WO2001096732A1 - Valve for regulating fluids - Google Patents
Valve for regulating fluids Download PDFInfo
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- WO2001096732A1 WO2001096732A1 PCT/DE2001/001327 DE0101327W WO0196732A1 WO 2001096732 A1 WO2001096732 A1 WO 2001096732A1 DE 0101327 W DE0101327 W DE 0101327W WO 0196732 A1 WO0196732 A1 WO 0196732A1
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- Prior art keywords
- valve
- piston
- spring
- spring element
- controlling liquids
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—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
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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
- 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
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
Definitions
- the present invention relates to a valve for controlling liquids according to the preamble of patent claim 1.
- Valves for controlling liquids are known in a wide variety of configurations.
- a valve 1 for controlling liquids is shown in FIG. 2, which has a hydraulic intensifier 2, which has a first piston 3, a second piston 4, and a pressure chamber 5 arranged between the two pistons 3, 4.
- the first piston 3 can be actuated via an actuating piston 10 by a piezo element (not shown).
- the second piston 4 is connected via a tappet 9 to a valve ball 6 which is pressed against a valve seat 7 by means of a spring 8.
- the piezo actuator is actuated, the valve ball is moved via the hydraulic intensifier 2 and the plunger 9
- valve seat 7 thereby providing a pressure increase in an injection region of a valve needle in order to lift the valve needle from an injection opening and to supply fuel into a combustion chamber (not shown).
- the ball 6 pressed against the upper valve seat 7 by the spring force of the spring 8, and remains in this position until the engine is restarted. Since, as shown in FIG. 2, a volume 11 in the region of the valve ball 6 is relatively large due to the position of the valve ball 6 on the upper valve seat 7, the function of the injector is partially restricted, since certain delays occur during actuation. In order to provide a small volume 11, unfavorable spring designs have to be used, which have a complicated structure and lead to increased costs.
- valve ball 6 must be designed with a spring seat 18 in its lower region. This also increases the manufacturing costs. Since the spring 8 is arranged in the high-pressure region of the valve 1, it is also constantly exposed to high pressure loads, which can lead to a reduced service life of the spring 8.
- valve according to the invention for controlling liquids with the features of claim 1 has the advantage that the spring element is directly coupled to the second piston of the hydraulic translator. In other words, the spring element is arranged directly on the second piston. This allows the valve member
- Valve closing element are arranged spaced from the spring element. This separation of the spring element from the valve member makes it possible to provide a very small volume in the region of the valve member without complex structural measures. Furthermore, the valve member can also be produced simply and inexpensively, since it does not have to have receptacles or spring seats for the spring element that are expensive to produce. Furthermore, the spring element is arranged according to the invention in the low pressure region of the valve. Therefore, the installation space for the spring element be designed large; the latter has a long lifespan.
- the second piston of the hydraulic translator is preferably constructed in two parts. This enables a first part of the two-part piston to be designed as a standard part, e.g. meets high tolerance requirements for the diameter. A second part of the piston can then be designed accordingly for optimal coupling with the spring element.
- the two-part piston preferably has a cylindrical element and a plunger element. This means that a standard part such as e.g. Rolling bearing rollers or the like can be used.
- Tappet element can then be adapted to the spring element. It is possible that the tappet element is integrally formed with a tappet for actuating the valve ball. However, it is also possible to design the plunger element as a disk-shaped element. A plunger for actuating the valve member is then formed as a separate element.
- the spring element preferably has an opening in order to guide the tappet for actuating the valve member.
- the spring element can be designed as a diaphragm spring or as a plate spring or as a coil spring.
- the valve is designed as a single switching valve or as a double switching valve.
- the valve here has only one valve seat against which the valve member bears or is lifted off.
- Two valve seats are provided, the valve member either resting on one valve seat or the other valve seat or occupying an intermediate position in which both valve seats are open.
- the valve according to the invention is preferably used in a common rail injector. In this way, in particular the loads on the valve parts caused by the high pressures can be avoided.
- FIG. 1 shows a valve for controlling liquids according to a first embodiment of the present invention
- Figure 2 shows a valve for controlling liquids according to the prior art.
- FIG. 1 shows a valve according to the invention for controlling liquids, which is used as a fuel injection valve.
- the valve 1 comprises a holder 16, a valve piece 17, an intermediate disk 19 and a nozzle body 20 which are connected to one another via a nozzle clamping nut 22.
- the valve 1 comprises a hydraulic booster 2, which has a first piston 3, a second piston 4 and a pressure chamber 5 arranged between the two pistons 3, 4.
- the second piston 4 is connected via a tappet 9 to a valve member 6 designed as a ball.
- the valve ball 6 is such designed that it can be placed on an upper valve seat 7 and a lower valve seat 12.
- the first piston 3 of the hydraulic translator is arranged in a receiving body 15 which is firmly positioned in the holder 16.
- the second piston 4 of the hydraulic translator is arranged axially offset from the first piston 3.
- a valve needle 21 is arranged in the nozzle body 20, which opens and closes an inlet opening through which fuel is injected into a combustion chamber (not shown).
- the second piston 4 of the hydraulic translator 2 is formed in two parts.
- the second piston 4 consists of a cylindrical pin 4a and a pressure ram 4b.
- the cylindrical bolt 4a has a simple structure and thus high demands on tolerances or the like. can meet. This also means the use of
- the pressure ram 4b directly adjoins the cylindrical bolt 4a. Furthermore, the pressure tappet 4b is directly coupled to a spring element 8.
- the spring element 8 has a central opening in order to guide the plunger 9. Furthermore, the spring element 8 is designed such that it presses the pressure ram 4b against the cylindrical bolt 4a. If the engine of a motor vehicle is now switched off in the valve according to the exemplary embodiment shown, the second piston 4 is pressed into the pressure chamber 5 due to the spring force of the spring 8, since the fluid in the pressure chamber 5 passes through leakage gaps 13 and 14 at the two Pistons 3 and 4 escape. Since the valve ball 6 is not acted upon by spring force, it lies against the lower seat 12 undefined.
- Pressure chamber 5 of the hydraulic translator is filled with fluid again. Compared to the movement of the valve ball 6, however, this filling is a relatively slow process.
- the second piston 4 therefore only moves in the direction of the valve ball 6 after a certain time. However, the valve is only ready for operation when the second piston 4 is in contact with the valve ball 6 via the tappet 9.
- the arrangement of the spring element 8 directly on the second piston 4 of the hydraulic booster 2 enables a volume 11 in the region of the valve ball 6 to be made very small. It is also achieved that the spring element 8 is in the low pressure region of the valve. It is also not necessary to use a valve ball that is expensive to manufacture with spring receiving surfaces or spring seats. As a result, the manufacturing costs of the valve according to the invention are reduced and the individual parts of the valve can have simple designs. This also has advantages with regard to quick and inexpensive installation.
- a valve 1 for controlling liquids which comprises a piezo actuator and a hydraulic booster 2.
- the hydraulic translator 2 has a first piston 3, a second Piston 4 and a pressure chamber 5 arranged between the two pistons 3, 4.
- a valve member 6 and a spring element 8 are also provided.
- the spring element 8 is directly coupled to the second piston 4 of the hydraulic booster 2.
- the valve member 6 is not in contact with the spring element.
- the valve according to the invention is used in particular in a common rail injector. Furthermore, a diaphragm spring or a plate spring or a helical spring can be used as the spring element 8.
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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
Description
Ventil zum Steuern von FlüssigkeitenValve for controlling liquids
Stand der TechnikState of the art
Die vorliegende Erfindung betrifft ein Ventil zum Steuern von Flüssigkeiten gemäß dem Oberbegriff des Patentanspruchs 1.The present invention relates to a valve for controlling liquids according to the preamble of patent claim 1.
Ventile zum Steuern von Flüssigkeiten sind in verschiedensten Ausgestaltungen bekannt. Beispielsweise ist in Figur 2 ein Ventil 1 zum Steuern von Flüssigkeiten dargestellt, welches einen hydraulischen Übersetzer 2 aufweist, der einen ersten Kolben 3, einen zweiten Kolben 4, sowie einen zwischen den beiden Kolben 3 , 4 angeordneten Druckraum 5 aufweist . Der erste Kolben 3 ist über einen Betätigungskolben 10 durch ein Piezoelement (nicht dargestellt) betätigbar. Der zweite Kolben 4 steht über einen Stößel 9 mit einer Ventilkugel 6 in Verbindung, welche mittels einer Feder 8 an einen Ventilsitz 7 gedrückt wird. Bei einer Betätigung des Piezoaktors wird über den hydraulischen Übersetzer 2 und den Stößel 9 die VentilkugelValves for controlling liquids are known in a wide variety of configurations. For example, a valve 1 for controlling liquids is shown in FIG. 2, which has a hydraulic intensifier 2, which has a first piston 3, a second piston 4, and a pressure chamber 5 arranged between the two pistons 3, 4. The first piston 3 can be actuated via an actuating piston 10 by a piezo element (not shown). The second piston 4 is connected via a tappet 9 to a valve ball 6 which is pressed against a valve seat 7 by means of a spring 8. When the piezo actuator is actuated, the valve ball is moved via the hydraulic intensifier 2 and the plunger 9
6 vom Ventilsitz 7 abgehoben und dadurch ein Druckanstieg in einem Einspritzbereich einer Ventilnadel bereitgestellt, um die Ventilnadel von einer Einspritzöffnung abzuheben und Kraftstoff in einen Verbrennungsraum zuzuführen (nicht gezeigt) . Nach dem Abstellen eines Motors wird die Kugel 6 durch die Federkraft der Feder 8 wieder an den oberen Ventilsitz 7 gedrückt, und verbleibt in dieser Position bis zu einem Neustart des Motors. Da, wie in Figur 2 gezeigt, ein Volumen 11 im Bereich der Ventilkugel 6 in Folge der Position der Ventilkugel 6 am oberen Ventilsitz 7 relativ groß ist, ist die Funktion des Injektors teilweise eingeschränkt, da gewisse Verzögerungen bei der Betätigung auftreten. Um ein kleines Volumen 11 bereitzustellen, muß auf ungünstige Federausführungen zurückgegriffen werden, welche einen komplizierten Aufbau aufweisen und zu erhöhten Kosten führen. Weiter muß die Ventilkugel 6 in ihrem unteren Bereich mit einer Federaufnahme 18 ausgebildet sein. Auch dies erhöht die Herstellungskosten. Da die Feder 8 im Hochdruckbereich des Ventils 1 angeordnet ist, wird sie auch ständig hohen Druckbelastungen ausgesetzt, was zu einer verringerten Lebensdauer der Feder 8 führen kann.6 is lifted from the valve seat 7, thereby providing a pressure increase in an injection region of a valve needle in order to lift the valve needle from an injection opening and to supply fuel into a combustion chamber (not shown). After switching off an engine, the ball 6 pressed against the upper valve seat 7 by the spring force of the spring 8, and remains in this position until the engine is restarted. Since, as shown in FIG. 2, a volume 11 in the region of the valve ball 6 is relatively large due to the position of the valve ball 6 on the upper valve seat 7, the function of the injector is partially restricted, since certain delays occur during actuation. In order to provide a small volume 11, unfavorable spring designs have to be used, which have a complicated structure and lead to increased costs. Furthermore, the valve ball 6 must be designed with a spring seat 18 in its lower region. This also increases the manufacturing costs. Since the spring 8 is arranged in the high-pressure region of the valve 1, it is also constantly exposed to high pressure loads, which can lead to a reduced service life of the spring 8.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Ventil zum Steuern von Flüssigkeiten mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß das Federelement direkt mit dem zweiten Kolben des hydraulischen Übersetzers gekoppelt ist. Mit anderen Worten ist das Federelement unmittelbar am zweiten Kolben angeordnet. Dadurch kann das VentilgliedThe valve according to the invention for controlling liquids with the features of claim 1 has the advantage that the spring element is directly coupled to the second piston of the hydraulic translator. In other words, the spring element is arranged directly on the second piston. This allows the valve member
(Ventilschließelement) vom Federelement beabstandet angeordnet werden. Durch diese Trennung des Federelements von dem Ventilglied ist es möglich, ein sehr kleines Volumen im Bereich des Ventilglieds ohne aufwendige bauliche Maßnahmen bereitzustellen. Weiter kann auch das Ventilglied einfach und kostengünstig hergestellt werden, da es keine aufwendig herzustellenden Aufnahmen bzw. Federsitze für das Federelement aufweisen muß. Desweiteren ist das Federelement erfindungsgemäß im Niederdruckbereich des Ventils angeordnet. Daher kann der Einbauraum für das Federelement groß ausgelegt werden; letzteres weist eine lange Lebensdauer auf .(Valve closing element) are arranged spaced from the spring element. This separation of the spring element from the valve member makes it possible to provide a very small volume in the region of the valve member without complex structural measures. Furthermore, the valve member can also be produced simply and inexpensively, since it does not have to have receptacles or spring seats for the spring element that are expensive to produce. Furthermore, the spring element is arranged according to the invention in the low pressure region of the valve. Therefore, the installation space for the spring element be designed large; the latter has a long lifespan.
Vorzugsweise ist der zweite Kolben des hydraulischen Übersetzers zweiteilig ausgebildet. Dies ermöglicht es, daß ein erster Teil des zweiteiligen Kolbens als Standardteil ausgebildet sein kann, welches z.B. hohe Toleranzanforderungen an den Durchmesser erfüllt. Ein zweiter Teil des Kolbens kann dann entsprechend für eine optimale Kopplung mit dem Federelement ausgebildet sein.The second piston of the hydraulic translator is preferably constructed in two parts. This enables a first part of the two-part piston to be designed as a standard part, e.g. meets high tolerance requirements for the diameter. A second part of the piston can then be designed accordingly for optimal coupling with the spring element.
Vorzugsweise weist der zweiteilige Kolben ein zylindrisches Element und ein Stößelelement auf. Dadurch kann für das zylindrische Element ein Standardteil wie z.B. Wälzlagerrollen oder ähnliches verwendet werden. DasThe two-part piston preferably has a cylindrical element and a plunger element. This means that a standard part such as e.g. Rolling bearing rollers or the like can be used. The
Stößelelement kann dann an das Federelement angepaßt werden. Hierbei ist es möglich, daß das Stößelelement einstückig mit einem Stößel zur Betätigung der Ventilkugel ausgebildet ist. Es ist jedoch auch möglich, das Stößelelement als scheibenförmiges Element auszubilden. Hierbei ist dann ein Stößel für eine Betätigung des Ventilglieds als separates Element ausgebildet.Tappet element can then be adapted to the spring element. It is possible that the tappet element is integrally formed with a tappet for actuating the valve ball. However, it is also possible to design the plunger element as a disk-shaped element. A plunger for actuating the valve member is then formed as a separate element.
Vorzugsweise weist das Federelement eine Öffnung auf, um den Stößel zur Betätigung des Ventilglieds zu führen. Beispielsweise kann hierbei das Federelement als Membranfeder oder als Tellerfeder oder als Schraubenfeder ausgebildet sein.The spring element preferably has an opening in order to guide the tappet for actuating the valve member. For example, the spring element can be designed as a diaphragm spring or as a plate spring or as a coil spring.
Gemäß einer bevorzugten Ausgestaltung der vorliegendenAccording to a preferred embodiment of the present
Erfindung ist das Ventil als einfach schaltendes Ventil oder als doppelt schaltendes Ventil ausgebildet. Hierbei weist das Ventil bei einem einfach schaltenden Ventil nur einen Ventilsitz auf, an welchem das Ventilglied anliegt oder abgehoben ist. Bei einem doppelt schaltenden Ventil sind zwei Ventilsitze vorgesehen, wobei das Ventilglied entweder an dem einen Ventilsitz oder dem anderen Ventilsitz anliegt oder eine Zwischenstellung einnimmt, in der beide Ventilsitze geöffnet sind.Invention, the valve is designed as a single switching valve or as a double switching valve. In the case of a single-switching valve, the valve here has only one valve seat against which the valve member bears or is lifted off. With a double switching valve Two valve seats are provided, the valve member either resting on one valve seat or the other valve seat or occupying an intermediate position in which both valve seats are open.
Vorzugsweise wird das erfindungsgemäße Ventil bei einem Common-Rail-Injektor verwendet. Hierdurch können insbesondere die durch die hohen Drücke auftretenden Belastungen der Ventilteile umgangen werden.The valve according to the invention is preferably used in a common rail injector. In this way, in particular the loads on the valve parts caused by the high pressures can be avoided.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:An embodiment of the invention is shown in the drawing and explained in more detail in the following description. Show it:
Figur 1 ein Ventil zum Steuern von Flüssigkeiten gemäß einem ersten Ausführungsbeispiel der vorliegenden Erfindung und1 shows a valve for controlling liquids according to a first embodiment of the present invention and
Figur 2 ein Ventil zum Steuern von Flüssigkeiten gemäß dem Stand der Technik.Figure 2 shows a valve for controlling liquids according to the prior art.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In Figur 1 ist ein erfindungsgemäßes Ventil zum Steuern von Flüssigkeiten dargestellt, welches als Kraftstoffeinspritz- ventil verwendet wird. Das Ventil 1 umfaßt einen Halter 16, ein Ventilstück 17, eine Zwischenscheibe 19 und einen Düsenkörper 20, welche über eine Düsenspannmutter 22 miteinander verbunden sind. Weiter umfaßt das Ventil 1 einen hydraulischen Übersetzer 2, welcher einen ersten Kolben 3, einen zweiten Kolben 4 und einen zwischen den beiden Kolben 3 , 4 angeordneten Druckraum 5 auf eist . Der zweite Kolben 4 steht über einem Stößel 9 mit einem als Kugel ausgebildeten Ventilglied 6 in Verbindung. Die Ventilkugel 6 ist derart ausgelegt, daß sie an einem oberen Ventilsitz 7 und einem unteren Ventilsitz 12 anlegbar ist.FIG. 1 shows a valve according to the invention for controlling liquids, which is used as a fuel injection valve. The valve 1 comprises a holder 16, a valve piece 17, an intermediate disk 19 and a nozzle body 20 which are connected to one another via a nozzle clamping nut 22. Furthermore, the valve 1 comprises a hydraulic booster 2, which has a first piston 3, a second piston 4 and a pressure chamber 5 arranged between the two pistons 3, 4. The second piston 4 is connected via a tappet 9 to a valve member 6 designed as a ball. The valve ball 6 is such designed that it can be placed on an upper valve seat 7 and a lower valve seat 12.
Wie in Figur 1 gezeigt, ist der erste Kolben 3 des hydraulischen Übersetzers in einem Aufnahemkörper 15 angeordnet, welcher im Halter 16 fest positioniert ist. Der zweite Kolben 4 des hydraulischen Übersetzers ist zum ersten Kolben 3 axial versetzt angeordnet. Weiter ist im Düsenkörper 20 eine Ventilnadel 21 angeordnet, welche eine Einlaßöffnung öffnet und verschließt, durch die Kraftstoff in einen Verbrennungsraum eingespritzt wird (nicht dargestellt) .As shown in FIG. 1, the first piston 3 of the hydraulic translator is arranged in a receiving body 15 which is firmly positioned in the holder 16. The second piston 4 of the hydraulic translator is arranged axially offset from the first piston 3. Furthermore, a valve needle 21 is arranged in the nozzle body 20, which opens and closes an inlet opening through which fuel is injected into a combustion chamber (not shown).
Im vorliegenden Ausführungsbeispiel ist der zweite Kolben 4 des hydraulischen Übersetzers 2 zweiteilig ausgebildet. Der zweite Kolben 4 besteht aus einem zylindrischen Bolzen 4a und einem Druckstößel 4b. Durch diese Ausgestaltung ist es möglich, daß der zylindrische Bolzen 4a einen einfachen Aufbau aufweist und somit hohe Anforderungen an Toleranzen o.a. erfüllen kann. Auch ist dadurch die Verwendung vonIn the present exemplary embodiment, the second piston 4 of the hydraulic translator 2 is formed in two parts. The second piston 4 consists of a cylindrical pin 4a and a pressure ram 4b. With this configuration, it is possible that the cylindrical bolt 4a has a simple structure and thus high demands on tolerances or the like. can meet. This also means the use of
Standardteilen für den zylindrischen Bolzen 4a möglich. Der Druckstößel 4b grenzt unmittelbar an den zylindrischen Bolzen 4a an. Weiter ist der Druckstößel 4b direkt mit einem Federelement 8 gekoppelt. Das Federelement 8 weist eine mittlere Öffnung auf, um den Stößel 9 zu führen. Weiter ist das Federelement 8 derart ausgebildet, daß es den Druckstößel 4b gegen den zylindrischen Bolzen 4a drückt. Wenn nun bei dem Ventil gemäß dem dargestellten Aus- führungsbeispiel der Motor eines Kraftfahrzeugs abgestellt wird, wird der zweite Kolben 4 infolge der Federkraft der Feder 8 in den Druckraum 5 gedrückt, da das im Druckraum 5 befindliche Fluid über Leckspalte 13 und 14 an den beiden Kolben 3 und 4 entweicht . Da die Ventilkugel 6 nicht mit Federkraft beaufschlagt ist, liegt diese Undefiniert an unteren Sitz 12 an. Bei einem Neustart des Motors wird nun die relativ leichte Ventilkugel 6 durch die Hydraulikkräfte nach oben, d.h. in Richtung des hydraulischen Übersetzers 2 gedrückt . Infolge des geringen Gewichts der Ventilkugel 6 läuft dieser Vorgang sehr schnell ab, wodurch das Ventil am Sitz 7 abdichtet. Da sich der zweite Kolben 4 im Bereich des Druckraums 5 des hydraulischen Übersetzers befindet, wird dieser Vorgang auch nicht durch den zweiten Kolben 4 behindert .Standard parts for the cylindrical bolt 4a possible. The pressure ram 4b directly adjoins the cylindrical bolt 4a. Furthermore, the pressure tappet 4b is directly coupled to a spring element 8. The spring element 8 has a central opening in order to guide the plunger 9. Furthermore, the spring element 8 is designed such that it presses the pressure ram 4b against the cylindrical bolt 4a. If the engine of a motor vehicle is now switched off in the valve according to the exemplary embodiment shown, the second piston 4 is pressed into the pressure chamber 5 due to the spring force of the spring 8, since the fluid in the pressure chamber 5 passes through leakage gaps 13 and 14 at the two Pistons 3 and 4 escape. Since the valve ball 6 is not acted upon by spring force, it lies against the lower seat 12 undefined. When the engine is restarted the relatively light valve ball 6 is pushed upwards by the hydraulic forces, ie in the direction of the hydraulic translator 2. Due to the low weight of the valve ball 6, this process takes place very quickly, as a result of which the valve seals on the seat 7. Since the second piston 4 is located in the area of the pressure chamber 5 of the hydraulic booster, this process is not hampered by the second piston 4 either.
Gleichzeitig mit dem Start des Motors wird auch derAt the same time as the engine starts, the
Druckraum 5 des hydraulischen Übersetzers wieder mit Fluid befüllt . Im Vergleich zur Bewegung der Ventilkugel 6 ist diese Befüllung jedoch ein relativ langsamer Vorgang. Daher bewegt sich der zweite Kolben 4 erst nach einer gewissen Zeit in Richtung der Ventilkugel 6. Das Ventil ist jedoch erst betriebsbereit, wenn sich der zweite Kolben 4 über den Stößel 9 mit der Ventilkugel 6 in Kontakt befindet .Pressure chamber 5 of the hydraulic translator is filled with fluid again. Compared to the movement of the valve ball 6, however, this filling is a relatively slow process. The second piston 4 therefore only moves in the direction of the valve ball 6 after a certain time. However, the valve is only ready for operation when the second piston 4 is in contact with the valve ball 6 via the tappet 9.
Erfindungsgemäß ermöglicht somit die Anordnung des Feder- elements 8 unmittelbar am zweiten Kolben 4 des hydraulischen Übersetzers 2, daß ein Volumen 11 im Bereich der Ventilkugel 6 sehr klein ausgeführt sein kann. Weiter wird damit erreicht, daß das Federelement 8 im Niederdruckbereich des Ventils liegt. Auch ist es nicht notwendig, eine mit Federaufnahmeflächen oder Federsitzen aufwendig herzustellende Ventilkugel zu verwenden. Dadurch werden die Herstellungskosten des erfindungsgemäßen Ventils gesenkt und die Einzelteile des Ventils können einfache Bauformen aufweisen. Hierdurch ergeben sich auch Vorteile hinsichtlich einer schnellen und kostengünstigen Montage.According to the invention, the arrangement of the spring element 8 directly on the second piston 4 of the hydraulic booster 2 enables a volume 11 in the region of the valve ball 6 to be made very small. It is also achieved that the spring element 8 is in the low pressure region of the valve. It is also not necessary to use a valve ball that is expensive to manufacture with spring receiving surfaces or spring seats. As a result, the manufacturing costs of the valve according to the invention are reduced and the individual parts of the valve can have simple designs. This also has advantages with regard to quick and inexpensive installation.
Zusammenfassend wurde insoweit ein Ventil 1 zum Steuern von Flüssigkeiten beschrieben, welches einen Piezoaktor und einen hydraulischen Übersetzer 2 umfaßt. Der hydraulische Übersetzer 2 weist einen ersten Kolben 3, einen zweiten Kolben 4 und einen zwischen den beiden Kolben 3, 4 angeordneten Druckraum 5 auf. Weiter ist ein Ventilglied 6 und ein Federelement 8 vorgesehen. Das Federelement 8 ist mit dem zweiten Kolben 4 des hydraulischen Übersetzers 2 direkt gekoppelt. Dabei befindet sich das Ventilglied 6 nicht mit dem Federelement in Kontakt .In summary, a valve 1 for controlling liquids has been described, which comprises a piezo actuator and a hydraulic booster 2. The hydraulic translator 2 has a first piston 3, a second Piston 4 and a pressure chamber 5 arranged between the two pistons 3, 4. A valve member 6 and a spring element 8 are also provided. The spring element 8 is directly coupled to the second piston 4 of the hydraulic booster 2. The valve member 6 is not in contact with the spring element.
Das erfindungsgemäße Ventil findet insbesondere in einem Common-Rail-Injektor Anwendung. Weiter kann als Federelement 8 beispielsweise eine Membranfeder oder eine Tellerfeder oder eine Schraubenfeder verwendet werden.The valve according to the invention is used in particular in a common rail injector. Furthermore, a diaphragm spring or a plate spring or a helical spring can be used as the spring element 8.
Die vorhergehende Beschreibung des Ausführungsbeispiels gemäß der vorliegenden Erfindung dient nur zur Illustrationszwecken und nicht zum Zwecke der Beschränkung der Erfindung. Im Rahmen der Erfindung sind verschiedene Änderungen und Modifikationen möglich, ohne den Umfang der Erfindung sowie ihre Äquivalente zu verlassen. The preceding description of the exemplary embodiment according to the present invention is only for the purpose of illustration and not for the purpose of restricting the invention. Various changes and modifications are possible within the scope of the invention without leaving the scope of the invention and its equivalents.
Claims
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2000129297 DE10029297A1 (en) | 2000-06-14 | 2000-06-14 | Valve for controling liquids has piezo actuator, dual piston hydraulic converter, valve closure element and spring element directly coupled to second piston of hydraulic converter |
| DE10029297.6 | 2000-06-14 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2001096732A1 true WO2001096732A1 (en) | 2001-12-20 |
Family
ID=7645703
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/DE2001/001327 Ceased WO2001096732A1 (en) | 2000-06-14 | 2001-04-05 | Valve for regulating fluids |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE10029297A1 (en) |
| WO (1) | WO2001096732A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10122245A1 (en) * | 2001-05-08 | 2002-12-12 | Bosch Gmbh Robert | Leakage-reduced pressure-controlled fuel injector |
| DE10250720A1 (en) * | 2002-10-31 | 2004-05-13 | Robert Bosch Gmbh | Injector |
| JP4428357B2 (en) | 2006-04-03 | 2010-03-10 | 株式会社デンソー | Fuel injection valve |
| DE102006037175A1 (en) * | 2006-08-09 | 2008-02-14 | Robert Bosch Gmbh | An automotive fuel injection valve has concentric spring with elastic side-extensions subjected to lateral shift |
| DE102015211705A1 (en) * | 2015-06-24 | 2016-12-29 | Robert Bosch Gmbh | Fuel injector with control valve |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0816670A1 (en) * | 1996-07-02 | 1998-01-07 | Siemens Automotive Corporation | Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke |
| WO1999015783A1 (en) * | 1997-09-24 | 1999-04-01 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE59010904D1 (en) * | 1990-09-25 | 2000-05-31 | Siemens Ag | Arrangement for an adaptive, mechanical tolerance compensation acting in the stroke direction for the displacement transformer of a piezoelectric actuator |
| DE4306073C1 (en) * | 1993-02-26 | 1994-06-01 | Siemens Ag | Metering system for dosing of fluids with injection valve for IC engine - has piston acting on closing unit, and spring with actuator acting on large dia. piston moving in cylinder |
| DE19732802A1 (en) * | 1997-07-30 | 1999-02-04 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
| DE19813983A1 (en) * | 1998-03-28 | 1999-09-30 | Bosch Gmbh Robert | Valve for controlling liquids |
| DE19821768C2 (en) * | 1998-05-14 | 2000-09-07 | Siemens Ag | Dosing device and dosing method |
| DE19839125C1 (en) * | 1998-08-27 | 2000-04-20 | Siemens Ag | Device and method for dosing fluid |
-
2000
- 2000-06-14 DE DE2000129297 patent/DE10029297A1/en not_active Ceased
-
2001
- 2001-04-05 WO PCT/DE2001/001327 patent/WO2001096732A1/en not_active Ceased
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0816670A1 (en) * | 1996-07-02 | 1998-01-07 | Siemens Automotive Corporation | Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke |
| WO1999015783A1 (en) * | 1997-09-24 | 1999-04-01 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10029297A1 (en) | 2001-10-18 |
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