EP0976924B1 - Injecteur avec une servovalve - Google Patents

Injecteur avec une servovalve Download PDF

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Publication number
EP0976924B1
EP0976924B1 EP99112980A EP99112980A EP0976924B1 EP 0976924 B1 EP0976924 B1 EP 0976924B1 EP 99112980 A EP99112980 A EP 99112980A EP 99112980 A EP99112980 A EP 99112980A EP 0976924 B1 EP0976924 B1 EP 0976924B1
Authority
EP
European Patent Office
Prior art keywords
valve
injection
servo
chamber
throttle
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.)
Expired - Lifetime
Application number
EP99112980A
Other languages
German (de)
English (en)
Other versions
EP0976924A3 (fr
EP0976924A2 (fr
Inventor
Heinz Lixl
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP0976924A2 publication Critical patent/EP0976924A2/fr
Publication of EP0976924A3 publication Critical patent/EP0976924A3/fr
Application granted granted Critical
Publication of EP0976924B1 publication Critical patent/EP0976924B1/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
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F02M63/0045—Three-way valves

Definitions

  • the invention relates to an injection valve with a servo valve of the type known from EP-A-0 192 241.
  • Servo valve is generally used to control fluid flows.
  • the servo valve in fuel injection valves be used for internal combustion engines.
  • injection systems are increasingly used, where with very high injection pressures.
  • Such injection systems are common rail systems (for diesel engines) and HPDI injection systems (for gasoline engines).
  • HPDI injection systems for gasoline engines.
  • the fuel is pumped into a high pressure pump pressure accumulator common to all cylinders of the engine, from which the injectors on the individual cylinders are supplied become.
  • the opening and closing of the injectors will usually controlled electromagnetically.
  • the injection valves are often included in such systems Servo valves that hydraulically open and close control the nozzle needle of the injection valve, in particular the start and end of the injection process in time establish.
  • the servo valve influences in connection with Control throttles especially the speed at which the injector opens and closes.
  • the speed, with which the injector opens differ from the speed at which the injector closes.
  • the Injector should e.g. in common rail systems for diesel engines at the beginning of the injection for better mixing of the Slowly open the fuel with the air in a controlled manner. Against that the injector quickly at the end of the injection process close to prevent soot. Also The aim is to inject the smallest amounts of fuel for pre-injection (Pilot injection) before the actual injection be possible with which the combustion process can be optimized leaves.
  • An injection valve is also part of EP 0 199 632 A1 known a servo valve, in which the connection between the control room and the fuel supply via one Fuel choke to a room and on via a fuel choke to the control room. To open and When the injection valve is closed, the servo valve is activated. about which by opening and closing the pressure in the Control room is dismantled or built. This in turn does Opening or closing the injection valve.
  • the injection valve is designed with a servo valve in the form of a 3/2-way valve, in which the inlet via an inlet throttle and an outlet throttle principally a faster opening of the injection valve than with the 2/2-way valve. Furthermore, by design the inlet throttle also the closing process of the injection valve to be slowed down. For injectors for In contrast, you would like combustion engines in usually slow the opening of the injector while the closing should happen quickly.
  • a servo valve for controlling fluid flows is known in which the pressure exerted on the valve body of the servo valve in a first fluid chamber causes the servo valve to open and close.
  • the actuation of the servo valve results in the opening or closing of a separate fluid channel.
  • the fluid channel leads in the known arrangement of a master cylinder that applies pressure to the fluid to secondary cylinders, actuated by the pressurized fluid become.
  • the master cylinder provides this arrangement the master brake cylinder of a motor vehicle and the secondary cylinders are the wheel brake cylinders.
  • the known Servo valve is intended for an anti-lock braking system, and the fluid channel should open without delay in rapid succession and be closed.
  • the invention is based on the object of designing an injection valve with a servo valve so that the opening and closing processes of an injection valve can be influenced independently of one another in a relatively simple manner by the servo valve. It should also be possible to inject the smallest amounts of fuel in a controlled manner for pilot injection.
  • the injection valve according to the invention with a servo valve which is a type of 3/2-way valve for controlling the nozzle needle in particular represents a common rail injector, united with regard to the defined valve lift and the control of the Opening edges of the nozzle needle stroke via inlet and outlet throttle the advantages of the well-known 3/2-way valve with those of known 2/2-way valve.
  • the peculiarity of the invention Servo valve is in the flow through in both directions Outlet throttle.
  • Another advantage of the injection valve according to the invention with servo valve is the small stroke of the valve body of the servo valve, which are in the range of 20 to 40 ⁇ m can. This contributes to the rapid closing movement of the nozzle needle also at.
  • 1 shows a conventional injection valve with a 2/2-way valve as a servo valve
  • Fig. 2 a conventional injection valve with a 3/2-way valve as Servo valve.
  • the fuel is fed with system pressure from a high-pressure accumulator (not shown) via a high-pressure bore 1 and an inlet bore 2 with an inlet throttle 3 to a control chamber 4 in the injection valve body 5.
  • a control chamber 4 the pressure prevailing there acts on the rear end of an axially movable nozzle closing body 6 with a nozzle needle at its front end, which opens and closes injection holes 7 in the injection valve body 5 when the nozzle closing body 6 moves , which leads to the combustion chamber of the internal combustion engine.
  • the injection holes 7 are connected to a nozzle chamber 8 which is formed at the front end of the nozzle closing body 6 in the injection valve body 5 and which in turn is connected to the high-pressure accumulator. If the full system pressure is present both in the control chamber 4 and in the nozzle chamber 8, the nozzle closing body 6 is pressed down due to the larger effective area in the control chamber 4 and closes the injection holes 7.
  • the conventional injection valve 1 When designing the conventional injection valve 1 leads a bore 9 in the injection valve body in the control chamber 4 5 with a flow restrictor 10 to an in the injector body 5 integrated servo valve 12 in in the form of a 2/2-way valve.
  • the servo valve 12 comes in unpressurized fuel return 14 to the fuel tank.
  • the Servo valve 12 is operated by a plunger 16 from an electromagnetic and / or piezoelectric actuator 18 and operated.
  • the servo valve 12 has the task of increasing the pressure control the in the control room 4 to close and open the Injection valve on the movable nozzle closing body 6 is exercised.
  • the servo valve 12 If the servo valve 12 is closed, is in the control room 4 essentially the full system pressure so that the Nozzle needle at the front end of the nozzle closing body 6 Injection holes 7 closes in the combustion chamber to lead. If the actuator 18 is controlled electrically, the driver exercises Plunger 16 exerts a force on the spring-loaded servo valve 12 out. As a result, the servo valve 12 opens Servo valve 12 is positioned between the high pressure accumulator, Control room 4, servo valve 12 and return 14 a stationary Flow. This flow leads to the individual throttles, the inlet throttle 3 and the outlet throttle 10, to a defined Pressure drop. The inlet throttle 3 and the outlet throttle 10 are dimensioned so that the pressure in the control room 4 decreased.
  • This version with a known 2/2-way valve has the disadvantage that the opening and closing processes of the injection valve by the design of the inlet and Flow restrictors are independent only within very narrow limits be influenced.
  • the conventional one Execution of the injection valve with a servo valve 12 in the form of a 3/2-way valve, the inlet via the inlet throttle 3, the servo valve 12 and the flow restrictor 10 for Control room 4.
  • the discharge leads via the discharge throttle 10 and the servo valve 12 to the return 14.
  • the control room is at a closed injection valve 4 via the inlet throttle 3, the servo valve 12 and the Drain throttle 10 in connection with the high pressure bore 1.
  • the pressure in the control room 4 can without influence of the inlet throttle 3 on the Remove drain throttle 10. In principle, this is faster Opening of the injection valve is possible than with the 2/2-way valve. After closing the drain on the 3/2-way valve builds itself over the inlet throttle 3 and the outlet throttle 10 in Control room 4 again the system pressure.
  • FIG. 3 is an injection valve with the invention 3/2-way valve shown as servo valve 12.
  • servo valve 12 The same reference numerals as in Figs. 1 and 2 denote same or similar elements.
  • the room 20, which is part or Expansion of the inlet bore 2 can be considered arranged in the injection valve body 5 opposite the control chamber 4 and connected to it only by the inlet throttle 3.
  • the room 20 in turn expands on that of Nozzle closing body 6 facing away from a valve chamber 22, which merges into a bore 30 with further narrowing, on the one hand a guide for the plunger 16 of the actuator 18 represents and on the other hand the unpressurized fuel return 14 includes.
  • valve chamber 22 on the part of Room 20 is as a stop 24 for the bottom of one in the Valve chamber 22 used valve body 26 formed.
  • the valve chamber 22 On the opposite side, that is, at the transition to Bore 30, the valve chamber 22 has a valve seat 28 on to which the top of the valve body 26 to abut can come.
  • the servo valve according to the invention thus consists of the space 20 in the inlet bore 2 and the adjoining one Valve chamber 22 with the stop 24 and the valve seat 28 for the valve body 26.
  • valve body 26 sealing by the system pressure in the space 20 pressed against the valve seat 28. This is the hole 30 closed and the connection to the return 14 interrupted.
  • the nozzle closing body 6 is the pressure in the control room 4, which is also substantially equal to the system pressure is pressed down and thus the nozzle needle in the nozzle needle seat so that the injection holes 7 are closed are.
  • valve body 26 To actuate the valve, the actuator 18 on the Ram 16 exerted a force. The plunger 16 thus presses the Valve body 26 away from the valve seat 28 and sealing on the Stop 24. This is the connection from the valve chamber 22 opened to bore 30 with the return 14 and the connection interrupted between the space 20 and the valve chamber 22.
  • the valve lift ⁇ h of the valve body 26 is very high low, it is about 20 to 40 ⁇ m.
  • the pending in control room 4 under system pressure Fuel can thus via the drain hole 9, the drain throttle 10, the valve chamber 22 and the bore 30 drain. This reduces the pressure in the control room 4.
  • the pressure reduction In the control room 4, the inlet throttle 3 and the flow restrictor 10 determines. About the throttle ratio the smallest quantity capability and the minimum opening pressure the injector.
  • the pressure reduction in the control chamber 4 relieves the pressure on the nozzle closing body 6, so that the pressure present in the nozzle chamber 8 lifts the nozzle needle from its seat and releases the connection to the injection holes 7.
  • the injection process begins.
  • valve body 26 After the actuation of the actuator 5 is completed the system pressure still present in the room 20 the valve body 26 back into the valve seat 28, the valve body 26 stands out from the stop 24. That is the connection restored between space 20 and valve chamber 22 and the return 14 to the bore 30 is interrupted.
  • Valve spring (not shown) can be provided which on the Valve body 26 exerts a force towards the valve seat 28.
  • the restored connection between the room 20 and the valve chamber 22 causes the control chamber 4 both via the inlet throttle 3 and the valve chamber 22, the flow restrictor 10 and the drain hole 9 again with Fuel is filled.
  • the pressure in the control room 4 thus increases quickly back to system pressure.
  • the pressure in the control room 4 leads to a force on the nozzle closing body 6 Direction to the seat of the nozzle needle, which is the nozzle needle again presses into their seat and ends the injection process.
  • the speed at which the injector opens and closes is directly through the speed influenced, with which the pressure in the control room 4 down and back is built up.
  • the closing process should be as possible go quickly, which is why with the present Execution of the injection valve during the closing process
  • Fuel supply to the control room 4 also via the valve chamber 22 and the flow restrictor 10 takes place.
  • the effective flow cross-section for the fuel during the closing process from the additive cross sections of inlet throttle 3 and outlet throttle 10 formed, so that the pressure build-up very happens quickly.
  • the valve body 26 is preferably in the form of a Partial ball 261 formed on the center of the cut surface 263 a guide pin 262 is attached.
  • the partial ball is arranged in the valve chamber 22, the partial spherical surface of the partial ball being assigned to the valve seat 28 is.
  • the guide pin 262 is in a connecting bore introduced that the valve chamber 22 with the space 20th combines. In this way, the guide pin 262 adjusts the partial ball 261 in the center and symmetrical to the valve seat 28. This prevents tilting of the partial ball 261.
  • the Partial spherical shape of the partial sphere 261 offers the advantage that the Valve chamber 22 can be adapted well to the shape of the partial sphere can and thus the volume of the valve chamber 22, which is not from Valve body 26 is filled is small.
  • valve chamber 212 is preferably cylindrical formed, the cylindrical shape conical in the Hole 30 merges.
  • the conical transition area represents the Valve seat 30.

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)

Claims (3)

  1. Injecteur comprenant une servovalve pour l'injection de carburant dans un moteur à combustion interne, comprenant une chambre de commande (4), qui est en liaison par le biais d'un étrangleur d'entrée (3), d'une chambre (20), et par le biais d'un alésage d'entrée (2) à une alimentation de carburant, la pression régnant dans la chambre de commande (4) agissant sur un corps de fermeture d'injection mobile (6) qui est en liaison coopérante avec une aiguille d'injection qui libère ou ferme des orifices d'injection (7) lors du mouvement du corps de fermeture d'injection (6), la servovalve (12) présentant un corps de soupape mobile (26) qui est actionné par un actionneur (18) et qui peut venir en butée de manière hermétiquement sélective contre une butée (24) entre la chambre (20) et la chambre de soupape (22) ou contre un siège de soupape (28) entre la chambre de soupape (22) et la canalisation de retour (14), caractérisé en ce que lorsque le corps de soupape (26) s'applique contre le siège de soupape (28), le carburant s'écoule d'une part par le biais de l'étrangleur d'entrée (3) et d'autre part par le biais de la chambre de soupape (22) et de l'étrangleur de sortie (10) dans la chambre de commande (4) et en ce que la chambre de commande (4) peut être amenée en liaison par le biais d'un étrangleur de sortie (10) et par le biais d'une chambre de soupape (22) de la servovalve (12) avec une canalisation de retour sans pression (14).
  2. Injecteur avec une servovalve selon la revendication 1, caractérisé en ce que le corps de soupape (26) de la servovalve est sollicité par ressort dans la direction du siège de soupape (28).
  3. Injecteur avec une servovalve selon l'une quelconque des revendications précédentes, caractérisé en ce que
    le corps de soupape (26) est réalisé en forme de bille partielle,
    la surface en forme de bille partielle du corps de soupape (26) est associée au siège de soupape (28),
    l'organe de fermeture (26) présente un tourillon de guidage (262) qui est disposé dans l'alésage de liaison qui relie la chambre de soupape (22) à la chambre (20).
EP99112980A 1998-07-31 1999-07-05 Injecteur avec une servovalve Expired - Lifetime EP0976924B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19834667 1998-07-31
DE19834667 1998-07-31

Publications (3)

Publication Number Publication Date
EP0976924A2 EP0976924A2 (fr) 2000-02-02
EP0976924A3 EP0976924A3 (fr) 2001-06-13
EP0976924B1 true EP0976924B1 (fr) 2003-09-17

Family

ID=7876057

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99112980A Expired - Lifetime EP0976924B1 (fr) 1998-07-31 1999-07-05 Injecteur avec une servovalve

Country Status (2)

Country Link
EP (1) EP0976924B1 (fr)
DE (1) DE59906995D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7331329B2 (en) 2002-07-15 2008-02-19 Caterpillar Inc. Fuel injector with directly controlled highly efficient nozzle assembly and fuel system using same

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19939450A1 (de) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
JP4048699B2 (ja) * 1999-11-10 2008-02-20 株式会社デンソー 燃料噴射弁
DE10015268A1 (de) 2000-03-28 2001-10-04 Siemens Ag Einspritzventil mit Bypaßdrossel
DE10024703A1 (de) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem einer Verbrennungsmaschine
DE10024702A1 (de) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem einer Verbrennungsmaschine
DE10063698A1 (de) * 2000-12-20 2002-07-04 Siemens Ag Hochdruckeinspritzsystem mit Ausführung einer Steuerdrossel als Kaskadendrossel
JP3556921B2 (ja) * 2001-04-27 2004-08-25 株式会社日本自動車部品総合研究所 燃料噴射弁
DE10123775B4 (de) * 2001-05-16 2005-01-20 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für Brennkraftmaschinen, insbesondere Common-Rail-Injektor, sowie Kraftstoffsystem und Brennkraftmaschine
DE10131640A1 (de) * 2001-06-29 2003-01-16 Bosch Gmbh Robert Kraftstoffinjektor mit Einspritzverlaufsformung durch schaltbare Drosselelemente
DE10131619A1 (de) * 2001-06-29 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor mit Einspritzverlaufsformung
DE10131618A1 (de) * 2001-06-29 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor mit zuschaltbarem Steuerraumzulauf
DE10131642A1 (de) * 2001-06-29 2003-01-16 Bosch Gmbh Robert Kraftstoffinjektor mit variabler Steuerraumdruckbeaufschlagung
DE10132249A1 (de) * 2001-07-04 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor mit kraftausgeglichenem Steuerventil
JP3864764B2 (ja) * 2001-11-22 2007-01-10 株式会社デンソー 燃料噴射弁
DE102005046743B3 (de) * 2005-09-29 2007-05-16 Siemens Ag Verfahren zur Ermittlung des Zeitpunktes des Anschlags eines Ventilkörpers in einem von einem elektromechanischen Aktor betätigten Ablaufventil
CN101395366B (zh) 2006-03-03 2012-09-12 甘瑟-许德罗玛格股份公司 内燃机的燃料喷射阀
DE102010001612A1 (de) * 2010-02-05 2011-08-11 Robert Bosch GmbH, 70469 Kraftstoffinjektor
DE102011015753A1 (de) 2011-03-31 2012-10-04 Raphael Füchslin Einspritzventil

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2580728B1 (fr) * 1985-04-19 1989-05-05 Alsacienne Constr Meca Systeme d'injection de combustible pour moteur diesel
ES2042184T3 (es) * 1985-12-02 1993-12-01 Marco Alfredo Ganser Dispositivo para el control de los inyectores de combustible de accionamiento electrohidraulico.
US5732679A (en) * 1995-04-27 1998-03-31 Isuzu Motors Limited Accumulator-type fuel injection system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7331329B2 (en) 2002-07-15 2008-02-19 Caterpillar Inc. Fuel injector with directly controlled highly efficient nozzle assembly and fuel system using same

Also Published As

Publication number Publication date
EP0976924A3 (fr) 2001-06-13
EP0976924A2 (fr) 2000-02-02
DE59906995D1 (de) 2003-10-23

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