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EP1379779A2 - Soupape a siege/coulisse comportant une tige de compensation de pression - Google Patents

Soupape a siege/coulisse comportant une tige de compensation de pression

Info

Publication number
EP1379779A2
EP1379779A2 EP02727211A EP02727211A EP1379779A2 EP 1379779 A2 EP1379779 A2 EP 1379779A2 EP 02727211 A EP02727211 A EP 02727211A EP 02727211 A EP02727211 A EP 02727211A EP 1379779 A2 EP1379779 A2 EP 1379779A2
Authority
EP
European Patent Office
Prior art keywords
control piston
pressure
way valve
fuel
piston
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.)
Withdrawn
Application number
EP02727211A
Other languages
German (de)
English (en)
Inventor
Nestor Rodriguez-Amaya
Achim Brenk
Wolfgang Klenk
Uwe Gordon
Manfred Mack
Hubert Greif
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 EP1379779A2 publication Critical patent/EP1379779A2/fr
Withdrawn legal-status Critical Current

Links

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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated 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
    • F02M63/0014—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
    • 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
    • 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
    • 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
    • F02M63/0073—Pressure balanced valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86678—Combined disk or plug and gate or piston
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86686—Plural disk or plug

Definitions

  • the size of the metering or discharge cross section can be of any size.
  • a special embodiment of the invention is characterized in that the control piston has two guides has a larger guide diameter and a smaller guide diameter, and that the control piston has a valve seat edge, the diameter of which corresponds to the larger guide diameter.
  • the control piston can be actuated, for example, by an energized magnet. When the solenoid is energized, only the spring preload force of the closing spring has to be overcome to lift the control piston.
  • a special embodiment of the invention is characterized in that the end face of a control piston is acted upon by the prestressing force of a compression spring.
  • the pretensioning force of the compression spring ensures that the associated control piston is held in a switch position of the 3/2-way valve with its valve seat edge in contact with the associated valve seat surface.
  • a connection between a fuel inlet 40 and a connection 41 for the injector 7 (not shown) is interrupted.
  • a connection between the connection 41 and a fuel return 42 is opened.
  • the control piston 44 is pressed against its valve seat 46 by means of a compression spring 45.
  • the pressure at the injector can be reduced via flats 48 in the opened slide seal, which are formed on the circumference of the control piston 44.
  • a central blind hole 50 is recessed in the end of the control piston 44 facing the compression spring 45.
  • the blind hole 50 is connected via a bore 51 to a longitudinal bore 49, in which the control piston 44 is received so as to be able to move back and forth.
  • a piston 52 is received in the blind hole 50 so that it can be moved back and forth.
  • the piston 52 is supported on the valve housing.
  • a desired throttling effect can be set via the diameter of the bore 51, which leads to a time delay in the pressure equalization.
  • control piston 44 Since the control piston 44 has two guides, it is no longer pressure-balanced after opening. Additional hydraulic forces act in the opening direction, which act on the resulting annular surface between the lower and upper guide of the control piston. These forces must be balanced, since they act against the compression spring 45 and prevent the control piston 44 from closing.
  • the pressure equalization is made possible through the blind hole 50.
  • the bore 51 ensures that the hydraulic pressure acts in the blind hole 50 and generates forces in the closing direction of the control piston 44. These forces depend on the diameter of the blind hole 50, the surface of the connecting bore 51 having to be subtracted. If the pressure area in the blind hole 50 is as large as the circular area between the upper and lower guide, then the control piston 44 is completely pressure-balanced.
  • the diameter of the blind hole 50 can, however, also be larger than the pressure area on the control piston 44. As a result, additional forces can be generated which enable accelerated closing. However, the additional closing forces should remain so low that the balance of forces is not shifted too much.
  • fuel pressure is only present at the injector (not shown) when the injection is to be carried out.
  • a metering valve 8 is shown in FIG. 3, in which a control piston 56 is activated with the aid of a piezoceramic.
  • connection between the connection 55 and the fuel return 58 is interrupted at the same time.
  • fuel subjected to high pressure passes from the fuel inlet 54 via the connection 55 to the injector, from which the injection takes place.
  • a hydraulic medium contained in a coupling space 59 for example Fuel displaced by a booster piston 60.
  • the translation piston 60 is actuated by a piezo actuator 69.
  • a central blind hole 62 is recessed, in which a pressure compensation piston 61 is accommodated so that it can move back and forth.
  • the pressure compensation piston 61 is supported on the housing by a screw plug.
  • the blind hole 62 is connected to the interior of the valve body 53 via a bore 63.
  • the pressure equalization required to compensate for the additional forces is made possible by the blind hole 62.
  • the pressurization of the blind hole 62 generates forces in the closing direction of the control piston 56.
  • the magnitude of the forces is determined by the cross-sectional area of the blind hole 62. If the pressure area of the blind hole 62 is as large as the circular area between the upper and lower control piston guide, then the control piston 56 is completely pressure-balanced and can by the forces of the Closing spring 64 can be easily closed.
  • the diameter of the blind hole 62 can also be larger than the pressure area on the control piston 56. As a result, additional forces for accelerated closing of the control piston 56 can be generated.
  • the pressure compensation piston 61 guided in the blind hole 62 prevents fuel from permanently flowing out of the pressure compensation space of the blind hole 62 into the fuel return.
  • the piezoceramic enables faster switching times than with conventional valves.
  • the number of components used is also reduced.
  • Another advantage is that the actuator unit can be made compact and short.
  • the stroke curve of the piezo actuator can be regulated. By dispensing with a complex servo circuit, the manufacturing and testing effort is significantly reduced.
  • FIGS. 4 and 5 show a special form of pressure relief. This pressure relief can be used in all embodiments of the invention and is described below by way of example using a one-piece control piston.
  • a diameter widening 71 is formed on the control piston 70.
  • the Diameter expansion 71 merges into a cylindrical / section 72 with a larger outer diameter.
  • a circumferential groove 73 is formed in the cylindrical section 72 of the control piston 70 in the area of the fuel return 68.
  • the relief stroke of the control piston 70 is designated 74.
  • control space provided above the control piston 70 is relieved.
  • the control piston 70 makes a stroke movement in this way and the connection between the fuel accumulator and the injection nozzle is established.
  • the connection to the fuel return, which is still open until then, is interrupted by the further stroke movement, since the control edge on the control piston 70 dips into the valve housing 65.
  • the end of the injection is initiated by the energization of the solenoid valve, as a result of which the solenoid valve closes the flow restrictor.
  • pressure builds up again in the control chamber through the inlet throttle in the control piston. This pressure pushes the control piston back into its seat. This opens the relief cross-section.
  • the injection nozzle and pressure line are thus connected to the fuel return. The injection pressure drops quickly and the control piston closes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une soupape à 3/2 voies destinée à la commande de l'injection de carburant dans un système d'injection à rampe commune d'un moteur à combustion interne. Ladite soupape présente une première position dans laquelle un injecteur est relié à un retour de carburant, et une deuxième position dans laquelle l'injecteur est relié à un accumulateur de carburant haute pression. L'invention vise à améliorer la qualité de l'injection. A cet effet, ladite soupape à 3/2 voies comporte un piston de commande à équilibrage des forces (44), la rampe hélicoïdale du piston de commande (44) étant équilibrée en pression par l'intermédiaire d'un trou borgne (50).
EP02727211A 2001-03-13 2002-03-12 Soupape a siege/coulisse comportant une tige de compensation de pression Withdrawn EP1379779A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10111929A DE10111929A1 (de) 2001-03-13 2001-03-13 Sitz/Schieber-Ventil mit Druckausgleichsstift
DE10111929 2001-03-13
PCT/DE2002/000862 WO2002073028A2 (fr) 2001-03-13 2002-03-12 Soupape a siege/coulisse comportant une tige de compensation de pression

Publications (1)

Publication Number Publication Date
EP1379779A2 true EP1379779A2 (fr) 2004-01-14

Family

ID=7677215

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02727211A Withdrawn EP1379779A2 (fr) 2001-03-13 2002-03-12 Soupape a siege/coulisse comportant une tige de compensation de pression

Country Status (5)

Country Link
US (1) US6837451B2 (fr)
EP (1) EP1379779A2 (fr)
JP (1) JP2004518875A (fr)
DE (1) DE10111929A1 (fr)
WO (1) WO2002073028A2 (fr)

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Publication number Priority date Publication date Assignee Title
DK1577540T3 (da) * 2004-03-19 2010-09-13 Efi Hightech Ag Styreventil til en brændstofindsprøjtningsventil
DE102004020268A1 (de) * 2004-04-26 2005-11-10 Hydraulik-Ring Gmbh Druckregelventil
US8196844B2 (en) 2004-12-21 2012-06-12 Sturman Industries, Inc. Three-way valves and fuel injectors using the same
JP4865703B2 (ja) * 2005-04-08 2012-02-01 イーグル工業株式会社 容量制御弁
US20070113906A1 (en) * 2005-11-21 2007-05-24 Sturman Digital Systems, Llc Pressure balanced spool poppet valves with printed actuator coils
US20080264497A1 (en) * 2007-04-26 2008-10-30 Rodriguez James E Valve position indicator
DE102009046563A1 (de) * 2009-11-10 2011-05-12 Robert Bosch Gmbh Kraftstoffinjektor
US8689772B2 (en) * 2011-05-19 2014-04-08 Caterpillar Inc. Fuel injector with telescoping armature overtravel feature
EP2706222B1 (fr) * 2012-09-06 2016-07-13 Delphi International Operations Luxembourg S.à r.l. Unité de pompage
CN106609856A (zh) * 2015-10-22 2017-05-03 中核苏阀科技实业股份有限公司 稳压器快速卸压闸阀
US10479159B2 (en) 2016-04-04 2019-11-19 Barksdale, Inc. Ride height leveling with selectable configurations: system and method

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DE2435569C2 (de) * 1974-07-24 1985-06-27 Alfred Teves Gmbh, 6000 Frankfurt Elektromagnetisch betätigbares 3/2-Wegeventil
US4175587A (en) * 1977-10-31 1979-11-27 Chrysler Corporation Fuel injection system and control valve for multi-cylinder engines
DE3406794A1 (de) * 1984-02-24 1985-09-05 Mannesmann Rexroth GmbH, 8770 Lohr Druckregelventil
EP0621426B1 (fr) * 1993-03-19 1998-09-16 Cummins Engine Company, Inc. Soupape à trois voies compensée de pression
EP0622573B1 (fr) * 1993-03-31 1996-06-12 Cummins Engine Company, Inc. Vanne compacte à trois voies, avec une tige dans un manchon
US5518030A (en) * 1994-12-12 1996-05-21 Cummins Engine Company, Inc. Three-way flow valve with variable drain orifice area
DE19605277B4 (de) * 1995-02-15 2004-06-03 Nippon Soken, Inc., Nishio Magnetbetätigtes hydraulisches Steuerventil zur Verwendung im Kraftstoffeinspritzsystem eines Verbrennungsmotors
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DE19701879A1 (de) * 1997-01-21 1998-07-23 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
US5853028A (en) * 1997-04-30 1998-12-29 Eaton Corporation Variable force solenoid operated valve assembly with dampener
DE19724637A1 (de) * 1997-06-11 1998-12-17 Bosch Gmbh Robert Einspritzventil
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Non-Patent Citations (1)

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Title
See references of WO02073028A2 *

Also Published As

Publication number Publication date
US6837451B2 (en) 2005-01-04
JP2004518875A (ja) 2004-06-24
DE10111929A1 (de) 2002-10-02
WO2002073028A2 (fr) 2002-09-19
WO2002073028A3 (fr) 2003-10-23
US20030172978A1 (en) 2003-09-18

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