EP0908617A1 - Fuel injection apparatus - Google Patents

Fuel injection apparatus Download PDF

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Publication number
EP0908617A1
EP0908617A1 EP98111577A EP98111577A EP0908617A1 EP 0908617 A1 EP0908617 A1 EP 0908617A1 EP 98111577 A EP98111577 A EP 98111577A EP 98111577 A EP98111577 A EP 98111577A EP 0908617 A1 EP0908617 A1 EP 0908617A1
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EP
European Patent Office
Prior art keywords
valve
fuel
closing body
fuel injection
valve seat
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
EP98111577A
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German (de)
French (fr)
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EP0908617B1 (en
Inventor
Rudolf Heinz
Roger Potschin
Klaus-Peter Schmoll
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0908617A1 publication Critical patent/EP0908617A1/en
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    • 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

Definitions

  • the invention is based on a fuel injection device according to the preamble of claim 1.
  • a 3-way valve is used, with whose help the control room either only with the high-pressure fuel source or only with a fuel return tank connected is.
  • the actuation of the valve member this 3-way valve is made using a Electromagnets.
  • This known configuration according to the control of the 3-way valve either that Injector link in fully open or fully open brought closed position.
  • the 3-way valve is included designed so that the valve member in a respective Closing position completely from resulting from pressures Forces should be free.
  • the ring surfaces and the Circular areas are kept the same size.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the compared to the advantage that the valve member in the respective End position of its closing body on one of the valve seats Ring and / or high pressure from the high pressure fuel source Has circular surfaces of different sizes, such that the closing body by this from the pressure load Resulting forces in a stable end position its respective valve seat is held.
  • difference area resulting from the difference of the areas dimensioned that the resulting forces in the respective End position of the closing body is not greater than about 40% of the forces that can be applied by the actuator.
  • difference area resulting from the difference of the areas dimensioned that the resulting forces in the respective End position of the closing body is not greater than about 40% of the forces that can be applied by the actuator.
  • the second Ring area smaller than the first ring area and the first Circular area smaller than the second circular area.
  • FIG. 1 shows a fuel injection valve the fuel injector in section and Figure 2 the valve member controlling the fuel injector 3-way valve.
  • the invention relates to a fuel injection device, the one high-pressure fuel pump not shown in the figure has, which from a fuel reservoir if necessary with the interposition of a pre-feed pump Receives fuel and via a pressure line, at high Bring pressure, a high-pressure fuel supply 8 supplies. These parts are considered to be high pressure fuel sources describe.
  • the high-pressure fuel reservoir 8 supplies via Fuel lines 15 each have a fuel injection valve 14 with the lowest fuel injection pressure Fuel.
  • These fuel injectors are made by a control unit, not shown, electrically controlled so that, according to operating parameters of the internal combustion engine the opening of the fuel injection valves 14 with Start of fuel injection and fuel injection duration be determined.
  • the fuel injection valve 14 has a housing 19, in which in a longitudinal bore 20 a needle-like injection valve member 21 is performed. At one end is this injection valve member with a conical sealing surface 23 provided on the in the combustion chamber of the internal combustion engine protruding tip 24 of the valve housing with a valve seat cooperates from which injection openings 25 dissipate the inside of the fuel injector, here the injection valve member 21st surrounding, with fuel under injection pressure filled annulus 27, with the combustion chamber of the associated Internal combustion engine connects so as to make an injection complete when the injector member is off its valve seat has lifted off.
  • the annular space 27 is with a pressure space 29 connected, in constant communication with a Pressure line 30 is connected to the fuel line 15 of the respective fuel injector is connected.
  • the one High-pressure fuel accumulator 8 supplied fuel pressure also acts in the pressure chamber 29 and there on a pressure shoulder 31 of the fuel injection valve member 21, via the the fuel injection valve member in a known manner suitable conditions lifted from its valve seat can be.
  • At the other end of the fuel injector member is this in a cylinder bore 33 and closes a control chamber 36 with its end face 34 on.
  • the closed position of the fuel injector member is thereby by the pressure in the control room 36 and by a compression spring 12, which is between a spring plate 10 of the fuel injector member and the housing 19 supports, controls. While the one acting in the closing direction Compression spring 12 unchangeable in its characteristics is, with the help of the pressure in the control room 36 Opening and closing movement of the fuel injection valve member triggered.
  • control room 36 is over a channel 37 with a 3-way valve Valve 40 connected.
  • the canal opens here from the control room 37 into a valve chamber 41, in which a closing body 42 of the valve member 43 of the valve 40 is adjustably arranged is.
  • the valve member 43 has one with the closing body 42 firmly connected plunger 45.
  • the second end face goes into a connecting part 48 to the plunger 45, which is a smaller one Diameter than the rest, in a guide bore 50 guided plunger 45.
  • annular space 51 is formed, into which an inflow channel 53 opens.
  • the annular space 51 forms a flow channel between the inlet channel 53 and the valve chamber 41.
  • a reduced diameter part 52 on which at the mouth of this part of the guide bore 50 in the Valve chamber 41 is a valve seat 54 which is designed as second valve seat together with the second sealing surface 47 works.
  • a first valve seat 55 Coaxial with this and coaxial with the valve member 43 or the closing body 42 is at the opposite end of the Valve chamber 41 formed a first valve seat 55 with which the first sealing surface 46 acts together. From valve seat 55 leads from a drain channel 57 from the valve chamber 41.
  • the first and second sealing surfaces 46 and 47 as well as the first 55 and second valve seat 54 are present Trap conical with a cone tip angle, which is smaller in the first valve seat 55 than the corresponding one Cone tip angle of the first sealing surface 46 and with a cone tip angle of the second valve seat 54 is greater than the cone tip angle of the second sealing surface 47.
  • the actuation of the valve member 43 takes place via the plunger 45 from a not shown Drive 59, which as a piezo arrangement, e.g.
  • Piezostack or as a magnetostrictive element is.
  • These drives have the advantage that they are analogous to Carry out actuation travel with and high actuation force, even if the absolutely producible way is relatively small, so that large travel ranges also large Piezo element packs must be used.
  • the other The advantage of such drives is that they are very fast act so that quick switching operations can be carried out, which is particularly advantageous when it comes to injection technology are.
  • This annular surface is RF2 smaller than the ring area RF1, so that in the closing direction on the valve body 42 to the side of its drive 59 forces resulting from the area difference predominate. These forces keep the closing body 42 in one stable end position on the second valve seat 54. The forces are dimension so that the drive 59 the closing body 42nd Lift off this second valve seat 54 to open it can. If the closing body comes in its other position System on the first valve seat 55, so again arise stable conditions. It can be assumed that the closing body 42 in the opening direction at most a first Circular area KF1 can act from the diameter of the Guide bore 50 results. This circular area is on the side of the plunger 45 facing away from the valve chamber 41 relieved of pressure.
  • a maximum of a second circular area KF2 to be effective from the plant of the first sealing surface 46 on the first valve seat 55 is determined.
  • the first circular area KF1 is smaller than the second circular area KF2, so that a difference surface from the difference of these surfaces results from the high fuel pressure of the high-pressure fuel reservoir 8 is loaded and generates a force that again in the closing direction of the closing body 42 to the first Valve seat 55 acts. This also in the closing direction Acting forces are such that they are 59 of the closing body 42 can be overcome.
  • the respective forces in the stable end positions of the closing body are so large that they are about 40% of those that can be applied by the drive Actuating forces. That is with one required effort for the actuator and one appropriate energy requirements an economical mode of operation of the three-way valve possible. For the rest can this way a drive only for adjusting the Closing body may be required.
  • the closing body in its respective end positions become stable in the closed position held. This does not apply to the duration of being closed any power to actuator 59. This is for safe and cost-saving operation of the valve an essential advantage.

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

Abstract

A fuel injection system for an internal combustion engine has a three-way valve (40) between the high pressure fuel feed (8) and the injection valve. The control valve opens and closes the injection valve by switching between two stable settings. The control valve has a valve element (42) with conical valve seals (46,47) at each end, and with the upper end of the valve element connected by a shaft to a piston (45) and to a servo drive (59) e.g. a solenoid. The relative sizes of the piston, the connecting shaft and the fuel feeds are such that when the valve is lifted, to close the high pressure fuel feed, and to vent the control side of the injection valve to the fuel sump (6), the pressure of the high pressure fuel feed (53) holds the valve in this position until the servo drive pushes the valve back into the open position, where it is also held by the pressure of the fuel.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzeinrichtung nach der Gattung des Patentanspruchs 1 aus. Bei einer solchen, durch die WO 95/25888 bekannten Kraftstoffeinspritzeinrichtung wird ein 3-Wegeventil verwendet, mit dessen Hilfe der Steuerraum entweder nur mit der Kraftstoffhochdruckquelle oder nur mit einem Kraftstoffrücklaufbehälter verbunden ist. Die Betätigung des Ventilgliedes dieses 3-Wegeventils erfolgt mit Hilfe eines Elektromagneten. Mit dieser bekannten Ausgestaltung wird entsprechend der Ansteuerung des 3-Wegeventils entweder das Einspritzventilglied in völlig geöffnete oder in völlig geschlossene Stellung gebracht. Das 3-Wegeventil ist dabei so ausgestaltet, daß das Ventilglied in einer jeweiligen Schließstellung vollkommen von aus Drücken resultierenden Kräften frei sein soll. Dazu sind die Ringflächen und die Kreisflächen jeweils gleich groß gehalten.The invention is based on a fuel injection device according to the preamble of claim 1. At a such fuel injection device known from WO 95/25888 a 3-way valve is used, with whose help the control room either only with the high-pressure fuel source or only with a fuel return tank connected is. The actuation of the valve member this 3-way valve is made using a Electromagnets. With this known configuration according to the control of the 3-way valve either that Injector link in fully open or fully open brought closed position. The 3-way valve is included designed so that the valve member in a respective Closing position completely from resulting from pressures Forces should be free. The ring surfaces and the Circular areas are kept the same size.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat dem gegenüber den Vorteil, daß das Ventilglied in der jeweiligen Endstellung seines Schließkörpers an einem der Ventilsitze vom Hochdruck der Krafstoffhochdruckquelle belastete Ring- bzw. Kreis-Flächen unterschiedlicher Größe aufweist, derart, daß der Schließköper durch aus der Druckbelastung dieser Flächen resultierenden Kräften in einer stabilen Endlage an seinem jeweiligen Ventilsitz gehalten wird.The fuel injection device according to the invention with the characterizing features of claim 1 has the compared to the advantage that the valve member in the respective End position of its closing body on one of the valve seats Ring and / or high pressure from the high pressure fuel source Has circular surfaces of different sizes, such that the closing body by this from the pressure load Resulting forces in a stable end position its respective valve seat is held.

In vorteilhafter Weise ist dabei gemäß Anspruch 2 die sich aus der Differenz der Flächen ergebende Differenzfläche so bemessen, daß die resultierenden Kräfte in der jeweiligen Endstellung des Schließkörpers nicht größer als etwa 40% der vom Stellantrieb aufbringbaren Kräfte sind. In weiterhin vorteilhafter Ausgestaltung nach Anspruch 3 ist die zweite Ringfläche kleiner als die erste Ringfläche und die erste Kreisfläche kleiner als die zweite Kreisfläche.Advantageously, according to claim 2 difference area resulting from the difference of the areas dimensioned that the resulting forces in the respective End position of the closing body is not greater than about 40% of the forces that can be applied by the actuator. In continue advantageous embodiment according to claim 3 is the second Ring area smaller than the first ring area and the first Circular area smaller than the second circular area.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein Kraftstoffeinspritzventil der Kraftstoffeinspritzeinrichtung im Schnitt und Figur 2 das das Kraftstoffeinspritzventil steuernde Ventilglied des 3-Wegeventils.An embodiment of the invention is in the drawing shown and is described in more detail in the following description explained. FIG. 1 shows a fuel injection valve the fuel injector in section and Figure 2 the valve member controlling the fuel injector 3-way valve.

Beschreibungdescription

Die Erfindung betrifft eine Kraftstoffeinspritzeinrichtung, die eine in der Figur nicht weiter gezeigte Kraftstoffhochdruckpumpe aufweist, welche aus einem Kraftstoffvorratsbehälter ggf. unter Zwischenschaltung einer Vorförderpumpe Kraftstoff erhält und über eine Druckleitung, auf hohen Druck gebracht, einem Kraftstoffhochdruckspeicher 8 zuführt. Diese Teile sind als Kraftstoffhochdruckquelle zu bezeichnen. Der Kraftstoffhochdruckspeicher 8 versorgt über Kraftstoffleitungen 15 jeweils ein Kraftstoffeinspritzventil 14 mit auf wenigsten Kraftstoffeinspritzdruck gebrachtem Kraftstoff. Diese Kraftstoffeinspritzventile werden von einem nicht dargestelltem Steuergerät elektrisch gesteuert so daß, entsprechend Betriebsparametern der Brennkraftmaschine die Öffnung der Kraftstoffeinspritzventile 14 mit Kraftstoffeinspritzbeginn und Kraftstoffeinspritzdauer bestimmt werden.The invention relates to a fuel injection device, the one high-pressure fuel pump not shown in the figure has, which from a fuel reservoir if necessary with the interposition of a pre-feed pump Receives fuel and via a pressure line, at high Bring pressure, a high-pressure fuel supply 8 supplies. These parts are considered to be high pressure fuel sources describe. The high-pressure fuel reservoir 8 supplies via Fuel lines 15 each have a fuel injection valve 14 with the lowest fuel injection pressure Fuel. These fuel injectors are made by a control unit, not shown, electrically controlled so that, according to operating parameters of the internal combustion engine the opening of the fuel injection valves 14 with Start of fuel injection and fuel injection duration be determined.

Das Kraftstoffeinspritzventil 14 weist ein Gehäuse 19 auf, in dem in einer Längsbohrung 20 ein nadelartiges Einspritzventilglied 21 geführt ist. An seinem einen Ende ist dieses Einspritzventilglied mit einer kegelförmigen Dichtfläche 23 versehen, die an der in den Brennraum der Brennkraftmaschine ragenden Spitze 24 des Ventilgehäuses mit einem Ventilsitz zusammen wirkt, von dem aus Einspritzöffnungen 25 abführen, die das Innere des Kraftstoffeinspritzventils, hier den das Einspritzventilglied 21 umgebenden, mit unter Einspritzdruck stehenden Kraftstoff gefüllten Ringraum 27, mit dem Brennraum der zugehörigen Brennkraftmaschine verbindet, um so eine Einspritzung zu vollziehen, wenn das Einspritzventilglied von seinem Ventilsitz abgehoben hat. Der Ringraum 27 ist mit einem Druckraum 29 verbunden, der in ständiger Verbindung mit einer Druckleitung 30 steht, die mit der Kraftstoffleitung 15 des jeweiligen Kraftstoffeinspritzventils verbunden ist. Der dem Kraftstoffhochdruckspeicher 8 zugeführte Kraftstoffdruck wirkt auch in dem Druckraum 29 und dort auf eine Druckschulter 31 des Krafstoffeinspritzventilglieds 21, über die in bekannter Weise das Kraftstoffeinspritzventilglied bei geeigneten Bedingungen von seinem Ventilsitz abgehoben werden kann. Am anderen Ende des Kraftstoffeinspritzventilglieds ist diese in einer Zylinderbohrung 33 geführt und schließt dort mit seiner Stirnseite 34 einen Steuerraum 36 ein. Die Schließstellung des Kraftstoffeinspritzventilgliedes wird dabei durch den Druck im Steuerraum 36 und auch durch eine Druckfeder 12, die sich zwischen einem Federteller 10 des Kraftstoffeinspritzventilgliedes und dem Gehäuse 19 abstützt, gesteuert. Während die in Schließrichtung wirkende Druckfeder 12 in ihrer Charakteristik unveränderlich ist, wird mit Hilfe des Druckes im Steuerraum 36 die Öffnungs- bzw. Schließbewegung des Kraftstoffeinspritzventilglieds ausgelöst. Dazu ist der Steuerraum 36 über einen Kanal 37 mit einem als 3-Wegeventil ausgebildeten Ventil 40 verbunden. Dieses ist in Figur 3 in den Details näher dargestellt. Vom Steuerraum her mündet hier der Kanal 37 in einen Ventilraum 41 ein, in dem ein Schließkörper 42 des Ventilglieds 43 des Ventils 40 verstellbar angeordnet ist. Dazu hat das Ventilglied 43 einen mit dem Schließkörper 42 fest verbundenen Stößel 45. Am Schließkörper ist eine erste Dichtfläche 46 an seiner einen Stirnseite und eine zweite Dichtfläche 47 an seiner anderen Stirnseite angeordnet. Die zweite Stirnfläche geht dabei in ein Verbindungsteil 48 zum Stößel 45 über, der einen kleineren Durchmesser hat als der übrige, in einer Führungsbohrung 50 geführte Stößel 45. Zwischen Führungsbohrung und dem Verbindungsteil 48 des Stößels 45 wird ein Ringraum 51 gebildet, in den ein Zuflußkanal 53 mündet. Der Ringraum 51 bildet einen Durchflußkanal zwischen Zuflußkanal 53 und dem Ventilraum 41. Zur Seite des Ventilraumes 41 hat die Führungsbohrung 50 einen im Durchmesser reduzierten Teil 52, an dem an der Mündung dieses Teils der Führungsbohrung 50 in den Ventilraum 41 ein Ventilsitz 54 ausgebildet ist, der als zweiter Ventilsitz mit der zweiten Dichtfläche 47 zusammen wirkt. Koaxial zu diesem und koaxial zu dem Ventilglied 43 bzw. dem Schließkörper 42 ist am gegenüberliegenden Ende des Ventilraums 41 ein erster Ventilsitz 55 ausgebildet, mit dem die erste Dichtfläche 46 zusammen wirkt. Vom Ventilsitz 55 aus führt ein Abflußkanal 57 vom Ventilraum 41 ab. Dieser ist in der Figur 1 ebenfalls dargestellt und führt zu dem Kraftstoffvorratsbehälter 6 zurück oder zu einem anders gestalteten Entlastungsraum. In dem Abflußkanal ist eine Drossel 58 vorgesehen, die den Abflußquerschnitt bei vom ersten Ventilsitz 55 abgehobenen Ventilkörper bestimmt. Der Zuflußkanal 53, der ebenfalls in Figur 1 erkennbar ist, ist mit der Kraftstoffleitung 15 verbunden und kann somit Kraftstoff aus dem Kraftstoffhochdruckspeicher über den Ventilraum 41 bei vom zweiten Ventilsitz 54 abgehobenen Ventilglied 43 dem Steuerraum 36 zuführen.The fuel injection valve 14 has a housing 19, in which in a longitudinal bore 20 a needle-like injection valve member 21 is performed. At one end is this injection valve member with a conical sealing surface 23 provided on the in the combustion chamber of the internal combustion engine protruding tip 24 of the valve housing with a valve seat cooperates from which injection openings 25 dissipate the inside of the fuel injector, here the injection valve member 21st surrounding, with fuel under injection pressure filled annulus 27, with the combustion chamber of the associated Internal combustion engine connects so as to make an injection complete when the injector member is off its valve seat has lifted off. The annular space 27 is with a pressure space 29 connected, in constant communication with a Pressure line 30 is connected to the fuel line 15 of the respective fuel injector is connected. The one High-pressure fuel accumulator 8 supplied fuel pressure also acts in the pressure chamber 29 and there on a pressure shoulder 31 of the fuel injection valve member 21, via the the fuel injection valve member in a known manner suitable conditions lifted from its valve seat can be. At the other end of the fuel injector member is this in a cylinder bore 33 and closes a control chamber 36 with its end face 34 on. The closed position of the fuel injector member is thereby by the pressure in the control room 36 and by a compression spring 12, which is between a spring plate 10 of the fuel injector member and the housing 19 supports, controls. While the one acting in the closing direction Compression spring 12 unchangeable in its characteristics is, with the help of the pressure in the control room 36 Opening and closing movement of the fuel injection valve member triggered. For this purpose, the control room 36 is over a channel 37 with a 3-way valve Valve 40 connected. This is shown in detail in FIG. 3 shown in more detail. The canal opens here from the control room 37 into a valve chamber 41, in which a closing body 42 of the valve member 43 of the valve 40 is adjustably arranged is. For this purpose, the valve member 43 has one with the closing body 42 firmly connected plunger 45. There is one on the closing body first sealing surface 46 on one end face and one second sealing surface 47 arranged on its other end face. The second end face goes into a connecting part 48 to the plunger 45, which is a smaller one Diameter than the rest, in a guide bore 50 guided plunger 45. Between the guide bore and the connecting part 48 of the plunger 45, an annular space 51 is formed, into which an inflow channel 53 opens. The annular space 51 forms a flow channel between the inlet channel 53 and the valve chamber 41. To the side of the valve chamber 41 has the guide hole 50 a reduced diameter part 52 on which at the mouth of this part of the guide bore 50 in the Valve chamber 41 is a valve seat 54 which is designed as second valve seat together with the second sealing surface 47 works. Coaxial with this and coaxial with the valve member 43 or the closing body 42 is at the opposite end of the Valve chamber 41 formed a first valve seat 55 with which the first sealing surface 46 acts together. From valve seat 55 leads from a drain channel 57 from the valve chamber 41. This is also shown in Figure 1 and leads to the Fuel tank 6 back or to another designed relief room. In the drainage channel is one Throttle 58 provided that the discharge cross-section at determined first valve seat 55 lifted valve body. Of the Inflow channel 53, which can also be seen in Figure 1 connected to the fuel line 15 and can therefore fuel from the high-pressure fuel reservoir via the valve compartment 41 when the valve member is lifted off the second valve seat 54 43 to the control room 36.

Die erste und die zweite Dichtfläche 46 bzw. 47 sowie der erste 55 und der zweite Ventilsitz 54 sind im vorliegenden Falle kegelförmig ausgebildet mit einem Kegelspitzenwinkel, der beim ersten Ventilsitz 55 kleiner ist als der entsprechende Kegelspitzenwinkel der ersten Dichtfläche 46 und mit einem Kegelspitzenwinkel der beim zweiten Ventilsitz 54 größer ist als der Kegelspitzenwinkel der zweiten Dichtfläche 47. Damit ergeben sich bei der Auflage der zweiten Dichtfläche 47 auf dem zweiten Ventilsitz 54 eine Berührungslinie, die durch den Innendurchmesser des zweiten Ventilsitzes 54 bestimmt ist und umgekehrt bei Auflage der ersten Dichtfläche 46 auf dem ersten Ventilsitz 55 eine Berührungslinie, die durch den Außenumfang der ersten Dichtfläche 46 bestimmt ist. Die Betätigung des Ventilglieds 43 erfolgt über den Stößel 45 von einem nicht weiter dargestelltem Antrieb 59, der als Piezoanordnung, z.B. als sogn. Piezostack oder als magnetostriktives Element ausgeführt ist. Diese Antriebe haben den Vorteil, daß sie analog zur Spannungsbeaufschlagung Stellwege durchführen und zwar mit hoher Betätigungskraft, wenn auch der absolut erzeugbare Weg relativ klein ist, so daß bei großen Stellwegen auch große Piezoelementpackungen verwendet werden müssen. Der weitere Vorteil solcher Antriebe besteht darin, daß sie sehr schnell wirken, so daß schnelle Schaltvorgänge durchführbar sind, die insbesondere bei der Einspritztechnik von hohem Vorteil sind. The first and second sealing surfaces 46 and 47 as well as the first 55 and second valve seat 54 are present Trap conical with a cone tip angle, which is smaller in the first valve seat 55 than the corresponding one Cone tip angle of the first sealing surface 46 and with a cone tip angle of the second valve seat 54 is greater than the cone tip angle of the second sealing surface 47. This results in the second edition Sealing surface 47 on the second valve seat 54 a Line of contact through the inner diameter of the second Valve seat 54 is determined and vice versa when the first sealing surface 46 on the first valve seat 55 a Line of contact through the outer circumference of the first sealing surface 46 is determined. The actuation of the valve member 43 takes place via the plunger 45 from a not shown Drive 59, which as a piezo arrangement, e.g. as sogn. Piezostack or as a magnetostrictive element is. These drives have the advantage that they are analogous to Carry out actuation travel with and high actuation force, even if the absolutely producible way is relatively small, so that large travel ranges also large Piezo element packs must be used. The other The advantage of such drives is that they are very fast act so that quick switching operations can be carried out, which is particularly advantageous when it comes to injection technology are.

Für die Betätigung des Schließkörpers 42 sind die auf ihn aus der Druckbeaufschlagung von der Kraftstoffhochdruckquelle 8 her resultierenden Kräfte von Bedeutung. Dies gilt insbesondere bei den jeweiligen Schließstellungen des Schließkörpers 42. Befindet sich der Schließkörper 42 mit seiner zweiten Dichtfläche 47 in Anlage am zweiten Ventilsitz 54, so ist eine zwischen dem Durchmesser des Stössels 45 und des Verbindungsteils 48 verbleibende Ringfläche RF1 vom hohen Druck der Kraftstoffhochdruckquelle 8 beaufschlagt. An der dieser Fläche gegenüberliegenden Seite wird eine Ringfläche RF2 gebildet zwischen dem Verbindungsteil 48 und der auf der zweiten Dichtfläche 47 aufliegenden Kante des zweiten Ventilsitzes 54. Diese Ringfläche RF2 ist kleiner als die Ringfläche RF1, so daß die in Schließrichtung auf den Ventilkörper 42 zur Seite seines Antriebs 59 hin aus der Flächendifferenz resultierenden Kräfte überwiegen. Diese Kräfte halten den Schließkörper 42 in einer stabilen Endlage am zweiten Ventilsitz 54. Die Kräfte sind dabei so bemessen, daß der Antrieb 59 den Schließkörper 42 zum Öffnen wieder von diesem zweiten Ventilsitz 54 abheben kann. Kommt der Schließkörper in seiner anderen Stellung zur Anlage an dem ersten Ventilsitz 55, so ergeben sich wiederum stabile Verhältnisse. Dabei ist davon auszugehen, daß auf den Schließkörper 42 in Öffnungsrichtung maximal eine erste Kreisfläche KF1 wirken kann, die aus dem Durchmesser der Führungsbohrung 50 resultiert. Diese Kreisfläche ist auf der dem Ventilraum 41 abgewandten Seite des Stössels 45 druckentlastet.For the actuation of the closing body 42 are on it from the pressurization from the high-pressure fuel source 8 forth resulting forces of importance. this applies especially in the respective closed positions of the Closing body 42. Is the closing body 42 with its second sealing surface 47 in contact with the second valve seat 54, so is one between the diameter of the ram 45 and the connecting part 48 remaining ring surface RF1 acted upon by the high pressure of the high-pressure fuel source 8. On the side opposite this surface an annular surface RF2 is formed between the connecting part 48 and the edge resting on the second sealing surface 47 of the second valve seat 54. This annular surface is RF2 smaller than the ring area RF1, so that in the closing direction on the valve body 42 to the side of its drive 59 forces resulting from the area difference predominate. These forces keep the closing body 42 in one stable end position on the second valve seat 54. The forces are dimension so that the drive 59 the closing body 42nd Lift off this second valve seat 54 to open it can. If the closing body comes in its other position System on the first valve seat 55, so again arise stable conditions. It can be assumed that the closing body 42 in the opening direction at most a first Circular area KF1 can act from the diameter of the Guide bore 50 results. This circular area is on the side of the plunger 45 facing away from the valve chamber 41 relieved of pressure.

Auf der anderen Seite kann maximal eine zweite Kreisfläche KF2 wirksam sein, die aus der Anlage der ersten Dichtfläche 46 am ersten Ventilsitz 55 bestimmt ist. Wie oben dargestellt, liegt die erste Dichtfläche 46 mit ihrem Außenumfang am ersten Ventilsitz 55 an und ist zur Seite des Abflußkanals 57 wiederum druckentlastet. Die erste Kreisfläche KF1 ist dabei kleiner als die zweite Kreisfläche KF2, so daß sich aus der Differenz dieser Flächen eine Differenzfläche ergibt, die vom hohen Kraftstoffdruck des Kraftstoffhochdruckspeichers 8 belastet ist und eine Kraft erzeugt, die wiederum in Schließrichtung des Schließkörpers 42 zum ersten Ventilsitz 55 hin wirkt. Auch diese in Schließrichtung wirkenden Kräfte sind so bemessen, daß sie vom Antrieb 59 des Schließkörpers 42 überwunden werden können. Die jeweiligen Kräfte in den stabilen Endlagen des Schließkörpers sind so groß, daß sie etwa 40 % der vom Antrieb aufbringbaren Stellkräfte betragen. Damit ist bei einem erforderlichen Aufwand für den Stellantrieb und einem entsprechenden Energiebedarf eine wirtschaftliche Betriebsweise des Drei-Wege-Ventils möglich. Im übrigen kann auf diese Weise ein Antrieb jeweils nur zur Verstellung des Schließkörpers erforderlich sein. Der Schließkörper in seinen jeweiligen Endlagen wird stabil in Schließstellung gehalten. Damit entfällt über die Dauer des Geschlossenseines jegliche Energiezufuhr zum Stellantrieb 59. Dies ist für einen sicheren und kostensparenden Betrieb des Ventils von wesentlichem Vorteil.On the other hand, a maximum of a second circular area KF2 to be effective from the plant of the first sealing surface 46 on the first valve seat 55 is determined. As shown above lies the first sealing surface 46 with its outer circumference at the first valve seat 55 and is to the side of the drain channel 57 again relieved of pressure. The first circular area KF1 is smaller than the second circular area KF2, so that a difference surface from the difference of these surfaces results from the high fuel pressure of the high-pressure fuel reservoir 8 is loaded and generates a force that again in the closing direction of the closing body 42 to the first Valve seat 55 acts. This also in the closing direction Acting forces are such that they are 59 of the closing body 42 can be overcome. The respective forces in the stable end positions of the closing body are so large that they are about 40% of those that can be applied by the drive Actuating forces. That is with one required effort for the actuator and one appropriate energy requirements an economical mode of operation of the three-way valve possible. For the rest can this way a drive only for adjusting the Closing body may be required. The closing body in its respective end positions become stable in the closed position held. This does not apply to the duration of being closed any power to actuator 59. This is for safe and cost-saving operation of the valve an essential advantage.

Claims (5)

Kraftstoffeinspritzeinrichtung für Brennkraftmaschine mit einer Kraftstoffhochdruckquelle (8), an die ein Kraftstoffeinspritzventil (14) angeschlossen ist, das ein Einspritzventilglied (21) zur Steuerung einer Einspritzöffnung (25) und einen Steuerraum (36) aufweist, der von einer beweglichen Wand (34) begrenzt wird, die mit dem Kraftstoffeinspritzventilglied (21) wenigstens mittelbar verbunden ist, und mit einem Zuflußkanal (53), über den eine Hochdruckquelle (8), vorzugsweise die Kraftstoffhochdruckquelle, mit dem Steuerraum (36) verbindbar ist, und mit einem Abflußkanal (57) über den der Steuerraum (36) mit einem Entlastungsraum (6) verbindbar ist, wobei die genannten Verbindungen zum und von Steuerraum über ein Ventil (40) steuerbar sind, das ein Ventilglied (43) mit einem mit zwei kegelförmigen Dichtflächen versehenen, in einem Ventilraum (41) verschiebbaren Schließkörper (42) aufweist, der koaxial zu zwei Ventilsitzen (54, 55) angeordnet ist und je nach Stellung mit der ersten oder der zweiten seiner Dichtfächen in dichter Anlagen an den entsprechenden ersten oder zweiten der Ventilsitze gelangt, und der Ventilraum über ein Kanal (37) ständig mit dem Steuerraum (36) verbunden ist und mit einem von einem elektrisch betätigtem Stellantrieb (59) bewegten mit dem Schließkörper (42) verbundenen Stößel (45) durch den der Schließkörper (42) zwischen den Ventilsitzen (54, 55) bewegt wird und der in einer sich koaxial zu dem einen der Ventilsitze (54) anschließenden Führungsbohrung (50) geführt ist, wobei ein an den Schließkörper (42) angrenzender Teil (48) des Stößels (45) im Durchmesser reduziert ist und zwischen diesem Teil des Stößels und der Wand der am einen der Ventilsitze endenden Führungsbohrung (50) ein Durchflußkanal (51) mit ringförmigem Querschnitt gebildet wird, in den der Zuflußkanal mündet und an dem anderen der Ventilsitze (55) angrenzend der Abflußkanal koaxial abführt, wobei zwischen dem zur Seite des Ventilraumes weisenden Teil des Stößels und dem im Durchmesser reduzierten Teil des Stößels (45) eine erste in Achsrichtung des Stößels wirksame Ringfläche (RF1) gebildet wird und zwischen dem im Durchmesser reduzierten Teil des Stößels und der durch das Aufsetzen der ersten Dichtfläche auf den ersten Ventilsitz definierten erste Dichtkante eine in Achsrichtung wirksame zweite Ringfläche (RF 2) gebildet wird und daß ferner der Durchmesser der Führungsbohrung eine erste Kreisfläche (KF 1) hat und die vom Umfang einer beim Aufsetzen der zweiten Dichtfläche (47) auf dem zweiten Ventilsitz (54) gebildeten zweiten Dichtkante eine zweite Kreisfläche (KF2) definiert, dadurch gekennzeichnet, daß die auf das Ventilglied aus der Druckbelastung der Kreisflächen (KF1, KF2) und der Ringflächen (RF1, RF2) entstehenden Kräfte so groß sind, daß in den Endstellungen des Schließkörpers (42) am einen oder anderen der Ventilsitze (54, 55) eine auf den jeweiligen Ventilsitz hin resultierende Kraft in Schließstellung gebildet wird.Fuel injection device for internal combustion engines with a high-pressure fuel source (8) to which a fuel injection valve (14) is connected, which is an injection valve member (21) for controlling an injection opening (25) and has a control space (36) that is movable Wall (34) is bounded with the fuel injector member (21) at least indirectly connected and with an inflow channel (53) through which a high pressure source (8), preferably the high-pressure fuel source, can be connected to the control room (36), and to a Drain channel (57) through which the control chamber (36) with a relief chamber (6) is connectable, said connections controllable to and from the control room via a valve (40) are a valve member (43) with one with two conical sealing surfaces provided in a valve chamber (41) has displaceable closing body (42) which is coaxial is arranged to two valve seats (54, 55) and depending on Position with the first or the second of its sealing surfaces in dense plants on the corresponding first or second the valve seats and the valve chamber via a channel (37) is permanently connected to the control room (36) and with one of an electrically operated actuator (59) moved plunger (45) connected to the closing body (42) through which the closing body (42) between the valve seats (54, 55) is moved and which is coaxial to the one of the valve seats (54) connecting guide bore (50) is guided, wherein one on the closing body (42) adjacent part (48) of the plunger (45) in diameter is reduced and between this part of the plunger and the Wall of the guide bore ending at one of the valve seats (50) a flow channel (51) with an annular cross section is formed, into which the inflow channel opens and on the other of the valve seats (55) adjacent the drain channel leads coaxially, between which to the side of the Valve chamber facing part of the tappet and in the Reduced part of the plunger (45) a first in Axial direction of the tappet effective ring surface (RF1) is formed is and between the reduced diameter part of the Tappet and by placing the first sealing surface on the first valve seat defined a first sealing edge effective second ring surface (RF 2) formed in the axial direction and that the diameter of the guide bore is also a has first circular area (KF 1) and the circumference of one at Place the second sealing surface (47) on the second one Valve seat (54) formed a second sealing edge a second Circular area (KF2) defined, characterized in that the on the valve member from the pressure load of the circular surfaces (KF1, KF2) and the ring surfaces (RF1, RF2) Forces are so great that in the end positions of the Closing body (42) on one or the other of the valve seats (54, 55) one towards the respective valve seat resulting force is formed in the closed position. Kraftstoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die sich aus der Differenz der Kreisflächen und/oder der Ringflächen ergebenden Differenzfläche so groß ist, daß die aus der Beaufschlagung durch den Kraftstoffhochdruck sich ergebenden resultierenden Kräfte jeweils nicht größer als etwa 40% der von der Stellantrieb aufbringbaren Kraft ist.Fuel injection device according to claim 1, characterized characterized in that the difference between the circular areas and / or the differential area resulting in ring areas is so large that it is caused by the high pressure fuel resulting resulting forces each not greater than about 40% of that of the actuator applicable force. Kraftstoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die zweite Ringfläche (RF2) kleiner als die erste Ringfläche (RF1) ist und die erste Kreisfläche (KF1) kleiner als die zweite Kreisfläche (KF2) ist.Fuel injection device according to claim 1, characterized characterized in that the second ring area (RF2) is smaller than is the first ring area (RF1) and the first circular area (KF1) is smaller than the second circular area (KF2). Kraftstoffeinspritzeinrichtung nach Anspruch 3, dadurch gekennzeichnet, daß der erste Ventilsitz auf einem im Durchmesser reduzierten Teil (52) der Führungsbohrung (50) angeordnet ist.Fuel injection device according to claim 3, characterized characterized in that the first valve seat on one in diameter reduced part (52) of the guide bore (50) is arranged. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Stellantrieb nur zur Betätigung des Schließkörpers mit Energie versorgt wird.Fuel injection device according to one of Claims 1 to 4, characterized in that the actuator only for Actuation of the closing body is supplied with energy.
EP98111577A 1997-10-10 1998-06-24 Fuel injection apparatus Expired - Lifetime EP0908617B1 (en)

Applications Claiming Priority (2)

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DE19744723A DE19744723A1 (en) 1997-10-10 1997-10-10 Fuel injector
DE19744723 1997-10-10

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JPH11193765A (en) 1999-07-21
DE59813510D1 (en) 2006-06-01
EP0908617B1 (en) 2006-04-26
DE19744723A1 (en) 1999-04-15

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