EP2580462B1 - Soupape d'injection dotée d'une commande directe et d'une servocommande - Google Patents

Soupape d'injection dotée d'une commande directe et d'une servocommande Download PDF

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Publication number
EP2580462B1
EP2580462B1 EP11724213.1A EP11724213A EP2580462B1 EP 2580462 B1 EP2580462 B1 EP 2580462B1 EP 11724213 A EP11724213 A EP 11724213A EP 2580462 B1 EP2580462 B1 EP 2580462B1
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EP
European Patent Office
Prior art keywords
valve
drive component
deflection
valve needle
electric drive
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.)
Not-in-force
Application number
EP11724213.1A
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German (de)
English (en)
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EP2580462A1 (fr
Inventor
Attila Reimer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Automotive GmbH
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Continental Automotive GmbH
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Publication date
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Publication of EP2580462A1 publication Critical patent/EP2580462A1/fr
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Publication of EP2580462B1 publication Critical patent/EP2580462B1/fr
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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
    • 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
    • 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
    • F02M45/08—Injectors 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic 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
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid 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
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-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
    • 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
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
    • F02M2200/702—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to a valve device for conveying lubricating and non-lubricating liquids, in particular for use in the field of fuel injection in an internal combustion engine.
  • the valve device has a two-stage drive device which comprises both an electric direct drive and a hydraulic servo drive.
  • the servo drive can be switched on in addition to the direct drive, if a larger valve needle stroke is needed.
  • Valve devices are used to convey or distribute a wide variety of liquids.
  • Such valve devices may for example be designed as so-called injectors, in which the opening of an injection nozzle is controlled very precisely by means of a valve needle.
  • injectors With the aid of a modern injection valve, even the smallest amounts of liquid can be accurately portioned. This accuracy is needed, for example, in internal combustion engines, where fuel is injected by means of appropriate fuel injectors under high pressure in the combustion chamber. The fuel supply must be done in exactly predetermined conditions and at predetermined times.
  • the fuel injection valve of a modern internal combustion engine generally performs multiple injections, wherein the amount of fuel used is varied depending on the injection phase. Thus, typically relatively small amounts of fuel are injected for pre-injection, while in the main injection relatively large amounts of fuel are carried into the combustion chamber.
  • the range of fuel required in each phase of fuel injection in an internal combustion engine represents an important criterion in the construction of a suitable injection valve.
  • the provided for movement of the valve needle drive means must be designed large enough to ensure the required during the main injection maximum needle stroke.
  • the valve needle must also be able to be controlled sufficiently quickly and precisely in order to allow optimum injection of small or smallest amounts of fuel during the pre-injection.
  • a drive device typically used for the deflection of the valve needle therefore has an electric drive means, such.
  • the actuator acts as a direct drive
  • the valve needle is deflected due to a mechanical contact with components of the drive immediately following the deflection or expansion of the actuator from its closed position. Therefore, the direct drive allows particularly fast switching times and exact controllability, especially in combination with a closed-loop control.
  • the switching path feasible with it is limited to the maximum deflection of the actuator. For a piezo stack, for example, these are only about 60 to 70 microns. However, such a small needle stroke is unfavorable to promote larger amounts of liquid.
  • a more complex structure of the direct drive is necessary, which is reflected among other things in higher production costs.
  • hydraulic drive devices can also be used.
  • this drive concept utilizing the different pressure conditions within the valve device, a hydraulic force is generated which effects the deflection of the valve needle.
  • the deflection of the valve needle takes place in ballistic flight, which allows a much larger compared to the electric direct drive needle stroke becomes.
  • the possibilities of a closed-loop control and thus the precise injection of very small amounts of liquid in this drive concept are significantly limited.
  • a generic valve device is in the DE 10 2005 041 994 shown.
  • the valve device for conveying a liquid has a housing, a valve needle which is arranged deflectably in a valve needle chamber of the housing, and a drive device for the valve needle.
  • the drive device comprises an electrical drive component, which causes a direct deflection of the valve needle and a hydraulic drive component which can be activated in addition to the electric drive component and causes a ballistic deflection of the valve needle.
  • the drive device is designed to effect the activation of the hydraulic drive component by the electric drive component. This allows automatic activation of the hydraulic drive component.
  • the two modes of operation “pure electric operation” and “mixed operation”, are controlled only by the means used to control the electric drive component, a simplified and therefore also inexpensive construction is made possible.
  • the hydraulic drive component is designed as a servo valve, which connects the valve needle chamber with a low-pressure channel, wherein the servo valve comprises a valve element, which is transferred by the deflection of the electric drive component from a closed position to an open position.
  • servo valves allow a relatively large needle stroke.
  • the direct activation of the valve element by the deflection of the electric drive component allows the realization of a particularly simple automatic activation of the hydraulic drive component.
  • a further embodiment provides that the deflection of the electric drive component leads to activation of the hydraulic drive component only after overcoming an activation threshold, wherein the activation threshold is predetermined by a tolerance in the mechanical transmission path from the electric drive component to the valve element.
  • the mechanical transmission path from the electric drive component to the valve element comprises at least one mechanical transmission element with the aid of which the deflection of the electric drive component is transmitted to the valve element of the hydraulic drive component.
  • the use of mechanical transmission elements allows an optimization of the transmission of the movement of the electric drive to the valve element and thus the opening behavior of the valve element.
  • tolerances can be realized particularly easily with mechanical transmission elements which enable activation of the hydraulic component only after overcoming a predetermined needle stroke.
  • a further embodiment provides that the transmission element is formed pin-shaped. This allows a direct and therefore simple transmission the movement of the electric drive to the valve element.
  • a further embodiment provides that the mechanical transmission path comprises a lifting-shaped transmission element, which is actuated by the pin-shaped transmission element.
  • the deflection of the electric drive component can be arbitrarily converted into a movement for activating the valve element.
  • the direction of movement can be reversed, so that the valve element is opened counter to the deflection direction of the electric drive component.
  • a further embodiment provides that a tolerance is provided between the two transmission elements, which allows a deflection of the valve needle by a predetermined distance, without an activation of the hydraulic drive component takes place. This makes it possible to realize in a simple manner, an automatic activation of the hydraulic drive component, which only from a predetermined Needle stroke, that is done only after overcoming an activation threshold.
  • the electric drive component comprises a piezoelectric element, which causes the desired deflection when an electrical voltage is applied.
  • piezoelectric elements have a fast response, which is why they can be optimally used for precise control of the valve needle, in particular in combination with a suitable control. This is particularly advantageous when injecting the smallest amounts of liquid. Furthermore, piezoelectric elements can be produced relatively inexpensively.
  • the electric drive component is operated by means of a closed-loop control.
  • the precision of the valve needle control can be significantly increased.
  • valve device is designed as an injection valve for injecting fuel into a combustion chamber of an internal combustion engine. Due to the combined properties of the two drive concepts, the valve device according to the invention is particularly suitable for the pre-injection and the main injection in an internal combustion engine.
  • the needle stroke of the combined drive which is increased compared with the purely electric drive, also enables a more favorable nozzle needle angle, which can have a positive effect on the combustion parameters.
  • the FIG. 1 shows a valve device 100 according to the invention for the promotion of lubricating and non-lubricating fluids.
  • the valve device shown here is preferably a fuel injection valve for an internal combustion engine of a motor vehicle.
  • the injection valve 100 comprises a housing 110.
  • the generally multi-part housing comprises an upper and a lower housing part 111, 112, wherein the distribution of the housing may vary depending on the application.
  • the valve device 100 further comprises a valve needle 120 arranged in a valve needle chamber 113 in the interior of the housing 110.
  • the valve needle 120 controls an injection nozzle (not shown here) provided in the lower part of the housing 110, through which high-pressure fuel is discharged into the combustion chamber , The supply of the fuel takes place via a high pressure passage 116 running in the housing 110.
  • the valve needle 120 is movably mounted in the axial direction and typically comprises a shaft-shaped section 121, at the lower end of which a valve needle tip 125 serving as a closure element for the opening of the injection nozzle is formed.
  • the valve needle 120 is typically held in its valve seat by spring force.
  • a helical compression spring 130 is provided, which accommodates in a spring chamber 150 formed by a part of the valve needle chamber 113 is.
  • the pressure spring 130 attached to a collar-shaped valve needle part 124 exerts a downward pressure on the valve needle 120. To open the injection valve, the valve needle 120 is therefore deflected against the spring force of the compression spring 130 upwards.
  • a drive device 200 is provided, which is preferably integrated in the housing 110 of the valve device 100.
  • the drive device 200 comprises an electric drive component 210, which serves as a direct drive.
  • any suitable electrically operated actuator in question using electrical signals such. B. current or voltage pulses is controlled.
  • injectors are often made of piezoelectric materials existing actuators, in which a change in the voltage applied thereto leads to an expansion or contraction.
  • piezoelectric actuators are typically manufactured as so-called piezo-stacks which are formed from a plurality of piezoelectric layers arranged one above the other.
  • electromagnetic actuators are used in which the desired deflection is effected by applying corresponding current pulses.
  • the electric drive component is formed by a piezo stack 210.
  • the accommodated in an inner housing chamber piezo stack 210 is cylindrical and has a central bore 211 for receiving the shaft-shaped portion 121 of the valve needle 120.
  • the piezo stack 210 does not completely fill the inner housing chamber, whereby a pressure chamber 114 for receiving a plate structure 121 of the valve needle 120 is formed above the piezo stack 210.
  • the plate structure 121 forms the upper end of the valve needle 120 and is connected to the shaft-shaped valve needle part 121 which extends within the bore 211.
  • On the cylindrical piezo stack 210 is a disk-shaped ring member 212, which serves to support the valve needle plate 121.
  • valve needle pad 122 will be dislodged from the ring member located thereunder 212 entrained, whereby the valve needle 120 deflected against the force of the compression spring 130 and the nozzle opening is released. Due to the mechanical contact between piezo stack 210, ring element 212 and valve needle plate 122 during deflection, the valve needle 120 reacts directly to the movement of the piezo stack 210. Thus, in particular in combination with a closed-loop control, a very fast and precise control of the valve needle 120th possible. However, the deflection of the valve needle 120 in pure direct operation is limited by the maximum deflection of the piezo stack 210.
  • the drive device 200 therefore additionally has a hydraulic drive 220, which in the present case is designed as a servo valve connecting the pressure chamber 114 with a low-pressure passage 117.
  • Servo valve 220 comprises a conical valve element 221 which closes a likewise conically shaped valve opening in the upper ceiling element of pressure chamber 114.
  • To open the servo valve 220 is an arranged in a side chamber 118 of the low pressure passage 117 arcuate lever member 223, which attaches to the valve element 221 and is actuated by means of a pin-shaped transmission element 213.
  • the pin-shaped transmission element 213 is arranged guided in a bore of the upper ceiling element of the pressure chamber 114 and lies with its lower end on the ring element 212.
  • a corresponding opening with sufficient tolerance to the pin-shaped transmission element 213 is provided in the plate-shaped end element 122 of the valve needle 120.
  • the two transmission elements 213, 223 are preferably formed so that they do not touch in the closed state of the valve device 200 and the actuation of the arcuate transmission element 223 thus takes place only after overcoming a predetermined by their distance 214 route. This ensures that the hydraulic drive component 220 is activated only after overcoming an activation threshold, ie only from a greater deflection of the valve needle 120 by means of the piezo stack 210 becomes. With the aid of the gap 214 formed between the two transmission elements 213, 223, an activation threshold of the hydraulic drive component 220 is thus realized.
  • the gap width determines the maximum Ventilnadelhub, which can be done without the connection of the hydraulic drive 220.
  • a corresponding activation threshold can also be realized by means of appropriate tolerances at other points of the mechanical transmission path comprising the two transmission elements 213, 223 from the electric drive component 210 to the valve element 221.
  • FIG. 2 a section of the drive device 200 from the FIG. 1 .
  • the plate-shaped closing element 122 of the valve needle 120 is not located directly on the ring element 212. Rather, both elements are separated by a small gap, by which a so-called idle stroke is defined. Only after overcoming the idle stroke, the two elements come into contact with each other (not shown here).
  • the FIG. 2 represents the initial situation in which the valve needle 120 is pressed into the valve seat with the force of the compression spring 130 and thus keeps the injection nozzle closed.
  • valve needle chamber 113 communicates hydraulically with the high-pressure passage 116, the high fuel pressure prevails in the pressure chamber 114 at this time. Since the servo valve 220 is still closed, the pressure conditions in the entire pressure chamber 114, ie, above and below the plate-shaped closing element 122 of the valve needle 120, are substantially balanced.
  • the piezoelectric actuator 210 By driving the direct drive, which takes place in the present example by applying a corresponding electrical voltage to the piezo stack, the piezoelectric actuator 210 expands in the direction of the valve needle plate 122. After overcoming the Leerhubs the valve needle plate 122 is taken from the ring member 212, resulting in a deflection of the valve needle 120 from its rest position. A similar situation is in the FIG. 3 shown. It can be seen that a small deflection of the valve needle 120, the gap width 214 between the two transmission elements 213, 223 reduced without the servo valve 220 is activated. Therefore, by applying a correspondingly small voltage to the piezoelectric stack 210, a precise opening of the injection valve can be effected in order, for example, to inject a smallest amount of fuel into the combustion chamber during the pre-injection.
  • the sudden pressure drop in the upper part of the pressure chamber 114 causes a force acting on the valve needle plate 122 and consequently on the entire valve needle 120 in the direction of the pressure gradient.
  • the valve needle plate 122 lifts off from the ring element 212 and, together with the entire valve needle 120, returns a path dependent on the respective hydraulic parameters in ballistic flight.
  • the significantly greater deflection of the valve needle 120 during the ballistic flight phase produces a correspondingly large opening of the injection nozzle, whereby a larger amount of liquid is conveyed. Therefore, this hydraulically assisted mode of operation is particularly suitable good for fuel injection during the main injection phase of an internal combustion engine.
  • the valve needle is pushed back by the compression spring 130 in the direction of the valve opening and the injection valve is closed again.
  • This process can be influenced by premature closing of the servo valve 220, which can be effected by a corresponding contraction of the piezo stack 210.
  • the valve element 221 is pressed by the prevailing between the pressure chamber 114 and low pressure passage 117 pressure difference back into its valve seat, whereby the pressure drop across the low pressure passage 117 is stopped abruptly.
  • the closing process can be assisted by means of a spring element which presses the valve element 221 into its valve seat (not shown here).
  • FIG. 5 shows a further alternative embodiment of the valve device 100 according to the invention, in which the valve needle 120 is also hydraulically assisted in a ballistic flight is transferred as soon as the deflection of the valve needle 120 exceeds a predetermined needle stroke.
  • the electric drive component 210 is substantially analogous to the corresponding drive component of the FIGS. 1 to 4 educated.
  • the servo valve of the injection valve 200 shown here is arranged such that the opening of the valve element 221 now takes place in the direction of expansion of the piezo stack 210. As a result, the deflection of the piezoelement 210 can be transmitted directly to the valve element 221 via a simple pin-shaped transmission element 224.
  • the transmission element 224 is not sitting directly on the ring member 214.
  • the gap 214 provided between the two elements 212, 224 correspondingly determines the activation threshold, that is to say the maximum distance by which the valve needle 120 only by means of the direct drive 210 without the assistance by the hydraulic drive component 220 can be deflected.
  • the activation threshold is reached, contact of the ring element 212 with the transmission element 224 occurs, which, in the case of a further deflection of the piezo stack 210, causes the valve element 221 to lift out of its valve seat.
  • a hydraulic connection of the pressure chamber 114 to the low-pressure passage 117 is established through the passage 119 and the servo valve 220 similar to the first embodiment.
  • FIG. 6 shows a possible injection process in which fuel is injected using the injection valve according to the invention in several individual sprays the combustion chamber of an internal combustion engine.
  • fuel 301 are already injected as part of a pre-injection, which takes place in advance of the main injection.
  • the smallest amount injection is preferably carried out in a purely electrical Berieb, the deflection of the valve needle is effected only by the direct drive.
  • the piezoelectric actuator is driven only small, so that its low deflection does not lead to the activation of the servo valve.
  • a relatively high electrical voltage is applied to the piezoelectric actuator during the subsequent main injection phase in order to achieve activation of the servo valve by the correspondingly large deflection of the piezoactuator.
  • the valve needle in ballistic flight reaches a larger needle stroke, which is noticeable in significantly larger injection quantities 302.
  • the main injections may also be followed by so-called post-injections in order to increase the energy content of the exhaust gases for the exhaust gas aftertreatment. Since in a post-injection also only very small amounts of fuel are injected into the combustion chamber, it is sufficient in this case to open the injection valve only by means of direct drive.
  • the embodiments explained with reference to the figures represent only preferred or exemplary embodiments of the invention. In addition to the described and illustrated embodiments, further embodiments are conceivable, which may comprise further modifications and combinations of features.
  • the valve device disclosed herein in connection with fuel injection may also be used to deliver or portion other lubricating or non-lubricating fluids.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (9)

  1. Dispositif à soupape (100) pour le refoulement d'un liquide, avec un boîtier (110), une aiguille de soupape (120), disposée de façon à pouvoir être déplacée dans une chambre d'aiguille de soupape (113) du boîtier (110) et un dispositif d'entraînement (200) pour l'aiguille de soupape (120),
    le dispositif d'entraînement (200) comprenant un composant d'entraînement électrique (210) qui provoque un déplacement direct de l'aiguille de soupape (120),
    le dispositif d'entraînement (200) comprenant en outre un composant d'entraînement hydraulique (220) qui peut être activé en plus du composant d'entraînement électrique (210) et provoque un déplacement balistique de l'aiguille de soupape (120), caractérisé en ce que le composant d'entraînement hydraulique (220) est conçu comme une servo-soupape qui relie la chambre d'aiguille de soupape (113) à un canal basse pression (117), la servo-soupape (220) comprenant un élément de soupape (221) qui peut être déplacée, grâce au déplacement du composant d'entraînement électrique (210), d'une position fermée vers une position ouverte et en ce que le déplacement du composant d'entraînement électrique (210) ne conduit à une activation du composant d'entraînement hydraulique (220) qu'après le dépassement d'un seuil d'activation,
    le seuil d'activation étant prédéterminé par une tolérance (214) dans la chaîne de transmission mécanique du composant d'entraînement électrique (210) vers l'élément de soupape (221).
  2. Dispositif à soupape (100) selon la revendication 1, caractérisé en ce que le dispositif d'entraînement (200) est conçu pour provoquer l'activation du composant d'entraînement hydraulique (220) par l'intermédiaire du composant d'entraînement électrique (210).
  3. Dispositif à soupape (100) selon la revendication 1 ou 2, caractérisé en ce que la chaîne de transmission mécanique du composant d'entraînement électrique (210) vers l'élément de soupape (221) comprend au moins un élément de transmission mécanique (213, 224, 232) qui transmet le déplacement du composant d'entraînement électrique (210) à l'élément de soupape (221) du composant d'entraînement hydraulique (220).
  4. Dispositif à soupape (100) selon la revendication 3, caractérisé en ce que l'élément de transmission (213, 224) présente la forme d'une tige.
  5. Dispositif à soupape (100) selon la revendication 4, caractérisé en ce que la chaîne de transmission mécanique comprend un élément de transmission en forme de levier (223) qui est actionné par l'élément de transmission en forme de tige (224).
  6. Dispositif à soupape (100) selon la revendication 5, caractérisé en ce que, entre les deux éléments de transmission (223, 224), une tolérance (214) est prévue, qui permet un déplacement de l'aiguille de soupape (120) sur un trajet prédéterminé sans qu'une activation du composant d'entraînement hydraulique (220) ait lieu.
  7. Dispositif à soupape (100) selon l'une des revendications précédentes, caractérisé en ce que le composant d'entraînement électrique (210) comprend un élément piézo-électrique qui provoque, lors de l'application d'une tension électrique, le déplacement souhaité.
  8. Dispositif à soupape (100) selon l'une des revendications précédentes, caractérisé en ce que le composant d'entraînement électrique (210) fonctionne à l'aide d'une régulation à boucle fermée.
  9. Dispositif à soupape (100) selon l'une des revendications précédentes, caractérisé en ce que le dispositif à soupape (100) est conçu comme une soupape d'injection pour l'injection de carburant dans la chambre à combustion d'un moteur à combustion.
EP11724213.1A 2010-06-14 2011-06-09 Soupape d'injection dotée d'une commande directe et d'une servocommande Not-in-force EP2580462B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010023698A DE102010023698A1 (de) 2010-06-14 2010-06-14 Einspritzventil mit Direkt- und Servoantrieb
PCT/EP2011/059542 WO2011157613A1 (fr) 2010-06-14 2011-06-09 Soupape d'injection dotée d'une commande directe et d'une servocommande

Publications (2)

Publication Number Publication Date
EP2580462A1 EP2580462A1 (fr) 2013-04-17
EP2580462B1 true EP2580462B1 (fr) 2015-12-02

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Application Number Title Priority Date Filing Date
EP11724213.1A Not-in-force EP2580462B1 (fr) 2010-06-14 2011-06-09 Soupape d'injection dotée d'une commande directe et d'une servocommande

Country Status (5)

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US (1) US9429119B2 (fr)
EP (1) EP2580462B1 (fr)
CN (1) CN102933833B (fr)
DE (1) DE102010023698A1 (fr)
WO (1) WO2011157613A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010023698A1 (de) 2010-06-14 2011-12-15 Continental Automotive Gmbh Einspritzventil mit Direkt- und Servoantrieb
CN108274701A (zh) * 2017-12-19 2018-07-13 东莞市热恒注塑科技有限公司 一种方形小间距针阀式热流道系统
DE102021114302A1 (de) 2021-06-02 2022-12-08 Vermes Microdispensing GmbH Dosiersystem

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0692743B2 (ja) 1985-04-01 1994-11-16 日本電装株式会社 流体制御用電磁弁
DK170121B1 (da) 1993-06-04 1995-05-29 Man B & W Diesel Gmbh Gliderventil og stor totakts forbrændingsmotor
DE19515508C2 (de) 1994-04-28 1999-01-28 Hitachi Ltd Verfahren und Steuervorrichtung zur Antriebssteuerung eines Fahrzeugs mit Verbrennungsmotor und Getriebe
DE19742073A1 (de) 1997-09-24 1999-03-25 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US6595436B2 (en) 2001-05-08 2003-07-22 Cummins Engine Company, Inc. Proportional needle control injector
DE10308613A1 (de) * 2003-02-27 2004-09-16 Siemens Ag Ventil mit einem Hebel, Hebel und Verfahren zur Herstellung eines Hebels
DE102005041994B4 (de) * 2005-09-05 2017-12-14 Robert Bosch Gmbh Kraftstoffinjektor mit direkt betätigbarem Einspritzventilglied und zweistufiger Übersetzung
DE102006036444A1 (de) * 2006-03-30 2007-10-04 Robert Bosch Gmbh Kraftstoffinjektor
DE102006036780A1 (de) * 2006-08-07 2008-02-21 Robert Bosch Gmbh Krafstoffinjektor mit direkter Nadelsteuerung und Servoventil-Unterstützung
DE102007026946B4 (de) * 2007-06-12 2009-06-04 Continental Automotive Gmbh Verfahren und Vorrichtung zum Betreiben eines Einspritzventils, Computerprogramm und Einspritzventil
JP4591555B2 (ja) * 2008-06-12 2010-12-01 株式会社日本自動車部品総合研究所 燃料噴射ノズルおよびそれを用いた燃料噴射制御装置
DE102008042136A1 (de) * 2008-09-16 2010-03-18 Robert Bosch Gmbh Kraftstoffinjektor mit mechanischer Übersetzung
DE102010023698A1 (de) 2010-06-14 2011-12-15 Continental Automotive Gmbh Einspritzventil mit Direkt- und Servoantrieb

Also Published As

Publication number Publication date
US9429119B2 (en) 2016-08-30
CN102933833A (zh) 2013-02-13
CN102933833B (zh) 2015-01-14
US20130200180A1 (en) 2013-08-08
DE102010023698A1 (de) 2011-12-15
EP2580462A1 (fr) 2013-04-17
WO2011157613A1 (fr) 2011-12-22

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