EP0675281A1 - Soupape d'injection pour moteur, particulierement pour moteur diesel - Google Patents

Soupape d'injection pour moteur, particulierement pour moteur diesel Download PDF

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Publication number
EP0675281A1
EP0675281A1 EP95103548A EP95103548A EP0675281A1 EP 0675281 A1 EP0675281 A1 EP 0675281A1 EP 95103548 A EP95103548 A EP 95103548A EP 95103548 A EP95103548 A EP 95103548A EP 0675281 A1 EP0675281 A1 EP 0675281A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve body
control
chamber
injection
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
EP95103548A
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German (de)
English (en)
Other versions
EP0675281B1 (fr
Inventor
Christian Dipl.Masch.Ing. Eth Mathis
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.)
Mathis Christian Diplmasching Eth
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Mathis Christian Diplmasching Eth
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Filing date
Publication date
Application filed by Mathis Christian Diplmasching Eth filed Critical Mathis Christian Diplmasching Eth
Publication of EP0675281A1 publication Critical patent/EP0675281A1/fr
Application granted granted Critical
Publication of EP0675281B1 publication Critical patent/EP0675281B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped

Definitions

  • the invention relates to an injection valve for an internal combustion engine, in particular provided as a diesel engine, with a nozzle needle which is displaceably arranged in a valve housing and which, for injecting fuel, closes or opens an injection opening leading into a fuel cylinder and which protrudes opposite into a control chamber which contains a control medium containing a control medium High-pressure part is connected on the one hand and via a line part and a control valve which can be closed to a drain line on the other, a further valve being provided which, by automatic opening, provides an additional connection between the high-pressure part and the control chamber produces when the nozzle needle executes the closing movement, thereby causing an increased closing speed.
  • the control chamber into which the nozzle needle projects with its upper end is connected, on the one hand, to the high-pressure part via a throttle bore and, on the other hand, to a drain line via a bore and a valve body closing the same .
  • the control valve which is designed as a solenoid valve, opens, the pressure in the star chamber drops and the nozzle needle opens due to the fuel, which acts unchanged at high pressure on its underside facing the injection opening.
  • the nozzle needle moves up to an upper stop, which is formed by another valve body.
  • This valve body is arranged coaxially to the nozzle needle and its upper end face is acted upon by the high-pressure part of the control medium, specifically on a cross section which is formed by two or more bores arranged approximately vertically to it.
  • the additional connection between the high-pressure connection and the control chamber is established immediately after the closing of the solenoid valve, because the high-pressure acting in the bores presses the valve body against the nozzle needle and causes its increased closing speed.
  • the disadvantage here is that the aforementioned flat end face of this valve body forms the valve seat, in which manufacturing inaccuracies or signs of wear impair the function of this valve as a whole. For example, there is a risk that the pressure fluctuations that often occur in the high-pressure part can trigger an unintentional closing of the valve.
  • the object of the present invention is to develop an injection valve of the type described at the outset in such a way that an optimal closing speed of its nozzle needle is achieved, that even after a long period of operation it is guaranteed to function properly and reliably, and its manufacture is simple and with less requirements the manufacturing tolerances can be realized.
  • the object is achieved in that the valve producing this additional connection between the high-pressure part and the star chamber has an annular chamber connected to the high-pressure part of the control medium and an annular valve seat forming the end face.
  • a bore is provided in the control valve body, starting from its front valve seat and communicating with the line part, which is expanded inside the control valve body for the purpose of generating a closing force acting in the closing direction and is also limited by a pin which is longitudinally movable in the control valve body, the latter on its upper end is supported independently of the control valve body.
  • the injection valve 2 for an internal combustion engine which is provided in particular as a diesel engine and which is not shown.
  • the injection valve 2 is suitable for a conventional injection system of a diesel engine, so that a detailed explanation can be dispensed with in this regard. It essentially has a multi-part valve housing 47, 53, a single or multi-part nozzle needle 15 guided longitudinally displaceably therein, a control valve 20 actuating the latter, designed as an electromagnetic valve 227, an inflow line 13 for the high-pressure fuel and an outflow line 10.
  • the lower part of the nozzle needle 15 is surrounded by a storage chamber 14 supplied with fuel by the inflow line 13, and it closes or opens an injection opening 4 or its feed line leading into a fuel cylinder of the diesel engine.
  • control chamber 17a is connected via the inflow line 13 to a high-pressure part, which contains the fuel, on the one hand, and via the line part 19 and the control valve 20, which can be closed, to the outflow line 10, on the other hand.
  • a radial connection 92 to the injection valve 2 is provided for the inflow line 13, which has a connecting ring 70 encompassing the valve housing 47 and a threaded nut 72 pressing the inflow line 13 against the housing.
  • a further valve 25 is arranged above this nozzle needle 15, which via the inflow line 13 has an annular chamber 28 connected to the high-pressure part of the control medium and an annular valve seat 27 closing it at the top on the front side when opening this additional connection between the high pressure part and the control chamber 17a generated.
  • the valve 25 has a valve body 26, which extends coaxially to the nozzle needle 15 and is guided laterally in a sealing manner in the valve housing 47. This cylindrical valve body 26 and the valve housing 47 together form the annular chamber 28 and the valve seat 27 which closes this chamber 28.
  • the valve body 26 projects with one end facing the nozzle needle 15 into the control chamber 17a and with the other end into one with the Drain line 10 via the additional chamber 17b communicating with the control valve 20, which is connected to the control chamber 17a via a throttle bore 23 through the valve body 26 and adjoins the valve seat 27 on the circumferential side.
  • the latter is designed in such a way that the valve body 26 with its upper oblique ring edge lies in the closed state in a sealing manner against a corresponding ring surface in the housing bore and the annular chamber 28 surrounds the valve body 26 at least in its upper region.
  • This conical valve seat 27 could also be cylindrical or a flat surface.
  • the valve body 26 is provided with a transverse throttle bore 21 connecting the inflow line 13 to the control chamber 17a, by means of which the control medium is permanently connected from the high-pressure part into this control chamber.
  • valve body 26 In the closed position, the valve body 26 is at a predetermined distance from the nozzle needle 15 located beneath it, and a compression spring 96 which presses it apart is provided between them, while in the open position the nozzle needle 15, which is released by releasing the control valve 20 and a pressure drop associated therewith Control chamber 17a is caused, this nozzle needle 15 strikes the lower end face 16 of the valve body 26.
  • the control valve 20 is closed on the one hand by the transverse throttle bore 21 initially builds up pressure in the additional chamber 17b, as a result of which the valve body 26 moves against the nozzle needle 15 and thus causes the valve seat 27 to open automatically.
  • valve body 26 With its upper ring edge forming the valve seat 27, the valve body 26 advantageously has a similar or slightly smaller diameter than in its lower region, which is sealed with the valve housing 47. As a result, the influence of pressure fluctuations in the supply pressure on the switching behavior of this valve body 26 can be virtually eliminated.
  • the control valve body 38 is furthermore pressed in the closing direction by an essentially plate-shaped spring element 58 which is held in the valve housing 47 and which is composed of triangular spring segments which act on the control valve body with their inner tips.
  • the valve body 26a shown in FIG. 3 is of hollow cylindrical design and the nozzle needle 15 extends therein. This enables a relatively larger diameter of the valve body cross section to that of the nozzle needle and a reduction in the volume of the control chamber 17a, in particular because the compression spring 96 is outside of the valve body 26a is arranged. Furthermore, the permanent throttle bore 21a leads into the additional chamber 17b. Otherwise, this injection valve 2 is designed in the same way as that according to FIG. 1, and its remaining configurations are therefore no longer commented in detail.
  • the control valve 20, designed as an electromagnetic valve 227, has a control valve body 38, which closes or opens the vertical line part 19 in the valve housing 47, which subsequently merges into a horizontal drain line 10, through a lower end valve seat 57.
  • This control valve body 38 has a bore 60 'which starts from its valve seat 57 and communicates with the line part 19 and which is widened in the interior of the control valve body 38 for the purpose of generating a closing force acting in the closing direction thereof.
  • this bore 60 ' is delimited at the top by a pin 60, which is arranged coaxially in the control valve body 38 and is longitudinally movably arranged at its upper end independently of the control valve body 38, in the present example on the lower end face of a pin arranged in the magnetic core 22, with sufficient hardness provided pin is supported.
  • a magnet armature 62 is fastened to the control valve body 38 on the side facing away from the valve seat 57, which armature forms a residual gap to a magnet core 22 of the magnet valve even in the open position of the valve 20, which gap is also provided between the pin 60 and the magnet core 22.
  • This residual gap in particular causes the solenoid valve to react more quickly when it is switched off, which has an indirectly positive effect on the exhaust gas emissions and on the efficiency of the. Engine affects.
  • a non-magnetic, possibly perforated foil disk 61 which determines the remaining gap, the pin 60 being provided with end play to the control valve body 38 even when the solenoid valve 227 is activated.
  • the lower end face of the magnetic core 22 lies directly on the film disk 61, which in turn is fixed on the flat annular surface of the valve housing.
  • recesses 66 are provided in the magnet armature 62, through which a flow around the fuel surrounding the armature is made possible when the armature is moved.
  • the damping effect of the reciprocating control valve body 38 can be adjusted by a corresponding choice of the cross section of the recesses 66.
  • FIG. 4 shows, in a further variant of the injection valve 2, the one which is formed in the valve housing 47 and leads into the annular chamber 28 Line formed from a plurality of nozzle openings 93 or from a fine-meshed sieve 94.
  • both filter inserts are shown, in practice one or the other would alternatively be used, but not both together.
  • the diameter of the cylindrical valve body 26 in the area forming the annular chamber 28 is somewhat reduced compared to the lower area guided in a cylinder part of the valve housing 47. As a result, the bore in the cylinder part of the valve housing 47 can be made with an unchanged diameter.
  • valve body 26b in which the transverse throttle bore 21b is arranged below the annular chamber 28 and a narrow annular gap between them produces a certain filter effect.
  • a single nozzle opening 93 or its cross section of a mesh from the screen 94 or the gap dimension of the narrow annular gap mentioned are chosen to be smaller than the diameter of the throttle 21 which determines the flow rate. This traps particles before they can clog the throttle 21.
  • the throttle 21 is advantageously divided into a number of smaller cross sections. The clogging of a single cross-section then adversely affects the function, but it does not cause destruction of the internal combustion engine, as can occur with existing injection valves.
  • FIGS. 6 to 9 illustrate various variants of spring elements which, according to FIG. 6, are each fixed on the outer circumference by a spacer ring 90 against the valve housing 47 and through which the control valve body 38 extends, which extends from a respective spring element is pressed away from the magnetic core 22 in the closing direction.
  • the spring element 58, 358, 258 can be designed in a cross shape, as a leaf spring 358 with lateral support plates 358 'or in a plate shape with radial slots 258'.
  • these novel spring elements can be produced very cheaply, since they can be manufactured from stamped sheet metal, and on the other hand, they prevent the same from generating their own vibrations during operation. Due to the low mass of these spring elements, however, this causes a rapid reaction of the valve.
  • control medium flowing into the control chambers is normally fuel which is, as it were, injected into the storage chamber and subsequently through the injection openings into a fuel cylinder.
  • a separate liquid could be used as the control medium, while the fuel would only be provided for the injection.
  • valve seat 27 brings about a complete closure of the annular chamber 28, but it would also be conceivable that it could be provided with one or more recesses and this valve 20 would thereby function as a throttle valve.

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)
EP95103548A 1994-03-29 1995-03-11 Soupape d'injection pour moteur, particulierement pour moteur diesel Expired - Lifetime EP0675281B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH936/94 1994-03-29
CH00936/94A CH689282A5 (de) 1994-03-29 1994-03-29 Einspritzventil fuer eine insbesondere als Dieselmotor vorgesehene Brennkraftmaschine.

Publications (2)

Publication Number Publication Date
EP0675281A1 true EP0675281A1 (fr) 1995-10-04
EP0675281B1 EP0675281B1 (fr) 1998-05-06

Family

ID=4198629

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95103548A Expired - Lifetime EP0675281B1 (fr) 1994-03-29 1995-03-11 Soupape d'injection pour moteur, particulierement pour moteur diesel

Country Status (6)

Country Link
US (1) US5655716A (fr)
EP (1) EP0675281B1 (fr)
JP (1) JP3707824B2 (fr)
AT (1) ATE165900T1 (fr)
CH (1) CH689282A5 (fr)
DE (1) DE59502083D1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999037909A1 (fr) * 1998-01-22 1999-07-29 Robert Bosch Gmbh Soupape d'injection de carburant pour moteur a combustion interne
DE19827267A1 (de) * 1998-06-18 1999-12-23 Bosch Gmbh Robert Kraftstoff-Einspritzventil für Hochdruck-Einspritzung mit verbesserter Steuerung der Kraftstoffzufuhr
DE19859537A1 (de) * 1998-12-22 2000-07-06 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE19956522A1 (de) * 1999-11-24 2001-06-07 Bosch Gmbh Robert Injektor für unter Hochdruck erfolgender Kraftstoffeinspritzung
EP1273791A2 (fr) 2001-07-03 2003-01-08 CRT Common Rail Technologies AG Soupape d'injection de combustible pour moteurs à combustion interne
DE19605277B4 (de) * 1995-02-15 2004-06-03 Nippon Soken, Inc., Nishio Magnetbetätigtes hydraulisches Steuerventil zur Verwendung im Kraftstoffeinspritzsystem eines Verbrennungsmotors
WO2015024692A1 (fr) * 2013-08-20 2015-02-26 Delphi International Operations Luxembourg S.À R.L. Ensemble de vanne de commande

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3653882B2 (ja) * 1996-08-31 2005-06-02 いすゞ自動車株式会社 エンジンの燃料噴射装置
IT1295462B1 (it) * 1997-10-02 1999-05-12 Elasis Sistema Ricerca Fiat Iniettore di combustibile a comando elettromagnetico per motori a combustione interna.
US6003790A (en) * 1998-10-14 1999-12-21 Ford Global Technologies, Inc. Pre-load mechanism having self-mounting coil spring
EP1118765A3 (fr) * 2000-01-19 2003-11-19 CRT Common Rail Technologies AG Injecteur de combustible pour moteur à combustion interne
DE10025497A1 (de) * 2000-05-23 2001-11-29 Bosch Gmbh Robert Kraftstoffeinspritzventil
ITTO20010027A1 (it) * 2001-01-16 2002-07-16 Fiat Ricerche Metodo per realizzare iniettori di combustibile ed iniettore di combustibile.
DE10132246A1 (de) * 2001-07-04 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor mit hochdruckfestem Zulauf
EP1293664A3 (fr) * 2001-09-18 2004-03-10 Siemens Aktiengesellschaft Injecteur de combustible pour un moteur à combustion interne
US6698666B2 (en) * 2001-09-20 2004-03-02 Denso Corporation Fuel injection valve
JP2005508475A (ja) * 2001-11-09 2005-03-31 シーメンス　アクチエンゲゼルシヤフト 蓄圧式噴射システムのインジェクタのための制御モジュール
WO2003071122A1 (fr) * 2002-02-22 2003-08-28 Crt Common Rail Technologies Ag Soupape d'injection de carburant pour moteurs a combustion interne
US6955114B2 (en) * 2003-12-05 2005-10-18 Caterpillar Inc Three way valve and electro-hydraulic actuator using same
DE502005010478D1 (de) * 2004-02-25 2010-12-16 Ganser Hydromag Brennstoffeinspritzventil für verbrennungskraftmaschinen
US7900604B2 (en) * 2005-06-16 2011-03-08 Siemens Diesel Systems Technology Dampening stop pin
CH697562B1 (de) * 2005-08-09 2008-11-28 Ganser Hydromag Brennstoffeinspritzventil.
RU2438035C2 (ru) * 2006-03-03 2011-12-27 Ганзер-Хюдромаг Аг Инжекторный клапан для топлива для двигателя внутреннего сгорания (варианты)
WO2014131497A1 (fr) * 2013-03-01 2014-09-04 Ganser-Hydromag Ag Dispositif permettant d'injecter un carburant dans la chambre de combustion d'un moteur à combustion interne

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0119894A1 (fr) * 1983-02-21 1984-09-26 Regie Nationale Des Usines Renault Perfectionnement aux systèmes d'injection à commande électromagnétique pour moteur Diesel de type pression-temps où l'aiguille de l'injecteur est pilotée par la décharge puis la charge d'une capacité
EP0393590A2 (fr) * 1989-04-17 1990-10-24 Nippondenso Co., Ltd. Dispositif d'injection de combustible pour moteurs diesel
EP0426205A2 (fr) * 1985-12-02 1991-05-08 Marco Alfredo Ganser Dispositif de commande d'injecteurs de combustible actionnés électro-hydrauliquement

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT378242B (de) * 1981-07-31 1985-07-10 Berchtold Max Prof Kraftstoffeinspritzanlage fuer brennkraftmaschinen, insbesondere dieselmotoren
CH668621A5 (de) * 1986-01-22 1989-01-13 Dereco Dieselmotoren Forschung Kraftstoffeinspritzanlage fuer eine brennkraftmaschine.

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0119894A1 (fr) * 1983-02-21 1984-09-26 Regie Nationale Des Usines Renault Perfectionnement aux systèmes d'injection à commande électromagnétique pour moteur Diesel de type pression-temps où l'aiguille de l'injecteur est pilotée par la décharge puis la charge d'une capacité
EP0426205A2 (fr) * 1985-12-02 1991-05-08 Marco Alfredo Ganser Dispositif de commande d'injecteurs de combustible actionnés électro-hydrauliquement
EP0393590A2 (fr) * 1989-04-17 1990-10-24 Nippondenso Co., Ltd. Dispositif d'injection de combustible pour moteurs diesel

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19605277B4 (de) * 1995-02-15 2004-06-03 Nippon Soken, Inc., Nishio Magnetbetätigtes hydraulisches Steuerventil zur Verwendung im Kraftstoffeinspritzsystem eines Verbrennungsmotors
WO1999037909A1 (fr) * 1998-01-22 1999-07-29 Robert Bosch Gmbh Soupape d'injection de carburant pour moteur a combustion interne
DE19827267A1 (de) * 1998-06-18 1999-12-23 Bosch Gmbh Robert Kraftstoff-Einspritzventil für Hochdruck-Einspritzung mit verbesserter Steuerung der Kraftstoffzufuhr
DE19859537A1 (de) * 1998-12-22 2000-07-06 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE19956522A1 (de) * 1999-11-24 2001-06-07 Bosch Gmbh Robert Injektor für unter Hochdruck erfolgender Kraftstoffeinspritzung
KR100714852B1 (ko) * 1999-11-24 2007-05-08 로베르트 보쉬 게엠베하 고압연료 분사용 인젝터
EP1273791A2 (fr) 2001-07-03 2003-01-08 CRT Common Rail Technologies AG Soupape d'injection de combustible pour moteurs à combustion interne
WO2015024692A1 (fr) * 2013-08-20 2015-02-26 Delphi International Operations Luxembourg S.À R.L. Ensemble de vanne de commande

Also Published As

Publication number Publication date
US5655716A (en) 1997-08-12
DE59502083D1 (de) 1998-06-10
ATE165900T1 (de) 1998-05-15
JP3707824B2 (ja) 2005-10-19
JPH0835461A (ja) 1996-02-06
EP0675281B1 (fr) 1998-05-06
CH689282A5 (de) 1999-01-29

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