EP1387946A1 - Injecteur de carburant commande par pression, a reduction de fuite - Google Patents

Injecteur de carburant commande par pression, a reduction de fuite

Info

Publication number
EP1387946A1
EP1387946A1 EP02740295A EP02740295A EP1387946A1 EP 1387946 A1 EP1387946 A1 EP 1387946A1 EP 02740295 A EP02740295 A EP 02740295A EP 02740295 A EP02740295 A EP 02740295A EP 1387946 A1 EP1387946 A1 EP 1387946A1
Authority
EP
European Patent Office
Prior art keywords
control
valve body
pressure
chamber
housing
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.)
Granted
Application number
EP02740295A
Other languages
German (de)
English (en)
Other versions
EP1387946B1 (fr
Inventor
Friedrich BÖCKING
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 EP1387946A1 publication Critical patent/EP1387946A1/fr
Application granted granted Critical
Publication of EP1387946B1 publication Critical patent/EP1387946B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F02M63/0005—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 valves actuated by fluid 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
    • F02M63/0003—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

Definitions

  • High pressure pumps are used to achieve and maintain the operating pressure level. Part of the delivery capacity of the high-pressure pumps is consumed by leakage losses that can occur on the moving components of fuel injectors of such injection systems, with which the fuel under high pressure is injected into the combustion chamber of an internal combustion engine.
  • the required delivery rate of a high pressure pump is a criterion influencing its size.
  • a supply line to a spring-loaded nozzle needle is provided, which can be shut off by a control piston with a valve function.
  • the nozzle needle is pressed onto its needle seat via a needle needle spring, which is supported in a spring chamber.
  • a throttled line connection is designed as a bypass between the supply line and the relief line, the line connection containing a leakage valve connected to the solenoid valve, by means of which the line connection can be interrupted during the injection.
  • the solution according to the invention has the advantage that the control valve is integrated in the inlet from the high-pressure accumulation chamber (common rail) and the leakage is considerably reduced by avoiding the reduction in pressure to leakage oil pressure at the control valve.
  • the control chamber acting on the valve body of the control part is advantageously surrounded by a pot-shaped pressure piece, on which the high-pressure seed pending high pressure is present.
  • the pressure piece that delimits the control chamber rests with a flat seat on the housing of the control unit and is acted upon by this spring element, which in addition to the high pressure prevailing in the housing space holds the pressure element in contact with a wall of the housing space of this control unit.
  • a servo valve is accommodated above the pressure piece, with the servo valve body of which an outlet throttle which relieves the control space can be closed or released.
  • the leakage losses are limited to the control volume that flows through the outlet throttle when the control chamber is relieved of pressure after the servo valve has been activated. Due to the pressure piece integrated in the inlet from the high-pressure accumulation chamber (common rail), this is pressed into the flat seat by the high pressure prevailing there, supported by the spring accommodated below the pressure piece. A pressure reduction at the control part to the leakage oil pressure level can be avoided, which has a favorable influence on the leakage at the control valve.
  • the servo valve and the valve space surrounding the servo valve body are sealed against the high pressure in the inlet from the high pressure collection space.
  • the control volume flowing out of the control chamber when the pressure is relieved of pressure is limited by the dimensioning of the outlet throttle and represents the only volume which flows out of the high-pressure part of the control unit.
  • the high-pressure pump can therefore be designed much more favorably in terms of its delivery rate, which has a favorable influence on its manufacturing costs and size.
  • Another advantage associated with the reduction in the pump size is the lowering of the fuel temperature in the return line of the injector. Too high a fuel temperature would result in the need for a cooler, which represents an additional effort which can be avoided with the reduction in pump size proposed according to the invention.
  • the single figure shows a section through a pressure-controlled control unit without guide leakage, which can be used, for example, on a nozzle holder combination. variants
  • the single figure shows a longitudinal section through the control unit designed according to the invention, the control unit 1 comprising a housing 2.
  • a housing space 4 is formed, which is connected via an inlet 3 to a storage space or high-pressure accumulation space (common rail), in which fuel is acted upon by a high-pressure pump, and is kept at an extremely high pressure level.
  • this high pressure level generated in the accumulator or high-pressure accumulation space (common rail) is also present in the housing space 4 of the control unit 1.
  • a pressure piece 21 is accommodated in the housing space 4 of the control unit 1 as shown in FIG. 1.
  • the pressure piece 21 is essentially designed as a pot-shaped body which is open on one side and bears with a flat surface 23 on a wall of the housing 2 of the control unit 1.
  • a control valve body 5 is inserted into its interior, the end face 8 of which delimits a control chamber 6 with the inner wall of the pressure piece 21.
  • an inlet throttle 7 is formed in the wall of the pressure piece 21 in the area of the control chamber; on the other hand, the control chamber 6, which is delimited by the inside of the pressure piece 21 and the end face 8 of the control valve body 5, can be relieved of pressure via an outlet throttle 28 formed in the upper area of the pressure piece 21.
  • the pressure relief of the control chamber 6 takes place via a servo valve 24 assigned to the outlet throttle 28.
  • the pressure piece 21, received in the housing space 4 of the control unit 1 is on the one hand via a spring element 20 acting on an annular end face 22 of the pressure piece 21 into a flat seat 23 on a wall of the housing 2 of the control unit 1 pressed.
  • the spring element 20 which is supported on the annular end face 22 on the pressure piece 21 on the one hand, is supported on the other hand by the bottom of the housing space 4 in the housing 2 of the control unit 1.
  • the fuel which is under high pressure in the housing space 4 via the inlet 3 from the high-pressure accumulation chamber (common rail) and which acts on the annular end face 22 of the pressure piece 21, places it in its flat seat 23 on the wall of the housing 2.
  • the action of the high pressure present in the housing space 4 on the annular end face 22 of the pressure piece 21 ensures that it rests on the flat seat 23 on the wall of the housing 2 of the control unit 1.
  • the flat seat 23 both on the wall of the housing 2 and on the corresponding side of the pressure piece 21 can be manufactured in a particularly simple manner in terms of production technology.
  • An annular sealing surface 23 is thus available between the pressure piece 21 and the corresponding wall of the housing 2 of the control unit 1, with which a valve chamber 32 of the servo voventils 24 against the housing space 4 and the prevailing high pressure level is sealable.
  • the control valve body 5 of the control unit 1 projects with its upper end face 8 into the control chamber 6, which receives a control volume flowing in via the inlet throttle 7, which can be opened or closed by actuating the servo valve 24 by an actuator 29, which is only shown schematically here.
  • the control valve body 5 is also provided with an annularly extending seat 19 which terminates in a constriction 9 on the control valve body 5.
  • the constriction 9 is followed by flow-free surfaces 10 on the circumference of the control valve body 5, which for example can be formed opposite one another by 180 ° on the circumference of the control valve body 5.
  • control valve body 5 Opposed to the constriction 9 on the control valve body 5 in the housing 2 of the control unit 1 is an annular space 11, from which a nozzle inlet 14 branches off to a nozzle holder combination (not shown here) with an injection nozzle.
  • the control valve body 5 is centered and guided on the one hand in the pressure piece 21 with its upper region; on the other hand, the control valve body 5 is guided below the constriction 9 on the housing surfaces 15. If the control chamber 6, which is delimited by the pressure piece 21 and the upper end face 8 of the control valve body 5, is subjected to a high-pressure control volume via the outlet throttle 7, the control valve body 5 is moved into its seat 18 in the floor of the housing space 4.
  • the ring-shaped seat 19 on the control valve body 5 lies against the conically configured sealing seat in the bottom of the housing 4, so that when the control valve body 5 is closed, that is to say its contact in its sealing seat 18 on the housing side, the nozzle inlet 14 via the annular space 11 in the housing 2 of the control unit 1 and is relieved of pressure via the flow free areas 10 into the leak oil chamber 12.
  • the fuel volume continues to flow from the leak oil chamber 12 in the direction of the leak oil drain 13.
  • the lifting height into which the control valve body 5 enters with its end face 8 when the control chamber 6 is depressurized by actuating the outlet throttle 28 is designated by reference number 30 (h 2 ).
  • a residual overlap 16 of the flow free areas 10 is dimensioned on the circumference of the control valve body 5.
  • the remaining coverage is labeled hi.
  • the outlet throttle 28 in the pressure piece 21 for relieving the pressure in the control chamber 6 is switched by means of a servo valve 24.
  • the servo valve 24 is over here only schematically indicated actuator, for example actuates a piezo actuator 29, which actuates a servo valve body 25 of the servo valve 24 in the direction of the arrow 31.
  • the servo valve body 25 of the servo valve 24 is hemispherical in the illustration according to FIG.
  • the curved side of the hemispherically configured servo valve body 25 interacts with a second seat 27 formed in the housing 2 of the control unit 1, while the essentially flat side of the servo valve body 25 cooperates with a first seat 26 on the upper side of the pressure piece 21.
  • the servo valve body 25 can either be switched into the first seat 26 to close the flow restrictor 28 or into its second seat to close the drain in the housing 2 of the control unit 1.
  • the servo valve body 25 is surrounded by a servo valve space 32, which is formed on the one hand by a wall of the housing 2 of the control unit 1 and on the other hand by the pressure piece 21. Since the servo valve body 25 of the servo valve 24 merely extends between its first seat 26 and its second seat 27 and can be switched, the leakage losses are limited to the control volume controllable from the control chamber 6 via the discharge throttle 28.
  • control volume flows from the control chamber 6 via the outlet throttle 28 into the servo valve chamber 32, so that the Front face 8 of the control valve body 5 moves upwards into the control chamber 6.
  • the servo valve chamber 32 is sealed at its second seat 27, which is closed by the curved part of the control valve body 25. If, on the other hand, the control valve body 25 is actuated by the actuator 29 in the direction of movement 31, the control valve body per 25 with its flat side to the first seat 26 above the outlet throttle 28 in the pressure piece 21 and closes it.
  • a pressure build-up 6 in the control chamber 6 takes place due to the high pressure of the fuel which continuously flows into the control chamber 6 via the inlet throttle 7, as a result of which the control valve body 5 is pressed into its sealing seat 18 in the bottom of the housing chamber 4.
  • the pressure relief of the nozzle inlet 14 takes place via the constriction 9, the annular space 11 and the flow-free areas 10 into the leakage oil space 11 in the low-pressure area of the control unit 1.
  • the servo valve chamber 32 serves, as it were, as a buffer for receiving fuel serving as control volume, which flows into the servo valve chamber 32 from its first seat 26 by releasing the servo valve body 25 by releasing the servo valve body 25. Only the fuel volume flowing out when the servo valve 24 is actuated via the piezo actuator 29 schematically shown here and emerging from the control chamber 6 via the outlet throttle 28 constitutes a leak operate a fuel injection system with the control unit 1 according to the invention, which can be equipped with a substantially smaller dimensioned high pressure pump.

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)

Abstract

La présente invention concerne un système pour injecter du carburant dans la chambre de combustion d'un moteur à combustion interne. Ce système comprend une unité de commande (1) présentant un espace de logement (4) qui est continuellement alimenté en carburant sous haute pression, par l'intermédiaire d'un orifice d'admission d'un espace de stockage (rampe commune). Ce carburant sous haute pression est toujours mis à disposition au niveau d'un espace de commande (6) d'un corps de soupape de commande (5), par l'intermédiaire d'un étranglement d'admission (7). Ce corps de soupape de commande (5) commande l'ouverture ou la fermeture d'un orifice d'admission d'injecteur (14) par rapport à un injecteur. Un élément de pression (21) délimitant l'espace de commande (6) est logé dans l'espace de logement (4) de l'unité de commande (1) et s'appuie avec une surface plane (23) sur le logement (2). Un étranglement de sortie (28) relâchant la pression de l'espace de commande (6) est logé dans cet élément de pression et peut être commandé au moyen d'une servo-soupape (24).
EP02740295A 2001-05-08 2002-04-26 Injecteur de carburant commande par pression, a reduction de fuite Expired - Lifetime EP1387946B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10122245A DE10122245A1 (de) 2001-05-08 2001-05-08 Leckagereduzierter druckgesteuerter Kraftstoffinjektor
DE10122245 2001-05-08
PCT/DE2002/001541 WO2002090759A1 (fr) 2001-05-08 2002-04-26 Injecteur de carburant commande par pression, a reduction de fuite

Publications (2)

Publication Number Publication Date
EP1387946A1 true EP1387946A1 (fr) 2004-02-11
EP1387946B1 EP1387946B1 (fr) 2004-12-15

Family

ID=7683970

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02740295A Expired - Lifetime EP1387946B1 (fr) 2001-05-08 2002-04-26 Injecteur de carburant commande par pression, a reduction de fuite

Country Status (5)

Country Link
US (1) US20040011889A1 (fr)
EP (1) EP1387946B1 (fr)
JP (1) JP2004519602A (fr)
DE (2) DE10122245A1 (fr)
WO (1) WO2002090759A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7650779B2 (en) * 2007-06-05 2010-01-26 Caterpillar Inc. Method and apparatus for determining correct installation for gear-driven fuel pump on a fuel injected IC engine
JP4670878B2 (ja) * 2008-03-07 2011-04-13 株式会社デンソー 制御弁およびインジェクタ
US9212639B2 (en) * 2012-11-02 2015-12-15 Caterpillar Inc. Debris robust fuel injector with co-axial control valve members and fuel system using same

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD102772A1 (fr) * 1973-01-08 1973-12-20
DE3788406T2 (de) * 1986-09-25 1994-04-14 Ganser Hydromag Zuerich Elektronisch gesteuertes Einspritzsystem.
IT1261149B (it) * 1993-12-30 1996-05-09 Elasis Sistema Ricerca Fiat Valvola di dosaggio per il comando dell'otturatore di un iniettore di combustibile
DE19701879A1 (de) * 1997-01-21 1998-07-23 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE19715234A1 (de) * 1997-04-12 1998-06-25 Daimler Benz Ag Magnetventilgesteuertes direkteinspritzendes Kraftstoffeinspritzventil für Speichereinspritzsysteme von mehrzylindrigen Brennkraftmaschinen
DE19742073A1 (de) * 1997-09-24 1999-03-25 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE59908941D1 (de) * 1998-05-28 2004-04-29 Siemens Ag Kraftstoffeinspritzventil für brennkraftmaschinen
DE19936668A1 (de) * 1999-08-04 2001-02-22 Bosch Gmbh Robert Common-Rail-Injektor
DE19939424A1 (de) * 1999-08-20 2001-03-08 Bosch Gmbh Robert Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE19939450A1 (de) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19946841A1 (de) * 1999-09-30 2001-05-03 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10029297A1 (de) * 2000-06-14 2001-10-18 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10100390A1 (de) * 2001-01-05 2002-07-25 Bosch Gmbh Robert Einspritzventil
ITTO20010814A1 (it) * 2001-08-14 2003-02-14 Fiat Ricerche Iniettore di combustibile per un motore endotermico e relativo metododi fabbricazione.

Non-Patent Citations (1)

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Title
See references of WO02090759A1 *

Also Published As

Publication number Publication date
DE10122245A1 (de) 2002-12-12
DE50201793D1 (de) 2005-01-20
EP1387946B1 (fr) 2004-12-15
JP2004519602A (ja) 2004-07-02
US20040011889A1 (en) 2004-01-22
WO2002090759A1 (fr) 2002-11-14

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