EP3184801A1 - Hydraulic coupler system and fuel injection valve with same - Google Patents
Hydraulic coupler system and fuel injection valve with same Download PDFInfo
- Publication number
- EP3184801A1 EP3184801A1 EP16197724.4A EP16197724A EP3184801A1 EP 3184801 A1 EP3184801 A1 EP 3184801A1 EP 16197724 A EP16197724 A EP 16197724A EP 3184801 A1 EP3184801 A1 EP 3184801A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- groove
- hydraulic coupler
- working space
- hydraulic
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—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
- F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
Definitions
- the invention relates to a hydraulic coupler device, such as is used for transmitting a movement of an electrical actuator to a movable component, and a fuel injector with such a coupler.
- coupler devices are known from the prior art, which serve to transmit the movement of an electrical actuator, for example a piezoelectric actuator or a magnetic actuator, to another movable component.
- the coupler device serves on the one hand a possible displacement or force amplification and on the other hand to compensate for tolerances between the actuator and the component to be moved.
- a fuel injection device such as a coupler, for example, from DE 103 22 672 A1 known.
- a fuel injector is described, which provides a piezoelectric actuator for opening and closing a control valve.
- a piezo actuator is very fast and can apply a high force, it can only produce a small stroke compared to its size.
- a hydraulic coupler is provided between the piezoelectric actuator and the component to be moved, which is part of a control valve.
- the hydraulic coupler comprises a primary piston and a secondary piston, between which a hydraulic working space is formed.
- the hydraulic working space is always filled with a liquid fluid.
- Gaseous fluids are generally not suitable because they are too compressible, while largely incompressible fluids can easily transfer the longitudinal movement of the primary piston to the secondary piston in the rule. It must therefore be prevented in any case that the hydraulic working space idles or is only partially filled with liquid, which is achieved in the known hydraulic coupler by leakage gaps.
- leakage gaps are formed, for example, between a surrounding sleeve and the primary piston and dimensioned such that the hydraulic working space can be filled or emptied by fuel through or out of fuel through this throttle gap with fuel when hydraulic coupler is not operated, and thus always straight is filled with fuel or a liquid working medium.
- the throttle gaps have the property that their flow resistance at a given pressure difference between both sides of the throttle gap scales with the cube of the height of the throttle gap.
- the flow through the throttle gap is correspondingly sensitive to geometric fluctuations, ie to manufacturing tolerances or to changes due to thermal expansion.
- the throttle gap must fulfill certain characteristics: On the one hand, it must not be too large, so that during the power stroke of the hydraulic coupler as possible no fuel is displaced from the hydraulic working space, because only so the hydraulic coupler transfers the movement of the piezoelectric actuator directly to the moving component.
- the throttle gaps must not be too small, so that the hydraulic working space must be filled quickly and effectively again with the liquid fluid during the operating pauses of the hydraulic coupler. Since, as already mentioned, the Flow resistance through the throttle gap is very sensitive to geometric changes, the exact production of such a hydraulic coupler is complex and thus costly.
- the hydraulic coupler according to the invention for transmitting a movement of an electrical actuator to a movable component has the advantage that the hydraulic coupler is inexpensive to manufacture and reliably controls the inflow and outflow from the hydraulic working space.
- the hydraulic coupler on a piston which is guided on a guide surface with a guide portion, so that a throttle gap remains between the guide surface and the piston.
- a groove is formed, which opens into the working space.
- the groove which can be produced in a simple manner, it is possible to provide a certain inflow cross-section whose flow cross section can easily be varied over the depth and shape of the groove.
- the hydraulic working space can be filled or emptied via the groove, whereby this flow cross section is independent of the throttle gap of the coupler.
- the throttle gap which is formed between the piston and the guide surface, can be selected as closely as possible, so that the inflow and outflow of liquid fluid into the hydraulic working space occurs exclusively or at least predominantly through the groove.
- the groove connects the hydraulic working space with a fluid space, so that an inflow or outflow of liquid fluid from the hydraulic working space is made possible. As a result, the steady filling of the hydraulic working space is reliably guaranteed.
- hydraulic working space is additionally limited by the end face of another piston.
- the further piston is guided with a guide section on a further guide surface, wherein a remaining between the other piston and the further guide surface throttle gap opens into the working space.
- the hydraulic working space can be additionally filled with fluid via this throttle gap.
- a further groove is formed in the guide section of the further piston or in the further guide surface in addition to or instead of the groove, which opens into the working space.
- the hydraulic working space can be filled via an additional groove with liquid fluid, so that the cross section of the first groove can be kept small.
- the guide section of the further piston separates the working space from a fluid space, wherein the further groove connects the fluid space and the hydraulic working space.
- the guide surface and the further guide surface are formed as holes in the same sleeve.
- the sleeve also serves to receive the piston and the other piston, so that the hydraulic working space is limited by the sleeve, the end face of the piston and another end face of the other piston. In this way, a compact design of the hydraulic coupler can be achieved, in particular a small outer diameter.
- the groove or the further groove is at least partially formed meander-shaped, whereby both grooves may have this shape.
- the flow resistance of the groove can be adjusted, since in a direct connection in the longitudinal direction of the piston or the other piston, the flow resistance to be too low can.
- they can also be at least partially helical and surround the piston or the other piston.
- the groove or the further groove can be made by means of a laser, which allows a surface treatment with the necessary precision and at low cost.
- an inventive fuel injector for high-pressure fuel injection which has a nozzle needle for opening and closing at least one injection port and having a fuel-filled control chamber, the pressure in the control chamber at least indirectly exerts a closing force on the nozzle needle.
- a control valve for connecting the control chamber with a fluid space is provided, wherein the control valve comprises a movable control valve element.
- an electric actuator which cooperates with a hydraulic coupler according to claim 1 so that the movement of the electric actuator is transmitted to the control valve member at least indirectly.
- FIG. 1 an inventive fuel injector is shown with a hydraulic coupler according to the invention.
- the fuel injector 1 is used for the injection of fuel under high pressure in a combustion chamber, not shown in the drawing of an internal combustion engine.
- a fuel tank 3 is provided, from which a fuel line 4 emanates, via which fuel is fed to a high-pressure fuel pump 5.
- the high-pressure fuel pump 5 compresses the fuel and passes it via a high-pressure line 7 to a high-pressure fuel accumulator 8, in which the compressed fuel is stored.
- the fuel injector 1 has a housing 10, which comprises a valve plate 20, a throttle plate 30, and a nozzle body 40, which abut each other in this order and are clamped by a clamping nut 42 liquid-tight against each other.
- a high-pressure line 9 emanating from the high-pressure fuel accumulator 8 opens into a high-pressure passage 12 formed in the housing 10, it also being possible for a plurality of fuel injectors to be connected to the high-pressure fuel accumulator.
- the high-pressure fuel passage 12 opens within the nozzle body 40 in a pressure chamber 18 which is formed as a longitudinal bore in the nozzle body 40.
- a longitudinally movable piston-shaped nozzle needle 17 is longitudinally movably received, which cooperates with a nozzle body formed in the nozzle body 40 19 and one or more injection openings 22 opens and closes by their longitudinal movement.
- the nozzle needle 17 With its end facing away from the nozzle seat 19, the nozzle needle 17 is guided in a guide sleeve 23, between which and a shoulder of the nozzle needle 17, a nozzle spring 21 is arranged under compressive prestress, on the one hand, the nozzle needle 17 biases against the nozzle seat 19 and on the other hand, the guide sleeve 23 against the Throttle plate 30.
- control chamber 25 To control the longitudinal movement of the nozzle needle 17, the pressure in a control chamber 25, which is bounded by the nozzle seat facing away from the end face of the nozzle needle 17, the guide sleeve 23 and the throttle plate 30.
- the control chamber 25 is connected via an inlet throttle 29, which is formed in the throttle plate 30, to the high-pressure passage 12, so that there is always a connection to the high pressure.
- a control valve 26 To relieve the control chamber 25 is a control valve 26 which is disposed within the valve plate 20 and which is a control valve element 27, which is movably arranged.
- a piezoelectric actuator 14 For the movement of the control valve element 27 is an electric actuator, which is designed here as a piezoelectric actuator 14 and which is disposed within the low-pressure space 11.
- a hydraulic coupler 15 To transmit the linear expansion of the piezoelectric actuator 14 to the control valve element 27 is a hydraulic coupler 15, which is arranged between the piezoelectric actuator 14 and the control valve element 27.
- enlarged hydraulic coupler unit 15 in this case comprises a piston 32 which is connected directly to the piezoelectric actuator, so that it is moved by the longitudinal extent of the piezoelectric actuator 14 in its longitudinal direction.
- the piston 32 is guided in a sleeve 35, wherein the piston 32 has a guide portion 132, with which it is guided in the sleeve 35, wherein the sleeve 35 forms on its inner side a guide surface 39, in which the guide portion 132 is guided.
- a throttle gap 54 is formed, since the piston 32 has a slightly smaller diameter than the guide surface 39, which is formed here as a bore in the sleeve 35.
- the sleeve 35 also has a second guide surface 41, in which a further piston 34 is guided longitudinally movable.
- a hydraulic working space 37 is limited, which is enclosed radially outwardly from the sleeve 35.
- a spring sleeve 38 which is arranged under bias between a shoulder of the sleeve 35 and a support plate 36, which in turn is supported on a shoulder of the piston 32 so that by the bias of the spring sleeve 38 on the one hand, the piston 32 against the piezoelectric actuator 14 is pressed and on the other hand, the sleeve 35 against a shoulder in the housing 11 of the fuel injector 1.
- a further piston 34 surrounding closing spring 43 is provided, which is supported on the sleeve 35 with one end and the other end to a Support sleeve 45 rests, wherein the support sleeve 45 is fixedly connected to the other piston 34.
- This closing spring 43 serves to push the other piston 34 back to its starting position when the volume of the hydraulic working chamber 37 is changed after the injection has been completed.
- the hydraulic working chamber 37 is filled with fuel at low pressure, which also surrounds the entire sleeve 35, as well as the piezoelectric actuator 14.
- the filling of the hydraulic working chamber 37 takes place on the one hand via the throttle gaps 54 and 56, the latter throttle gap between the sleeve 35th and the further piston 34 is formed.
- a groove 52 which is provided in the piston 32 and which extends here in the longitudinal direction of the piston 32.
- This groove 52 forms a hydraulic connection between the low pressure chamber 11 and the hydraulic working chamber 37.
- a groove 152 may be provided which is not provided in the piston 32, but on the guide surface 39 of the sleeve 35 and in the FIG. 2 is drawn on the right side, the depth of this groove is shown for clarity's sake significantly exaggerated.
- Operation of the fuel injection valve and the hydraulic coupler is as follows: In the fuel injector 1 is located in the high-pressure bore 12 of the high fuel pressure, which is provided by the high-pressure fuel accumulator 8. At the beginning, the control valve 26 is closed, so that in the control chamber 25 - due to the connection via the inlet throttle 29 with the high pressure passage 12 - the high fuel pressure of the injection pressure prevails, through which the nozzle needle 17 is pressed against the nozzle seat 19 and the injection ports 22 closes , If an injection of fuel happens, the piezoelectric actuator 14 is energized. As a result, the piezoactuator 14 expands in its longitudinal direction and presses the piston 32 in the direction of the further piston 34 or the nozzle body 40, in the FIG. 2 or the FIG.
- the fuel is, due to the high pressure, atomized and enters the combustion chamber of an internal combustion engine, where it burns. If the injection is to be terminated, the energization of the piezoactuator 14 is interrupted, so that it contracts again, it being ensured by the spring sleeve 38 that the piezoactuator always remains under pressure bias.
- the piston 32 in turn moves upward in the longitudinal direction and increases the volume of the hydraulic working chamber 37. Accordingly, the pressure in the hydraulic working chamber 37 decreases, so that the further piston 34 is also pressed in the direction of the piston 32, which is driven by a spring element 31 is that surrounds the control valve element 27.
- the control valve member 27 closes the connection from the control chamber 25 to the low-pressure chamber 11 and it can build up in the control chamber 25 again the high fuel pressure, which prevailed at the beginning of the injection, which presses the nozzle needle 17 back into its closed position to the nozzle seat 19.
- the power transmission is mediated by the piston 32 to the other piston 34 by the hydraulic pressure in the hydraulic working space 37.
- the fuel pressure in the hydraulic working chamber 37 is increased by the movement of the piston 32, the result is a pressure difference between the hydraulic working chamber 37 on the one hand and the surrounding fuel in the low-pressure chamber 11 in which the entire hydraulic coupling unit floats.
- this pressure gradient some fuel flows from the hydraulic working chamber 37 via the throttle gap 54 and the further throttle gap 56 into the low-pressure chamber 11, so that at the end of the injection, when the nozzle needle has closed again, the volume in the hydraulic working chamber 37 has become somewhat smaller.
- the groove 52 is provided, which extends in the longitudinal direction on the surface of the piston 32 and which establishes a hydraulic connection between the hydraulic working space 37 and the low-pressure space 11. Due to the depth and width of this groove 52, so the flow cross-section, the flow resistance can be easily adjusted.
- a groove 152 may also be formed on the guide surface 39, which likewise establishes a hydraulic connection between the hydraulic working space 37 and the low-pressure space 11.
- the flow resistance of the groove 52 can be dimensioned so that the inflow and outflow of fuel into the hydraulic working chamber 37 occurs almost exclusively via this groove 52, when at the same time the throttle gaps 54, 56 are made very tight.
- FIG. 3 an alternative embodiment of the hydraulic coupler is shown.
- the piston 32 ' is here provided with a bore which forms the guide surface 39' and in which the further piston 34 'is received.
- the hydraulic working chamber 37 is thereby formed within the piston 32 'and is also limited here by the piston 32' and the other piston 34 '.
- a coupler sleeve 46 which is arranged in the lower region of the hydraulic coupler device and between the piston 32' and the other piston 34. Between the coupler sleeve 46 and the piston 32, the spring sleeve 38 is arranged under pressure bias.
- the groove 52 ' is formed on the further piston 34' extends in the longitudinal direction of the other piston 34 'and connects the hydraulic working chamber 37 with the low pressure chamber 11.
- the between the front side of the coupler sleeve 46 and the piston 32' remaining annular space is connected via a transverse bore 50 with the low-pressure chamber 11, to prevent any pressure pad arise here.
- the function of the coupler is identical to the hydraulic coupler according to Fig. 2 , where at in Fig. 3 illustrated displacement means between the piston 32 'and the other piston 34', ie that the longitudinal movement of the piston 32 'is translated into an equally large longitudinal movement of the other piston 34'.
- FIG. 4 is a further embodiment of the hydraulic coupler according to the invention shown, with these embodiments of the FIGS. 4 . 5 and 6 of which Fig. 2 differs only in the formation of the groove or grooves 52, 52 'and in the dimensions of the piston 32 and the further piston 34, which here have the same diameter.
- Fig. 2 differs only in the formation of the groove or grooves 52, 52 'and in the dimensions of the piston 32 and the further piston 34, which here have the same diameter.
- the groove 52 is not parallel to the longitudinal axis of the piston 32, but has a serrated profile.
- the groove 52 has a greater length than the length of the piston 32, so that the flow resistance of the fuel through the groove 52 is increased.
- a further groove 52 ' is shown in the further piston 34, which may alternatively or additionally be present in addition to the groove 52. It is also possible that in the further guide surface 41, which is formed by a further bore in the further piston 34 and at the further piston 34 is guided, a further groove 152 'is formed, which may alternatively or additionally to the further groove 52 may be present.
- FIG. 5 shows a further embodiment, which differs from that of the Fig. 4 only by the course of the groove 52 and 52 'differs.
- the groove 52, 52 ' is for this purpose at least partially meander-shaped, in order to increase the length and thus to increase the flow resistance.
- a very shallow groove is difficult to produce with the necessary low tolerances, while a relatively deep groove whose flow resistance is adjusted over the length, is easy and inexpensive to produce.
- FIG. 6 shows a further embodiment of the hydraulic coupler according to the invention, wherein the groove 52 and 52 'is formed here helically and the piston 32 and the other piston 34 surrounds helically.
- the groove 52 or 52 ' establishes a hydraulic connection between the hydraulic working space 37 and the low-pressure space 11.
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Abstract
Hydraulische Kopplereinrichtung zur Übertragung einer Bewegung eines elektrischen Aktors (14) auf ein bewegliches Bauteil mit einem Kolben (32), der an einer Führungsfläche (39; 39') mit einem Führungsabschnitt (132) geführt ist. Zwischen der Führungsfläche (39; 39') und dem Kolben (32) verbleibt ein Drosselspalt (54), wobei der Drosselspalt (54) in einen mit Fluid befüllbaren Arbeitsraum (37) mündet, der durch eine Stirnseite des Kolbens (47) begrenzt wird. An dem Führungsabschnitt (132) des Kolbens (32) und/oder an der Führungsfläche (39; 39') ist eine Nut (52; 152) ausgebildet ist, die in den Arbeitsraum (37) mündet. Die hydraulische Kopplereinrichtung kann in einem Kraftstoffeinspritzventil (1) verwendet werden, um die Bewegung eines elektrischen Aktors (14) auf ein Steuerventilelement (27) zu übertragen.Hydraulic coupler device for transmitting a movement of an electrical actuator (14) to a movable component with a piston (32) guided on a guide surface (39; 39 ') with a guide section (132). A throttle gap (54) remains between the guide surface (39; 39 ') and the piston (32), the throttle gap (54) opening into a fluid-fillable working space (37) delimited by an end face of the piston (47) , On the guide portion (132) of the piston (32) and / or on the guide surface (39; 39 ') is formed a groove (52; 152) which opens into the working space (37). The hydraulic coupler may be used in a fuel injector (1) to transmit the movement of an electrical actuator (14) to a control valve member (27).
Description
Die Erfindung betrifft eine hydraulische Kopplereinrichtung, wie sie zur Übertragung einer Bewegung eines elektrischen Aktors auf ein bewegliches Bauteil Verwendung findet, und einen Kraftstoffinjektor mit einer solchen Kopplereinrichtung.The invention relates to a hydraulic coupler device, such as is used for transmitting a movement of an electrical actuator to a movable component, and a fuel injector with such a coupler.
Aus der Stand der Technik sind verschiedene Kopplereinrichtungen bekannt, die dazu dienen, die Bewegung eines elektrischen Aktors, beispielsweise eines Piezoaktors oder eines magnetischen Stellers, auf ein anderes bewegliches Bauteil zu übertragen. Die Kopplereinrichtung dient dabei einerseits einer möglichen Weg- oder Kraftverstärkung und andererseits dazu, Toleranzen zwischen dem Aktor und dem zu bewegenden Bauteil auszugleichen. Als Element einer Kraftstoffeinspritzvorrichtung ist ein solcher Koppler beispielsweise aus der
Für eine einwandfreie Funktion ist es unerlässlich, dass der hydraulische Arbeitsraum stets mit einem flüssigen Fluid gefüllt ist. Gasförmige Fluide sind in aller Regel nicht geeignet, da sie zu kompressibel sind, während weitgehend inkompressible Flüssigkeiten die Längsbewegung des Primärkolbens auf den Sekundärkolben in der Regel problemlos übertragen können. Es muss also in jedem Fall verhindert werden, dass der hydraulische Arbeitsraum leerläuft oder nur teilweise mit Flüssigkeit gefüllt ist, was bei dem bekannten hydraulischen Koppler durch Leckagespalte erreicht wird. Diese Leckagespalte sind beispielsweise zwischen einer umgebenden Hülse und dem Primärkolben ausgebildet und so bemessen, dass der hydraulische Arbeitsraum dann, wenn hydraulische Koppler nicht betrieben wird, durch Zu- oder Abfluss von Kraftstoff durch diese Drosselspalte mit Kraftstoff gefüllt oder entleert werden kann und so immer gerade mit Kraftstoff bzw. einem flüssigen Arbeitsmedium gefüllt ist.For a perfect function, it is essential that the hydraulic working space is always filled with a liquid fluid. Gaseous fluids are generally not suitable because they are too compressible, while largely incompressible fluids can easily transfer the longitudinal movement of the primary piston to the secondary piston in the rule. It must therefore be prevented in any case that the hydraulic working space idles or is only partially filled with liquid, which is achieved in the known hydraulic coupler by leakage gaps. These leakage gaps are formed, for example, between a surrounding sleeve and the primary piston and dimensioned such that the hydraulic working space can be filled or emptied by fuel through or out of fuel through this throttle gap with fuel when hydraulic coupler is not operated, and thus always straight is filled with fuel or a liquid working medium.
Die Drosselspalte haben die Eigenschaft, dass deren Durchflusswiderstand bei gegebener Druckdifferenz zwischen beiden Seiten des Drosselspaltes mit der dritten Potenz der Höhe des Drosselspaltes skaliert. Der Durchfluss durch den Drosselspalt ist entsprechend empfindlich auf geometrische Schwankungen, also auf Fertigungstoleranzen oder auch auf Änderungen in Folge thermischer Ausdehnung. Darüber hinaus muss der Drosselspalt ganz bestimmte Eigenschaften erfüllen: Einerseits darf er nicht zu groß sein, damit während des Arbeitshubs des hydraulischen Kopplers möglichst kein Kraftstoff aus dem hydraulischen Arbeitsraum verdrängt wird, denn nur so überträgt der hydraulische Koppler die Bewegung des Piezoaktors unmittelbar auf das zu bewegende Bauteil. Andererseits dürfen die Drosselspalte nicht zu klein sein, damit der hydraulische Arbeitsraum während der Betriebspausen des hydraulischen Kopplers schnell und effektiv wieder mit dem flüssigen Fluid befüllt werden muss. Da, wie schon erwähnt, der Durchflusswiderstand durch den Drosselspalt sehr empfindlich auf geometrische Änderungen ist, ist die exakte Fertigung eines solchen hydraulischen Kopplers aufwendig und damit kostenintensiv.The throttle gaps have the property that their flow resistance at a given pressure difference between both sides of the throttle gap scales with the cube of the height of the throttle gap. The flow through the throttle gap is correspondingly sensitive to geometric fluctuations, ie to manufacturing tolerances or to changes due to thermal expansion. In addition, the throttle gap must fulfill certain characteristics: On the one hand, it must not be too large, so that during the power stroke of the hydraulic coupler as possible no fuel is displaced from the hydraulic working space, because only so the hydraulic coupler transfers the movement of the piezoelectric actuator directly to the moving component. On the other hand, the throttle gaps must not be too small, so that the hydraulic working space must be filled quickly and effectively again with the liquid fluid during the operating pauses of the hydraulic coupler. Since, as already mentioned, the Flow resistance through the throttle gap is very sensitive to geometric changes, the exact production of such a hydraulic coupler is complex and thus costly.
Die erfindungsgemäße hydraulische Kopplereinrichtung zur Übertragung einer Bewegung eines elektrischen Aktors auf ein bewegliches Bauteil weist demgegenüber den Vorteil auf, dass der hydraulische Koppler günstig zu fertigen ist und dabei der Zu- und Abfluss aus dem hydraulischen Arbeitsraum zuverlässig kontrolliert. Dazu weist die hydraulische Kopplereinrichtung einen Kolben auf, der an einer Führungsfläche mit einem Führungsabschnitt geführt ist, so dass zwischen der Führungsfläche und dem Kolben ein Drosselspalt verbleibt. Darüber hinaus ist ein mit einem Fluid befüllbarer Arbeitsraum vorhanden, der durch eine Stirnseite des Kolbens begrenzt wird und in den der Drosselspalt mündet. An dem Führungsabschnitt des Kolbens und/oder an der Führungsfläche ist eine Nut ausgebildet, die in den Arbeitsraum mündet.The hydraulic coupler according to the invention for transmitting a movement of an electrical actuator to a movable component, in contrast, has the advantage that the hydraulic coupler is inexpensive to manufacture and reliably controls the inflow and outflow from the hydraulic working space. For this purpose, the hydraulic coupler on a piston which is guided on a guide surface with a guide portion, so that a throttle gap remains between the guide surface and the piston. In addition, there is a working space that can be filled with a fluid, which is delimited by an end face of the piston and into which the throttle gap opens. At the guide portion of the piston and / or on the guide surface, a groove is formed, which opens into the working space.
Durch die Ausbildung der Nut, die in einfacher Weise hergestellt werden kann, lässt sich so ein bestimmter Zuflussquerschnitt zur Verfügung stellen, dessen Durchflussquerschnitt über die Tiefe und Form der Nut leicht variiert werden kann. Über die Nut lässt sich der hydraulische Arbeitsraum befüllen oder entleeren, wobei dieser Durchflussquerschnitt unabhängig vom Drosselspalt des Kopplers ist. Der Drosselspalt, der zwischen dem Kolben und der Führungsfläche ausgebildet ist, kann entsprechend so eng wie möglich gewählt werden, damit der Zu- bzw. Abfluss von flüssigem Fluid in den hydraulischen Arbeitsraum ausschließlich oder zumindest überwiegend durch die Nut geschieht.As a result of the formation of the groove, which can be produced in a simple manner, it is possible to provide a certain inflow cross-section whose flow cross section can easily be varied over the depth and shape of the groove. The hydraulic working space can be filled or emptied via the groove, whereby this flow cross section is independent of the throttle gap of the coupler. The throttle gap, which is formed between the piston and the guide surface, can be selected as closely as possible, so that the inflow and outflow of liquid fluid into the hydraulic working space occurs exclusively or at least predominantly through the groove.
In einer ersten vorteilhaften Ausgestaltung verbindet die Nut den hydraulischen Arbeitsraum mit einem Fluidraum, so dass ein Zu- bzw. Abfluss von flüssigem Fluid aus dem hydraulischen Arbeitsraum ermöglicht wird. Dadurch ist die stetige Befüllung des hydraulischen Arbeitsraums zuverlässig gewährleistet.In a first advantageous embodiment, the groove connects the hydraulic working space with a fluid space, so that an inflow or outflow of liquid fluid from the hydraulic working space is made possible. As a result, the steady filling of the hydraulic working space is reliably guaranteed.
In einer weiteren vorteilhaften Ausgestaltung ist der hydraulische Arbeitsraum zusätzlich von der Stirnseite eines weiteren Kolbens begrenzt. Dadurch wird die Bewegung des Kolbens, der das flüssige Fluid im hydraulischen Arbeitsraum komprimiert, zuverlässig auf einen weiteren Kolben übertragen, der wiederum entweder das zu bewegende Bauteil darstellt oder der ein weiteres Bauteil bewegt, welches mit dem weiteren Kolben verbunden ist.In a further advantageous embodiment of the hydraulic working space is additionally limited by the end face of another piston. Thereby, the movement of the piston, which compresses the liquid fluid in the hydraulic working space, reliably transferred to another piston, which in turn either represents the component to be moved or moves another component, which is connected to the other piston.
In einer weiteren vorteilhaften Ausgestaltung ist der weitere Kolben mit einem Führungsabschnitt an einer weiteren Führungsfläche geführt, wobei ein zwischen dem weiteren Kolben und der weiteren Führungsfläche verbleibender Drosselspalt in den Arbeitsraum mündet. Auf diese Weise lässt sich der hydraulische Arbeitsraum zusätzlich über diesen Drosselspalt mit Fluid befüllen.In a further advantageous embodiment, the further piston is guided with a guide section on a further guide surface, wherein a remaining between the other piston and the further guide surface throttle gap opens into the working space. In this way, the hydraulic working space can be additionally filled with fluid via this throttle gap.
In einer weiteren vorteilhaften Ausgestaltung ist im Führungsabschnitt des weiteren Kolbens oder in der weiteren Führungsfläche zusätzlich oder an Stelle der Nut eine weitere Nut ausgebildet, die in den Arbeitsraum mündet. Dadurch lässt sich der hydraulische Arbeitsraum über eine weitere Nut mit flüssigem Fluid befüllen, so dass der Querschnitt der ersten Nut klein gehalten werden kann. Auch hier trennt in vorteilhafterweise der Führungsabschnitt des weiteren Kolbens den Arbeitsraum von einem Fluidraum, wobei die weitere Nut den Fluidraum und den hydraulischen Arbeitsraum verbindet.In a further advantageous embodiment, a further groove is formed in the guide section of the further piston or in the further guide surface in addition to or instead of the groove, which opens into the working space. As a result, the hydraulic working space can be filled via an additional groove with liquid fluid, so that the cross section of the first groove can be kept small. Here again, advantageously, the guide section of the further piston separates the working space from a fluid space, wherein the further groove connects the fluid space and the hydraulic working space.
In einer weiteren vorteilhaften Ausgestaltung sind die Führungsfläche und die weitere Führungsfläche als Bohrungen in derselben Hülse ausgebildet. Die Hülse dient weiterhin der Aufnahme des Kolbens und des weiteren Kolbens, so dass der hydraulische Arbeitsraum durch die Hülse, die Stirnseite des Kolbens und eine weitere Stirnseite des weiteren Kolbens begrenzt wird. Auf diese Weise lässt sich ein kompakter Aufbau des hydraulischen Kopplers erreichen, insbesondere ein geringer Außendurchmesser.In a further advantageous embodiment, the guide surface and the further guide surface are formed as holes in the same sleeve. The sleeve also serves to receive the piston and the other piston, so that the hydraulic working space is limited by the sleeve, the end face of the piston and another end face of the other piston. In this way, a compact design of the hydraulic coupler can be achieved, in particular a small outer diameter.
In einer weiteren vorteilhaften Ausgestaltung ist die Nut oder die weitere Nut zumindest abschnittsweise mäaanderförmig ausgebildet, wobei auch beide Nuten diese Form aufweisen können. Über die Länge der Nut lässt sich der Durchflusswiderstand der Nut einstellen, da bei einer direkten Verbindung in Längsrichtung des Kolbens bzw. des weiteren Kolbens der Durchflusswiderstand zu gering sein kann. Um die Länge der Nuten zu erhöhen, können diese auch zumindest abschnittsweise schraubenförmig ausgebildet sein und den Kolben bzw. den weiteren Kolben umgeben. Dabei kann die Nut oder die weitere Nut mittels eines Lasers hergestellt sein, der eine Oberflächenbearbeitung mit der notwendigen Präzision und mit niedrigen Kosten erlaubt.In a further advantageous embodiment, the groove or the further groove is at least partially formed meander-shaped, whereby both grooves may have this shape. Over the length of the groove, the flow resistance of the groove can be adjusted, since in a direct connection in the longitudinal direction of the piston or the other piston, the flow resistance to be too low can. To increase the length of the grooves, they can also be at least partially helical and surround the piston or the other piston. In this case, the groove or the further groove can be made by means of a laser, which allows a surface treatment with the necessary precision and at low cost.
Weiterhin ist ein erfindungsgemäßer Kraftstoffinjektor zur Kraftstoffhochdruckeinspritzung vorgesehen, der eine Düsennadel zum Öffnen und Schließen wenigstens einer Einspritzöffnung aufweist und der einen mit Kraftstoff befüllbaren Steuerraum aufweist, wobei der Druck im Steuerraum zumindest mittelbar eine Schließkraft auf die Düsennadel ausübt. Weiterhin ist ein Steuerventil zur Verbindung des Steuerraums mit einem Fluidraum vorhanden, wobei das Steuerventil ein bewegliches Steuerventilelement umfasst. Und es ist ein elektrischer Aktor vorhanden, der mit einer hydraulischen Kopplereinrichtung gemäß Anspruch 1 so zusammenwirkt, dass die Bewegung des elektrischen Aktors auf das Steuerventilelement zumindest mittelbar übertragen wird. Durch das Vorsehen der hydraulischen Kopplereinheit im Kraftstoffinjektor lässt sich eine zuverlässige Funktion des Steuerventils gewährleisten und damit eine einwandfreie Funktion des Kraftstoffeinspritzventils über die gesamte Lebensdauer.Furthermore, an inventive fuel injector for high-pressure fuel injection is provided which has a nozzle needle for opening and closing at least one injection port and having a fuel-filled control chamber, the pressure in the control chamber at least indirectly exerts a closing force on the nozzle needle. Furthermore, a control valve for connecting the control chamber with a fluid space is provided, wherein the control valve comprises a movable control valve element. And there is an electric actuator which cooperates with a hydraulic coupler according to claim 1 so that the movement of the electric actuator is transmitted to the control valve member at least indirectly. By providing the hydraulic coupler unit in the fuel injector, a reliable function of the control valve can be ensured and thus a perfect function of the fuel injection valve over the entire service life.
In der Zeichnung ist eine erfindungsgemäße hydraulische Kopplereinrichtung dargestellt, und ein erfindungsgemäßes Kraftstoffinjektor. Dazu zeigt
- Figur 1
- ein erfindungsgemäßes Kraftstoffinjektor mit den wesentlichen Anbaukomponenten, welches eine hydraulische Kopplereinrichtung aufweist,
- Figur 2
- eine vergrößerte Darstellung der in
Figur 1 gezeigten hydraulischen Kopplereinrichtung, - Figur 3
- eine alternative Ausgestaltung der erfindungsgemäßen hydraulischen Kopplereinrichtung und
- Figur 4,
Figur 5 und Figur 6 - weitere Ausführungsbeispiele der erfindungsgemäßen Kopplereinrichtung.
- FIG. 1
- a fuel injector according to the invention with the essential attachment components, which has a hydraulic coupler device,
- FIG. 2
- an enlarged view of in
FIG. 1 shown hydraulic coupler, - FIG. 3
- an alternative embodiment of the hydraulic coupler according to the invention and
- FIG. 4, FIG. 5 and FIG. 6
- further embodiments of the coupler according to the invention.
In
Zur Steuerung der Längsbewegung der Düsennadel 17 dient der Druck in einem Steuerraum 25, der von der düsensitzabgewandten Stirnseite der Düsennadel 17, der Führungshülse 23 und der Drosselplatte 30 begrenzt wird. Der Steuerraum 25 ist über eine Zulaufdrossel 29, die in der Drosselplatte 30 ausgebildet ist, mit dem Hochdruckkanal 12 verbunden, so dass stets eine Verbindung zum Hochdruck besteht. Zur Entlastung des Steuerraums 25 dient ein Steuerventil 26, das innerhalb der Ventilplatte 20 angeordnet ist und das ein Steuerventilelement 27 umfasst, welches beweglich angeordnet ist. Durch die Bewegung des Steuerventilelements 27 wird eine Ablaufdrossel 28 geöffnet oder geschlossen, durch die der Steuerraum 25 mit einem im Gehäuse 10 ausgebildeten Niederdruckraum 11 verbindbar ist, der über eine Rücklaufleitung 13 mit dem Kraftstofftank 3 verbunden ist, so dass im Niederdruckraum 11 immer ein niedriger Kraftstoffdruck herrscht.To control the longitudinal movement of the
Zur Bewegung des Steuerventilelements 27 dient ein elektrischer Aktor, der hier als Piezoaktor 14 ausgebildet ist und der innerhalb des Niederdruckraums 11 angeordnet ist. Zur Übertragung der Längenausdehnung des Piezoaktors 14 auf das Steuerventilelement 27 dient eine hydraulische Kopplereinrichtung 15, welche zwischen dem Piezoaktor 14 und dem Steuerventilelement 27 angeordnet ist. Die in
Durch die Stirnseite 47 des Kolbens 32 und die weitere Stirnseite 48 des weiteren Kolbens 34 wird ein hydraulischer Arbeitsraum 37 begrenzt, der radial nach außen von der Hülse 35 umschlossen wird. Zur Lagefixierung der Hülse 35 dient eine Federhülse 38, die unter Vorspannung zwischen einem Absatz der Hülse 35 und einer Stützplatte 36 angeordnet ist, die sich wiederum an einem Absatz des Kolbens 32 abstützt, so dass durch die Vorspannung der Federhülse 38 einerseits der Kolben 32 gegen den Piezoaktor 14 gedrückt wird und andererseits die Hülse 35 gegen einen Absatz im Gehäuse 11 des Kraftstoffinjektors 1. Weiterhin ist eine den weiteren Kolben 34 umgebende Schließfeder 43 vorgesehen, die sich an der Hülse 35 mit einem Ende abstützt und deren anderes Ende an einer Stützhülse 45 anliegt, wobei die Stützhülse 45 fest mit dem weiteren Kolben 34 verbunden ist. Diese Schließfeder 43 dient dazu, den weiteren Kolben 34 wieder an seine Ausgangsposition zu drücken, wenn nach Beendigung der Einspritzung das Volumen des hydraulischen Arbeitsraums 37 verändert ist.By the
Der hydraulische Arbeitsraum 37 ist mit Kraftstoff unter niedrigem Druck befüllt, der auch die gesamte Hülse 35 umgibt, ebenso wie den Piezoaktor 14. Die Befüllung des hydraulischen Arbeitsraums 37 geschieht dabei einerseits über die Drosselspalte 54 bzw. 56, wobei letzterer Drosselspalt zwischen der Hülse 35 und dem weiteren Kolben 34 ausgebildet ist. Zur zuverlässigen Befüllung des hydraulischen Arbeitsraums 37 mit Kraftstoff dient jedoch hauptsächlich eine Nut 52, welche im Kolben 32 vorgesehen ist und die hier in Längsrichtung des Kolbens 32 verläuft. Diese Nut 52 bildet eine hydraulische Verbindung zwischen dem Niederdruckraum 11 und dem hydraulischen Arbeitsraum 37. Alternativ oder zusätzlich kann auch eine Nut 152 vorgesehen sein, die nicht im Kolben 32, sondern an der Führungsfläche 39 der Hülse 35 vorgesehen ist und die in der
Funktionsweise des Kraftstoffeinspritzventils und der hydraulischen Kopplereinrichtung ist wie folgt: Im Kraftstoffinjektor 1 liegt in der Hochdruckbohrung 12 der hohe Kraftstoffdruck an, der durch den Kraftstoffhochdruckspeicher 8 zur Verfügung gestellt wird. Zu Beginn ist das Steuerventil 26 geschlossen, so dass im Steuerraum 25 - bedingt durch die Verbindung über die Zulaufdrossel 29 mit dem Hochdruckkanal 12 - der hohe Kraftstoffdruck des Einspritzdrucks herrscht, durch den die Düsennadel 17 gegen den Düsensitz 19 gedrückt wird und die Einspritzöffnungen 22 verschließt. Soll eine Einspritzung von Kraftstoff geschehen, so wird der Piezoaktor 14 bestromt. Dadurch dehnt sich der Piezoaktor 14 in seiner Längsrichtung aus und drückt den Kolben 32 in Richtung des weiteren Kolbens 34 bzw. des Düsenkörpers 40, in der
Im hydraulischen Koppler, wie in
In
In
Claims (12)
dadurch gekennzeichnet, dass
an dem Führungsabschnitt (132) des Kolbens (32) und/oder an der Führungsfläche (39; 39') eine Nut (52; 152) ausgebildet ist, die in den Arbeitsraum (37) mündet.Hydraulic coupler device for transmitting a movement of an electric actuator (14) to a movable component with a piston (32) which is guided on a guide surface (39; 39 ') with a guide section (132), so that between the guide surface (39; 39 ') and the piston (32) a throttle gap (54) remains, and with a fluid-fillable working space (37) which is delimited by an end face of the piston (47) and in which the throttle gap (54) opens,
characterized in that
on the guide portion (132) of the piston (32) and / or on the guide surface (39; 39 ') a groove (52; 152) is formed, which opens into the working space (37).
dadurch gekennzeichnet, dass
das Kraftstoffeinspritzventil (1) eine hydraulische Kopplereinrichtung (15) nach einem der Ansprüche 1 bis 11 umfasst, die die Bewegung des elektrischen Aktors (14) auf das Steuerventilelement (27) zumindest mittelbar überträgt.Fuel injection valve for high-pressure fuel injection with a nozzle needle (17) for opening and closing at least one injection port (22), and with a fuel-filled control chamber (25), wherein the pressure in the control chamber (25) at least indirectly a closing force on the nozzle needle (17 ) and a control valve (26) for connecting the control space (25) to a fluid space (11), the control valve (26) comprising a movable control valve element (27), and an electric actuator (14),
characterized in that
the fuel injection valve (1) comprises a hydraulic coupler device (15) according to one of claims 1 to 11, which at least indirectly transmits the movement of the electrical actuator (14) to the control valve element (27).
Applications Claiming Priority (1)
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DE102015226326.6A DE102015226326A1 (en) | 2015-12-21 | 2015-12-21 | Hydraulic coupler and fuel injection valve with such |
Publications (1)
Publication Number | Publication Date |
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EP3184801A1 true EP3184801A1 (en) | 2017-06-28 |
Family
ID=57249754
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EP16197724.4A Withdrawn EP3184801A1 (en) | 2015-12-21 | 2016-11-08 | Hydraulic coupler system and fuel injection valve with same |
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DE (1) | DE102015226326A1 (en) |
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DE102018217383A1 (en) * | 2018-10-11 | 2020-04-16 | Thyssenkrupp Ag | High pressure valve for controlled pressure reduction |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19743668A1 (en) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Fuel injection valve for motor vehicle IC engine |
EP1195515A2 (en) * | 2000-10-04 | 2002-04-10 | Robert Bosch Gmbh | Fuel injector |
DE10102234A1 (en) * | 2001-01-19 | 2002-07-25 | Bosch Gmbh Robert | High pressure fuel supply unit, for an IC motor with fuel injection, has a drilling through the valve body to take a piston with a sealing section against the guide section of the drilling, with a hydraulic piston centering action |
DE10322672A1 (en) | 2003-05-20 | 2004-12-09 | Robert Bosch Gmbh | Valve for controlling liquids |
DE102011090148A1 (en) * | 2011-12-30 | 2013-07-04 | Continental Automotive Gmbh | Nozzle needle for an injector for injecting fuel into cylinder combustion chambers of an internal combustion engine and injector with such a nozzle needle |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19951144A1 (en) * | 1999-10-23 | 2001-04-26 | Bosch Gmbh Robert | Injector for fuel injection system in IC engines has guide bore in hydraulic connection with leakage oil return, to create pressure differential between pressure chamber and leakage oil return |
DE10213858A1 (en) * | 2002-03-27 | 2003-10-30 | Bosch Gmbh Robert | Fuel injector |
DE102005026514B4 (en) * | 2005-02-18 | 2008-12-24 | Robert Bosch Gmbh | injection |
DE102013224404A1 (en) * | 2013-11-28 | 2015-05-28 | Robert Bosch Gmbh | fuel injector |
-
2015
- 2015-12-21 DE DE102015226326.6A patent/DE102015226326A1/en not_active Withdrawn
-
2016
- 2016-11-08 EP EP16197724.4A patent/EP3184801A1/en not_active Withdrawn
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19743668A1 (en) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Fuel injection valve for motor vehicle IC engine |
EP1195515A2 (en) * | 2000-10-04 | 2002-04-10 | Robert Bosch Gmbh | Fuel injector |
DE10102234A1 (en) * | 2001-01-19 | 2002-07-25 | Bosch Gmbh Robert | High pressure fuel supply unit, for an IC motor with fuel injection, has a drilling through the valve body to take a piston with a sealing section against the guide section of the drilling, with a hydraulic piston centering action |
DE10322672A1 (en) | 2003-05-20 | 2004-12-09 | Robert Bosch Gmbh | Valve for controlling liquids |
DE102011090148A1 (en) * | 2011-12-30 | 2013-07-04 | Continental Automotive Gmbh | Nozzle needle for an injector for injecting fuel into cylinder combustion chambers of an internal combustion engine and injector with such a nozzle needle |
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