EP1440237A1 - Valve for controlling liquids - Google Patents

Valve for controlling liquids

Info

Publication number
EP1440237A1
EP1440237A1 EP02754530A EP02754530A EP1440237A1 EP 1440237 A1 EP1440237 A1 EP 1440237A1 EP 02754530 A EP02754530 A EP 02754530A EP 02754530 A EP02754530 A EP 02754530A EP 1440237 A1 EP1440237 A1 EP 1440237A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
actuating piston
valve according
hydraulic chamber
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
EP02754530A
Other languages
German (de)
French (fr)
Other versions
EP1440237B1 (en
Inventor
Patrick Mattes
Hans Brekle
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 EP1440237A1 publication Critical patent/EP1440237A1/en
Application granted granted Critical
Publication of EP1440237B1 publication Critical patent/EP1440237B1/en
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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from 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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/24—Piezoelectric 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention is based on a valve for controlling liquids according to the type defined in more detail in the preamble of claim 1.
  • Such a valve is known from practice and serves in particular as a control module of a fuel injection valve, in particular a common rail injector of a motor vehicle.
  • a known valve of the type mentioned in the introduction has a piezoelectric actuator for actuation.
  • a deflection of the piezoelectric actuator is transmitted to a valve closing element when the valve is actuated via a hydraulic chamber, which works as a hydraulic transmission or coupling and tolerance compensation element.
  • Hydraulic coupler hydraulic chamber is arranged between an actuating piston connected to the piezoelectric actuator and an actuating piston connected to the valve closing member.
  • the diameter of the actuating piston is larger than that of the actuating piston, so that the actuating piston makes a stroke enlarged by the ratio of the piston diameters when the actuating piston experiences a certain deflection by means of the piezoelectric actuator.
  • the hydraulic chamber is designed in such a way that leakages that occur during operation can be compensated for by refilling.
  • fluid pressure prevailing in a system area or system space of the valve acts on the hydraulic chamber, for example via leak gaps formed on the circumference of the pistons.
  • the system area is acted upon by the fluid pressure in such a way that when the valve is actuated, the valve closing member is moved into an open position and a fluid flow can thus flow into the system area.
  • the amount of fluid flowing into the system area represents the so-called control amount, which is subsequently discharged from the system area via a so-called control channel.
  • the system pressure of approximately 30 bar prevailing in the system area is accumulated by means of a check valve arranged in the control channel, so that the pressure prevailing in the system area is sufficiently large to ensure that the hydraulic chamber is refilled.
  • this valve When this valve is used in a fuel injection valve of a motor vehicle, such as in a common rail injector, in which there is a pressure of approximately 1.5 kbar upstream of the valve closing element, the discharge quantity flows into the system area at a high pressure, so that Pressure peaks occur in the system area, which may impair the functionality of the actuator module, which is also exposed to the system pressure. Furthermore, a factory filling of the hydraulic coupler is required.
  • valve according to the invention for controlling liquids with the features according to the preamble of claim 1, in which the system space is pressurized with a fluid pressure via the drainage channel, has the advantage that an initial filling of the hydraulic coupler at the factory is not necessary, since the filling during commissioning of the valve takes place by supplying fluid into the system area via the control channel, which may be designed as an opening of the valve housing, and thus a sufficiently high refilling pressure is always provided in the system room or area.
  • the control can be connected to a pressure device which can simultaneously represent a fuel pump of the motor vehicle.
  • the fuel pump used can be a fuel feed pump arranged in a fuel storage tank for conveying fuel to a high-pressure pump, which provides the so-called common rail pressure.
  • the pre-feed pump acts, for example, on the system area with a pressure of about 5 bar via the discharge channel.
  • Pressures which build up as a result of control processes in the system area can be controlled in the valve according to the invention in such a way that the amount of fluid produced is fed directly to the high-pressure pump instead of the control amount being returned to the fuel supply tank.
  • the fuel pump is expediently equipped with a pressure relief valve, so that the pump is protected against high pressures.
  • a throttle is provided on the control channel.
  • the throttle causes a pressure that builds up in the system area to be slowly discharged to a downstream fluid circuit. Possibly occurring pressure peaks in the system area, which can be up to 60 bar, can be reduced via the throttle. A pressure increase in the system area is taken dynamically by means of the throttle, which in turn leads to tolerable loads on the piezoelectric actuator module and thus to a robust valve.
  • the throttle is preferably formed by a pipe screw-in part.
  • a pipe screw-in part is a simple and robust component that is insensitive to tolerances, in which no adjustment processes are required and whose space requirement is small and which is easy to manufacture.
  • the valve according to the invention can be easily adapted to changing operating conditions simply by replacing the pipe screw-in part with a certain inner diameter by a pipe screw-in part with a different inner diameter.
  • FIG. 1 shows a simplified longitudinal section through a valve according to the invention in a common rail injection system of a diesel motor vehicle
  • FIGS. 2a and 2b show a throttle of the valve according to FIG. 1.
  • FIG. 1 shows part of a system for injecting fuel in a diesel internal combustion engine of a motor vehicle, the system comprising a valve 10 for controlling liquids in a fuel injection valve.
  • the valve 10 forms a control module for a nozzle module of the fuel injection valve or injector, which is not shown here.
  • the nozzle module connects to the control module in the axial direction and comprises a nozzle needle arranged and guided in a nozzle body, which controls openings of the nozzle body leading to a combustion chamber of the internal combustion engine.
  • the nozzle needle forms a structural unit with a valve control piston, the valve control piston bordering a so-called valve control chamber.
  • the valve control chamber is operatively connected via an inlet throttle to a high-pressure fuel channel and via an outlet throttle to a valve chamber 11 of the valve 10.
  • the high-pressure fuel channel is acted upon by a high-pressure pump 12 with fuel at a pressure of approximately 1.5 kbar, which is conveyed by means of a pre-feed pump 13 from a fuel tank 14 via a feed line 15 to the suction side of the high-pressure pump 12.
  • the high-pressure pump 12 has a pressure side 16, which leads to a so-called common rail, not shown here, via which a plurality of fuel injectors are fed with fuel and which is connected, inter alia, to the aforementioned high-pressure fuel channel.
  • the Fuel injectors are each equipped with a control module in the manner of valve 10.
  • An injection process carried out by means of the fuel injection valve described here is controlled via the pressure prevailing in the valve control chamber, which pressure can be adjusted by means of the valve or control module 10.
  • the valve or control module 10 comprises a valve housing 20 in which a so-called system area or system space 21 is formed.
  • a valve housing 20 in which a so-called system area or system space 21 is formed.
  • an actuator module 22 and, on the other hand, a coupler module 23 are arranged.
  • the actuator module 22 which comprises a piezoelectric actuator and is supported on the valve housing 20, is connected to an actuating piston 24, which is assigned to the coupler module 23 and is axially movably guided in a cylindrical bore 25 of a coupler housing 26.
  • actuating piston 24 is biased in the direction of the actuator module 22 by means of a helical spring 27, which engages on a support plate 28 connected to the actuating piston 24 and is supported on the coupler housing 26.
  • the actuating piston 24 is operatively connected via a hydraulic coupler 29 designed as a hydraulic chamber to a so-called actuating piston 30, which is used to actuate a valve closing member 31 and is connected to the latter via a guide piston 32.
  • the actuating piston 30 which in a cylindrical bore 35 of the Coupler housing 26 is guided, is biased in the direction of the valve closing member 31 by means of a coil spring 33, which is supported on the coupler body 26 and engages on a further support plate 34.
  • the diameter of the actuating piston 30 is smaller than that of the actuating piston 24, so that the hydraulic coupler 29 acts as a hydraulic translator.
  • the valve closing member 31 is arranged in the valve chamber 11 connected to the valve control chamber of the nozzle module and is held in the closed position by means of a plate spring 36 when the piezoelectric actuator 22 is not actuated, so that it bears against a valve seat 37.
  • a branch duct 38 which is designed as an opening, branches off from the system space 21 and is provided with a throttle 39 designed as a pipe screw-in part and is connected via a line 40 to the fuel feed pump 13 and to the supply line 15 leading to the high pressure pump 12.
  • the throttle 39 is shown in more detail in FIGS. 2a and 2b and comprises a connection area 41 for a pressure hose assigned to the line 40 and a screw thread 42 for fixing to the valve housing 20 and has an inner diameter d of approximately 1 mm.
  • the valve 10 shown in Figures 1 and -2 ' operates in the manner described below.
  • fuel is conveyed from the fuel tank 14 by means of the pre-feed pump 13 via the delivery line 15 into the high-pressure pump 12, by means of which the common rail and thus the high-pressure fuel channel of the fuel injection valve are supplied with fuel, so that in the valve control chamber of the nozzle module and in the valve chamber 11 of the valve 10 shown in FIG. 1 the so-called rail pressure prevails.
  • This pressure causes the hydraulic coupler 29 to be filled via annular leak gaps which surround the pistons 24 and 30 in the region of the bores 25 and 35.
  • the pressure for filling the hydraulic coupler 29 is therefore taken over by a pressure device present in the motor vehicle, here the fuel feed pump.
  • the actuator module 22 is subjected to a voltage, so that it is axially elongated and the actuating piston 24 is deflected in the direction of the valve closing member 31, which in turn triggers a stroke of the actuating piston 30 and thus the valve closing member 31.
  • the valve closing member 31 is moved into the open position, which results in a control quantity fuel flows out of the valve chamber 11 into the system chamber 21.
  • the discharge quantity is provided via the opening 38 and the throttle 39 as well as the lines 40 and 15 of the high-pressure pump 12.
  • the throttle 39 causes pressure peaks, which can possibly be up to 60 bar, to be reduced dynamically.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Control Of Non-Electrical Variables (AREA)

Abstract

A valve for controlling fluids, in particular in an injection valve of an internal combustion engine, including a valve housing ( 20 ), in which housing a system region ( 21 ) is embodied, in which region a piezoelectric actuator module ( 22 ) and a hydraulic coupler module ( 23 ) are disposed, which has both an adjusting piston ( 24 ), on which the actuator module ( 22 ) acts, and an actuating piston ( 30 ) that is operatively connected via a hydraulic chamber ( 29 ) to the adjusting piston ( 24 ) and that is connected to a valve closing member ( 31 ) cooperating with a valve seat ( 37 ), and the adjusting piston ( 24 ) and the actuating piston ( 30 ) define the hydraulic chamber ( 29 ), and a system pressure for refilling the hydraulic chamber ( 29 ) prevails in the system region ( 21 ), from which a diversion conduit ( 38 ) branches off. The system region ( 21 ) is acted upon by a fluid via the diversion conduit ( 38 ).

Description

Ventil zum Steuern von FlüssigkeitenValve for controlling liquids
Stand der TechnikState of the art
Die Erfindung geht von einem Ventil zum Steuern von Flüssigkeiten gemäß der im Oberbegriff des Patentanspruches 1 näher definierten Art aus.The invention is based on a valve for controlling liquids according to the type defined in more detail in the preamble of claim 1.
Ein derartiges Ventil ist aus der Praxis bekannt und dient insbesondere als Steuermodul eines Kraftstoffeinspritzventils, insbesondere eines Common-Rail-Inj ektors eines Kraftfahrzeuges.Such a valve is known from practice and serves in particular as a control module of a fuel injection valve, in particular a common rail injector of a motor vehicle.
Ein bekanntes Ventil der einleitend genannten Art weist zur Betätigung einen piezoelektrischen Aktor auf. Eine Auslenkung des piezoelektrischen Aktors wird bei Betätigung des Ventils über eine Hydraulikkammer, welche als hydraulische Übersetzung bzw. Kopplungs- und Toleranzausgleichselement arbeitet, auf ein Ventilschließglied übertragen. Die als hydraulischer Koppler wirkende Hydraulikkammer ist zwischen einem mit dem piezoelektrischen Aktor verbundenen Stellkolben und einem mit dem Ventilschließglied verbundenen Betätigungskolben angeordnet. Der Durchmesser des Stellkolbens ist größer als derjenige des Betätigungskolbens, so daß der Betätigungskolben einen um das Übersetzungsverhältnis der Kolbendurchmesser vergrößerten Hub macht, wenn der Stellkolben mittels des piezoelektrischen Aktors eine bestimmte Auslenkung erfährt.A known valve of the type mentioned in the introduction has a piezoelectric actuator for actuation. A deflection of the piezoelectric actuator is transmitted to a valve closing element when the valve is actuated via a hydraulic chamber, which works as a hydraulic transmission or coupling and tolerance compensation element. As Hydraulic coupler hydraulic chamber is arranged between an actuating piston connected to the piezoelectric actuator and an actuating piston connected to the valve closing member. The diameter of the actuating piston is larger than that of the actuating piston, so that the actuating piston makes a stroke enlarged by the ratio of the piston diameters when the actuating piston experiences a certain deflection by means of the piezoelectric actuator.
Die Hydraulikkammer ist derart ausgelegt, daß während des Betriebes auftretende Leckagen durch eine WiederbefuUung ausgeglichen werden können. Hierzu wirkt beispielsweise über am Umfang der Kolben ausgebildete Leckspalte ein in einem Systembereich bzw. Systemraum des Ventils herrschender Fluiddruck, der sogenannte Systemdruck, auf die Hydraulikkammer.The hydraulic chamber is designed in such a way that leakages that occur during operation can be compensated for by refilling. For this purpose, fluid pressure prevailing in a system area or system space of the valve, the so-called system pressure, acts on the hydraulic chamber, for example via leak gaps formed on the circumference of the pistons.
Der Systembereich wird derart mit dem Fluiddruck beaufschlagt, daß bei einem Betätigen des Ventils das Ventilschließglied in eine Öffnungsstellung verfahren wird und so ein Fluidstrom in den Systembereich strömen kann. Die in den Systembereich strömende Fluidmenge stellt die sogenannte Absteuermenge dar, welche nachfolgend über einen sogenannten Absteuerkanal aus dem Systembereich abgeführt wird.The system area is acted upon by the fluid pressure in such a way that when the valve is actuated, the valve closing member is moved into an open position and a fluid flow can thus flow into the system area. The amount of fluid flowing into the system area represents the so-called control amount, which is subsequently discharged from the system area via a so-called control channel.
Bei einem bekannten Ventil wird der in dem Systembereich herrschende Systemdruck von etwa 30 bar mittels eines in dem Absteuerkanal angeordneten Rückschlagventils aufgestaut, so daß der in dem Systembereich herrschende Druck hinreichend groß ist, um eine WiederbefuUung der Hydraulikkammer zu gewährleisten.In a known valve, the system pressure of approximately 30 bar prevailing in the system area is accumulated by means of a check valve arranged in the control channel, so that the pressure prevailing in the system area is sufficiently large to ensure that the hydraulic chamber is refilled.
Bei einem Einsatz dieses Ventils bei einem Kraftstoffein- spritzventil eines Kraftfahrzeuges, wie bei einem Common- Rail-Injektor, bei dem stromauf des Ventilschließglieds ein Druck von etwa 1,5 kbar herrscht, strömt die Absteuermenge mit einem hohen Druck in den Systembereich, so daß in dem Systembereich Druckspitzen entstehen, die die Funktionsfähigkeit des ebenfalls dem Systemdruck ausgesetzten Aktormoduls gegebenenfalls beeinträchtigen können. Ferner ist eine werksseitige Erstbefüllung des hydraulischen Kopplers erforderlich.When this valve is used in a fuel injection valve of a motor vehicle, such as in a common rail injector, in which there is a pressure of approximately 1.5 kbar upstream of the valve closing element, the discharge quantity flows into the system area at a high pressure, so that Pressure peaks occur in the system area, which may impair the functionality of the actuator module, which is also exposed to the system pressure. Furthermore, a factory filling of the hydraulic coupler is required.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Ventil zum Steuern von Flüssigkeiten mit den Merkmalen nach dem Oberbegriff des Patentanspruches 1, bei welchem der Systemraum über den Absteuerkanal mit einem Fluiddruck beaufschlagt ist, hat den Vorteil, daß eine werksseitige Erstbefüllung des hydraulischen Kopplers nicht erforderlich ist, da die Befüllung bei Inbetriebnahme des Ventils durch die Zufuhr von Fluid in den Systembereich über den gegebenenfalls als Öffnung des Ventilgehäuses ausgebildeten Absteuerkanal erfolgt und somit stets ein hinreichend großer Wiederbefülldruck in dem Systemraum bzw. -bereich bereitgestellt wird.The valve according to the invention for controlling liquids with the features according to the preamble of claim 1, in which the system space is pressurized with a fluid pressure via the drainage channel, has the advantage that an initial filling of the hydraulic coupler at the factory is not necessary, since the filling during commissioning of the valve takes place by supplying fluid into the system area via the control channel, which may be designed as an opening of the valve housing, and thus a sufficiently high refilling pressure is always provided in the system room or area.
Bei Einsatz des Ventils nach der Erfindung bei einem Kraftstoffeinspritzventil eines Kraftfahrzeuges kann der Absteu- erkanal mit einer Druckvorrichtung verbunden sein, welche gleichzeitig eine Kraftstoffpumpe des Kraftfahrzeuges darstellen kann. Im Fall eines Common-Rail-Injektors kann die eingesetzte Kraftstoffpumpe eine in einem Kraftstoffvorratstank angeordnete Kraftstoffvorförderpumpe zur Förderung von Kraftstoff zu einer Hochdruckpumpe sein, welche den sogenannten Common-Rail-Druck bereitstellt. Die Vorförderpum- pe wirkt beispielsweise mit einem Druck von etwa 5 bar über den Absteuerkanal auf den Systembereich.When using the valve according to the invention in a fuel injection valve of a motor vehicle, the control can be connected to a pressure device which can simultaneously represent a fuel pump of the motor vehicle. In the case of a common rail injector, the fuel pump used can be a fuel feed pump arranged in a fuel storage tank for conveying fuel to a high-pressure pump, which provides the so-called common rail pressure. The pre-feed pump acts, for example, on the system area with a pressure of about 5 bar via the discharge channel.
Drücke, welche sich infolge von Absteuervorgängen in dem Systembereich aufstauen, können bei dem Ventil nach der Erfindung so abgesteuert werden, daß die anfallende Fluidmen- ge direkt zu der Hochdruckpumpe geführt wird, statt daß die Absteuermenge in den Kraftstoffvorratstank zurückgeführt wird. Die Kraftstoffpumpe ist zweckmäßigerweise mit einem Druckbegrenzungsventil ausgestattet, so daß die Pumpe gegenüber hohe Drücke geschützt ist.Pressures which build up as a result of control processes in the system area can be controlled in the valve according to the invention in such a way that the amount of fluid produced is fed directly to the high-pressure pump instead of the control amount being returned to the fuel supply tank. The fuel pump is expediently equipped with a pressure relief valve, so that the pump is protected against high pressures.
Bei einer vorteilhaften Ausführungsform des Ventils nach der Erfindung ist an dem Absteuerkanal eine Drossel vorgesehen. Die Drossel bewirkt, daß ein sich in dem Systembereich aufstauender Druck langsam an einen nachgeschalteten Fluidkreis abgeführt wird. Gegebenenfalls in dem Systembereich anfallende Druckspitzen, die bis zu 60 bar betragen können, können über die Drossel abgebaut werden. Eine Druckerhöhung in dem Systembereich wird mittels der Drossel dynamisch mitgenommen, was wiederum zu tolerablen Belastungen des piezoelektrischen Aktormoduls und somit zu einem robusten Ventil führt. Die Drossel ist bevorzugt von einem Rohreinschraubteil gebildet. Ein Rohreinschraubteil stellt ein einfaches und robustes sowie toleranzunempfindliches Bauteil dar, bei dem keine Einstellvorgänge erforderlich sind und dessen Bauraumbedarf gering ist und das leicht herstellbar ist . Durch bloßen Austausch des Rohreinschraubteils mit einem bestimmten Innendurchmesser gegen ein Rohreinschraubteil mit einem anderen Innendurchmesser kann das Ventil nach der Erfindung ohne weiteres an sich ändernde Betriebsbedingungen angepaßt werden .In an advantageous embodiment of the valve according to the invention, a throttle is provided on the control channel. The throttle causes a pressure that builds up in the system area to be slowly discharged to a downstream fluid circuit. Possibly occurring pressure peaks in the system area, which can be up to 60 bar, can be reduced via the throttle. A pressure increase in the system area is taken dynamically by means of the throttle, which in turn leads to tolerable loads on the piezoelectric actuator module and thus to a robust valve. The throttle is preferably formed by a pipe screw-in part. A pipe screw-in part is a simple and robust component that is insensitive to tolerances, in which no adjustment processes are required and whose space requirement is small and which is easy to manufacture. The valve according to the invention can be easily adapted to changing operating conditions simply by replacing the pipe screw-in part with a certain inner diameter by a pipe screw-in part with a different inner diameter.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes nach der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous refinements of the subject matter according to the invention can be found in the description, the drawing and the patent claims.
Zeichnungdrawing
Ein Ausführungsbeispiel des Ventils nach der Erfindung ist in der Zeichnung schematisch vereinfacht dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigenAn embodiment of the valve according to the invention is shown schematically simplified in the drawing and is explained in more detail in the following description. Show it
Figur 1 einen vereinfachten Längsschnitt durch ein Ventil nach der Erfindung bei einem Common-Rail-Einspritzsystem eines Dieselkraftfahrzeuges; und1 shows a simplified longitudinal section through a valve according to the invention in a common rail injection system of a diesel motor vehicle; and
Figuren 2a und 2b eine Drossel des Ventils nach Figur 1.FIGS. 2a and 2b show a throttle of the valve according to FIG. 1.
Beschreibung des Ausführungsbeispiels In Figur 1 ist ein Teil eines Systems zum Einspritzen von Kraftstoff bei einem Diesel-Verbrennungsmotor eines Kraftfahrzeuges dargestellt, wobei das System ein Ventil 10 zum Steuern von Flüssigkeiten bei einem Kraftstoffeinspritzven- til umfaßt. Das Ventil 10 bildet ein Steuermodul für ein hier nicht näher dargestelltes Düsenmodul des Kraftstoffeinspritzventils bzw. -injektors.Description of the embodiment FIG. 1 shows part of a system for injecting fuel in a diesel internal combustion engine of a motor vehicle, the system comprising a valve 10 for controlling liquids in a fuel injection valve. The valve 10 forms a control module for a nozzle module of the fuel injection valve or injector, which is not shown here.
Das Düsenmodul schließt sich an das Steuermodul in axialer Richtung an und umfaßt eine in einem Düsenkörper angeordnete und geführte Düsennadel, die zu einem Brennraum des Verbrennungsmotors führende Öffnungen des Düsenkörpers steuert .The nozzle module connects to the control module in the axial direction and comprises a nozzle needle arranged and guided in a nozzle body, which controls openings of the nozzle body leading to a combustion chamber of the internal combustion engine.
Die Düsennadel bildet mit einem Ventilsteuerkolben eine Baueinheit, wobei der Ventilsteuerkolben an einen sogenannten Ventilsteuerraum grenzt. Der Ventilsteuerraum steht über eine Zulaufdrossel mit einem Kraftstoffhochdruckkanal und über eine Ablaufdrossel mit einem Ventilraum 11 des Ventils 10 in Wirkverbindung. Der Kraftstoffhochdruckkanal ist mittels einer Hochdruckpumpe 12 mit unter einem Druck von etwa 1,5 kbar stehendem Kraftstoff beaufschlagt, welcher mittels einer Vorförderpumpe 13 aus einem Kraftstofftank 14 über eine Zufuhrleitung 15 an die Saugseite der Hochdruckpumpe 12 gefördert wird.The nozzle needle forms a structural unit with a valve control piston, the valve control piston bordering a so-called valve control chamber. The valve control chamber is operatively connected via an inlet throttle to a high-pressure fuel channel and via an outlet throttle to a valve chamber 11 of the valve 10. The high-pressure fuel channel is acted upon by a high-pressure pump 12 with fuel at a pressure of approximately 1.5 kbar, which is conveyed by means of a pre-feed pump 13 from a fuel tank 14 via a feed line 15 to the suction side of the high-pressure pump 12.
Die Hochdruckpumpe 12 hat eine Druckseite 16, welche zu einem sogenannten, hier nicht näher dargestellten Common-Rail führt, über welchen mehrere Kraftstoff-Injektoren mit Kraftstoff gespeist werden und der u.a. mit dem vorstehend genannten Kraftstoffhochdruckkanal verbunden ist. Die Kraftstoff-Injektoren sind jeweils mit einem Steuermodul nach Art des Ventils 10 ausgestattet.The high-pressure pump 12 has a pressure side 16, which leads to a so-called common rail, not shown here, via which a plurality of fuel injectors are fed with fuel and which is connected, inter alia, to the aforementioned high-pressure fuel channel. The Fuel injectors are each equipped with a control module in the manner of valve 10.
Ein mittels des hier beschriebenen Kraftstoffeinspritzven- tils ausgeübter Einspritzvorgang wird über den in dem Ventilsteuerraum herrschenden Druck gesteuert, welcher mittels des Ventils bzw. Steuermoduls 10 einstellbar ist.An injection process carried out by means of the fuel injection valve described here is controlled via the pressure prevailing in the valve control chamber, which pressure can be adjusted by means of the valve or control module 10.
Das Ventil bzw. Steuermodul 10 umfaßt ein Ventilgehäuse 20, in welchem ein sogenannter Systembereich bzw. Systemraum 21 ausgebildet ist. In dem Systemraum 21 ist einerseits ein Aktormodul 22 und andererseits ein Kopplermodul 23 angeordnet .The valve or control module 10 comprises a valve housing 20 in which a so-called system area or system space 21 is formed. In the system room 21, on the one hand, an actuator module 22 and, on the other hand, a coupler module 23 are arranged.
Das Aktormodul 22, das einen piezoelektrischen Aktor umfaßt und sich an dem Ventilgehäuse 20 abstützt, ist mit einem dem Kopplermodul 23 zugeordneten Stellkolben 24 verbunden, der in einer zylindrischen Bohrung 25 eines Kopplergehäuses 26 axial beweglich geführt ist.The actuator module 22, which comprises a piezoelectric actuator and is supported on the valve housing 20, is connected to an actuating piston 24, which is assigned to the coupler module 23 and is axially movably guided in a cylindrical bore 25 of a coupler housing 26.
Des weiteren ist der Stellkolben 24 mittels einer Schraubenfeder 27, welche an einer mit dem Stellkolben 24 verbundenen Stützplatte 28 angreift und sich an dem Kopplergehäuse 26 abstützt, in Richtung des Aktormoduls 22 vorgespannt.Furthermore, the actuating piston 24 is biased in the direction of the actuator module 22 by means of a helical spring 27, which engages on a support plate 28 connected to the actuating piston 24 and is supported on the coupler housing 26.
Der Stellkolben 24 steht über einen als Hydraulikkammer ausgebildeten, hydraulischen Koppler 29 mit einem sogenannten Betätigungskolben 30 in Wirkverbindung, der zur Betätigung eines Ventilschließglieds 31 dient und mit letzterem über einen Führungskolben 32 verbunden ist. Der Betätigungskolben 30, der in einer zylindrischen Bohrung 35 des Kopplergehäuses 26 geführt ist, ist mittels einer Schraubenfeder 33, die sich an dem Kopplerkörper 26 abstützt und an einer weiteren Stützplatte 34 angreift, in Richtung des Ventilschließglieds 31 vorgespannt. Der Durchmesser des Betätigungskolbens 30 ist kleiner als derjenige des Stellkolbens 24, so daß der hydraulische Koppler 29 als hydraulischer Übersetzer wirkt.The actuating piston 24 is operatively connected via a hydraulic coupler 29 designed as a hydraulic chamber to a so-called actuating piston 30, which is used to actuate a valve closing member 31 and is connected to the latter via a guide piston 32. The actuating piston 30 which in a cylindrical bore 35 of the Coupler housing 26 is guided, is biased in the direction of the valve closing member 31 by means of a coil spring 33, which is supported on the coupler body 26 and engages on a further support plate 34. The diameter of the actuating piston 30 is smaller than that of the actuating piston 24, so that the hydraulic coupler 29 acts as a hydraulic translator.
Das Ventilschließglied 31 ist in dem mit dem Ventilsteuerraum des Düsenmoduls verbundenen Ventilraum 11 angeordnet und mittels einer Tellerfeder 36 bei nicht betätigtem piezoelektrischen Aktor 22 in Schließstellung gehalten, so daß es an einem Ventilsitz 37 anliegt.The valve closing member 31 is arranged in the valve chamber 11 connected to the valve control chamber of the nozzle module and is held in the closed position by means of a plate spring 36 when the piezoelectric actuator 22 is not actuated, so that it bears against a valve seat 37.
Des weiteren zweigt von dem Systemraum 21 ein als Öffnung ausgebildeter Absteuerkanal 38 ab, der mit einer als Rohreinschraubteil ausgebildeten Drossel 39 versehen ist und über eine Leitung 40 mit der Kraftstoffvorförderpumpe 13 sowie der zu der Hochdruckpumpe 12 führenden Zufuhrleitung 15 verbunden ist.Furthermore, a branch duct 38, which is designed as an opening, branches off from the system space 21 and is provided with a throttle 39 designed as a pipe screw-in part and is connected via a line 40 to the fuel feed pump 13 and to the supply line 15 leading to the high pressure pump 12.
Die Drossel 39 ist in den Figuren 2a und 2b näher dargestellt und umfaßt einen Anschlußbereich 41 für einen der Leitung 40 zugeordneten Druckschlauch sowie ein Einschraubgewinde 42 zur Fixierung an dem Ventilgehäuse 20 und hat einen Innendurchmesser d von etwa 1 mm.The throttle 39 is shown in more detail in FIGS. 2a and 2b and comprises a connection area 41 for a pressure hose assigned to the line 40 and a screw thread 42 for fixing to the valve housing 20 and has an inner diameter d of approximately 1 mm.
Das in den Figuren 1 und -2 ' dargestellte Ventil 10 arbeitet in nachfolgend beschriebener Weise. Im Betrieb des in Figur 1 dargestellten Einspritzsystems wird aus dem Kraftstofftank 14 mittels der Vorförderpumpe 13 über die Förderleitung 15 Kraftstoff in die Hochdruckpumpe 12 gefördert, mittels welcher die Common-Rail und so der Kraftstoffhochdruckkanal des Kraftstoffeinspritzventils mit Kraftstoff versorgt werden, so daß in dem Ventilsteuerraum des Düsenmoduls sowie in dem Ventilraum 11 des in Figur 1 dargestellten Ventils 10 der sogenannte Rail-Druck herrscht .The valve 10 shown in Figures 1 and -2 ' operates in the manner described below. In operation of the injection system shown in Figure 1, fuel is conveyed from the fuel tank 14 by means of the pre-feed pump 13 via the delivery line 15 into the high-pressure pump 12, by means of which the common rail and thus the high-pressure fuel channel of the fuel injection valve are supplied with fuel, so that in the valve control chamber of the nozzle module and in the valve chamber 11 of the valve 10 shown in FIG. 1 the so-called rail pressure prevails.
Des weiteren ist der Systemraum 21 bei Inbetriebnahme des Systems, d. h. beim Start der Vorförderpumpe 13, über die von der Zufuhrleitung 15 abzweigende Leitung 40 und die Drossel 39 mit Kraftstoff, also mit einem Fluid beaufschlagt, das unter dem Förderdruck der Vorförderpumpe 13 steht, der in dem Bereich von 3 bar bis 5 bar liegt. Dieser Druck bewirkt, daß über ringförmige Leckspalte, welche die Kolben 24 und 30 im Bereich der Bohrungen 25 und 35 umgeben, eine Befüllung des hydraulischen Kopplers 29 erfolgt. Der Druck für die Befüllung des hydraulischen Kopplers 29 wird mithin von einer in dem Kraftfahrzeug vorhandenen Druckvorrichtung, hier der Kraftstoffvorförderpumpe, übernommen.Furthermore, the system room 21 when the system is started up, i. H. at the start of the pre-feed pump 13, via the line 40 branching off from the supply line 15 and the throttle 39 with fuel, that is to say with a fluid which is under the delivery pressure of the pre-feed pump 13, which is in the range from 3 bar to 5 bar. This pressure causes the hydraulic coupler 29 to be filled via annular leak gaps which surround the pistons 24 and 30 in the region of the bores 25 and 35. The pressure for filling the hydraulic coupler 29 is therefore taken over by a pressure device present in the motor vehicle, here the fuel feed pump.
Bei einem Einspritzvorgang wird das Aktormodul 22 mit einer Spannung beaufschlagt, so daß dieses eine axiale Längung erfährt und der Stellkolben 24 in Richtung des Ventilschließglieds 31 ausgelenkt wird, wodurch wiederum ein Hub des Betätigungskolbens 30 und damit des Ventilschließglieds 31 ausgelöst wird. Dadurch wird das Ventilschließglied 31 in Öffnungsstellung verfahren, wodurch eine Absteuermenge an Kraftstoff von dem Ventilraum 11 in den Systemraum 21 abströmt. Die Absteuermenge wird über die Öffnung 38 und die Drossel 39 sowie die Leitungen 40 und 15 der Hochdruckpumpe 12 bereitgestellt. Die Drossel 39 bewirkt, daß Druckspitzen, die gegebenenfalls bis zu 60 bar betragen können, dynamisch abgebaut werden. During an injection process, the actuator module 22 is subjected to a voltage, so that it is axially elongated and the actuating piston 24 is deflected in the direction of the valve closing member 31, which in turn triggers a stroke of the actuating piston 30 and thus the valve closing member 31. As a result, the valve closing member 31 is moved into the open position, which results in a control quantity fuel flows out of the valve chamber 11 into the system chamber 21. The discharge quantity is provided via the opening 38 and the throttle 39 as well as the lines 40 and 15 of the high-pressure pump 12. The throttle 39 causes pressure peaks, which can possibly be up to 60 bar, to be reduced dynamically.

Claims

AnsprücheExpectations
Ventil zum Steuern von Flüssigkeiten, insbesondere bei einem Einspritzventil eines Verbrennungsmotors, umfassend ein Ventilgehäuse (20), in welchem ein Systembereich (21) ausgebildet ist, in dem ein piezoelektrisches Aktormodul (22) und ein hydraulisches Kopplermodul (23) angeordnet sind, welches einen StellkolbenValve for controlling liquids, in particular in an injection valve of an internal combustion engine, comprising a valve housing (20) in which a system area (21) is formed, in which a piezoelectric actuator module (22) and a hydraulic coupler module (23) are arranged, which one actuating piston
(24), auf den das Aktormodul (22) wirkt, sowie einen über eine Hydraulikkammer (29) mit dem Stellkolben (24) in Wirkverbindung stehenden Betätigungskolben (30) aufweist, der mit einem mit einem Ventilsitz (37) zusammenwirkenden Ventilschließglied (31) verbunden ist, wobei der Stellkolben (24) und der Betätigungskolben (30) die Hydraulikkammer (29) begrenzen und in dem Systembereich (21), von dem ein Absteuerkanal (38) abzweigt, ein Systemdruck zur WiederbefuUung der Hydraulikkammer(24), on which the actuator module (22) acts, and has an actuating piston (30) which is operatively connected to the actuating piston (24) via a hydraulic chamber (29) and which has a valve closing member (31) which interacts with a valve seat (37). is connected, the actuating piston (24) and the actuating piston (30) delimiting the hydraulic chamber (29) and in the system area (21), from which a control duct (38) branches off, a system pressure for refilling the hydraulic chamber
(29) herrscht, dadurch gekennzeichnet, daß der Systembereich (21) über den Absteuerkanal (38) mit einem Fluid beaufschlagt ist. (29) prevails, characterized in that the system area (21) is acted upon by a fluid via the control channel (38).
2. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der Absteuerkanal (38) mit einer Druckvorrichtung (13) verbunden ist.2. Valve according to claim 1, characterized in that the control channel (38) is connected to a pressure device (13).
3. Ventil nach Anspruch 2, dadurch gekennzeichnet, daß die Druckvorrichtung eine Kraftstoffpumpe (13) eines Kraftfahrzeuges ist.3. Valve according to claim 2, characterized in that the pressure device is a fuel pump (13) of a motor vehicle.
4. Ventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß an dem Absteuerkanal (38) eine Drossel (39) vorgesehen ist.4. Valve according to one of claims 1 to 3, characterized in that a throttle (39) is provided on the control channel (38).
5. Ventil nach Anspruch 4, dadurch gekennzeichnet, daß die Drossel aus einem Rohreinschraubteil (39) gebildet ist.5. Valve according to claim 4, characterized in that the throttle is formed from a pipe screw-in part (39).
6. Ventil nach Anspruch 4, dadurch gekennzeichnet, daß das Rohreinschraubteil (39) einen Innendurchmesser zwischen etwa 0,5 mm und 3 mm hat.6. Valve according to claim 4, characterized in that the pipe screw-in part (39) has an inner diameter between approximately 0.5 mm and 3 mm.
7. Ventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Absteuerkanal (38) mit einer Hochdruckpumpe (12) zur Erzeugung eines Raildrucks bei einem Common-Rail-Einspritzsystem verbunden ist. 7. Valve according to one of claims 1 to 6, characterized in that the control channel (38) is connected to a high pressure pump (12) for generating a rail pressure in a common rail injection system.
EP02754530A 2001-10-19 2002-08-16 Valve for controlling liquids Expired - Lifetime EP1440237B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10151688 2001-10-19
DE10151688A DE10151688A1 (en) 2001-10-19 2001-10-19 Valve for controlling liquids
PCT/DE2002/003005 WO2003038269A1 (en) 2001-10-19 2002-08-16 Valve for controlling liquids

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EP1440237A1 true EP1440237A1 (en) 2004-07-28
EP1440237B1 EP1440237B1 (en) 2005-11-16

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US (1) US6899069B2 (en)
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JP (1) JP2005507053A (en)
AT (1) ATE310162T1 (en)
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WO (1) WO2003038269A1 (en)

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EP1440237B1 (en) 2005-11-16
ATE310162T1 (en) 2005-12-15
WO2003038269A1 (en) 2003-05-08
US20040154562A1 (en) 2004-08-12
JP2005507053A (en) 2005-03-10
US6899069B2 (en) 2005-05-31
DE10151688A1 (en) 2003-04-30
DE50204975D1 (en) 2005-12-22

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