12 Robert Bosch Gmbh Kraftstoffinjektor
DE102013211855A1 (de) * 2013-06-21 2014-12-24 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE602004004254T2 (de) 2004-06-30 2007-07-12 C.R.F. S.C.P.A. Servoventil zum Steuern eines Einspritzventils einer Brennkraftmaschine
EP1707797B1 (fr) * 2005-03-14 2007-08-22 C.R.F. Società Consortile per Azioni Soupape de dosage asservie réglable pour un injecteur de carburant
DE102006027485A1 (de) 2006-06-14 2007-12-20 Robert Bosch Gmbh Kraftstoffeinspritzventil mit Sicherheitssteuerventil

Also Published As

Publication number Publication date
WO2009027215A1 (fr) 2009-03-05
DE102007040248A1 (de) 2009-03-05
EP2185807A1 (fr) 2010-05-19

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