EP2743489B1 - Fuel injector valve for combustion engines - Google Patents
Fuel injector valve for combustion engines Download PDFInfo
- Publication number
- EP2743489B1 EP2743489B1 EP13188667.3A EP13188667A EP2743489B1 EP 2743489 B1 EP2743489 B1 EP 2743489B1 EP 13188667 A EP13188667 A EP 13188667A EP 2743489 B1 EP2743489 B1 EP 2743489B1
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- EP
- European Patent Office
- Prior art keywords
- pressure
- chamber
- control
- fuel injection
- control chamber
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- 239000000446 fuel Substances 0.000 title claims description 53
- 238000002485 combustion reaction Methods 0.000 title claims description 15
- 238000002347 injection Methods 0.000 claims description 55
- 239000007924 injection Substances 0.000 claims description 55
- 230000000875 corresponding effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000004422 calculation algorithm Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000009530 blood pressure measurement Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000002123 temporal effect Effects 0.000 description 1
Images
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
- 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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/005—Fuel-injectors combined or associated with other devices the devices being sensors
-
- 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
- F02M2200/24—Fuel-injection apparatus with sensors
- F02M2200/244—Force sensors
Definitions
- the present application relates to a fuel injection valve for internal combustion engines, as it is preferably used for the injection of fuel under high pressure in combustion chambers of high-speed, self-igniting internal combustion engines.
- Fuel injectors as will be used to inject fuel directly into combustion chambers of internal combustion engines, are well known in the art which can eject fuel under high pressure from currently up to 2500 bar.
- the fuel injection valves have a housing in which a longitudinally displaceable nozzle needle for opening and closing at least one injection opening cooperates with a nozzle seat.
- the control of the nozzle needle is usually servo-hydraulic, that is, a control chamber is provided, the hydraulic pressure exerts a closing force on the nozzle needle, while an opening pressure is exerted by the upcoming high fuel pressure to the nozzle needle in the opposite direction.
- control valves used are usually operated either by means of an electromagnet or a piezoelectric actuator, wherein the required control current is generated by a control unit, which must know the precise state of the internal combustion engine for precise control.
- a control unit which must know the precise state of the internal combustion engine for precise control.
- a whole series of needle lift sensors have been developed, which determine the needle stroke either directly or indirectly, for example by measuring the structure-borne noise of the injector or by detecting the pressure in certain areas of the injection valve.
- a fuel injection valve in which the control valve comprises a movable control sleeve in the form of a magnet armature, which is moved by means of an electromagnet.
- the control valve member limits a pressure chamber which is connected to the actual control chamber via an outlet throttle.
- the pressure chamber is also limited by a pressure pin, which rests with the other end to a force sensor. A change in the pressure in this pressure chamber is correlated with the pressure change in the control chamber and can be measured by the force exerted by the pressure pin on the force sensor.
- the fuel injection valve according to the invention has the advantage that the pressure can be measured directly in the control chamber and thus accurate detection of the nozzle needle movement, regardless of the switching state of Control valve allows without the functionality of the fuel injection valve is limited and without having to be made to the previous designs significant structural changes.
- a pressure pin is provided in the fuel injection valve whose end face delimits the control chamber and whose end face remote from the control chamber interacts with a force sensor. Since the pressure pin within the fuel injection valve does not move, the pressure pin does not affect the operation of the control valve and thus of the entire injection valve, so that it can be operated in the usual manner.
- the exact analysis of the force on the pressure pin, the movement of the nozzle needle can be detected very accurately, in particular the opening and closing time of the nozzle needle, these data are used to control the exact injection quantity and the injection timing in the control unit, the control current of the electromagnetic or piezoelectric actuator controls.
- the control valve comprises a control valve member which cooperates with a valve seat and thus opens and closes a hydraulic connection between the control chamber and the low-pressure chamber.
- This hydraulic connection advantageously comprises an outlet throttle, so that the outflow of fuel from the control chamber into the low-pressure chamber is precisely metered.
- the outlet throttle is formed in the pressure pin, which provides great advantages in terms of manufacturing, since the outlet throttle is a precision bore that can be made separately on a pressure pin that is easily accessible during the production process.
- the outlet throttle is formed in the housing.
- this can also be advantageous, which also has the advantage that one and the same pressure pin can be used in various injectors without having to make any structural changes.
- control valve member is sleeve-shaped and surrounds the pressure pin. This allows a compact design the control valve and thus the fuel injection valve, so that no or only insignificant structural changes of the fuel injection valve over the known types are necessary.
- a pilot chamber is provided which surrounds the pressure pin and which is connectable via the control valve to the low-pressure chamber, wherein the pilot chamber is connected via the outlet throttle to the control chamber.
- the pressure pin facing the control chamber is guided in a guide bore of the housing. This ensures that the pressure pin, which must be movable in the longitudinal direction, remains immobile in the radial direction and the force is transmitted directly to the force sensor at the other end of the pressure pin.
- FIG. 1 a fuel injection valve according to the invention is shown schematically in longitudinal section, wherein only the essential components of the fuel injection valve are shown.
- the fuel injection valve has a housing 1, which comprises a holding body 2 and a valve body 3, which are braced against each other by means of a clamping nut 4 and thus define a low-pressure space 18. Facing the combustion chamber, the housing 1 further includes a nozzle body 5, which is also braced against the holding body 2 by means of a tensioning device, not shown in the drawing.
- a nozzle needle 8 is arranged longitudinally displaceable, which is guided within a bore 7 in the holding body 2 and which projects with its combustion chamber end into the nozzle body 5.
- the nozzle needle 8 is surrounded by a pressure chamber 12 which is filled via a high pressure inlet 14 with fuel at high pressure.
- the high-pressure inlet is connected in a so-called common-rail injection system with a high-pressure accumulator, not shown in the drawing, which is filled via a high-pressure pump with compressed fuel.
- the nozzle needle 8 cooperates with its combustion chamber end with a nozzle seat 15 and thereby closes or opens one or more injection openings 16 which are formed in the nozzle body 5 and can flow through the fuel from the pressure chamber 12 with open nozzle needle 8 into a combustion chamber of an internal combustion engine.
- a control chamber 10 is limited, which is connected via an inlet throttle 20 to the pressure chamber 12, so that with the desired throttling fuel under high pressure from the pressure chamber 12 into the control chamber 10th can flow.
- the control valve 22 is provided, which is arranged in the low pressure chamber 18, which is formed by a recess in the holding body 2 and the valve body 3.
- the control valve 22 in this case comprises a magnetic armature 28, which also forms the control valve member of the control valve 22.
- the armature 28 is guided radially in a guide sleeve 30 so that it can move only in the longitudinal direction, which is predetermined by the longitudinal axis of the nozzle needle 8.
- the armature 28 is thereby moved by means of an electromagnet 25 which is disposed within a magnetic core 24 and is pressed by a leaf spring 26 to a corresponding shoulder in the valve body 3 and thus remains stationary.
- the control valve member 28 has a through hole 32 in which a pressure pin 33 is received.
- the pressure pin 33 is supported on the nozzle needle 8 facing away from a force sensor 35, which is arranged in an end plate 6 of the valve body 3.
- the force sensor 35 measures the force on the pressure pin 33 and forwards this measured value to an evaluation unit.
- the pressure pin 33 defines with its opposite end face 133 the control chamber 10, so that the pressure of the control chamber 10 acts directly on this end face 133 and the longitudinal force caused thereby is transmitted to the force sensor 35.
- valve spring 29 Opposite the force of the electromagnet 25 is the force of a valve spring 29, which presses the magnet armature 28 against a control valve seat 31, which is formed within the guide sleeve 30.
- the valve spring 29 surrounds the pressure pin 33 and is supported at one end on the control valve member 28 and at the other end to the end plate 6 from.
- an outlet throttle 37 is formed within the pressure pin.
- the outlet throttle 37 consists of a longitudinal bore and a longitudinal bore connected to the transverse bore, so that a hydraulic connection between the control chamber 10 and a pilot chamber 39 which by a diameter taper of the Pressure pin 33 is formed at the level of the control valve seat 31.
- the pilot chamber 39 can be connected by the control valve 22 with the low-pressure chamber 18 by the control valve member 28 lifts from the control valve seat 31.
- control valve 22 is closed, i. the control valve member 28 is in contact with the control valve seat 31, so that the pilot control chamber 39 is separated from the low-pressure chamber 18. Because of the inlet throttle 20 prevails in the control chamber 10, the same high fuel pressure as in the pressure chamber 12 so that the nozzle needle 8 is pressed by the hydraulic pressure in the control chamber 10 against the nozzle seat 15 and the injection ports 16 closes.
- the control valve 22 is actuated by passing a current through the solenoid 25 so that a magnetic force is applied to the control valve member 28 and pulls it away from the control valve seat 31. As a result, a hydraulic connection between the pilot control chamber 39 and the low-pressure chamber 18 is opened.
- the pressure in the pilot chamber 39 then drops off instantaneously, which also leads to a pressure drop in the control chamber 10 due to the outlet throttle 37 with a slight time delay.
- the outlet throttle 37 is designed in relation to the inlet throttle 20 so that when the control valve is open 22 more fuel flows through the outlet throttle 37, as in the same period on the inlet throttle 20 flows.
- the reduced fuel pressure in the control chamber 10 causes a reduction in the hydraulic pressure on the end face 108 of the nozzle needle 8, so that the nozzle needle 8, driven by the hydraulic pressure to corresponding pressure surfaces within the pressure chamber 12, is pushed away from the nozzle seat 15 and the injection openings 16 releases.
- fuel flows under high pressure from the pressure chamber 12 into the injection openings 16 and is injected through them into a combustion chamber of an internal combustion engine.
- the energization of the electromagnet 25 is interrupted, so that the control valve member 28 is pressed by the valve spring 29 back into its closed position in contact with the control valve seat 31.
- FIG. 2 is the pressure curve within the control chamber 10 and shown in the pilot chamber 39 during an injection cycle.
- the upper part of the diagram shows the pressure curve p 1 within the control chamber 10 and p 2 the pressure in the pilot chamber 39.
- the injection valve is in its initial position, ie the control valve 22 is closed and the nozzle needle 8 is in contact with the nozzle seat 15.
- time t 1 opens the control valve, resulting in a very rapid pressure drop (dashed lines pressure curve p 2 ) within the pilot chamber 39, since the pressure in the pilot chamber 39, the pressure of the low pressure chamber 18 assumes.
- the pressure in the control chamber p 1 (solid line) drops slightly at the time t 1 until the time t 2 , wherein the pressure drop does not fall as quickly and not as deep as in the pilot chamber 39, as fuel from the pressure chamber 12 continues to flow through the inlet throttle 12 nachströmt.
- the lower diagram shows the stroke h of the nozzle needle 8, which leaves the nozzle seat 15 at time t 2 and begins its ⁇ réelleshubiolo.
- a pressure builds up under the nozzle needle 8 and the pressure in the control chamber 10 does not drop any further since the nozzle needle 8 now displaces the fuel from the control chamber 10 and presses it into the pilot control chamber 39 via the outlet throttle , This results in spite of the open control valve 22 to a pressure increase, which continues until the time t 3 .
- time t 3 closes the control valve 22 and the nozzle needle 8 is in its maximum open position.
- the pressure in the pilot chamber 39 then builds up again very quickly to the original pressure and follows in the course of the pressure p 1 in the control chamber 10, as via the outlet throttle 37, a hydraulic connection between the two chambers 10, 39th
- the pressure p 1 in the control room 10 begins to fall again from the time t 3 , since the nozzle needle 8 slides back into its closed position and thereby increases the volume of the control chamber 10.
- the space thus obtained is filled via the inlet throttle, which effectively results in an approximately constant pressure until the time t 4 leads, to which the nozzle needle 8 again reaches its initial position and back into contact with the nozzle seat 15.
- the pressure is measured only within the pilot chamber 39, as can be seen on the diagram of the FIG. 2 detects, although recognize the needle closing at time t 4 , when a corresponding algorithm analyzes the pressure or force data of the force sensor 35.
- the time at which the nozzle needle 8 opens could not be detected because at time t 2, no significant change in the pressure curve p 2 can be seen.
- the pressure p 1 is measured directly in the control chamber 10, then all movements of the nozzle needle 8 can be accurately detected, in particular the exact opening and closing time of the nozzle needle 8, so that the injection can be optimized, for example, wear or other influences, such as due to temperature or changed fuel quality.
- FIG. 3 shows a further embodiment of the fuel injection valve according to the invention, wherein only the area around the control chamber 10 is shown.
- the pressure pin 33 has in this embodiment in the region of the control chamber 10 has a diameter extension, with which it is guided in a guide bore 34 in the holding body 2.
- the outlet throttle 37 is as in the FIG. 1 shown embodiment by a longitudinal bore and a transverse bore into which the longitudinal bore opens formed.
- the control valve seat 31 is shown in this embodiment as a cone, against which the control valve member 28 rests with a spherical valve sealing surface.
- an enlargement of the diameter in the holding body 2 is provided here.
- the mode of operation is identical to that in FIG. 1.
- the outlet throttle 37 is formed in this embodiment by the longitudinal bore within the pressure pin 33. However, this can also be designed in other ways.
- the FIG. 5 shows a section line along the line VV the FIG. 3 an alternative embodiment.
- the outlet throttle 37 within the pressure pin 33 is replaced in this embodiment by three bevels 40 which are formed on the outside of the pressure pin 33. By appropriate dimensioning of these ports 40 can be a flow restrictor 37 "form, which has the desired properties.
- FIG. 4 is another embodiment of the fuel injection valve according to the invention in the same illustration as FIG. 3 shown.
- the drain throttle 37 is shown as an oblique bore within the pressure pin 33
- the outlet throttle 37 ' is formed as a bore within the holding body 2, in which case the outlet throttle 37 can be omitted within the pressure pin 33. If the outlet throttle is formed in the holding body 2, then the same pressure pin 33 can be used for different injection valves, since only the outlet throttle 37 'has to be adapted to the respective requirements, while the pressure pin 33 can remain unchanged.
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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)
- Analytical Chemistry (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die vorliegende Anmeldung betrifft ein Kraftstoffeinspritzventil für Brennkraftmaschinen, wie es vorzugsweise zur Einspritzung von Kraftstoff unter hohem Druck in Brennräume von schnelllaufenden, selbstzündenden Brennkraftmaschinen verwendet wird.The present application relates to a fuel injection valve for internal combustion engines, as it is preferably used for the injection of fuel under high pressure in combustion chambers of high-speed, self-igniting internal combustion engines.
Kraftstoffeinspritzventile, wie sie zur Einspritzung von Kraftstoff direkt in Brennräume von Brennkraftmaschinen verwenden werden, sind aus dem Stand der Technik bekannt, die dabei Kraftstoff unter hohem Druck von derzeit bis zu 2500 bar ausspritzen können. Hierbei weisen die Kraftstoffeinspritzventile ein Gehäuse auf, in dem eine längsverschiebbare Düsennadel zum Öffnen und Schließen wenigstens einer Einspritzöffnung mit einem Düsensitz zusammenwirkt. Die Steuerung der Düsennadel erfolgt zumeist servo-hydraulisch, das heißt, dass ein Steuerraum vorgesehen ist, dessen hydraulischer Druck eine Schließkraft auf die Düsennadel ausübt, während gleichzeitig ein öffnender Druck durch den anstehenden hohen Kraftstoffdruck auf die Düsennadel in entgegengesetzter Richtung ausgeübt wird. Zur Steuerung der Längsbewegung der Düsennadel und damit zum Öffnen und Schließen der Einspritzöffnungen wird der Druck im Steuerraum mit Hilfe eines Steuerventils reguliert, das den Steuerraum mit einem Niederdruckraum verbindet oder von diesem trennt. Damit die Einspritzung in der richtigen Menge und zum genau richtigen Zeitpunkt stattfindet, wobei jede Einspritzung noch in mehrere Teileinspritzungen unterteilt sein kann, ist eine äußerst präzise Ansteuerung der Düsennadel notwendig.Fuel injectors, as will be used to inject fuel directly into combustion chambers of internal combustion engines, are well known in the art which can eject fuel under high pressure from currently up to 2500 bar. In this case, the fuel injection valves have a housing in which a longitudinally displaceable nozzle needle for opening and closing at least one injection opening cooperates with a nozzle seat. The control of the nozzle needle is usually servo-hydraulic, that is, a control chamber is provided, the hydraulic pressure exerts a closing force on the nozzle needle, while an opening pressure is exerted by the upcoming high fuel pressure to the nozzle needle in the opposite direction. To control the longitudinal movement of the nozzle needle and thus to open and close the injection openings of the pressure in the control chamber is regulated by means of a control valve which connects the control chamber with a low-pressure chamber or separates from this. In order for the injection to take place in the correct amount and at the exact right time, with each injection still being able to be subdivided into several partial injections, an extremely precise control of the nozzle needle is necessary.
Die verwendeten Steuerventile werden in der Regel entweder mittels eines Elektromagneten oder eines Piezoaktors betätigt, wobei der benötigte Steuerstrom mit einem Steuergerät erzeugt wird, das zur präzisen Ansteuerungen den genauen Zustand der Brennkraftmaschine kennen muss. Darüber hinaus ist es auch zur Regulierung von Verschleiß und zum Ausgleich von Bauteilunterschieden zwischen den Einspritzventilen sehr hilfreich, wenn bekannt ist, zu welchem Zeitpunkt die Düsennadel öffnet und schließt, wenn ein bestimmter Steuerstrom am Elektromagneten bzw. Piezoaktor angelegt wird. Zu diesem Zweck sind eine ganze Reihe von Nadelhubsensoren entwickelt worden, die den Nadelhub entweder direkt bestimmen oder aber indirekt, indem beispielsweise der Körperschall des Injektors gemessen wird oder indem der Druck in bestimmten Bereichen des Einspritzventils detektiert wird.The control valves used are usually operated either by means of an electromagnet or a piezoelectric actuator, wherein the required control current is generated by a control unit, which must know the precise state of the internal combustion engine for precise control. In addition, it is also very helpful in regulating wear and for compensating component differences between the injectors when it is known at what time the nozzle needle opens and closes when a particular control current is applied to the solenoid or piezo actuator. For this purpose, a whole series of needle lift sensors have been developed, which determine the needle stroke either directly or indirectly, for example by measuring the structure-borne noise of the injector or by detecting the pressure in certain areas of the injection valve.
Aus den Offenlegungsschriften
Das erfindungsgemäße Kraftstoffeinspritzventil weist demgegenüber den Vorteil auf, dass sich der Druck direkt im Steuerraum messen lässt und damit einen genaue Detektion der Düsennadelbewegung unabhängig vom Schaltzustand des Steuerventils erlaubt, ohne dass die Funktionsfähigkeit des Kraftstoffeinspritzventils eingeschränkt wird und ohne dass gegenüber den früheren Bauformen wesentliche bauliche Änderungen vorgenommen werden müssen. Zu diesem Zweck ist im Kraftstoffeinspritzventil ein Druckstift vorgesehen, dessen Stirnseite den Steuerraum begrenzt und dessen dem Steuerraum abgewandte Stirnfläche mit einem Kraftsensor zusammenwirkt. Da sich der Druckstift innerhalb des Kraftstoffeinspritzventils nicht bewegt, beeinflusst der Druckstift die Funktionsweise des Steuerventils und damit des gesamten Einspritzventils nicht, sodass es in der gewohnten Art und Weise betrieben werden kann. Gleichzeitig kann über die genaue Analyse der Kraft auf den Druckstift die Bewegung der Düsennadel sehr genau detektiert werden, insbesondere der Öffnungs- und Schließzeitpunkt der Düsennadel, wobei diese Daten zur Steuerung der genauen Einspritzmenge und des Einspritzzeitpunkts in dem Steuergerät verwendet werden, das den Steuerstrom des elektromagnetischen oder piezoelektrischen Aktors steuert.In contrast, the fuel injection valve according to the invention has the advantage that the pressure can be measured directly in the control chamber and thus accurate detection of the nozzle needle movement, regardless of the switching state of Control valve allows without the functionality of the fuel injection valve is limited and without having to be made to the previous designs significant structural changes. For this purpose, a pressure pin is provided in the fuel injection valve whose end face delimits the control chamber and whose end face remote from the control chamber interacts with a force sensor. Since the pressure pin within the fuel injection valve does not move, the pressure pin does not affect the operation of the control valve and thus of the entire injection valve, so that it can be operated in the usual manner. At the same time, the exact analysis of the force on the pressure pin, the movement of the nozzle needle can be detected very accurately, in particular the opening and closing time of the nozzle needle, these data are used to control the exact injection quantity and the injection timing in the control unit, the control current of the electromagnetic or piezoelectric actuator controls.
In einer ersten vorteilhaften Ausgestaltung des Gegenstandes der Erfindung umfasst das Steuerventil ein Steuerventilglied, das mit einem Ventilsitz zusammenwirkt und damit eine hydraulische Verbindung zwischen dem Steuerraum und dem Niederdruckraum öffnet und schließt. Diese hydraulische Verbindung umfasst in vorteilhafter Weise eine Ablaufdrossel, sodass der Abfluss von Kraftstoff aus dem Steuerraum in den Niederdruckraum genau dosiert geschieht. In vorteilhafter Weise ist dabei die Ablaufdrossel im Druckstift ausgebildet, was große Vorteile hinsichtlich der Fertigung erbringt, da die Ablaufdrossel eine Präzisionsbohrung darstellt, die an einem Druckstift separat gefertigt werden kann, der während des Produktionsprozesses leicht zugänglich ist.In a first advantageous embodiment of the subject of the invention, the control valve comprises a control valve member which cooperates with a valve seat and thus opens and closes a hydraulic connection between the control chamber and the low-pressure chamber. This hydraulic connection advantageously comprises an outlet throttle, so that the outflow of fuel from the control chamber into the low-pressure chamber is precisely metered. Advantageously, while the outlet throttle is formed in the pressure pin, which provides great advantages in terms of manufacturing, since the outlet throttle is a precision bore that can be made separately on a pressure pin that is easily accessible during the production process.
In einer weiteren vorteilhaften Ausgestaltung ist die Ablaufdrossel im Gehäuse ausgebildet. In bestimmten Bauformen kann auch dies vorteilhaft sein, was auch den Vorteil hat, dass ein und derselbe Druckstift in verschiedenen Injektoren eingesetzt werden kann, ohne dass bauliche Änderungen vorgenommen werden müssen.In a further advantageous embodiment, the outlet throttle is formed in the housing. In certain designs, this can also be advantageous, which also has the advantage that one and the same pressure pin can be used in various injectors without having to make any structural changes.
In einer weiteren vorteilhaften Ausgestaltung ist das Steuerventilglied hülsenförmig ausgebildet und umgibt den Druckstift. Dies erlaubt eine kompakte Bauweise des Steuerventils und damit des Kraftstoffeinspritzventils, sodass keine oder nur unwesentliche bauliche Änderungen des Kraftstoffeinspritzventils gegenüber den bekannten Bauformen notwendig sind.In a further advantageous embodiment, the control valve member is sleeve-shaped and surrounds the pressure pin. This allows a compact design the control valve and thus the fuel injection valve, so that no or only insignificant structural changes of the fuel injection valve over the known types are necessary.
In einer weiteren vorteilhaften Ausgestaltung ist ein Vorsteuerraum vorgesehen, der den Druckstift umgibt und der über das Steuerventil mit dem Niederdruckraum verbindbar ist, wobei der Vorsteuerraum über die Ablaufdrossel mit dem Steuerraum verbunden ist. Die Größe des Vorsteuerraums und dessen Form beeinflusst die Funktionsweise des Kraftstoffeinspritzventils, da es insbesondere beim Schließen des Kraftstoffeinspritzventils zu einem Druckausgleich zwischen dem Vorsteuerraum und dem Steuerraum kommt. Da die Ablaufdrossel zwischen dem Vorsteuerraum und dem Steuerraum vorgesehen ist, lässt sich so auch ein Teil der Druckschwingungen, die sich beim Schließen des Steuerventils bilden können, abbauen.In a further advantageous embodiment, a pilot chamber is provided which surrounds the pressure pin and which is connectable via the control valve to the low-pressure chamber, wherein the pilot chamber is connected via the outlet throttle to the control chamber. The size of the pilot chamber and its shape affect the operation of the fuel injection valve, since there is a pressure equalization between the pilot chamber and the control chamber in particular when closing the fuel injection valve. Since the outlet throttle is provided between the pilot chamber and the control chamber, so can also part of the pressure oscillations, which can form when closing the control valve, reduce.
In einer weiteren vorteilhaften Ausgestaltung ist der Druckstift dem Steuerraum zugewandt in einer Führungsbohrung des Gehäuses geführt. Dies stellt sicher, dass der Druckstift, der in Längsrichtung beweglich sein muss, in radialer Richtung unbeweglich bleibt und die Kraft direkt auf den Kraftsensor am anderen Ende des Druckstifts übertragen wird. Darüber hinaus ist es in vorteilafter Weise möglich, dass am Druckstift ein oder mehrere Anschliffe ausgebildet sind, die die Ablaufdrossel bilden, sodass keine weiteren Bohrungen innerhalb des Druckstifts oder im Gehäuse ausgebildet werden müssen, die die Ablaufdrossel bilden.In a further advantageous embodiment, the pressure pin facing the control chamber is guided in a guide bore of the housing. This ensures that the pressure pin, which must be movable in the longitudinal direction, remains immobile in the radial direction and the force is transmitted directly to the force sensor at the other end of the pressure pin. In addition, it is possible in vorteilafter way that one or more contours are formed on the pressure pin, which form the outlet throttle, so that no further holes must be formed within the pressure pin or in the housing, which form the outlet throttle.
Weitere Vorteile und vorteilhafte Ausgestaltungen sind der Beschreibung und der Zeichnung entnehmbar.Further advantages and advantageous embodiments of the description and the drawing can be removed.
In der Zeichnung sind mehrere Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt
- Figur 1
- in einer schematischen Darstellung im Längsschnitt ein erfindungsgemäßes Kraftstoffeinspritzventil, wobei nur die wesentlichen Komponenten des Kraftstoffeinspritzventils dargestellt sind,
Figur 2- den zeitlichen Druckverlauf innerhalb des Steuerraums des erfindungsgemäßen Kraftstoffeinspritzventils und im Vorsteuerraum,
- Figur 3
- eine vergrößerte Darstellung im Bereich des Steuerraums eines weiteren Ausführungsbeispiels des erfindungsgemäßen Kraftstoffeinspritzventils, ebenso wie
Figur 4,- wobei
zwei alternative Ausgestaltungen der Ablaufdrossel enthält, undFigur 4 Figur 5- einen Querschnitt durch den dem Steuerraum zugewandten Endabschnitt des Druckstifts eines weiteren Ausführungsbeispiels.
- FIG. 1
- in a schematic representation in longitudinal section of an inventive fuel injection valve, wherein only the essential components of the fuel injection valve are shown,
- FIG. 2
- the temporal pressure curve within the control chamber of the fuel injection valve according to the invention and in the pilot control chamber,
- FIG. 3
- an enlarged view in the region of the control chamber of another embodiment of the fuel injection valve according to the invention, as well
- FIG. 4,
- in which
FIG. 4 contains two alternative embodiments of the outlet throttle, and - FIG. 5
- a cross section through the control chamber facing end portion of the pressure pin of another embodiment.
In
Im Gehäuse 1 ist eine Düsennadel 8 längsverschiebbar angeordnet, die innerhalb einer Bohrung 7 im Haltekörper 2 geführt ist und die mit ihrem brennraumseitigen Ende bis in den Düsenkörper 5 ragt. Die Düsennadel 8 ist dabei von einem Druckraum 12 umgeben, der über einen Hochdruckzulauf 14 mit Kraftstoff unter hohem Druck befüllbar ist. Der Hochdruckzulauf ist bei einem sogenannten Common-Rail-Einspritzsystem mit einem in der Zeichnung nicht dargestellten Hochdruckspeicher verbunden, der über eine Hochdruckpumpe mit verdichtetem Kraftstoff befüllt ist. Die Düsennadel 8 wirkt mit ihrem brennraumseitigen Ende mit einem Düsensitz 15 zusammen und verschließt oder öffnet dadurch eine oder mehrere Einspritzöffnungen 16, die im Düsenkörper 5 ausgebildet sind und über die Kraftstoff aus dem Druckraum 12 bei geöffneter Düsennadel 8 in einen Brennraum einer Brennkraftmaschine strömen kann.In the housing 1, a
Durch die Bohrung 7 und eine dem Düsensitz 15 abgewandte Stirnfläche 108 der Düsennadel 8 wird ein Steuerraum 10 begrenzt, der über eine Zulaufdrossel 20 mit dem Druckraum 12 verbunden ist, sodass mit der gewünschten Drosselwirkung Kraftstoff unter hohem Druck aus dem Druckraum 12 in den Steuerraum 10 strömen kann. Zur Steuerung des Kraftstoffdrucks im Steuerraum 10 ist das Steuerventil 22 vorgesehen, das im Niederdruckraum 18 angeordnet ist, der durch eine Aussparung im Haltekörper 2 bzw. dem Ventilkörper 3 gebildet wird. Das Steuerventil 22 umfasst dabei einen Magnetanker 28, der auch das Steuerventilglied des Steuerventils 22 bildet. Der Magnetanker 28 wird dabei in einer Führungshülse 30 radial geführt, sodass er sich nur in Längsrichtung bewegen kann, die durch die Längsachse der Düsennadel 8 vorgegeben ist. Der Magnetanker 28 wird dabei mittels eines Elektromagneten 25 bewegt, der innerhalb eines Magnetkerns 24 angeordnet ist und durch eine Blattfeder 26 an einen entsprechenden Absatz im Ventilkörper 3 gedrückt wird und so ortsfest verbleibt.Through the
Das Steuerventilglied 28 weist eine Durchgangsbohrung 32 auf, in der ein Druckstift 33 aufgenommen ist. Der Druckstift 33 stützt sich der Düsennadel 8 abgewandt an einem Kraftsensor 35 ab, der in einer Endplatte 6 des Ventilkörpers 3 angeordnet ist. Der Kraftsensor 35 misst die Kraft auf den Druckstift 33 und leitet diesen Messwert an eine Auswerteeinheit weiter. Der Druckstift 33 begrenzt mit seiner gegenüberliegenden Stirnseite 133 den Steuerraum 10, sodass der Druck des Steuerraums 10 direkt auf diese Stirnseite 133 wirkt und die dadurch verursachte Längskraft auf den Kraftsensor 35 übertragen wird.The
Der Kraft des Elektromagneten 25 entgegengesetzt wirkt die Kraft einer Ventilfeder 29, die den Magnetanker 28 gegen einen Steuerventilsitz 31 drückt, der innerhalb der Führungshülse 30 ausgebildet ist. Die Ventilfeder 29 umgibt dabei den Druckstift 33 und stützt sich mit einem Ende am Steuerventilglied 28 und mit dem anderen Ende an der Endplatte 6 ab.Opposite the force of the
Zur Verbindung des Steuerraums 10 mit dem Niederdruckraum 18 ist innerhalb des Druckstifts eine Ablaufdrossel 37 ausgebildet. Die Ablaufdrossel 37 besteht dabei aus einer Längsbohrung und einer mit der Längsbohrung verbundenen Querbohrung, sodass eine hydraulische Verbindung zwischen dem Steuerraum 10 und einem Vorsteuerraum 39, der durch eine Durchmesserverjüngung des Druckstifts 33 auf Höhe des Steuerventilsitzes 31 ausgebildet ist. Der Vorsteuerraum 39 lässt sich durch das Steuerventil 22 mit dem Niederdruckraum 18 verbinden, indem das Steuerventilglied 28 vom Steuerventilsitz 31 abhebt.To connect the
Die Funktionsweise des Steuerventils ist wie folgt: Zu Beginn der Einspritzung ist das Steuerventil 22 geschlossen, d.h. das Steuerventilglied 28 befindet sich in Anlage am Steuerventilsitz 31, sodass der Vorsteuerraum 39 vom Niederdruckraum 18 getrennt ist. Wegen der Zulaufdrossel 20 herrscht im Steuerraum 10 der gleiche hohe Kraftstoffdruck wie im Druckraum 12, sodass die Düsennadel 8 durch den hydraulischen Druck im Steuerraum 10 gegen den Düsensitz 15 gepresst wird und die Einspritzöffnungen 16 verschließt. Zur Initiierung einer Einspritzung wird das Steuerventil 22 betätigt, indem ein Strom durch den Elektromagneten 25 geleitet wird, sodass eine magnetische Kraft auf das Steuerventilglied 28 ausgeübt wird und dieses vom Steuerventilsitz 31 wegzieht. Dadurch wird eine hydraulische Verbindung zwischen dem Vorsteuerraum 39 und dem Niederdruckraum 18 aufgesteuert. Der Druck im Vorsteuerraum 39 fällt darauf hin instantan ab, was wegen der Ablaufdrossel 37 mit einem leichten Zeitverzug auch zu einem Druckabfall im Steuerraums 10 führt. Die Ablaufdrossel 37 ist dabei im Verhältnis zur Zulaufdrossel 20 so ausgelegt, dass bei geöffnetem Steuerventil 22 mehr Kraftstoff über die Ablaufdrossel 37 abfließt, als im gleichen Zeitraum über die Zulaufdrossel 20 zufließt.The operation of the control valve is as follows: At the beginning of the injection, the
Der verringerte Kraftstoffdruck im Steuerraum 10 bewirkt eine Minderung des hydraulischen Drucks auf die Stirnfläche 108 der Düsennadel 8, sodass die Düsennadel 8, angetrieben durch den hydraulischen Druck auf entsprechende Druckflächen innerhalb des Druckraums 12, vom Düsensitz 15 weggedrückt wird und die Einspritzöffnungen 16 freigibt. Dadurch strömt Kraftstoff unter hohem Druck aus dem Druckraum 12 in die Einspritzöffnungen 16 und wird durch diese hindurch in einen Brennraum einer Brennkraftmaschine eingespritzt. Zur Beendigung der Einspritzung wird die Bestromung des Elektromagneten 25 unterbrochen, sodass das Steuerventilglied 28 durch die Ventilfeder 29 zurück in seine Schließstellung in Anlage an den Steuerventilsitz 31 gedrückt wird. Durch den nachströmenden Kraftstoff über die Zulaufdrossel 20 baut sich im Steuerraum 10 sehr rasch wieder der ursprüngliche hohe Kraftstoffdruck auf, der die Düsennadel 8 zurück in ihre Schließstellung in Anlage an den Düsensitz 15 drückt. Dabei wird die Schließbewegung der Düsennadel in der Regel noch durch in der Zeichnung nicht dargestellte Schließfeder unterstützt. Dadurch wird die Einspritzung beendet, und das Kraftstoffeinspritzventil erreicht wieder seinen ursprünglichen Zustand.The reduced fuel pressure in the
In
Das untere Diagramm zeigt den Hub h der Düsennadel 8, die zum Zeitpunkt t2 den Düsensitz 15 verlässt und ihre Öffnungshubbewegung beginnt. Sobald die Düsennadel 8 vom Düsensitz 15 abgehoben hat, baut sich unter der Düsennadel 8 ein Druck auf und der Druck im Steuerraum 10 sinkt nicht weiter, da die Düsennadel 8 nun den Kraftstoff aus dem Steuerraum 10 verdrängt und über die Ablaufdrossel in den Vorsteuerraum 39 drückt. Dadurch kommt es trotz des geöffneten Steuerventils 22 zu einem Druckanstieg, der sich bis zum Zeitpunkt t3 fortsetzt. Zum Zeitpunkt t3 schließt das Steuerventil 22 und die Düsennadel 8 befindet sich in ihrer maximalen Öffnungsstellung. Der Druck im Vorsteuerraum 39 baut sich daraufhin wieder sehr rasch auf den ursprünglichen Druck auf und folgt im weiteren Verlauf dem Druck p1 im Steuerraum 10, da über die Ablaufdrossel 37 eine hydraulische Verbindung zwischen beiden Räumen 10, 39. Der Druck p1 im Steuerraum 10 beginnt etwa ab dem Zeitpunkt t3 wieder zu fallen, da die Düsennadel 8 in ihre Schließstellung zurückgleitet und dabei das Volumen des Steuerraums 10 vergrößert. Der so gewonnene Raum wird über die Zulaufdrossel aufgefüllt, was effektiv zu einem in ungefähr konstanten Druck bis zum Zeitpunkt t4 führt, zu dem die Düsennadel 8 wieder ihre Ausgangsstellung erreicht und zurück in Anlage am Düsensitz 15 ist. Während der Schließbewegung bilden die hydraulischen Kräfte auf die Stirnfläche 108 und auf die dem Düsensitz 15 zugewandte Fläche der Düsennadel 8 ein Kräftepaar, mit dem die Düsennadel 8 bewegt wird. Der Steuerraumdruck stellt sich dabei so dein, dass sich ein Kräftegleichgewicht ausbildet. Wenn die Düsennadel 8 wieder geschlossen ist, steigt der Steuerraumdruck wieder auf den Druck im Druckraum 12, also auf das Ausgangsniveau, was zum Zeitpunkt t5 erreicht ist.The lower diagram shows the stroke h of the
Wird der Druck nur innerhalb des Vorsteuerraums 39 gemessen, so lässt sich, wie man am Diagramm der
In
Die Ablaufdrossel 37 ist in diesem Ausführungsbeispiel durch die Längsbohrung innerhalb des Druckstifts 33 ausgebildet. Diese kann jedoch auch in anderer Weise ausgebildet sein. Die
In
Claims (9)
- Fuel injection valve for internal combustion engines, having a housing (1) in which a longitudinally displaceable nozzle needle (8) interacts with a nozzle seat (15) in order to open and close at least one injection opening (16), wherein the nozzle needle (8), by means of its face surface (108) averted from the nozzle seat (15), delimits a control chamber (10) which is formed in the housing (1) and which can be filled with highly pressurized fuel, wherein the control chamber (10) is connectable by means of a control valve (22) to a low-pressure chamber (18), characterized in that a pressure pin (33) is provided whose face side (133) delimits the control chamber (33) and whose face surface averted from the control chamber (33) interacts with a force sensor (35).
- Fuel injection valve according to Claim 1, characterized in that the control valve (22) comprises a control valve element (28) which interacts with a control valve seat (31) and thereby opens and closes a hydraulic connection between the control chamber (10) and the low-pressure chamber (18).
- Fuel injection valve according to Claim 2, characterized in that the hydraulic connection comprises an outflow throttle (37).
- Fuel injection valve according to Claim 3, characterized in that the outflow throttle (37) is formed in the pressure pin (33).
- Fuel injection valve according to Claim 3, characterized in that the outflow throttle (37') is formed in the housing (1).
- Fuel injection valve according to Claim 2, 3, 4 or 5, characterized in that the control valve element (28) is of sleeve-shaped form and surrounds the pressure pin (33).
- Fuel injection valve according to Claim 4, 5 or 6, characterized in that a pilot-control chamber (39) is provided which surrounds the pressure pin (33) and which is connectable by means of the control valve (22) to the low-pressure chamber (18), wherein the pilot-control chamber (39) is connected via the outflow throttle (37; 37') to the control chamber (10).
- Fuel injection valve according to Claim 3, characterized in that the pressure pin (33) is, facing towards the control chamber (10), guided in a guide bore (34) of the housing (1).
- Fuel injection valve according to Claim 8, characterized in that, on that section of the pressure pin (33) which is guided in the guide bore, there are formed one or more ground portions (40) which form the outflow throttle (37").
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE102012223244.3A DE102012223244A1 (en) | 2012-12-14 | 2012-12-14 | Fuel injection valve for internal combustion engines |
Publications (2)
Publication Number | Publication Date |
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EP2743489A1 EP2743489A1 (en) | 2014-06-18 |
EP2743489B1 true EP2743489B1 (en) | 2017-07-12 |
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Family Applications (1)
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EP13188667.3A Active EP2743489B1 (en) | 2012-12-14 | 2013-10-15 | Fuel injector valve for combustion engines |
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DE (1) | DE102012223244A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102014220345A1 (en) * | 2014-10-08 | 2016-04-14 | Robert Bosch Gmbh | Fuel injection valve |
DE102015114828A1 (en) * | 2015-09-04 | 2017-03-09 | Denso Corporation | Fuel injector with control chamber damping |
CN115288902B (en) * | 2022-09-01 | 2023-12-08 | 哈尔滨工程大学 | Low oil return amount double-lift variable oil injection rule electric control oil injector |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102009002895A1 (en) * | 2009-05-07 | 2010-11-11 | Robert Bosch Gmbh | Fuel injector with pressure sensor |
DE102009046332A1 (en) | 2009-11-03 | 2011-05-05 | Robert Bosch Gmbh | Control valve assembly |
DE102010000827A1 (en) * | 2010-01-12 | 2011-07-14 | Robert Bosch GmbH, 70469 | fuel injector |
DE102010043306B4 (en) * | 2010-11-03 | 2023-06-07 | Robert Bosch Gmbh | Method for operating a magnetic switching element, electrical circuit for operating the magnetic switching element and a control and/or regulating device |
DE102010044012A1 (en) * | 2010-11-16 | 2012-05-16 | Robert Bosch Gmbh | fuel injector |
DE102011078947A1 (en) * | 2011-04-07 | 2012-10-11 | Robert Bosch Gmbh | fuel injector |
-
2012
- 2012-12-14 DE DE102012223244.3A patent/DE102012223244A1/en not_active Withdrawn
-
2013
- 2013-10-15 EP EP13188667.3A patent/EP2743489B1/en active Active
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DE102012223244A1 (en) | 2014-06-18 |
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