EP0770776B1 - Metering valve for a fuel injector - Google Patents
Metering valve for a fuel injector Download PDFInfo
- Publication number
- EP0770776B1 EP0770776B1 EP96116113A EP96116113A EP0770776B1 EP 0770776 B1 EP0770776 B1 EP 0770776B1 EP 96116113 A EP96116113 A EP 96116113A EP 96116113 A EP96116113 A EP 96116113A EP 0770776 B1 EP0770776 B1 EP 0770776B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- aperture
- high pressure
- housing
- power assisted
- 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
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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
- 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
-
- 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
Definitions
- the invention relates to a servo valve for an injection nozzle.
- Such a servo valve is described in SAE paper No. 910252 "Development of New Electronically Controlled Fuel Injection System ECD-U2 for Diesel Engines " described.
- Its valve member consists of an outer valve body and an in this guided inner valve body.
- the outer valve body is usually from a spring pushed down into contact with the first valve seat, so that the Return opening is closed.
- the inner valve member is the pressure in the Valve chamber moves upward and there is one formed in the outer valve member High pressure opening free.
- an electromagnetic coil When an electromagnetic coil is excited, it moves the outer valve member up and lifts off the first seat so that the Connection opening is connected to the return opening.
- the upward movement of the outer valve member stops until the second seat formed thereon is in System moves to the inner valve member, which closes the high pressure opening becomes.
- the known servo valve is relatively complex in its construction, since one in its housing trained guide for the outer valve member and one on the Inside of the outer valve member formed guide for the inner valve member must be manufactured precisely. The guidance between the inner valve member and the outer valve member is with the second seat open with high pressure fluid acts, which leads to leakage losses.
- the electromagnetic Actuation of the outer valve member inherently relatively large Delay times between the start of the excitation of the solenoid and the Movement of the outer valve member, which is relatively fraught with friction, since the outer valve member on its outside opposite the housing and on its inside moved relative to the inner valve member.
- a servo valve according to the preamble of claim 1 is known from DE-A-4 406 901.
- the usage of piezo actuators for servo valves is in the GB-A-2 087 660.
- the invention has for its object a generic servo valve to develop further so that the problems mentioned do not occur.
- the servo valve according to the invention characterized in the main claim is compact and extremely simple and therefore inexpensive to manufacture, especially because none Double fits are required.
- the valve member that passes directly through the return port is actuated by the actuator, can by means of Piezo actuator directly against that in the valve chamber prevailing high pressure can be opened, strokes in the order of 20 up to 30 ⁇ m are sufficient to switch the servo valve.
- the Piezo actuators and the small strokes are extremely fast switching times and precise Actuations of the servo valve possible.
- the speed curve is the Stroke movement of the valve member by appropriate control of the variable length component or actuators controllable so that the valve member in soft System comes to the seats, which is advantageous for a long life.
- the thermal coordination of the housing material to that of the piezo actuator avoids temperature influences on the position of the actuating element.
- the piezo actuator is advantageously arranged so that the injection nozzle is closed in the de-energized or de-energized state, which for system security is advantageous.
- With the servo valve according to the invention are extremely high System pressures possible.
- the high pressure line is directly to the valve chamber connected, whereby no piston guides or seals against high pressure similar are required.
- the subclaims relate to advantageous developments of the servo valve according to the invention directed.
- a fuel tank 2 via a filter and a prefeed pump 4 with a common rail (CR) high pressure pump 6 connected.
- CR common rail
- From the high pressure pump leads a line of a distribution line (common rail) 8, which leads 10 with each Cylinder assigned to a multi-cylinder internal combustion engine Injector 12 is connected.
- the injection nozzle units 12 are via return lines 14 with one leading to the tank 2 Return line 16 connected.
- the system pressure is limited by means of a limiting valve 18 and can last up to 2000 bar.
- the outputs of an electronic control unit 20 are connected to the high-pressure pump 6 and the injection nozzle units 12 connected.
- the inputs 22 of the control device are with a pressure sensor 24 in the distribution line 8 and other, not shown Sensors connected, for example for the position of an accelerator pedal, the driving speed, Temperatures, boost pressure, air mass, speed, etc.
- Fig. 2 shows the basic structure of an injection nozzle unit with the associated Hydraulic scheme.
- the injection nozzle unit contains a nozzle body 26 which ends in a nozzle needle, which rests on a valve seat when the injector is closed.
- the Nozzle body 26 extends through a nozzle chamber 28, which is connected to the feed line 10.
- the nozzle body 26 is connected to an actuator piston 30 or in one piece with this trained who works in a working chamber 32.
- the working chamber 32 is via a connecting line 34 with a connecting throttle 36 to a Connection opening 38 connected to a valve chamber 40 of a total is designed with 42 designated servo valve.
- the valve chamber 40 also has a high-pressure opening 44, which is connected via a an inlet throttle 46 provided high pressure line 48 connected to the feed line 10 is.
- a return opening 50 of the valve chamber 40 is connected to the return line 14.
- a valve member designed as a ball 52 protrudes through the Return opening 50 through a shaft 56 actuated by a piezo actuator 54
- Piezo actuator 54 is connected to the control unit via electrical connections (not shown) 20 (Fig. 1) connected.
- Piezo actuators are known per se and constructed like capacitors, their dielectric made of piezoelectric material, for example lead zirconate titanate ceramic consists. Modern actuators work with field strengths of up to 2000 V / mm and reach relative changes in length of up to 1.5 per mille. In the example shown With a length of the piezo actuator 40 of approximately 30 mm, a stroke of approximately Achieve 0.03 mm. A typical switching time is 50 ⁇ s, with the Speed of movement of the shaft 56 by appropriate control of the Piezo actuator 54 is controllable.
- FIG. 3 shows an overall sectional view of an injection nozzle unit 12 with housing 58 and High pressure connection 60 for connection to the distribution line 8 (Fig. 1). Not electrical connections are shown, by means of which the piezo actuator 54 with the Control unit 20 is connected.
- the entire injector unit 12 is directly on the cylinder head of an internal combustion engine attached, it is intended for the precision of valve actuation, different elongations between the piezo actuator 54 and the housing 58, which accommodates the piezo actuator 54.
- the housing 58 consists of one at least in the region of the piezo actuator 54 Low thermal expansion material similar to that of the piezo actuator 54, for example made of Invar steel.
- a screw 62 on the housing 58 attached insert bolts 64 are made of a material that is larger Has thermal expansion than that of the housing material, for example made of aluminum.
- FIG. 4 shows the middle area of the injector unit 12 of FIG. 3 in 5 again shows the central region of FIG. 4 in enlarged scale.
- Fig. 4 is the injection valve with the actuator piston 30 and that Servo valve receiving housing part 65 screwed to the housing 58.
- the Valve ball 52 of the servo valve is advantageously moved upwards by a spring 66 Contact with a pin 68 actuated by the piezo actuator 54 or a first seat 70 (Fig. 5) crowded.
- the pin 68 works with a in a bore of the housing 58, in which the piezo actuator 54 is also accommodated, brought together component 72 which is supported on the piezo actuator 54 via a hemisphere 74.
- a component 78 is provided for component 72 and the inner wall of bore 76.
- the Components 58, 72 and 74 form the shaft designated 56 in FIG. 2.
- a needle stroke transmitter 80 is provided for the displacement of the actuator piston 30 with the degree of opening of the injector, not shown in Fig. 4 exactly is determinable.
- FIG. 5 shows the central part of the servo valve
- the two housing bodies 82 and 84 has that between the housing 58 and the screwed to this housing part 65 are strained against each other.
- the housing body 82 and 84 have mutually aligned bores, one Form part of the high pressure line 10. Further is that Housing body 82 is provided with a through hole 86 with a blind hole 88 of the housing body 84 is aligned. One leads from the blind bore 88 to the feed line 10 the bore representing the high pressure line 48.
- the through hole 86 ends at the top in an annular recess 90, from which from the return line 14, not shown in FIGS. 4 and 5.
- the one in Fig. 4 The pin 68 shown advantageously has longitudinal grooves on its outside, so that it does not close the through hole 86.
- the ball 52 In the de-energized state of the piezo actuator 54, the ball 52 is on the in the Fig. upper, i.e. first seat 70 (Fig. 5). Thus, the return line 14 is closed and the High pressure line 48 connected to the connecting line 34 so that the Working chamber 32 is pressurized with high pressure when the system pressure is present. The Injection nozzle is then closed, since the nozzle body 26 on the Working chamber 32 forth force is greater than that from the nozzle chamber 28 forth Acting force.
- the dynamics of the system is due to the extremely small valve lift and that rapid response behavior of the piezo actuator is extremely precise and can Appropriate choice of chokes 46 and / or 36 can be varied.
- the period, meanwhile both seats are open and the high pressure line 48 with the return line 14 is extremely short, so that losses to a minimum are reduced.
Description
Die Erfindung betrifft ein Servoventil für eine Einspritzdüse.The invention relates to a servo valve for an injection nozzle.
Ein solches Servoventil ist im SAE paper Nr. 910252 "Development of New Electronically Controlled Fuel Injection System ECD-U2 for Diesel Engines" beschrieben. Sein Ventilglied besteht aus einem äußeren Ventilkörper und einem in diesem geführten inneren Ventilkörper. Der äußere Ventilkörper ist normalerweise von einer Feder nach unten in Anlage an den ersten Ventilsitz gedrängt, so daß die Rücklauföffnung geschlossen ist. Das innere Ventilglied wird vom Druck in der Ventilkammer nach oben bewegt und gibt dabei eine im äußeren Ventilglied ausgebildete Hochdrucköffnung frei. Wenn eine elektromagnetische Spule erregt wird, bewegt sich das äußere Ventilglied aufwärts und hebt vom ersten Sitz ab, so daß die Verbindungsöffnung mit der Rücklauföffnung verbunden wird. Die Aufwärtsbewegung des äußeren Ventilglieds hält an, bis sich der an diesem ausgebildete zweite Sitz in Anlage an das innere Ventilglied bewegt, wodurch die Hochdrucköffnung verschlossen wird.Such a servo valve is described in SAE paper No. 910252 "Development of New Electronically Controlled Fuel Injection System ECD-U2 for Diesel Engines " described. Its valve member consists of an outer valve body and an in this guided inner valve body. The outer valve body is usually from a spring pushed down into contact with the first valve seat, so that the Return opening is closed. The inner valve member is the pressure in the Valve chamber moves upward and there is one formed in the outer valve member High pressure opening free. When an electromagnetic coil is excited, it moves the outer valve member up and lifts off the first seat so that the Connection opening is connected to the return opening. The upward movement of the outer valve member stops until the second seat formed thereon is in System moves to the inner valve member, which closes the high pressure opening becomes.
Das vorbekannte Servoventil ist in seinem Aufbau verhältnismäßig aufwendig, da eine in seinem Gehäuse ausgebildete Führung für das äußere Ventilglied und eine an der Innenseite des äußeren Ventilglieds ausgebildete Führung für das innere Ventilglied präzise gefertigt sein müssen. Die Führung zwischen dem inneren Ventilglied und dem äußeren Ventilglied ist bei offenem zweiten Sitz mit unter Hochdruck stehendem Fluid beaufschlagt, was zu Leckverlusten führt. Zusätzlich bedingt die elektromagnetische Betätigung des äußeren Ventilgliedes systemimmanent verhältnismäßig große Verzögerungszeiten zwischen dem Beginn der Erregung der Magnetspule und der Bewegung des äußeren Ventilglieds, die verhältnismäßig reibungsbehaftet ist, da sich das äußere Ventilglied an seiner Außenseite gegenüber dem Gehäuse und an seiner Innenseite gegenüber dem inneren Ventilglied bewegt.The known servo valve is relatively complex in its construction, since one in its housing trained guide for the outer valve member and one on the Inside of the outer valve member formed guide for the inner valve member must be manufactured precisely. The guidance between the inner valve member and the outer valve member is with the second seat open with high pressure fluid acts, which leads to leakage losses. In addition, the electromagnetic Actuation of the outer valve member inherently relatively large Delay times between the start of the excitation of the solenoid and the Movement of the outer valve member, which is relatively fraught with friction, since the outer valve member on its outside opposite the housing and on its inside moved relative to the inner valve member.
Ein Servoventil gemäß dem Oberbegriff von Anspruch 1 ist aus der DE-A-4 406 901 bekannt. Die Verwendung von Piezoaktuatoren für Servoventile ist in der GB-A-2 087 660 beschrieben.A servo valve according to the preamble of claim 1 is known from DE-A-4 406 901. The usage of piezo actuators for servo valves is in the GB-A-2 087 660.
Der Erfindung liegt die Aufgabe zugrunde, ein gattungsgemäßes Servoventil dahingehend weiter zu entwickeln, daß die genannten Probleme nicht auftreten. The invention has for its object a generic servo valve to develop further so that the problems mentioned do not occur.
Das im Hauptanspruch gekennzeichnete erfindungsgemäße Servoventil ist kompakt und außerordentlich einfach und somit kostengünstig herstellbar, insbesondere weil keine Doppelpassungen erforderlich sind. Das Ventilglied, das unmittelbar durch die Rücklauföffnung hindurch vom Betätigungsglied her betätigt wird, kann mittels des Piezoaktuators unmittelbar gegen den in der Ventilkammer herrschenden hohen Druck geöffnet werden, wobei Hübe in der Größenordnung von 20 bis 30 µm ausreichen, um das Servoventil umzuschalten. Mittels des Piezoaktuators und der kleinen Hübe sind außerordentlich rasche Schaltzeiten und präzise Betätigungen des Servoventils möglich. Desweiteren ist der Geschwindigkeitsverlauf der Hubbewegung des Ventilgliedes durch entsprechende Ansteuerung des längenveränderlichen Bauteils bzw. Aktautors steuerbar, so daß das Ventilglied in weiche Anlage an die Sitze kommt, was für eine lange Lebensdauer vorteilhaft ist. Die thermische Abstimmung des Gehäusematerials auf das des Piezoaktuators vermeidet Temperatur einflüsse auf die Lage des Betätigungselements. Der Piezoaktuator ist vorteilhafterweise so angeordnet, daß die Einspritzdüse im spannungs- bzw. stromlosen Zustand geschlossen ist, was für die Systemsicherheit vorteilhaft ist. Mit dem erfindungsgemäßen Servoventil sind außerordentlich hohe Systemdrücke möglich. Die Hochdruckleitung ist unmittelbar an die Ventilkammer angeschlossen, wodurch keine gegenüber Hockdruck dichtenden Kolbenführungen oder ähnliches erforderlich sind.The servo valve according to the invention characterized in the main claim is compact and extremely simple and therefore inexpensive to manufacture, especially because none Double fits are required. The valve member that passes directly through the return port is actuated by the actuator, can by means of Piezo actuator directly against that in the valve chamber prevailing high pressure can be opened, strokes in the order of 20 up to 30 µm are sufficient to switch the servo valve. By means of the Piezo actuators and the small strokes are extremely fast switching times and precise Actuations of the servo valve possible. Furthermore, the speed curve is the Stroke movement of the valve member by appropriate control of the variable length component or actuators controllable so that the valve member in soft System comes to the seats, which is advantageous for a long life. The thermal coordination of the housing material to that of the piezo actuator avoids temperature influences on the position of the actuating element. The piezo actuator is advantageously arranged so that the injection nozzle is closed in the de-energized or de-energized state, which for system security is advantageous. With the servo valve according to the invention are extremely high System pressures possible. The high pressure line is directly to the valve chamber connected, whereby no piston guides or seals against high pressure similar are required.
Die Unteransprüche sind auf vorteilhafte Weiterbildungen des erfindungsgemäßen Servoventils gerichtet.The subclaims relate to advantageous developments of the servo valve according to the invention directed.
Die Erfindung wird im folgenden anhand schematischer Zeichnungen beispielsweise und mit weiteren Einzelheiten erläutert.The invention is described below with reference to schematic drawings, for example and explained with further details.
Es stellen dar:
- Fig. 1
- ein Gesamtschema eines common-rail-Systems,
- Fig. 2
- das Hydraulikschema mit einem erfindungsgemäßen Servoventil,
- Fig. 3
- einen Schnitt durch ein erfindungsgemäßes Servoventil mit integrierter Ein spritzdüse,
- Fig. 4
- eine vergrößerte Ansicht eines Ausschnitts der Fig. 3 und
- Fig. 5
- eine vergrößerte Ansicht eines Ausschnitts der Fig. 4.
- Fig. 1
- an overall diagram of a common rail system,
- Fig. 2
- the hydraulic diagram with a servo valve according to the invention,
- Fig. 3
- 2 shows a section through a servo valve according to the invention with an integrated injection nozzle,
- Fig. 4
- an enlarged view of a section of FIGS. 3 and
- Fig. 5
- 4 shows an enlarged view of a section of FIG. 4.
Gemäß Fig. 1 ist ein Kraftstofftank 2 über ein Filter und eine Vorförderpumpe 4 mit
einer common-rail (CR)-Hochdruckpumpe 6 verbunden. Von der Hochdruckpumpe führt
eine Leitung einer Verteilerleitung (common-rail) 8, die über Zuleitungen 10 mit jedem
Zylinder einer mehrzylindrischen Brennkraftmaschine zugeordneten
Einspritzdüseneinheiten 12 verbunden ist.1 is a fuel tank 2 via a filter and a prefeed
Die Einspritzdüseneinheiten 12 sind über Rückleitungen 14 mit einer zum Tank 2 führenden
Rücklaufleitung 16 verbunden.The
Der Systemdruck wird mit Hilfe eines Begrenzungsventils 18 begrenzt und kann bis 2000
bar betragen.The system pressure is limited by means of a limiting
Ein elektronisches Steuergerät 20 ist mit seinen Ausgängen mit der Hochdruckpumpe 6
sowie den Einspritzdüseneinheiten 12 verbunden. Die Eingänge 22 des Steuergerätes sind
mit einem Drucksensor 24 in der Verteilerleitung 8 sowie weiteren, nicht dargestellten
Sensoren verbunden, beispielsweise für die Stellung eines Fahrpedals, die Fahrgeschwindigkeit,
Temperaturen, Ladedruck, Luftmasse, Drehzahl usw..The outputs of an
Fig. 2 zeigt den prinzipiellen Aufbau einer Einspritzdüseneinheit mit dem zugehörigen Hydraulikschema.Fig. 2 shows the basic structure of an injection nozzle unit with the associated Hydraulic scheme.
Die Einspritzdüseneinheit enthält einen Düsenkörper 26, der in einer Düsennadel endet,
die im geschlossenen Zustand der Einspritzdüse an einem Ventilsitz anliegt. Der
Düsenkörper 26 durchragt einen Düsenraum 28, der mit der Zuleitung 10 verbunden ist.
Der Düsenkörper 26 ist mit einem Aktuatorkolben 30 verbunden bzw. einteilig mit
diesem ausgebildet, der in einer Arbeitskammer 32 arbeitet. Die Arbeitskammer 32 ist
über eine Verbindungsleitung 34 mit einer Verbindungsdrossel 36 an eine
Verbindungsöffnung 38 angeschlossen, die an einer Ventilkammer 40 eines insgesamt
mit 42 bezeichneten Servoventils ausgebildet ist.The injection nozzle unit contains a
Die Ventilkammer 40 weist weiter eine Hochdrucköffnung 44 auf, die über eine mit
einer Zulaufdrossel 46 versehene Hochdruckleitung 48 mit der Zuleitung 10 verbunden
ist.The
Eine Rücklauföffnung 50 der Ventilkammer 40 ist an die Rückleitung 14 angeschlossen.
Zur Betätigung eines als Kugel 52 ausgebildeten Ventilgliedes ragt durch die
Rücklauföffnung 50 hindurch ein von einem Piezoaktuator 54 betätigter Schaft 56. Der
Piezoaktuator 54 ist über nicht dargestellte elektrische Anschlüsse mit dem Steuergerät
20 (Fig. 1) verbunden.A return opening 50 of the
Piezoaktuatoren sind an sich bekannt und aufgebaut wie Kondensatoren, deren Dielektrikum
aus piezoelektrischen Material, beispielsweise Blei-Zirkonat-Titanat-Keramik
besteht. Moderne Aktuatoren arbeiten mit Feldstärken von bis zu 2000 V/mm und erreichen
relative Längenänderungen von bis zu 1,5 Promille. Im dargestellten Beispiel läßt
sich mit einer Länge des Piezoaktuators 40 von etwa 30 mm somit ein Hub von etwa
0,03 mm erzielen. Eine typische Schaltzeit liegt bei 50 µs, wobei die
Bewegungsgeschwindigkeit des Schaftes 56 durch entsprechende Ansteuerung des
Piezoaktuators 54 steuerbar ist.Piezo actuators are known per se and constructed like capacitors, their dielectric
made of piezoelectric material, for example lead zirconate titanate ceramic
consists. Modern actuators work with field strengths of up to 2000 V / mm and reach
relative changes in length of up to 1.5 per mille. In the example shown
With a length of the
Fig. 3 zeigt eine Gesamtschnittansicht einer Einspritzdüseneinheit 12 mit Gehäuse 58 und
Hochdruckanschluß 60 zum Anschließen an die Verteilerleitung 8 (Fig. 1). Nicht
dargestellt sind elektrische Anschlüsse, mittels derer der Piezoaktuator 54 mit dem
Steuergerät 20 verbunden ist.3 shows an overall sectional view of an
Da die gesamte Einspritzdüseneinheit 12 unmittelbar auf dem Zylinderkopf einer Brennkraftmaschine
angebracht ist, ist es für die Präzision der Ventilbetätigung vorgesehen,
unterschiedliche Längendehnungen zwischen dem Piezoaktuator 54 und dem Gehäuse 58,
das den Piezoaktuator 54 aufnimmt, auszugleichen. Dies geschieht beispielsweise
dadurch, daß das Gehäuse 58 zumindest im Bereich des Piezoaktuators 54 aus einem
Material ähnlich geringer Wärmedehnung wie das des Piezoaktuators 54 besteht,
beispielsweise aus Invarstahl. Bei einer anderen Variante, bei der das Gehäuse 58 aus
normalem Stahl besteht, kann ein mittels einer Schraube 62 an dem Gehäuse 58
befestigter Einsatzbolzen 64 aus einem Material bestehen, das eine größere
Wärmedehnung als die des Gehäusematerials aufweist, beispielsweise aus Aluminium.
Durch zweckentsprechende Abstimmung der Länge des Einsatzbolzens 64 bezüglich der
Länge des Piezoaktuators 54 und des Materials des Gehäuses 58 sowie dessen Länge
kann die geringe Wärmedehnung des Piezoaktuators 54 kompensiert werden.Since the
Fig. 4 stellt den mittleren Bereich der Einspritzdüseneinheit 12 der Fig. 3 in
vergrößertem Maßstab dar. Fig. 5 wiederum zeigt den mittleren Bereich der Fig. 4 in
vergrößertem Maßstab.FIG. 4 shows the middle area of the
Wie aus Fig. 4 ersichtlich, ist ein das Einspritzventil mit dem Aktuatorkolben 30 und das
Servoventil aufnehmendes Gehäuseteil 65 mit dem Gehäuse 58 verschraubt. Die
Ventilkugel 52 des servoventils wird vorteilhafterweise von einer Feder 66 nach oben in
Anlage an einen vom Piezoaktuator 54 betätigten Zapfen 68 bzw. einen ersten Sitz 70
(Fig. 5) gedrängt. Der Zapfen 68 arbeitet mit einem in einer Bohrung des Gehäuses 58,
in der auch der Piezoaktuator 54 aufgenommen ist, geführten Bauteil 72 zusammen, das
sich über eine Halbkugel 74 an dem Piezoaktuator 54 abstützt. Zur Abdichtung zwischen
dem Bauteil 72 und der Innenwand der Bohrung 76 ist eine Dichtung 78 vorgesehen. Die
Bauteile 58,72 und 74 bilden den in Fig. 2 mit 56 bezeichneten Schaft.As can be seen from Fig. 4, is the injection valve with the
Für die Wegaufnahme des Aktuatorkolbens 30 ist ein Nadelhubgeber 80 vorgesehen, mit
dem der Öffnungsgrad des in Fig. 4 nicht dargestellten Einspritzventils genau
bestimmbar ist.A
Fig. 5 zeigt den zentralen Teil des Servoventils, der zwei Gehäusekörper 82 und 84
aufweist, die zwischen dem Gehäuse 58 und dem mit diesem verschraubten Gehäuseteil
65 gegeneinander gespannt sind.5 shows the central part of the servo valve, the two
Der Gehäusekörper 82 und 84 weisen miteinander fluchtende Bohrungen auf, die einen
Teil der mit Hochdruck beaufschlagten Zuleitung 10 bilden. Weiter ist der
Gehäusekörper 82 mit einer Durchgangsbohrung 86 versehen, mit der eine Sackbohrung
88 des Gehäusekörpers 84 fluchtet. Von der Sackbohrung 88 zur Zuleitung 10 führt eine
die Hochdruckleitung 48 darstellende Bohrung.The
Die an die Trennflächen zwischen den Gehäusekörpern 82 und 84 mündenden Seiten der
Bohrungen 86 und 88 sind derart bearbeitet, daß sie mit Übermaß die das Ventilglied
bildende Kugel 52 aufnehmen und gemäß Fig. 5 oben einen ersten Sitz 70 und gemäß
Fig. 5 unten einen zweiten Sitz 90 bilden. Zwischen den Sitzen 70 und 90 führt von der
die Kugel 52 aufnehmenden Ventilkammer 40 (Fig. 2) die Verbindungsöffnung 38 zur
Verbindungsleitung 34, in der die Verbindungsdrossel 36 angeordnet ist. In Fig. 5 fehlt
die in Fig. 2 dargestellte Zulaufdrossel 46 in der Hochdruckleitung 48.The sides of the opening to the separating surfaces between the
Die Durchgangsbohrung 86 endet oben in einer ringförmigen Ausnehmung 90, von der
aus die in den Fig. 4 und 5 nicht dargestellte Rückleitung 14 abgeht. Der in Fig. 4
gezeigte Zapfen 68 weist an seiner Außenseite vorteilhafterweise Längsnuten auf, so daß
er die Durchgangsbohrung 86 nicht verschließt.The through
Die Funktion der beschriebenen Anordnung ist folgende:The function of the arrangement described is as follows:
Im nicht bestromten Zustand des Piezoaktuators 54 liegt die Kugel 52 am in den Fig.
oberen, d.h. ersten Sitz 70 (Fig. 5). Somit ist die Rückleitung 14 geschlossen und die
Hochdruckleitung 48 mit der Verbindungsleitung 34 verbunden, so daß die
Arbeitskammer 32 bei vorhandenem Systemdruck mit Hochdruck beaufschlagt ist. Die
Einspritzdüse ist dann geschlossen, da die auf dem Düsenkörper 26 von der
Arbeitskammer 32 her wirkenden Kraft größer ist als die vom Düsenraum 28 her
wirkende Kraft.In the de-energized state of the
Wird der Piezoaktuator 54 erregt, so wird die Kugel 52 gegen den hohen Systemdruck
vom ersten Sitz 70 abgehoben und gelangt in Anlage an den zweiten Sitz 90 (Fig. 5),
wodurch die Hochdruckleitung 48 von der Ventilkammer 40 getrennt wird und die Verbindungsleitung
34 mit der Rückleitung 14 verbunden wird. Fluid strömt aus der
Arbeitskammer 32 ab. Der Druckabfall bewirkt, daß sich der Düsenkörper 26 unter dem
Einfluß des vom Düsenraum 28 her wirkenden, hohen Drucks aufwärts bewegt und sich
die Düse öffnet.If the
Die Dynamik des Systems ist aufgrund des außerordentlich kleinen Ventilhubs und das
rasche Ansprechverhalten des Piezoaktuators außerordentlich präzise und kann durch
zweckentsprechende Wahl der Drosseln 46 und/oder 36 variiert werden. Der Zeitraum,
währenddessen beide Sitze offen sind und die Hochdruckleitung 48 mit der Rückleitung
14 verbunden ist, ist außerordentlich kurz, so daß Verluste auf ein Minimum
herabgesetzt sind.The dynamics of the system is due to the extremely small valve lift and that
rapid response behavior of the piezo actuator is extremely precise and can
Appropriate choice of
Claims (7)
- Power assisted valve for an injection nozzle, in particular for common-rail systems, containing:a housing (82,84) with a valve chamber (40), a high pressure aperture (44), a link aperture (38) and a return aperture (50),and a movable valve member (52) in the valve chamber, which, by means of an electrically driven triggered control member (68) of an activating apparatus (54,56) through the return aperture (58), can be installed either in first position (70) or in second position (90), whereby the control valve installed in the first position shuts off the return aperture and connects the high pressure aperture with the link aperture, and when installed in the second position shuts off the high pressure aperture and links the link aperture with the return aperture, andwhereby the link aperture is linked with a working chamber (32) of the injection nozzle, whose exit nozzle from a nozzle area (28) under constant high pressure is shut off by the high pressure of the pressurized working chamber, and opens under falling pressure in the working chamber,
- Power assisted valve according to claim 1, characterized in that between the piezo-actuator (54) and the component (62) there is a further component (64) fitted, whose material is so harmonized with that of the housing (58) and the piezo-actuator, that heat expansions have no effect on the installation of the control member (68).
- Power assisted valve according to claims 1 or 2, characterized in that the valve member is in the form of a sphere (52).
- Power assisted valve according to any of claims 1 to 3, characterized in that the valve chamber (40) is formed , between the ends turned towards each other of two aligned bore-holes (86,88) in different housing parts, these holes having front ends turned towards each other and forming the valve positions (70,90), and standing opposite the valve member (52) in the valve chamber with its stroke-corresponding extra dimensions.
- Power assisted valve according to claims 1 to 4, characterized in that the valve member is installed in the first position (70), when the piezo actuator (54) is without voltage.
- Power assisted valve according to any of claims 1 to 5, characterized by a feed throttle (46) being set in the high pressure duct (48) leading to the high pressure aperture (44).
- Power assisted valve according to any of claims 1 to 6, characterized in that a throttle (36) is set in the link duct (34) leading to the working chamber (32) with the link aperture (38).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19540155 | 1995-10-27 | ||
DE19540155A DE19540155C2 (en) | 1995-10-27 | 1995-10-27 | Servo valve for an injection nozzle |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0770776A1 EP0770776A1 (en) | 1997-05-02 |
EP0770776B1 true EP0770776B1 (en) | 2000-08-09 |
Family
ID=7776010
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96116113A Expired - Lifetime EP0770776B1 (en) | 1995-10-27 | 1996-10-08 | Metering valve for a fuel injector |
Country Status (6)
Country | Link |
---|---|
US (1) | US5819710A (en) |
EP (1) | EP0770776B1 (en) |
JP (1) | JPH09184463A (en) |
CN (1) | CN1062493C (en) |
DE (2) | DE19540155C2 (en) |
ES (1) | ES2151627T3 (en) |
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US5792045A (en) * | 1994-10-03 | 1998-08-11 | Adair; Edwin L. | Sterile surgical coupler and drape |
DE19727992C2 (en) * | 1997-07-01 | 1999-05-20 | Siemens Ag | Compensation element for compensation of temperature-related changes in length of electromechanical control systems |
DE19732802A1 (en) * | 1997-07-30 | 1999-02-04 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
DE19757659C1 (en) | 1997-12-23 | 1999-06-17 | Siemens Ag | Fuel injection valve with compensation surface e.g. for motor vehicle IC engine |
DE19823937B4 (en) * | 1998-05-28 | 2004-12-23 | Siemens Ag | Servo valve for fuel injection valve |
DE19826341A1 (en) * | 1998-06-12 | 1999-12-16 | Bosch Gmbh Robert | Valve for controlling liquids |
DE19844996A1 (en) * | 1998-09-30 | 2000-04-13 | Siemens Ag | Fluid dosage dispenser for common-rail fuel injection |
DE19919665A1 (en) * | 1999-04-29 | 2000-11-02 | Volkswagen Ag | Fuel injector |
DE19925308A1 (en) * | 1999-06-02 | 2000-12-14 | Orange Gmbh | Internal combustion engine fuel injector uses control and additional valves in reciprocal alternation to control feed and drain channel states. |
JP4038941B2 (en) * | 1999-08-02 | 2008-01-30 | 株式会社デンソー | Piezo injector |
US6253736B1 (en) | 1999-08-10 | 2001-07-03 | Cummins Engine Company, Inc. | Fuel injector nozzle assembly with feedback control |
DE19946833C2 (en) * | 1999-09-30 | 2002-02-21 | Bosch Gmbh Robert | Valve for controlling liquids |
DE19947772A1 (en) * | 1999-10-05 | 2001-04-19 | Hermann Golle | Injector, especially for common rail injection systems |
DE19949528A1 (en) * | 1999-10-14 | 2001-04-19 | Bosch Gmbh Robert | Double-switching control valve for an injector of a fuel injection system for internal combustion engines with hydraulic amplification of the actuator |
US6298829B1 (en) | 1999-10-15 | 2001-10-09 | Westport Research Inc. | Directly actuated injection valve |
US6564777B2 (en) | 1999-10-15 | 2003-05-20 | Westport Research Inc. | Directly actuated injection valve with a composite needle |
US6584958B2 (en) | 1999-10-15 | 2003-07-01 | Westport Research Inc. | Directly actuated injection valve with a ferromagnetic needle |
US6575138B2 (en) | 1999-10-15 | 2003-06-10 | Westport Research Inc. | Directly actuated injection valve |
DE19950224A1 (en) * | 1999-10-19 | 2001-04-26 | Bosch Gmbh Robert | Double-switching regulator valve for fuel injector in IC engines has ball-shaped regulator member centered by sealing seats of valve housing |
DE19952774B4 (en) * | 1999-11-03 | 2004-03-11 | Daimlerchrysler Ag | Device for draining fluid from a system |
JP4048699B2 (en) * | 1999-11-10 | 2008-02-20 | 株式会社デンソー | Fuel injection valve |
US6313568B1 (en) | 1999-12-01 | 2001-11-06 | Cummins Inc. | Piezoelectric actuator and valve assembly with thermal expansion compensation |
DE10003863B4 (en) * | 2000-01-28 | 2004-11-18 | Robert Bosch Gmbh | injection |
US6257203B1 (en) * | 2000-02-10 | 2001-07-10 | International Truck And Engine Corporation | Injector with variable needle valve opening pressure |
DE10195948T1 (en) | 2000-03-22 | 2003-07-10 | Siemens Vdo Automotive Corp N | Method for controlling a self-scanning magnetostrictive actuator |
DE10024703A1 (en) * | 2000-05-18 | 2001-11-22 | Bosch Gmbh Robert | Injection arrangement for fuel storage injection system has valve unit blocking auxiliary channel and outlet path in alternation |
US6363913B1 (en) * | 2000-06-09 | 2002-04-02 | Caterpillar Inc. | Solid state lift for micrometering in a fuel injector |
JP4356268B2 (en) | 2000-06-26 | 2009-11-04 | 株式会社デンソー | Fuel injection device |
US6400066B1 (en) | 2000-06-30 | 2002-06-04 | Siemens Automotive Corporation | Electronic compensator for a piezoelectric actuator |
US6345771B1 (en) | 2000-06-30 | 2002-02-12 | Siemens Automotive Corporation | Multiple stack piezoelectric actuator for a fuel injector |
DE10044389A1 (en) * | 2000-09-08 | 2002-04-04 | Bosch Gmbh Robert | Valve for controlling liquids |
DE10123775B4 (en) * | 2001-05-16 | 2005-01-20 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines, in particular common rail injector, and fuel system and internal combustion engine |
US6499471B2 (en) | 2001-06-01 | 2002-12-31 | Siemens Automotive Corporation | Hydraulic compensator for a piezoelectrical fuel injector |
DE10131631A1 (en) * | 2001-06-29 | 2003-01-16 | Bosch Gmbh Robert | Fuel injector with control chamber optimized for high pressure resistance |
DE10142798C2 (en) * | 2001-08-31 | 2003-07-31 | Bosch Gmbh Robert | Storage for a piezo actuator module in a common rail injector |
US6766965B2 (en) | 2001-08-31 | 2004-07-27 | Siemens Automotive Corporation | Twin tube hydraulic compensator for a fuel injector |
DE10155718C2 (en) * | 2001-11-13 | 2003-09-18 | Hermann Golle | Injection system for diesel engines |
US6837221B2 (en) | 2001-12-11 | 2005-01-04 | Cummins Inc. | Fuel injector with feedback control |
DE10257895A1 (en) * | 2002-12-11 | 2004-06-24 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engine, has piezoelectric or magnetostrictive actuator opening valve body in nozzle tip and has fuel feed tube running parallel to actuator body |
DE10315016A1 (en) * | 2003-04-02 | 2004-10-28 | Robert Bosch Gmbh | Fuel injector with a leak-free servo valve |
EP1685605B1 (en) * | 2003-11-20 | 2011-12-21 | Viking Technologies L.C. | Integral thermal compensation for an electro-mechanical actuator |
US7255290B2 (en) * | 2004-06-14 | 2007-08-14 | Charles B. Bright | Very high speed rate shaping fuel injector |
DE102005042342B4 (en) * | 2005-09-06 | 2009-04-02 | Continental Automotive Gmbh | Injection valve with separate fuel line |
EP1760306A1 (en) * | 2005-09-06 | 2007-03-07 | Siemens Aktiengesellschaft | Housing |
DE102009055362A1 (en) * | 2009-12-29 | 2011-06-30 | Robert Bosch GmbH, 70469 | Injection valve for a fluid |
GB2573522B (en) * | 2018-05-08 | 2020-08-19 | Delphi Tech Ip Ltd | Method of identifying faults in the operation of hydraulic fuel injectors having accelerometers |
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GB1470166A (en) * | 1973-05-12 | 1977-04-14 | Cav Ltd | Fuel injection pumping apparatus |
DE3037078C2 (en) * | 1980-10-01 | 1982-08-12 | Daimler-Benz Ag, 7000 Stuttgart | Electrically controlled actuator |
US4649886A (en) * | 1982-11-10 | 1987-03-17 | Nippon Soken, Inc. | Fuel injection system for an internal combustion engine |
US4550744A (en) * | 1982-11-16 | 1985-11-05 | Nippon Soken, Inc. | Piezoelectric hydraulic control valve |
JPS601877A (en) * | 1983-06-20 | 1985-01-08 | Nippon Soken Inc | Laminated piezoelectric unit |
FR2580728B1 (en) * | 1985-04-19 | 1989-05-05 | Alsacienne Constr Meca | FUEL INJECTION SYSTEM FOR DIESEL ENGINE |
IT1217260B (en) * | 1987-08-25 | 1990-03-22 | Weber Srl | ELECTROMAGNETICALLY OPERATED FUEL INJECTION VALVE FOR DIESEL CYCLE ENGINES |
JPH01187363A (en) * | 1988-01-21 | 1989-07-26 | Toyota Motor Corp | Fuel injection valve for internal combustion engine |
JPH0286953A (en) * | 1988-09-21 | 1990-03-27 | Kanesaka Gijutsu Kenkyusho:Kk | Fuel injection valve |
JP2712760B2 (en) * | 1990-05-29 | 1998-02-16 | トヨタ自動車株式会社 | Fuel injection valve |
DE4302668A1 (en) * | 1993-01-30 | 1994-08-04 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
DE4340305C2 (en) * | 1993-11-26 | 1998-02-19 | Daimler Benz Ag | Fuel injection nozzle for an internal combustion engine |
DE4406901C2 (en) * | 1994-03-03 | 1998-03-19 | Daimler Benz Ag | Solenoid valve controlled injector for an internal combustion engine |
US5605134A (en) * | 1995-04-13 | 1997-02-25 | Martin; Tiby M. | High pressure electronic common rail fuel injector and method of controlling a fuel injection event |
-
1995
- 1995-10-27 DE DE19540155A patent/DE19540155C2/en not_active Expired - Fee Related
-
1996
- 1996-10-08 DE DE59605709T patent/DE59605709D1/en not_active Expired - Fee Related
- 1996-10-08 EP EP96116113A patent/EP0770776B1/en not_active Expired - Lifetime
- 1996-10-08 ES ES96116113T patent/ES2151627T3/en not_active Expired - Lifetime
- 1996-10-24 JP JP8281197A patent/JPH09184463A/en not_active Withdrawn
- 1996-10-25 US US08/735,971 patent/US5819710A/en not_active Expired - Fee Related
- 1996-10-28 CN CN96120369A patent/CN1062493C/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH09184463A (en) | 1997-07-15 |
DE19540155A1 (en) | 1997-04-30 |
DE19540155C2 (en) | 2000-07-13 |
US5819710A (en) | 1998-10-13 |
ES2151627T3 (en) | 2001-01-01 |
CN1062493C (en) | 2001-02-28 |
EP0770776A1 (en) | 1997-05-02 |
CN1156216A (en) | 1997-08-06 |
DE59605709D1 (en) | 2000-09-14 |
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