EP1252429B1 - Valve for the control of fluids - Google Patents

Valve for the control of fluids Download PDF

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Publication number
EP1252429B1
EP1252429B1 EP01909462A EP01909462A EP1252429B1 EP 1252429 B1 EP1252429 B1 EP 1252429B1 EP 01909462 A EP01909462 A EP 01909462A EP 01909462 A EP01909462 A EP 01909462A EP 1252429 B1 EP1252429 B1 EP 1252429B1
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EP
European Patent Office
Prior art keywords
valve
piston
seat
passage
pressure 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.)
Expired - Lifetime
Application number
EP01909462A
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German (de)
French (fr)
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EP1252429A2 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1252429A2 publication Critical patent/EP1252429A2/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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric operating means
    • 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
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/502—Springs biasing the valve member to the open position

Definitions

  • the invention relates to a valve for controlling fluids according to the preamble of claim 1.
  • a valve is known in which in a stepped bore of the valve housing, an actuating piston of a valve member is slidably disposed in a portion of the stepped bore with a small diameter.
  • a movable by a piezoelectric actuator larger piston is arranged in a portion of the stepped bore with a larger diameter.
  • a filled with a pressure medium hydraulic pressure chamber is formed so that a hydraulic translation of a movement of the piezoelectric actuator takes place.
  • the actuating piston of the valve member makes a stroke increased by the gear ratio of the piston diameter, since the piston of the piezoelectric actuator has a larger area than the actuating piston of the valve member.
  • 3/2-control valves are used, as disclosed for example in US 5,738,075.
  • Such 3/2 control valves can be designed as a seat slide or seat-seat valves.
  • the pressure from a rail by means of a controllable piston via a pressure chamber and a booster piston to a control chamber, from which the fuel is injected into the combustion chamber, out.
  • the pressure chamber is connected to a leak oil line, so that there is leak oil pressure in the pressure chamber.
  • a connection between the high pressure area and the leak oil area occurs for a short time. This results in a so-called Ab Kunststoffmaschinen in the drain line.
  • the discharge of the control chamber of the valve is hindered until the valve has sealed the opening to the high pressure area.
  • a valve according to the preamble of claim 1 is known from DE-A-19 716 221.
  • the valve according to the invention for controlling fluids with the characterizing features of claim 1 has the advantage that such a Ab horrstoss to the leak oil line does not occur. This is prevented by an upstream of a slide element on the seat of the control valve.
  • the slide element is arranged in the opening direction immediately before the region of the piston, with which the piston is seated on the valve seat. This allows, depending on the stroke of the slide element, a delayed opening of the passage between the inlet line and the pressure chamber, but an immediate closing of the passage between the inlet line and the pressure chamber. Thus, it can be ensured at any time when switching the control valve that there is no connection between the inlet pipe and the drain line.
  • the stroke of the piston for opening the connection between the supply line and the pressure chamber is at least equal to, but advantageously larger than a stroke for closing or opening a passage between the pressure chamber of the.
  • the slide element of the piston is cylindrical. In this way, on the one hand, a simple production of the slide element can be achieved, on the other hand, a simple construction of the control valve is thereby made possible overall.
  • the piston of the control valve is designed in two parts.
  • a seat slide valve can be realized with an interposed pressure chamber.
  • the control valve is constructed as a force-equalizing valve.
  • the guide diameter on the valve seat corresponds to the diameter of the slide element.
  • the piston of the control valve is integrally formed. This allows a 3/2-seat gate valve to be used as an exhaust valve.
  • valve will be designed to control fluids as a 3/2-seat gate valve or a 3/2-seat seat valve.
  • an optimum slide ratio can be formed from the respective stroke lengths.
  • the coverage should be chosen so that no appreciable delays of the valve occur, but it is ensured that no Abgresific occurs in the drain line.
  • valve according to the invention is used in a pressure-translated common rail injector.
  • the valve according to the invention is designed here as a 3/2-seat slide control valve 1.
  • a fuel injection valve according to a first embodiment of the present invention is shown.
  • the fuel injection valve the 3/2-control valve 1.
  • the control valve 1 consists of an actuating element 2 and a first piston 3 and a second piston 4.
  • an actuating element 2 for example, a known magnetic actuator or a known piezo actuator can be used.
  • the first piston 3 consists of several piston sections 3a to 3e.
  • a first piston portion 3a is cylindrical and communicates with the actuator 2 in connection.
  • a second piston section 3b which is of concave design and, with a corresponding position of the piston 3, releases a first passage 10 on the valve seat.
  • the third piston section designed as a slide element 3c follows.
  • the third piston section 3 c is arranged directly on the valve seat or on the first passage 10.
  • the piston 2 still comprises a widening fourth piston section 3d and a further cylindrical fifth piston section 3e.
  • the fifth piston section 3e communicates with a pressure chamber 6 arranged between the first piston 3 and the second piston 4.
  • the second piston 4 consists of a slide element 4a and a base body 4b.
  • the piston 4 is held by a spring 9 in the open position, so that a second passage 5 between the pressure chamber 6 and a drain line 8 is open.
  • the leakage oil pressure prevails.
  • a guide diameter d 1 on the first piston 3 is equal to a slide diameter d 2 on the second piston 4.
  • the control valve 1 is constructed as a force-equalizing valve.
  • the pressure chamber 6 is connected via a line 19 with a booster piston 11 in connection.
  • the multi-stage designed booster piston 11 is connected via a Return spring 12 is held in its initial position and communicates with its smaller piston diameter with a control chamber 15 in connection.
  • the control chamber 15 is filled via a filling valve 13 and a fuel line 14 with fuel.
  • the fuel is discharged via a biased by a spring 17 injection nozzle 16 in a combustion chamber, not shown.
  • the stroke length h 2 of the slide element 3c is greater than or at least equal to the stroke length h 1 on the piston 4, it is thus ensured that there is no connection between the inlet line 7, in which high pressure prevails, and the leak oil line 8 occurs.
  • the pressure chamber 6 When the piston 3 has covered the stroke length h 2 in the direction of the pressure chamber 6, the pressure chamber 6 is in communication with the high-pressure feed line 7, so that against the force of the return spring 12, a high pressure is applied to the booster piston 11. This high pressure is transmitted due to the different diameter of the booster piston 11 to the fuel-filled control chamber 15. As a result, over the provided on the injection nozzle 16 pressure shoulder 18, the force of the spring 17 overcome and the Fuel is injected into the combustion chamber, not shown.
  • FIG. 2 a second embodiment of a valve according to the invention for controlling fluids is shown.
  • This control valve 1 can also be used in a fuel injection valve. Since the fuel injection valve of the second embodiment compared with the first embodiment has only changes to the control valve 1, has been dispensed with a representation of the other parts of the fuel injection valve in Fig. 2 and in the following description, as they are accurate as are formed in the first embodiment. Furthermore, the same reference numerals as in the first embodiment are used in the second embodiment for similar parts.
  • the control valve 1 of the second embodiment in contrast to the first embodiment, only a piston 3.
  • the piston comprises a plurality of piston sections 3a to 3e.
  • the piston 3 also has a first cylindrical piston portion 3a and a second piston portion 3b, which is concave.
  • the second piston section 3b is adjoined by a slide element 3c, which is arranged directly on the valve seat.
  • the piston 3 comprises a fourth, tapered piston portion 3d and a fifth, cylindrical piston portion 3e, which is in communication with an actuating element 2.
  • the piston 3 is partially arranged in a pressure chamber 6 and opens / closes the connection between a supply line 7 from a rail and a communicating with the pressure chamber 6 via a line 19 booster piston (not shown).
  • the control valve 1 also includes a drain line 8.
  • control valve 1 The operation of the control valve 1 according to the second embodiment is as follows.
  • the piston 3 When the actuator is actuated, the piston 3 is moved in the direction of the actuating element 2.
  • the fourth, tapered piston section 3d lifts off from the piston seat on the first passage 10.
  • the connection 10 between the high-pressure inlet line 7 and the pressure chamber 6 is opened only when the second piston section 3b facing edge of the slide element 3c has been moved past the valve seat 10.
  • the stroke length h 2 of the slider element 3c is greater than the second passage 5 provided stroke length h 1 between the first piston portion 3a and the second piston portion 3b, it is ensured that the connection between the pressure chamber 6 and the leak oil line 8 is closed before the connection via the first passage 10 between the supply line 7 and the pressure chamber 6 is opened.
  • the connection between the supply line 7 and the pressure chamber 6 is first closed before the passage 5 between the pressure chamber 6 and the drain line 8 is opened.
  • the desired coverage (h 1 -h 2 ) can be adjusted by the ratio of the stroke length h 2 of the slide element 3 c to the stroke length h 1 at the second passage 5.

Abstract

The invention relates to a valve for controlling fluids, having an inflow line (7) and a leak fuel line (8), which each communicate with a pressure chamber (6). A piston element (3, 4) is also provided, which is adjustable by a control element (2) and opens and closes a first passage (10) between the inflow line (7) and the pressure chamber (6). The piston element (3, 4) has a slide element (3c), which is disposed directly at the seat of the piston element. The stroke length (h2) of the bc (3c) for opening the first passage is greater than or equal to the stroke length (h1) for closing a second passage (5) between the pressure chamber (6) and the leak fuel line (8).

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Ventil zum Steuern von Flüssigkeiten gemäß der Gattung des Patentanspruchs 1. Aus der EP-0477400 Al ist ein Ventil bekannt, bei dem in einer Stufenbohrung des Ventilgehäuses ein Betätigungskolben eines Ventilglieds in einem Teil der Stufenbohrung mit kleinem Durchmesser verschiebbar angeordnet ist. Ein durch einen Piezoaktor bewegbarer größerer Kolben ist in einem Teil der Stufenbohrung mit größerem Durchmesser angeordnet. Zwischen den beiden Kolben ist ein mit einem Druckmedium gefüllter hydraulischer Druckraum ausgebildet, so daß eine hydraulische Übersetzung einer Bewegung des Piezoaktors erfolgt. Das heißt, wenn der große Kolben durch den Piezoaktor um eine bestimmte Wegstrecke bewegt wird, macht der Betätigungskolben des Ventilglieds einen um das Übersetzungsverhältnis des Kolbendurchmessers vergrößerten Hub, da der Kolben des Piezoaktors eine größere Fläche als der Betätigungskolben des Ventilglieds aufweist.The invention relates to a valve for controlling fluids according to the preamble of claim 1. From EP-0477400 Al a valve is known in which in a stepped bore of the valve housing, an actuating piston of a valve member is slidably disposed in a portion of the stepped bore with a small diameter. A movable by a piezoelectric actuator larger piston is arranged in a portion of the stepped bore with a larger diameter. Between the two pistons a filled with a pressure medium hydraulic pressure chamber is formed so that a hydraulic translation of a movement of the piezoelectric actuator takes place. That is, when the large piston is moved by the piezoelectric actuator by a certain distance, the actuating piston of the valve member makes a stroke increased by the gear ratio of the piston diameter, since the piston of the piezoelectric actuator has a larger area than the actuating piston of the valve member.

Bei derartigen Ventilen werden auch 3/2-Steuerventile eingesetzt, wie beispielsweise in der US 5,738,075 offenbart ist. Derartige 3/2-Steuerventile können als Sitz-Schieber oder Sitz-Sitz-Ventile ausgebildet sein. Hierbei wird beispielsweise der Druck aus einem Rail mittels eines steuerbaren Kolbens über einen Druckraum und einen Übersetzerkolben zu einem Steuerraum, aus welchem der Kraftstoff in den Verbrennungsraum eingespritzt wird, geführt. Hierbei ist im nichtbetätigten Zustand der Druckraum mit einer Leckölleitung verbunden, so daß im Druckraum Lecköldruck herrscht. Beim Umschalten des 3/2-Steuerventils tritt jedoch unabhängig von der Art des Ventils (Sitz-Schieber-Ventil oder Sitz-Sitz-Ventil) für eine kurze Zeit eine Verbindung zwischen dem Hockdruckbereich und dem Leckölbereich auf. Daraus resultiert ein sogenannter Absteuerstoß in die Leckölleitung. Hierdurch wird die Entlastung des Steuerraums des Ventils behindert, bis das Ventil die Öffnung zum Hochdruckbereich abgedichtet hat.In such valves also 3/2-control valves are used, as disclosed for example in US 5,738,075. Such 3/2 control valves can be designed as a seat slide or seat-seat valves. Here, for example, the pressure from a rail by means of a controllable piston via a pressure chamber and a booster piston to a control chamber, from which the fuel is injected into the combustion chamber, out. Here, in the non-actuated state, the pressure chamber is connected to a leak oil line, so that there is leak oil pressure in the pressure chamber. However, when switching the 3/2 control valve, regardless of the type of the valve (seat slide valve or seat-and-seat valve), a connection between the high pressure area and the leak oil area occurs for a short time. This results in a so-called Absteuerstoß in the drain line. As a result, the discharge of the control chamber of the valve is hindered until the valve has sealed the opening to the high pressure area.

Ein Ventil gemäß Oberbegriff des Anspruchs 1 ist aus der DE-A-19 716 221 bekannt.A valve according to the preamble of claim 1 is known from DE-A-19 716 221.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Ventil zum Steuern von Flüssigkeiten mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat den Vorteil, daß ein derartiger Absteuerstoß zur Leckölleitung nicht auftritt. Dies wird durch ein Vorschalten eines Schieberelements am Sitz des Steuerventils verhindert. Das Schieberelement wird dabei in Öffnungsrichtung unmittelbar vor dem Bereich des Kolbens angeordnet, mit dem der Kolben am Ventilsitz aufsitzt. Dies ermöglicht abhängig von dem Hubweg des Schieberelements eine verzögerte Öffnung des Durchlasses zwischen Zulaufleitung und Druckraum, aber ein sofortiges Schließen des Durchlasses zwischen Zulaufleitung und Druckraum. Somit kann zu jedem Zeitpunkt beim Umschalten des Steuerventils sichergestellt werden, daß keine Verbindung zwischen Zulaufleitung und Leckölleitung besteht. Der Hubweg des Kolbens zum Öffnen der Verbindung zwischen der Zulaufleitung und dem Druckraum ist durch Vorsehen des Schieberelements zumindest gleich, vorteilhaft jedoch größer als ein Hubweg zum Schließen bzw. Öffnen eines Durchlasses zwischen dem Druckraum des Steuerventils und der Leckölleitung. Dadurch kann vorteilhaft der Absteuerstoß in die Leckölleitung verhindert werden. Weiterhin vorteilhaft wird beim Umschalten des Steuerventils die Entlastung des Steuerraums nicht mehr behindert, da infolge des Schieberelements sofort eine Abdichtung zum Hochdruckbereich erfolgt.The valve according to the invention for controlling fluids with the characterizing features of claim 1 has the advantage that such a Absteuerstoss to the leak oil line does not occur. This is prevented by an upstream of a slide element on the seat of the control valve. The slide element is arranged in the opening direction immediately before the region of the piston, with which the piston is seated on the valve seat. This allows, depending on the stroke of the slide element, a delayed opening of the passage between the inlet line and the pressure chamber, but an immediate closing of the passage between the inlet line and the pressure chamber. Thus, it can be ensured at any time when switching the control valve that there is no connection between the inlet pipe and the drain line. The stroke of the piston for opening the connection between the supply line and the pressure chamber is at least equal to, but advantageously larger than a stroke for closing or opening a passage between the pressure chamber of the. By providing the slide element Control valve and the drain line. This can advantageously be prevented Absteuerstoß in the drain line. Further advantageous in the switching of the control valve, the discharge of the control chamber is no longer hindered, as a result of the slide immediately a seal to the high pressure area.

In einer besonders vorteilhaften Weise ist das Schieberelement des Kolbens zylinderförmig ausgebildet. Hierdurch kann zum einen eine einfache Herstellung des Schieberelements erreicht werden, andererseits wird dadurch insgesamt ein einfacher Aufbau des Steuerventils ermöglicht.In a particularly advantageous manner, the slide element of the piston is cylindrical. In this way, on the one hand, a simple production of the slide element can be achieved, on the other hand, a simple construction of the control valve is thereby made possible overall.

In vorteilhafter Weise ist der Kolben des Steuerventils zweiteilig ausgestaltet. Dadurch läßt sich ein Sitz-Schieber-Ventil mit einem dazwischen angeordneten Druckraum verwirklichen. Besonders vorteilhaft ist das Steuerventil dabei als kraftausgleichendes Ventil aufgebaut. Dabei entspricht der Führungsdurchmesser am Ventilsitz dem Durchmesser des Schieberelements.Advantageously, the piston of the control valve is designed in two parts. As a result, a seat slide valve can be realized with an interposed pressure chamber. Particularly advantageously, the control valve is constructed as a force-equalizing valve. The guide diameter on the valve seat corresponds to the diameter of the slide element.

Weiter vorteilhaft ist der Kolben des Steuerventils einstückig ausgebildet. Dadurch kann ein 3/2-Sitz-Schieber-Ventil als ein Auslaßventil eingesetzt werden.Further advantageously, the piston of the control valve is integrally formed. This allows a 3/2-seat gate valve to be used as an exhaust valve.

Bevorzugt wird das Ventil zum Steuern von Flüssigkeiten als 3/2-Sitz-Schieber-Ventil oder als 3/2-Sitz-Sitz-Ventil ausgebildet werden.Preferably, the valve will be designed to control fluids as a 3/2-seat gate valve or a 3/2-seat seat valve.

Insgesamt kann somit mit dem erfindungsgemäßen Ventil eine eindeutige Funktion eines Steuerventils ohne Absteuerstoß aus dem Hochdruckzulaufbereich in die Leckölleitung erreicht werden. Durch Variation der Hublängen bzw. Hubwege des Schieberelements am Ventilsitz bzw. der Hublänge zum Schließen/Öffnen der Verbindung zur Leckölleitung kann die Überdeckung am Leckölschieberelement optimiert werden.Overall, therefore, with the valve according to the invention a clear function of a control valve without Absteuerstoss be achieved from the high-pressure inlet area in the drain line. By varying the stroke lengths or stroke paths of the slide element on the valve seat or the stroke length for closing / opening the connection to the leak oil line, the overlap on the leak oil slide element can be optimized.

Hierbei kann je nach Anwendungszweck ein aus den jeweiligen Hublängen optimales Schieberverhältnis gebildet werden. Hierbei sollte die Überdeckung so gewählt werden, daß keine nennenswerten Verzögerungen des Ventils auftreten, jedoch sichergestellt ist, daß kein Absteuerstoß in die Leckölleitung auftritt.Depending on the application purpose, an optimum slide ratio can be formed from the respective stroke lengths. In this case, the coverage should be chosen so that no appreciable delays of the valve occur, but it is ensured that no Absteuerstoß occurs in the drain line.

Zeichnungdrawing

In der Zeichnung sind zwei Ausführungsbeispiele der Erfindung dargestellt. Die Ausführungsbeispiele werden in der nachfolgenden Beschreibung näher erläutert. Es zeigt:

Fig. 1
eine schematische Schnittansicht eines Kraftstoffeinspritzventils gemäß einem ersten Ausführungsbeispiel der vorliegenden Erfindung; und
Fig. 2
eine schematische Teilschnittansicht eines Kraftstoffeinspritzventils gemäß einem zweiten Ausführungsbeispiel der vorliegenden Erfindung.
In the drawing, two embodiments of the invention are shown. The exemplary embodiments are explained in more detail in the following description. It shows:
Fig. 1
a schematic sectional view of a fuel injection valve according to a first embodiment of the present invention; and
Fig. 2
a schematic partial sectional view of a fuel injection valve according to a second embodiment of the present invention.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In dem in Fig. 1 dargestellten Ausführungsbeispiel findet das erfindungsgemäße Ventil Anwendung in einem druckübersetzten Common-Rail-Injector. Das erfindungsgemäße Ventil ist hierbei als ein 3/2-Sitz-Schieber-Steuerventil 1 ausgebildet.In the embodiment shown in Fig. 1, the valve according to the invention is used in a pressure-translated common rail injector. The valve according to the invention is designed here as a 3/2-seat slide control valve 1.

In Fig. 1 ist ein Kraftstoffeinspritzventil gemäß einem ersten Ausführungsbeispiel der vorliegenden Erfindung dargestellt. Hierbei umfaßt das Kraftstoffeinspritzventil das 3/2-Steuerventil 1. Das Steuerventil 1 besteht aus einem Stellelement 2 sowie einem ersten Kolben 3 und einem zweiten Kolben 4. Als Stellelement 2 kann beispielsweise ein bekannter Magnetsteller oder ein bekannter Piezosteller verwendet werden.In Fig. 1, a fuel injection valve according to a first embodiment of the present invention is shown. Here, the fuel injection valve, the 3/2-control valve 1. The control valve 1 consists of an actuating element 2 and a first piston 3 and a second piston 4. As an actuating element 2, for example, a known magnetic actuator or a known piezo actuator can be used.

Der erste Kolben 3 besteht aus mehreren Kolbenabschnitten 3a bis 3e. Ein erster Kolbenabschnitt 3a ist zylinderförmig ausgebildet und steht mit dem Stellelement 2 in Verbindung. Daran schließt sich ein zweiter Kolbenabschnitt 3b an, welcher konkav ausgebildet ist und bei entsprechender Stellung des Kolbens 3 einen ersten Durchlaß 10 am Ventilsitz freigibt. Anschließend an den zweiten Kolbenabschnitt 3b folgt der als Schieberelement 3c ausgebildete dritte Kolbenabschnitt. Der dritte Kolbenabschnitt 3c ist direkt am Ventilsitz bzw. am ersten Durchlaß 10 angeordnet. Weiterhin umfaßt der Kolben 2 noch einen sich erweiternden vierten Kolbenabschnitt 3d sowie einen weiteren zylindrischen fünften Kolbenabschnitt 3e. Der fünfte Kolbenabschnitt 3e steht mit einem zwischen dem ersten Kolben 3 und dem zweiten Kolben 4 angeordneten Druckraum 6 in Verbindung.The first piston 3 consists of several piston sections 3a to 3e. A first piston portion 3a is cylindrical and communicates with the actuator 2 in connection. This is followed by a second piston section 3b, which is of concave design and, with a corresponding position of the piston 3, releases a first passage 10 on the valve seat. Subsequent to the second piston section 3b, the third piston section designed as a slide element 3c follows. The third piston section 3 c is arranged directly on the valve seat or on the first passage 10. Furthermore, the piston 2 still comprises a widening fourth piston section 3d and a further cylindrical fifth piston section 3e. The fifth piston section 3e communicates with a pressure chamber 6 arranged between the first piston 3 and the second piston 4.

Der zweite Kolben 4 besteht aus einem Schieberelement 4a sowie einem Grundkörper 4b. Bei nichtbetätigtem Steuerventil 1 wird der Kolben 4 durch eine Feder 9 in Offenstellung gehalten, so daß ein zweiter Durchlaß 5 zwischen dem Druckraum 6 und einer Leckölleitung 8 offen ist. Dadurch herrscht im nichtbetätigten Zustand im Druckraum 6 der Lecköldruck.The second piston 4 consists of a slide element 4a and a base body 4b. When not actuated control valve 1, the piston 4 is held by a spring 9 in the open position, so that a second passage 5 between the pressure chamber 6 and a drain line 8 is open. As a result, in the non-actuated state in the pressure chamber 6, the leakage oil pressure prevails.

Bei dem in Fig. 1 dargestellten Steuerventil 1 ist ein Führungsdurchmesser d1 am ersten Kolben 3 gleich einem Schieberdurchmesser d2 am zweiten Kolben 4. Somit ist das Steuerventil 1 als ein kraftausgleichendes Ventil aufgebaut.In the control valve 1 shown in Fig. 1, a guide diameter d 1 on the first piston 3 is equal to a slide diameter d 2 on the second piston 4. Thus, the control valve 1 is constructed as a force-equalizing valve.

Weiter steht der Druckraum 6 über eine Leitung 19 mit einem Übersetzerkolben 11 in Verbindung. Der mehrstufig ausgestaltete Übersetzerkolben 11 wird über eine Rückstellfeder 12 in seiner Ausgangsposition gehalten und steht mit seinem kleinerem Kolbendurchmesser mit einem Steuerraum 15 in Verbindung. Der Steuerraum 15 wird über ein Befüllungsventil 13 und eine Kraftstoffleitung 14 mit Kraftstoff befüllt. Der Kraftstoff wird über eine mittels einer Feder 17 vorgespannten Einspritzdüse 16 in einen nicht dargestellten Verbrennungsraum abgegeben.Next, the pressure chamber 6 is connected via a line 19 with a booster piston 11 in connection. The multi-stage designed booster piston 11 is connected via a Return spring 12 is held in its initial position and communicates with its smaller piston diameter with a control chamber 15 in connection. The control chamber 15 is filled via a filling valve 13 and a fuel line 14 with fuel. The fuel is discharged via a biased by a spring 17 injection nozzle 16 in a combustion chamber, not shown.

Nachfolgend wird die Wirkungsweise des Kraftstoffeinspritzventils beschrieben. Bei Betätigung des Stellelements 2 wird der Kolben 3 in Richtung des Druckraums 6 von seinem Ventilsitz fortbewegt. Beim Öffnen des Sitzes wird jedoch nicht sofort eine Verbindung zwischen der Zulaufleitung 7 aus dem Rail zum Druckraum 6 hergestellt, sondern es muß zuerst eine Schieberhöhe h2 des Schieberelements 3c überwunden werden, bevor diese Verbindung hergestellt ist. Infolge der Bewegung des Kolbens 3 in Richtung des Druckraums 6 wird der Kolben 4 entgegen der Federkraft der Feder 9 geschlossen. Dabei muß eine Hublänge h1 am Schieberelement 4 überwunden werden. Da erfindungsgemäß die Hublänge h2 des Schieberelements 3c größer oder wenigstens gleich der Hublänge h1 am Kolben 4 ist, ist somit sichergestellt, daß keine Verbindung zwischen der Zulaufleitung 7, in welcher Hochdruck herrscht, und der Leckölleitung 8 auftritt.The operation of the fuel injection valve will be described below. Upon actuation of the actuating element 2, the piston 3 is moved in the direction of the pressure chamber 6 from its valve seat. When opening the seat, however, a connection between the supply line 7 is not immediately made from the rail to the pressure chamber 6, but it must first be overcome a slide height h 2 of the slide element 3c, before this connection is made. As a result of the movement of the piston 3 in the direction of the pressure chamber 6, the piston 4 is closed against the spring force of the spring 9. In this case, a stroke length h 1 must be overcome on the slide element 4. Since according to the invention the stroke length h 2 of the slide element 3c is greater than or at least equal to the stroke length h 1 on the piston 4, it is thus ensured that there is no connection between the inlet line 7, in which high pressure prevails, and the leak oil line 8 occurs.

Wenn der Kolben 3 die Hublänge h2 in Richtung des Druckraums 6 zurückgelegt hat, steht der Druckraum 6 mit der Hochdruckzulaufleitung 7 in Verbindung, so daß entgegen der Kraft der Rückstellfeder 12 ein hoher Druck am Übersetzerkolben 11 anliegt. Dieser hohe Druck wird infolge der unterschiedlichen Durchmesser des Übersetzerkolbens 11 auf den mit Kraftstoff gefüllten Steuerraum 15 übertragen. Dadurch wird über die an der Einspritzdüse 16 vorgesehene Druckschulter 18 die Kraft der Feder 17 überwunden und der Kraftstoff wird in den nicht dargestellten Brennraum eingespritzt.When the piston 3 has covered the stroke length h 2 in the direction of the pressure chamber 6, the pressure chamber 6 is in communication with the high-pressure feed line 7, so that against the force of the return spring 12, a high pressure is applied to the booster piston 11. This high pressure is transmitted due to the different diameter of the booster piston 11 to the fuel-filled control chamber 15. As a result, over the provided on the injection nozzle 16 pressure shoulder 18, the force of the spring 17 overcome and the Fuel is injected into the combustion chamber, not shown.

Beim Rückstellen des Steuerventils 1 wird infolge der Hublänge des Schieberelements 3c die Verbindung zwischen der Zulaufleitung 7 und dem Druckraum 6 sofort unterbrochen, während der zweite Durchlaß 5 noch aufgrund des hohen Drucks im Druckraum 6 durch das Schieberelement 4a verschlossen ist. Erst wenn die Federkraft der Feder 9 größer als der Druck im Druckraum 6 wird, öffnet das Schieberelement 4a des Kolbens 4 den Durchlaß 5, so daß eine Verbindung zwischen dem Druckraum 6 und der Leckölleitung 8 freigegeben wird.When resetting the control valve 1, the connection between the supply line 7 and the pressure chamber 6 is immediately interrupted due to the stroke length of the slide element 3c, while the second passage 5 is still closed due to the high pressure in the pressure chamber 6 by the slide element 4a. Only when the spring force of the spring 9 is greater than the pressure in the pressure chamber 6, the slide element 4a of the piston 4 opens the passage 5, so that a connection between the pressure chamber 6 and the drain line 8 is released.

Somit ist immer eine eindeutige Funktion des Steuerventils 1 sowohl beim Öffnen als auch beim Schließen gewährleistet, ohne daß ein Absteuerstoß aus dem Druckraum 6 in die Leckölleitung 8 auftritt. Durch das Vorschalten des Schieberelements 3c in Öffnungsrichtung vor dem eigentlichen Öffnungsabschnitt 3d des Kolbens 3 können somit die im Stand der Technik vorhandenen Nachteile beseitigt werden. Weiterhin kann durch das Schieberverhältnis h2/h1 eine Überdeckung am Kolben 4 je nach Anwendung optimiert werden. In der Regel wird die Überdeckung (h2 - h1) verlängert werden (d.h. größer als 0 sein), um sicherzustellen, daß kein Leckölstoß auftritt.Thus, always a clear function of the control valve 1 is ensured both when opening and closing, without a Absteuerstoss from the pressure chamber 6 occurs in the drain line 8. By pre-switching the slide element 3c in the opening direction before the actual opening section 3d of the piston 3, the disadvantages existing in the prior art can thus be eliminated. Furthermore, by the slide ratio h 2 / h 1 an overlap on the piston 4 can be optimized depending on the application. As a rule, the coverage (h 2 -h 1 ) will be extended (ie greater than 0) to ensure that no leakage oil surge occurs.

In Fig. 2 ist ein zweites Ausführungsbeispiel eines erfindungsgemäßen Ventils zum Steuern von Flüssigkeiten dargestellt. Dieses Steuerventil 1 kann ebenfalls bei einem Kraftstoffeinspritzventil eingesetzt werden. Da das Kraftstoffeinspritzventil des zweiten Ausführungsbeispiels im Vergleich mit dem ersten Ausführungsbeispiel nur Änderungen am Steuerventil 1 aufweist, ist auf eine Darstellung der weiteren Teile des Kraftstoffeinspritzventils in der Fig. 2 und in der nachfolgenden Beschreibung verzichtet worden, da diese genau wie im erste Ausführungsbeispiel ausgebildet sind. Weiterhin werden im zweiten Ausführungsbeispiel für gleichartige Teile gleiche Bezugszeichen wie im ersten Ausführungsbeispiel verwendet.2, a second embodiment of a valve according to the invention for controlling fluids is shown. This control valve 1 can also be used in a fuel injection valve. Since the fuel injection valve of the second embodiment compared with the first embodiment has only changes to the control valve 1, has been dispensed with a representation of the other parts of the fuel injection valve in Fig. 2 and in the following description, as they are accurate as are formed in the first embodiment. Furthermore, the same reference numerals as in the first embodiment are used in the second embodiment for similar parts.

Das Steuerventil 1 des zweiten Ausführungsbeispiels weist im Gegensatz zum ersten Ausführungsbeispiel nur einen Kolben 3 auf. Der Kolben umfaßt mehrere Kolbenabschnitte 3a bis 3e. Der Kolben 3 weist ebenfalls einen ersten zylinderförmigen Kolbenabschnitt 3a und einen zweiten Kolbenabschnitt 3b auf, welcher konkav gebildet ist. An den zweiten Kolbenabschnitt 3b schließt sich ein Schieberelement 3c an, welches unmittelbar am Ventilsitz angeordnet ist. Weiter umfaßt der Kolben 3 einen vierten, sich verjüngenden Kolbenabschnitt 3d sowie einen fünften, zylinderförmigen Kolbenabschnitt 3e, welcher mit einem Stellelement 2 in Verbindung steht. Der Kolben 3 ist teilweise in einem Druckraum 6 angeordnet und öffnet/schließt die Verbindung zwischen einer Zulaufleitung 7 aus einem Rail und einem mit dem Druckraum 6 über eine Leitung 19 in Verbindung stehenden Übersetzerkolben (nicht dargestellt). Weiterhin umfaßt das Steuerventil 1 auch eine Leckölleitung 8.The control valve 1 of the second embodiment, in contrast to the first embodiment, only a piston 3. The piston comprises a plurality of piston sections 3a to 3e. The piston 3 also has a first cylindrical piston portion 3a and a second piston portion 3b, which is concave. The second piston section 3b is adjoined by a slide element 3c, which is arranged directly on the valve seat. Further, the piston 3 comprises a fourth, tapered piston portion 3d and a fifth, cylindrical piston portion 3e, which is in communication with an actuating element 2. The piston 3 is partially arranged in a pressure chamber 6 and opens / closes the connection between a supply line 7 from a rail and a communicating with the pressure chamber 6 via a line 19 booster piston (not shown). Furthermore, the control valve 1 also includes a drain line 8.

Die Wirkungsweise des Steuerventils 1 gemäß dem zweiten Ausführungsbeispiel ist wie folgt. Wenn das Stellelement betätigt wird, wird der Kolben 3 in Richtung des Stellelements 2 bewegt. Dadurch hebt der vierte, sich verjüngende Kolbenabschnitt 3d vom Kolbensitz an dem ersten Durchlaß 10 ab. Da jedoch im Anschluß an den zweiten Kolbenabschnitt 3b unmittelbar das Schieberelement 3c angeordnet ist, wird die Verbindung 10 zwischen der Hochdruckzulaufleitung 7 und dem Druckraum 6 erst geöffnet, wenn die dem zweiten Kolbenabschnitt 3b zugewandte Kante des Schieberelements 3c am Ventilsitz 10 vorbeigeführt worden ist.The operation of the control valve 1 according to the second embodiment is as follows. When the actuator is actuated, the piston 3 is moved in the direction of the actuating element 2. As a result, the fourth, tapered piston section 3d lifts off from the piston seat on the first passage 10. However, since immediately after the second piston portion 3b, the slider element 3c is arranged, the connection 10 between the high-pressure inlet line 7 and the pressure chamber 6 is opened only when the second piston section 3b facing edge of the slide element 3c has been moved past the valve seat 10.

Da, wie in Fig. 2 dargestellt, die Hublänge h2 des Schieberelements 3c größer ist als die am zweiten Durchlaß 5 vorgesehene Hublänge h1 zwischen dem ersten Kolbenabschnitt 3a und dem zweiten Kolbenabschnitt 3b, wird sichergestellt, daß die Verbindung zwischen dem Druckraum 6 und der Leckölleitung 8 geschlossen wird, bevor die Verbindung über den ersten Durchlaß 10 zwischen der Zulaufleitung 7 und dem Druckraum 6 geöffnet wird. Beim Schließen des Steuerventils 1 wird zuerst die Verbindung zwischen der Zulaufleitung 7 und dem Druckraum 6 geschlossen, bevor der Durchlaß 5 zwischen dem Druckraum 6 und der Leckölleitung 8 geöffnet wird.Since, as shown in Fig. 2, the stroke length h 2 of the slider element 3c is greater than the second passage 5 provided stroke length h 1 between the first piston portion 3a and the second piston portion 3b, it is ensured that the connection between the pressure chamber 6 and the leak oil line 8 is closed before the connection via the first passage 10 between the supply line 7 and the pressure chamber 6 is opened. When closing the control valve 1, the connection between the supply line 7 and the pressure chamber 6 is first closed before the passage 5 between the pressure chamber 6 and the drain line 8 is opened.

Somit wird auch beim zweiten erfindungsgemäßen Ausführungsbeispiel beim Umschalten des Steuerventils 1 ein Absteuerstoß in die Leckölleitung 8 in sicherer Weise verhindert. Weiterhin kann je nach Einsatzzweck die gewünschte Überdeckung (h1 - h2) durch das Verhältnis der Hublänge h2 des Schieberelements 3c zur Hublänge h1 am zweiten Durchlaß 5 eingestellt werden.Thus, a Absteuerstoss is prevented in the second embodiment of the invention when switching the control valve 1 in the drain line 8 in a secure manner. Furthermore, depending on the intended use, the desired coverage (h 1 -h 2 ) can be adjusted by the ratio of the stroke length h 2 of the slide element 3 c to the stroke length h 1 at the second passage 5.

Die vorhergehende Beschreibung der Ausführungbeispiele gemäß der vorliegenden Erfindung dient nur zu illustrativen Zwecken und nicht zum Zwecke der Beschränkung der Erfindung.The foregoing description of the embodiments according to the present invention is for illustrative purposes only, and not for the purpose of limiting the invention.

Claims (7)

  1. Valve for controlling fluids, having a feed line (7) and a leakage oil line (8) which are in each case connected to a pressure space (6), and having a piston element (3, 4) which can be displaced by an actuating element (2) and opens or closes a first passage (10) between the feed line (7) and the pressure space (6), characterized in that the piston element (3, 4) has a seat (10) and a slide element (3c) which is arranged so as to adjoin the seat of the piston element directly, for controlling the first passage, and having a slide element (4a) on the piston (4) of the piston element (3, 4), for controlling the second passage which is connected to the leakage oil line, the slide element (3c) having a displacement length (h2) for opening the first passage (10) which is greater than or equal to a displacement length (h1) of the slide element (4a) for closing the second passage.
  2. Valve for controlling fluids according to Claim 1, characterized in that the slide element (3c) is of cylindrical configuration.
  3. Valve for controlling fluids according to Claim 1 or 2, characterized in that the piston element comprises a first piston (3) and a second piston (4).
  4. Valve for controlling fluids according to Claim 1 or 2, characterized in that the piston element (3) is of one-piece configuration.
  5. Valve for controlling fluids according to one of Claims 1 to 4, characterized in that the valve is configured as a 3/2-seat-slide valve.
  6. Valve for controlling fluids according to one of Claims 1 to 4, characterized in that the valve is configured as a 3/2-seat-seat valve.
  7. Valve for controlling fluids according to one of Claims 1 to 6, characterized in that the valve is configured as a force-neutralizing valve.
EP01909462A 2000-01-22 2001-01-13 Valve for the control of fluids Expired - Lifetime EP1252429B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10002702A DE10002702A1 (en) 2000-01-22 2000-01-22 Valve for controlling liquids
DE10002702 2000-01-22
PCT/DE2001/000122 WO2001053685A2 (en) 2000-01-22 2001-01-13 Valve for the control of fluids

Publications (2)

Publication Number Publication Date
EP1252429A2 EP1252429A2 (en) 2002-10-30
EP1252429B1 true EP1252429B1 (en) 2006-01-04

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US (1) US6736331B2 (en)
EP (1) EP1252429B1 (en)
JP (1) JP2003520324A (en)
AT (1) ATE315174T1 (en)
CZ (1) CZ20022414A3 (en)
DE (2) DE10002702A1 (en)
ES (1) ES2255545T3 (en)
HU (1) HUP0301062A2 (en)
WO (1) WO2001053685A2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10002702A1 (en) * 2000-01-22 2001-08-02 Bosch Gmbh Robert Valve for controlling liquids
DE10141110A1 (en) * 2001-08-22 2003-03-20 Bosch Gmbh Robert Fuel injection device for internal combustion engines
JP4019934B2 (en) * 2002-12-26 2007-12-12 株式会社デンソー Control valve and fuel injection valve
DE10328245A1 (en) * 2003-06-24 2005-01-13 Robert Bosch Gmbh Fuel injection device for internal combustion engines
CN108506130A (en) * 2018-04-18 2018-09-07 莆田市宏业精密机械有限公司 Reduce the fuel injector of high-pressure common rail fuel oil dynamic leakage

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US3477344A (en) * 1967-05-24 1969-11-11 United Aircraft Corp Fluid mechanical hysteretic device
DE3741526A1 (en) * 1987-12-08 1989-06-22 Bosch Gmbh Robert Seat valve
US5241935A (en) * 1988-02-03 1993-09-07 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
ATE88971T1 (en) * 1990-09-26 1993-05-15 Knoblauch Georg Fa FLAT PACK CASSETTE FOR STORAGE OF LONG ITEMS.
DE4311627B4 (en) * 1993-04-08 2005-08-25 Robert Bosch Gmbh Fuel injection device for internal combustion engines
US5687693A (en) * 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5680988A (en) * 1995-01-20 1997-10-28 Caterpillar Inc. Axial force indentation or protrusion for a reciprocating piston/barrel assembly
DE19701879A1 (en) * 1997-01-21 1998-07-23 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19716221B4 (en) * 1997-04-18 2007-06-21 Robert Bosch Gmbh Fuel injection device with pre-injection and main injection in internal combustion engines, in particular for hard to ignite fuels
DE19937713C1 (en) * 1999-08-10 2001-03-15 Siemens Ag Control valve arrangement for use in a fuel injector for internal combustion engines
DE10002702A1 (en) * 2000-01-22 2001-08-02 Bosch Gmbh Robert Valve for controlling liquids
DE10031278A1 (en) * 2000-06-27 2002-01-17 Bosch Gmbh Robert Fuel injection device for internal combustion engines

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US20030089794A1 (en) 2003-05-15
WO2001053685A2 (en) 2001-07-26
ATE315174T1 (en) 2006-02-15
DE50108611D1 (en) 2006-03-30
DE10002702A1 (en) 2001-08-02
JP2003520324A (en) 2003-07-02
CZ20022414A3 (en) 2004-03-17
EP1252429A2 (en) 2002-10-30
ES2255545T3 (en) 2006-07-01
HUP0301062A2 (en) 2003-08-28
US6736331B2 (en) 2004-05-18
WO2001053685A3 (en) 2001-12-06

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