EP1526274B1 - Fuel injection device, especially for a direct injection internal combustion engine - Google Patents
Fuel injection device, especially for a direct injection internal combustion engine Download PDFInfo
- Publication number
- EP1526274B1 EP1526274B1 EP04021298.7A EP04021298A EP1526274B1 EP 1526274 B1 EP1526274 B1 EP 1526274B1 EP 04021298 A EP04021298 A EP 04021298A EP 1526274 B1 EP1526274 B1 EP 1526274B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve body
- valve element
- fuel injection
- valve
- fuel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 239000000446 fuel Substances 0.000 title claims description 79
- 238000002347 injection Methods 0.000 title claims description 34
- 239000007924 injection Substances 0.000 title claims description 34
- 238000002485 combustion reaction Methods 0.000 title claims description 10
- 238000007789 sealing Methods 0.000 claims description 33
- 230000036316 preload Effects 0.000 claims 1
- 238000004519 manufacturing process Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 241001295925 Gegenes Species 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000002655 kraft paper Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000009715 pressure infiltration Methods 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/042—The valves being provided with fuel passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/08—Injectors peculiar thereto
- F02M45/086—Having more than one injection-valve controlling discharge orifices
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
- F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/161—Means for adjusting injection-valve lift
-
- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
- F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
-
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
-
- 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
- F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
-
- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/167—Means for compensating clearance or thermal expansion
Definitions
- the invention relates to a fuel injection device, in particular for an internal combustion engine with direct injection, according to the preamble of claim 1.
- the DE 40 23 223 A1 shows a fuel injector with a housing in which two mutually coaxial valve elements are guided. Both valve elements are each assigned a series of fuel outlet openings, and both valve elements are pressed by means of screw compression springs with sealing edges against corresponding housing-side valve seats.
- the pressure in a pressure chamber which is limited by an acting in the opening direction pressure surface of the outer valve element, increased. As a result, this lifts against the force of the spring from the valve seat, so that fuel can escape through its associated fuel outlet channels. If the outside Valve element has lifted, the pressure associated with the inner valve element pressure surface is subjected to high pressure. Depending on how high the pressure of the fuel is, the inner valve element opens against the force of the compression spring.
- Such fuel injectors are also referred to as "coaxial vario nozzles.”
- a different fuel outlet cross-section can be made available with them. This has the advantage that even if only a small amount of fuel to be injected, this can be atomized relatively well.
- the WO 87/06650 also describes an injection nozzle for internal combustion engines with two coaxial valve elements.
- the present invention has the object, a fuel injection device of the type mentioned in such a way that an internal combustion engine operated with it shows a particularly good emission behavior.
- the HC values in the exhaust gas are significantly improved. This is due to the fact that is reliably prevented in the fuel injection device according to the invention that the inner valve element unintentionally opens during an opening or closing movement of the outer valve element and thereby leak small amounts of fuel from the fuel injection device.
- the inner valve element is divided into a guide body and a valve body.
- the valve body is that portion of the valve element which cooperates with the housing-side valve seat and which ultimately, by its movement, releases or blocks the flow path of the fuel to the corresponding fuel outlet opening.
- there is a radial gap between this valve body and the outer valve element so that the outer valve element can not transfer any transverse forces to this valve body during its closing operation (the outer valve element therefore does not touch the valve body of the inner valve element).
- These transverse forces could lead to tilting of the inner valve element and consequently to a reduced seal between inner valve element and housing. Instead, it is the inner valve element is guided via a guide body in the outer valve element, which acts on the valve body in the closing direction.
- the outer valve element transmits transverse forces on the guide body of the inner valve element and thereby tilts when closing the outer valve member of the guide body; However, this is not forwarded to the valve body by the decoupling of the guide body from the valve body, so that it can remain reliably in the closed position.
- the guide body has a guide and sealing portion, which is formed in the vicinity of the valve body and is guided in the outer valve element sliding and fluid-tight.
- the guide body has a guide and sealing portion, which is formed away from the valve body and is guided in the outer valve element sliding and fluid-tight. This corresponds to the embodiment in conventional fuel injection devices, which reduces the changes to be made for realizing the invention and keeps the manufacturing costs low.
- a particularly advantageous embodiment of the fuel injection device according to the invention is characterized in that in a valve body facing the end face of the guide body opens a connected to a leakage connection leakage channel.
- a "pressure infiltration" is avoided.
- the area where the guide body and the valve body abut each other, is subjected to high pressure, whereby a desired opening of the inner valve member or the valve body would possibly prevented or at least delayed.
- the leakage channel opens at its end facing away from the valve body in an annular space which is formed between the inner and outer valve element. It is understood that this annular space must be present on that side of the guide and sealing portion, which faces away from the fuel outlet channels.
- Such a leakage channel can be made simple, since this annulus is usually already connected to a leakage connection. This keeps the manufacturing costs low.
- the guide body and the valve body only approximately linear contact with a circumferential and relative to the valve body radially outer sealing edge.
- a high surface pressure is locally achieved, through which a high sealing effect can be realized.
- a pressurization of the valve seat facing away from the end face of the valve body is prevented or at least reduced, which increases the reliability of the function, in particular of the inner valve element.
- a recess is present in an end face of the valve body facing the guide body or in an end face of the guide body facing the valve body, the radially outer boundary of which is designed as an annular collar with a circumferential sealing edge.
- a particularly advantageous embodiment of the fuel injection device is further characterized in that the valve body has a rounded sealing surface which cooperates with a housing-side seat edge.
- so-called “runout tolerances” can be compensated to a certain extent, which can reduce the manufacturing costs and thus also the production costs.
- the "runout tolerances” are angular deviations of the contact surface between the valve body and the guide body from a plane orthogonal to the longitudinal axis.
- this rounded sealing surface corresponds to a ring segment of the surface of a ball whose center lies on the central axis of the inner valve element.
- This design which is known in principle from ball joints, also permits an "oblique" arrangement of the valve body during operation without reducing the seal between valve body and housing. As a result, it is possible to react automatically to angle deviations arising during operation without compromising the functionality of the fuel injection device.
- a fuel system carries the overall reference numeral 10. It is used to supply an internal combustion engine with fuel, which, however, in FIG. 1 not shown in detail.
- To the fuel system 10 includes a reservoir 12 from which a conveyor 14 promotes the fuel to a fuel rail ("rail") 16.
- the conveyor 14 compresses the fuel to a very high pressure at which it is stored in the fuel rail 16.
- several fuel injectors 18 are connected, of which in FIG. 1 only two are shown. These inject the fuel in each case in a directly associated combustion chamber 20 of the internal combustion engine.
- a leakage port 24 leads from the fuel injectors 28 via a leakage line 26 to the reservoir 12 back.
- the Figures 2 and 3 show one of the fuel injectors 18 in more detail: It comprises a housing 28, of which in FIG. 2 only a nozzle body 30 and a portion of an end piece 32 are shown. By doing Nozzle body 30 has an overall cylindrical and longitudinal recess 34 is present. In the upper region of an outer valve member 36 is slidably guided and fluid-tight. In the outer valve member 36, a through hole 38 is provided, in which an inner valve member 40 is inserted. This consists of a guide body 42 and a valve body 44th
- the outer valve element 36 has on its outer circumferential surface on a circumferential shoulder, which forms a pressure surface 46 acting in the opening direction. This limits an annular pressure chamber 48, which is formed in the wall of the recess 34 and is connected via a high pressure passage 50 to the high pressure port 22. At the in the Figures 2 and 3 lower end of the outer valve member 36 is also provided in the opening direction acting pressure surface 52 ( FIG. 3 ), which delimits a pressure chamber 54, which is connected via an annular space 56 formed between the outer valve element 36 and the wall of the recess 34 with the pressure chamber 48 and thus ultimately with the high pressure port 22.
- the pressure surface 52 is bounded radially inwardly by a sealing edge 58, which cooperates with an opposite conical seat surface 60 which is present on the nozzle body 30.
- the outer valve element 36 is acted upon by a compression spring 61, which is supported on the end piece 32 in the direction of the seat surface 60.
- the outer valve element 36 is associated with a number of fuel outlet channels 62.
- the guide body 42 of the inner valve element 40 is an elongate bolt-like part, which has a smaller overall outer diameter than the inner diameter of the through-bore 38 in the outer valve element 36 FIG. 2 lower end of the Guide body 42, however, a guide and sealing portion 64 is provided, via which the guide body 42 is guided in the outer valve element 36.
- the valve body 44 comprises a cylindrical central portion 66, a subsequent thereto, rounded tapered sealing portion 68, and a conical end portion 70. Between the central portion 66 and. The recess 38 in the outer valve member 36 is in FIG. 3 a radial gap 71 visible.
- a guide body 42 facing end face of the central portion 66 has a recess 72 is present.
- the radially outer boundary is formed as an annular collar 74 with a circumferential sealing edge 76.
- the sealing edge 76 is in normal operation on a flat end face 78 of the guide body 42.
- a leakage channel 79 leads from the end face 78 of the guide body 42 through the guide body 42 obliquely through and opens into a radial wall surface of the guide body 42, in FIG. 2 above the guide and sealing portion 64 in an annular space 77 formed between the guide body 42 and the recess 34. This is ultimately connected via the leakage connection 24 with the leakage line 26.
- the sealing section 68 has a rounded sealing surface 80 (FIG. FIG. 3 ), which corresponds to a ring segment of the surface of a sphere and limits a pressure space 81.
- a center 82 of this ball lies on a central axis 84 of the inner valve member 40.
- the sealing surface 80 of the valve body 44 cooperates with a seat edge 86 which is formed in the wall of the recess 34 in the nozzle body 30.
- the inner valve element 40 is acted upon by a compression spring 88, which is also supported on the end piece 32, against the seat edge 86.
- the inner Valve element 40 is also associated with a series of fuel trip channels 90.
- the pressure which then also prevails in the pressure chamber 81, is not sufficient in this case, however, to generate at the region of the sealing surface 80 of the valve body 44 located radially outside the seat edge 86 such a force acting in the opening direction that the inner valve element 40 against the force of the spring 88 opens. From the fuel outlet channels 90 thus no fuel can escape. Because the valve body 44 is not touched by the outer valve element 36 (gap 71), it can not transmit transverse forces to the valve body 44 either during the opening process or during the closing process. The outer valve element 36 can therefore also induce no tilting movement in the valve body 44, by which the sealing surface 80 at least partially lifted off from the seat edge 86 and thus would lead to the escape of a small amount of fuel.
- FIG. 4a shows the stroke of the outer valve element 36, in FIG. 4b the stroke of the valve body 44, each at a voltage applied to the high pressure port 22 average fuel pressure. It will be appreciated that the position of the valve body 44 is not affected during opening and closing of the outer valve member 36.
- the sealing edge 76 effectively prevents high-pressure fuel from reaching the recess 72 via the gap 71 and can generate a force acting in the closing direction of the valve body 44 there. This could affect the safe opening of the valve body 44.
- fuel entering the recess 72 is nevertheless discharged through the leakage channel 79 to the leakage connection 24.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung betrifft eine Kraftstoff-Einspritzvorrichtung, insbesondere für eine Brennkraftmaschine mit Direkteinspritzung, nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injection device, in particular for an internal combustion engine with direct injection, according to the preamble of claim 1.
Die
Derartige Kraftstoff-Einspritzvorrichtungen werden auch als "Koaxial-Variodüsen" bezeichnet. Mit ihnen kann je nach einzuspritzender Kraftstoffmenge ein unterschiedlicher Kraftstoff-Austrittsquerschnitt zur Verfügung gestellt werden. Dies hat den Vorteil, dass auch dann, wenn nur eine geringe Kraftstoffmenge eingespritzt werden soll, dieser vergleichsweise gut zerstäubt werden kann.Such fuel injectors are also referred to as "coaxial vario nozzles." Depending on the fuel quantity to be injected, a different fuel outlet cross-section can be made available with them. This has the advantage that even if only a small amount of fuel to be injected, this can be atomized relatively well.
Die
Die vorliegende Erfindung hat die Aufgabe, eine Kraftstoff-Einspritzvorrichtung der eingangs genannten Art so weiterzubilden, dass eine mit ihr betriebene Brennkraftmaschine ein besonders gutes Emissionsverhalten zeigt.The present invention has the object, a fuel injection device of the type mentioned in such a way that an internal combustion engine operated with it shows a particularly good emission behavior.
Diese Aufgabe wird durch eine Kraftstoff-Einspritzvorrichtung mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a fuel injection device having the features of claim 1.
Bei der Anwendung der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung bei einer Brennkraftmaschine werden die HC-Werte im Abgas deutlich verbessert. Dies hängt damit zusammen, dass bei der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung zuverlässig verhindert wird, dass das innere Ventilelement bei einer Öffnungs- oder Schließbewegung des äußeren Ventilelements ungewollt öffnet und hierdurch geringe Kraftstoffmengen aus der Kraftstoff-Einspritzvorrichtung austreten.When using the fuel injection device according to the invention in an internal combustion engine, the HC values in the exhaust gas are significantly improved. This is due to the fact that is reliably prevented in the fuel injection device according to the invention that the inner valve element unintentionally opens during an opening or closing movement of the outer valve element and thereby leak small amounts of fuel from the fuel injection device.
Erreicht wird dies durch eine Entkopplung eines Teils des inneren Ventilelements vom äußeren Ventilelement: Bei der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung ist das innere Ventilelement in einen Führungskörper und einen Ventilkörper aufgeteilt. Der Ventilkörper ist jener Bereich des Ventilelements, der mit dem gehäuseseitigen Ventilsitz zusammenarbeitet und der letztlich durch seine Bewegung den Strömungsweg des Kraftstoffs zu der entsprechenden Kraftstoff-Austrittsöffnung freigibt oder blockiert. Zwischen diesem Ventilkörper und dem äußeren Ventilelement ist jedoch ein radialer Spalt vorhanden, so dass das äußere Ventilelement insbesondere während seines Schließvorgangs keine Querkräfte auf diesen Ventilkörper übertragen kann (das äußere Ventilelement berührt den Ventilkörper des inneren Ventilelements also nicht). Diese Querkräfte könnten zu einem Verkippen des inneren Ventilelements und in der Folge zu einer reduzierten Abdichtung zwischen innerem Ventilelement und Gehäuse führen. Stattdessen ist das innere Ventilelement über einen Führungskörper im äußeren Ventilelement geführt, der den Ventilkörper in Schließrichtung beaufschlagt.This is achieved by decoupling a part of the inner valve element from the outer valve element. In the fuel injection device according to the invention, the inner valve element is divided into a guide body and a valve body. The valve body is that portion of the valve element which cooperates with the housing-side valve seat and which ultimately, by its movement, releases or blocks the flow path of the fuel to the corresponding fuel outlet opening. However, there is a radial gap between this valve body and the outer valve element, so that the outer valve element can not transfer any transverse forces to this valve body during its closing operation (the outer valve element therefore does not touch the valve body of the inner valve element). These transverse forces could lead to tilting of the inner valve element and consequently to a reduced seal between inner valve element and housing. Instead, it is the inner valve element is guided via a guide body in the outer valve element, which acts on the valve body in the closing direction.
So kann es zwar vorkommen, dass das äußere Ventilelement Querkräfte auf den Führungskörper des inneren Ventilelements überträgt und hierdurch beim Schließen des äußeren Ventilelements der Führungskörper verkippt; durch die Entkopplung des Führungskörpers vom Ventilkörper wird dies jedoch nicht an den Ventilkörper weitergeleitet, so dass dieser zuverlässig in der geschlossenen Stellung verbleiben kann.Thus, it may happen that the outer valve element transmits transverse forces on the guide body of the inner valve element and thereby tilts when closing the outer valve member of the guide body; However, this is not forwarded to the valve body by the decoupling of the guide body from the valve body, so that it can remain reliably in the closed position.
Dabei sei an dieser Stelle darauf hingewiesen, dass die erfindungsgemäßen Vorteile auch bei herkömmlichen Kraftstoff-Einspritzvorrichtungen erzielt werden können, wenn nur das innere Ventilelement durch die erfindungsgemäß vorgeschlagene zweigeteilte Ausgestaltung ersetzt wird. Hierdurch können die Kosten bei der Herstellung der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung niedrig gehalten werden.It should be noted at this point that the advantages of the invention can be achieved even with conventional fuel injection devices, if only the inner valve element is replaced by the present invention proposed two-part design. As a result, the costs in the production of the fuel injection device according to the invention can be kept low.
Vorteilhafte Weiterbildungen der Erfindung sind in Unteransprüchen angegeben.Advantageous developments of the invention are specified in subclaims.
Zunächst wird vorgeschlagen, dass der Führungskörper einen Führungs- und Dichtabschnitt aufweist, welcher in der Nähe des Ventilkörpers ausgebildet ist und im äußeren Ventilelement gleitend und fluiddicht geführt ist. Dies hat den Vorteil, dass ein dem inneren Ventilelement zugeordnetes Totvolumen vergleichsweise klein gehalten werden kann, was die Präzision bei der Einspritzung von Kraftstoff durch die erfindungsgemäße Kraftstoff-Einspritzvorrichtung verbessert, da ein ungewolltes Austreten von Kraftstoff nochmals verringert oder sogar ganz vermieden werden kann. Auch das Emissionsverhalten wird hierdurch nochmals verbessert.First, it is proposed that the guide body has a guide and sealing portion, which is formed in the vicinity of the valve body and is guided in the outer valve element sliding and fluid-tight. This has the advantage that a dead volume associated with the inner valve element can be kept comparatively small, which improves the precision in the injection of fuel by the fuel injection device according to the invention, since an unintentional escape of fuel is reduced even further or even can be completely avoided. The emission behavior is thereby further improved.
Alternativ hierzu ist es aber auch möglich, dass der Führungskörper einen Führungs- und Dichtabschnitt aufweist, welcher vom Ventilkörper entfernt ausgebildet ist und im äußeren Ventilelement gleitend und fluiddicht geführt ist. Dies entspricht der Ausführungsform bei herkömmlichen Kraftstoff-Einspritzvorrichtungen, was die zur Realisierung der Erfindung vorzunehmenden Änderungen reduziert und die Herstellkosten niedrig hält.Alternatively, it is also possible that the guide body has a guide and sealing portion, which is formed away from the valve body and is guided in the outer valve element sliding and fluid-tight. This corresponds to the embodiment in conventional fuel injection devices, which reduces the changes to be made for realizing the invention and keeps the manufacturing costs low.
Eine besonders vorteilhafte Ausgestaltung der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung zeichnet sich dadurch aus, dass in eine dem Ventilkörper zugewandte Stirnfläche des Führungskörpers ein mit einem Leckageanschluss verbundener Leckagekanal mündet. Hierdurch wird eine "Druckunterwanderung" vermieden. Hierunter wird verstanden, dass der Bereich, an dem der Führungskörper und der Ventilkörper aneinander stoßen, mit hohem Druck beaufschlagt wird, wodurch ein gewolltes Öffnen des inneren Ventilelements beziehungsweise des Ventilkörpers unter Umständen verhindert oder zumindest verzögert würde.A particularly advantageous embodiment of the fuel injection device according to the invention is characterized in that in a valve body facing the end face of the guide body opens a connected to a leakage connection leakage channel. As a result, a "pressure infiltration" is avoided. By this is meant that the area where the guide body and the valve body abut each other, is subjected to high pressure, whereby a desired opening of the inner valve member or the valve body would possibly prevented or at least delayed.
In Weiterbildung hierzu wird vorgeschlagen, dass der Leckagekanal an seinem vom Ventilkörper abgewandten Ende in einen Ringraum mündet, der zwischen dem inneren und dem äußeren Ventilelement ausgebildet ist. Es versteht sich, dass dieser Ringraum auf jener Seite des Führungs- und Dichtabschnitts vorhanden sein muss, der von den Kraftstoff-Austrittskanälen abgewandt ist. Ein solcher Leckagekanal kann einfach ausgeführt sein, da dieser Ringraum üblicherweise ohnehin mit einem Leckageanschluss verbunden ist. Dies hält die Herstellkosten niedrig.In a further development, it is proposed that the leakage channel opens at its end facing away from the valve body in an annular space which is formed between the inner and outer valve element. It is understood that this annular space must be present on that side of the guide and sealing portion, which faces away from the fuel outlet channels. Such a leakage channel can be made simple, since this annulus is usually already connected to a leakage connection. This keeps the manufacturing costs low.
Ferner wird vorgeschlagen, dass sich der Führungskörper und der Ventilkörper nur in etwa linienhaft mit einer umlaufenden und bezüglich des Ventilkörpers radial außen liegenden Dichtkante berühren. Durch eine solche linienhafte Berührung wird örtlich eine hohe Flächenpressung erzielt, durch die eine hohe Dichtwirkung realisiert werden kann. Hierdurch wird eine Druckbeaufschlagung der vom Ventilsitz abgewandten Stirnfläche des Ventilkörpers verhindert oder zumindest reduziert, was die Funktionszuverlässigkeit insbesondere des inneren Ventilelements erhöht.It is also proposed that the guide body and the valve body only approximately linear contact with a circumferential and relative to the valve body radially outer sealing edge. By such a linear contact a high surface pressure is locally achieved, through which a high sealing effect can be realized. As a result, a pressurization of the valve seat facing away from the end face of the valve body is prevented or at least reduced, which increases the reliability of the function, in particular of the inner valve element.
In Weiterbildung hierzu wird vorgeschlagen, dass in einer dem Führungskörper zugewandten Stirnfläche des Ventilkörpers oder in einer dem Ventilkörper zugewandten Stirnfläche des Führungskörpers eine Ausnehmung vorhanden ist, deren radial äußere Begrenzung als ringförmiger Kragen mit einer umlaufenden Dichtkante ausgebildet ist. Hierdurch wird die Herstellung der umlaufenden Dichtkante vereinfacht, was die Herstellkosten der Kraftstoff-Einspritzvorrichtung senkt.In a further development, it is proposed that a recess is present in an end face of the valve body facing the guide body or in an end face of the guide body facing the valve body, the radially outer boundary of which is designed as an annular collar with a circumferential sealing edge. As a result, the production of the peripheral sealing edge is simplified, which reduces the manufacturing cost of the fuel injection device.
Eine besonders vorteilhafte Ausgestaltung der Kraftstoff-Einspritzvorrichtung zeichnet sich ferner dadurch aus, dass der Ventilköper eine gerundete Dichtfläche aufweist, welche mit einer gehäuseseitigen Sitzkante zusammenarbeitet. Hierdurch können so genannte "Planlauftoleranzen" in einem gewissen Umfange ausgeglichen werden, was den Fertigungsaufwand und somit auch die Herstellungskosten senken kann. Bei den "Planlauftoleranzen" handelt es sich um Winkelabweichungen der Kontaktfläche zwischen dem Ventilkörper und dem Führungskörper von einer zur Längsachse orthogonalen Ebene.A particularly advantageous embodiment of the fuel injection device is further characterized in that the valve body has a rounded sealing surface which cooperates with a housing-side seat edge. As a result, so-called "runout tolerances" can be compensated to a certain extent, which can reduce the manufacturing costs and thus also the production costs. The "runout tolerances" are angular deviations of the contact surface between the valve body and the guide body from a plane orthogonal to the longitudinal axis.
Dabei ist es besonders vorteilhaft, wenn diese gerundete Dichtfläche einem Ringsegment der Oberfläche einer Kugel entspricht, deren Mittelpunkt auf der Mittelachse des inneren Ventilelements liegt. Diese vom Grundsatz her von Kugelgelenken bekannte Ausgestaltung ermöglicht auch im Betrieb eine "schräge" Anordnung des Ventilkörpers ohne Reduzierung der Abdichtung zwischen Ventilkörper und Gehäuse. Hierdurch kann auf während des Betriebs entstehende Winkelabweichungen automatisch reagiert werden, ohne dass die Funktionsfähigkeit der Kraftstoff-Einspritzvorrichtung beeinträchtigt wird.It is particularly advantageous if this rounded sealing surface corresponds to a ring segment of the surface of a ball whose center lies on the central axis of the inner valve element. This design, which is known in principle from ball joints, also permits an "oblique" arrangement of the valve body during operation without reducing the seal between valve body and housing. As a result, it is possible to react automatically to angle deviations arising during operation without compromising the functionality of the fuel injection device.
Nachfolgend werden besonders bevorzugte Ausführungsbeispiele der vorliegenden Erfindung unter Bezugnahme auf die beiliegende Zeichnung näher erläutert. In der Zeichnung zeigen:
- Figur 1
- eine schematische Darstellung eines Kraftstoffsystems einer Brennkraftmaschine mit mehreren Kraftstoff-Einspritzvorrichtungen;
- Figur 2
- eine teilweise geschnittene Darstellung einer der Kraftstoff-Einspritzvorrichtungen von
Figur 1 ; - Figur 3
- eine Detailansicht III von
Figur 2 ; - Figur 4a
- ein Diagramm, in dem der Hub eines äußeren Ventilelements der Kraftstoff-Einspritzvorrichtung von
Figur 2 über der Zeit aufgetragen ist; - Figur 4b
- ein Diagramm ähnlich
Figur 4a für ein inneres Ventilelement; und - Figur 5
- eine Darstellung ähnlich
Figur 2 einer alternativen Ausführungsform einer Kraftstoff-Einspritzvorrichtung.
- FIG. 1
- a schematic representation of a fuel system of an internal combustion engine having a plurality of fuel injection devices;
- FIG. 2
- a partially sectioned view of one of the fuel injectors of
FIG. 1 ; - FIG. 3
- a detailed view III of
FIG. 2 ; - FIG. 4a
- a diagram in which the stroke of an outer valve element of the fuel injection device of
FIG. 2 is plotted over time; - FIG. 4b
- a diagram similar
FIG. 4a for an inner valve element; and - FIG. 5
- a representation similar
FIG. 2 an alternative embodiment of a fuel injection device.
In
Zu dem Kraftstoffsystem 10 gehört ein Vorratsbehälter 12, aus dem eine Fördereinrichtung 14 den Kraftstoff zu einer Kraftstoff-Sammelleitung ("Rail") 16 fördert. Die Fördereinrichtung 14 komprimiert den Kraftstoff dabei auf einen sehr hohen Druck, bei dem er in der Kraftstoff-Sammelleitung 16 gespeichert ist. An Letztere sind mehrere Kraftstoff-Einspritzvorrichtungen 18 angeschlossen, von denen in
Die
Das äußere Ventilelement 36 weist auf seiner äußeren Mantelfläche einen umlaufenden Absatz auf, welcher eine in Öffnungsrichtung wirkende Druckfläche 46 bildet. Diese begrenzt einen ringförmigen Druckraum 48, der in der Wand der Ausnehmung 34 ausgebildet ist und über einen Hochdruckkanal 50 mit dem Hochdruckanschluss 22 verbunden ist. An dem in den
Beim Führungskörper 42 des inneren Ventilelements 40 handelt es sich um ein langgestrecktes bolzenartiges Teil, welches insgesamt einen kleineren Außendurchmesser aufweist als der Innendurchmesser der Durchgangsbohrung 38 im äußeren Ventilelement 36. Am in
In einer dem Führungskörper 42 zugewandten Stirnfläche des Zentralabschnitts 66 ist eine Ausnehmung 72 vorhanden. Deren radial äußere Begrenzung ist als ringförmiger Kragen 74 mit einer umlaufenden Dichtkante 76 ausgebildet. Die Dichtkante 76 liegt im Normalbetrieb an einer planen Endfläche 78 des Führungskörpers 42 an. Ein Leckagekanal 79 führt von der Endfläche 78 des Führungskörpers 42 durch den Führungskörper 42 schräg hindurch und mündet in eine radiale Wandfläche des Führungskörpers 42, und zwar in
Der Dichtabschnitt 68 weist eine gerundete Dichtfläche 80 auf (
Die Kraftstoff-Einspritzvorrichtung 18 arbeitet folgendermaßen:
- Wenn nur eine geringe Kraftstoffmenge eingespritzt werden soll, wird an
den Hochdruckanschluss 22 ein mittlerer Druck angelegt. Hierdurch liegt auchim Druckraum 48und im Druckraum 54 ein entsprechender Druck an, der anden Druckflächen 46 und 52 entsprechende in Öffnungsrichtung des äußeren Ventilelements 36 wirkende Kräfte erzeugt. Dies hat zur Folge, dassdas äußere Ventilelement 36 gegen die Kraft derFeder 61 öffnet, das heißt, dass dieDichtkante 58von der Sitzfläche 60 abhebt. Hierdurch kann Kraftstoff durch die Kraftstoff-Austrittskanäle 62 ausströmen.
- If only a small amount of fuel is to be injected, a medium pressure is applied to the
high pressure port 22. As a result, a corresponding pressure also prevails in thepressure chamber 48 and in thepressure chamber 54, which generates corresponding forces acting on the pressure surfaces 46 and 52 in the opening direction of theouter valve element 36. This has the consequence that theouter valve element 36 opens against the force of thespring 61, that is, the sealingedge 58 lifts from theseat surface 60. As a result, fuel can flow out through thefuel outlet channels 62.
Der Druck, der dann auch im Druckraum 81 herrscht, reicht in diesem Fall jedoch nicht aus, um an dem radial außerhalb von der Sitzkante 86 liegenden Bereich der Dichtfläche 80 des Ventilkörpers 44 eine solche in Öffnungsrichtung wirkende Kraft zu erzeugen, dass auch das innere Ventilelement 40 gegen die Kraft der Feder 88 öffnet. Aus den Kraftstoff-Austrittskanälen 90 kann somit kein Kraftstoff austreten. Dadurch, dass der Ventilkörper 44 vom äußeren Ventilelement 36 nicht berührt wird (Spalt 71), kann dieses weder während des Öffnungsvorganges noch während des Schließvorganges Querkräfte an den Ventilkörper 44 übertragen. Das äußere Ventilelement 36 kann daher auch keine Kippbewegung beim Ventilkörper 44 induzieren, durch die die Dichtfläche 80 wenigstens bereichsweise von der Sitzkante 86 abheben und somit zum Austritt einer geringen Kraftstoffmenge führen würde.The pressure, which then also prevails in the
Durch die Entkopplung des Ventilkörpers 44 vom äußeren Ventilelement 36 wird also wirkungsvoll verhindert, dass während des Öffnungsvorgangs des äußeren Ventilelements 36 oder/und während des anschließenden Schließvorganges (wenn der Druck am Hochdruckanschluss 22 wieder abgesenkt wird) Kraftstoff aus den Kraftstoff-Austrittskanälen 90 ungewollt austritt. Dies ergibt sich auch aus den
Soll eine größere Kraftstoffmenge eingespritzt werden, wird am Hochdruckanschluss 22 ein entsprechender hoher Kraftstoffdruck angelegt. Dieser ist so hoch, dass nach dem Öffnen des äußeren Ventilelements 36 der dann auch im Druckraum 81 herrschende und an der Dichtfläche 80 anliegende Druck ausreicht, um das innere Ventilelement 40 gegen die Kraft der Feder 88 zu öffnen.' Kraftstoff kann nun durch beide Reihen von Kraftstoff-Austrittskanälen 62 und 90 austreten.If a larger amount of fuel to be injected, a corresponding high fuel pressure is applied to the
Durch die Dichtkante 76 wird wirkungsvoll verhindert, dass unter hohem Druck stehender Kraftstoff über den Spalt 71 in die Ausnehmung 72 gelangen und dort eine in Schließrichtung des Ventilkörpers 44 wirkende Kraft erzeugen kann. Dies könnte das sichere Öffnen des Ventilkörpers 44 beeinträchtigen. Zusätzlich wird dennoch in die Ausnehmung 72 eintretender Kraftstoff durch den Leckagekanal 79 zum Leckageanschluss 24 abgeführt.The sealing
Eine alternative Ausführungsform einer Kraftstoff-Einspritzvorrichtung 18 ist in
- Während bei der in
Figur 2 gezeigten Ausführungsform der Führungs-und Dichtabschnitt 64 an dem in der dortigen Figur unteren Ende des äußeren Ventilelements 36 angeordnet ist, ist er bei der inFigur 5 gezeigten Ausführungsform am oberen Ende, alsovom Ventilkörper 44 entfernt, angeordnet. Entsprechend führt derLeckagekanal 79 nicht schräg, sondern koaxial zum äußeren Ventilelement 36 durch dieses hindurch und wird erst oberhalb von dem Führungs-und Dichtabschnitt 64 ineinem Zwischenstück 92 schräg nach außen geführt.
- While at the in
FIG. 2 embodiment shown, the guide and sealingportion 64 is disposed at the lower end in the local figure of theouter valve member 36, it is at the inFIG. 5 shown embodiment at the upper end, ie away from thevalve body 44, respectively. Accordingly, theleakage channel 79 does not lead obliquely, but coaxially to theouter valve member 36 therethrough and is guided above the guide and sealingportion 64 in anintermediate piece 92 obliquely outwards.
Claims (9)
- Fuel injection apparatus (18), in particular for an internal combustion engine with direct injection, having a housing (28) and having at least two valve elements (36, 40) which are arranged in the housing (28) and which are coaxial with respect to one another and to which there is assigned in each case at least one fuel outlet opening (62, 90), having a preload device (61, 88) which acts on the valve elements (36, 40) in a closing direction, and having in each case at least one pressure surface (46, 52, 80), acting in an opening direction, on the valve elements (36, 40), wherein the pressure surfaces (36, 52, 80) each delimit a pressure chamber (48, 54, 81) which can be connected to a high-pressure port (22), wherein the inner valve element (40) comprises at least the following: a valve body (44) which interacts with a valve seat (86) on the housing, and a guide body (42) which is guided in the outer valve element (36) and which, in the normal situation, acts on the valve body (44) in the closing direction, characterized in that, between the valve body (44) and the outer valve element (36), there is provided a radial gap (71) which is such that the outer valve element (36) does not make contact with the valve body (44) of the inner valve element (40).
- Fuel injection apparatus (18) according to Claim 1, characterized in that the guide body (42) has a guiding and sealing section (64) which is formed in the vicinity of the valve body (44) and which is guided in sliding and fluid-tight fashion in the outer valve element (36).
- Fuel injection apparatus (18) according to Claim 1, characterized in that the guide body (42) has a guiding and sealing section (64) which is formed remote from the valve body (44) and which is guided in sliding and fluid-tight fashion in the outer valve element (36).
- Fuel injection apparatus (18) according to one of the preceding claims, characterized in that a leakage duct (79) which is connected to a leakage port (24) opens out into a face surface (78), facing toward the valve body (44), of the guide body (42).
- Fuel injection apparatus (18) according to Claim 4, characterized in that the leakage duct (79) opens out, at its end facing away from the valve body (44), into a ring-shaped chamber (77) which is formed between the inner valve element (40) and the outer valve element (36).
- Fuel injection apparatus (18) according to one of the preceding claims, characterized in that the guide body (42) and the valve body (44) make contact only linearly with an encircling sealing edge (86) situated radially at the outside in relation to the valve body (42) .
- Fuel injection apparatus (18) as claimed in claim 6, characterized in that, in a face surface, facing toward the guide body (42), of the valve body (44) or in a face surface, facing toward the valve body, of the guide body, there is provided a recess (72) whose radially outer delimitation is in the form of a ring-shaped collar (74) with an encircling sealing edge (76).
- Fuel injection apparatus (18) according to one of the preceding claims, characterized in that the valve body (44) has a rounded sealing surface (80) which interacts with a seat edge (80) on the housing.
- Fuel injection apparatus (18) according to Claim 8, characterized in that the rounded sealing surface (80) corresponds to a ring-shaped segment of the surface of a sphere, the central point (82) of which lies on the central axis (84) of the inner valve element (40).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2003148978 DE10348978A1 (en) | 2003-10-22 | 2003-10-22 | Fuel injection device, in particular for a direct injection internal combustion engine |
DE10348978 | 2003-10-22 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1526274A1 EP1526274A1 (en) | 2005-04-27 |
EP1526274B1 true EP1526274B1 (en) | 2015-11-11 |
Family
ID=34384393
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04021298.7A Expired - Lifetime EP1526274B1 (en) | 2003-10-22 | 2004-09-08 | Fuel injection device, especially for a direct injection internal combustion engine |
Country Status (2)
Country | Link |
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EP (1) | EP1526274B1 (en) |
DE (1) | DE10348978A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
TR200402050A2 (en) * | 2004-08-18 | 2006-03-21 | Robert Bosch Gmbh | Dual seating diameter injector with coaxial areal contact |
EP1744050B1 (en) * | 2005-07-13 | 2008-04-09 | Delphi Technologies, Inc. | Injection nozzle |
ATE391849T1 (en) | 2005-07-13 | 2008-04-15 | Delphi Tech Inc | INJECTOR |
DE102007035752A1 (en) * | 2007-07-31 | 2009-02-05 | Robert Bosch Gmbh | Fuel injector with a seated on the cone valve seat of a nozzle needle centering as a guide for the nozzle needle |
EP2060774A1 (en) * | 2007-11-16 | 2009-05-20 | Delphi Technologies, Inc. | Fuel injector |
JP2009162184A (en) * | 2008-01-09 | 2009-07-23 | Toyota Motor Corp | Fuel injection valve |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2710138A1 (en) * | 1977-03-09 | 1978-09-14 | Maschf Augsburg Nuernberg Ag | MULTI-HOLE INJECTION NOZZLE |
JPS60125767A (en) * | 1983-12-09 | 1985-07-05 | Nissan Motor Co Ltd | Fuel injection nozzle of diesel engine |
JPS60259768A (en) * | 1984-06-06 | 1985-12-21 | Mitsubishi Heavy Ind Ltd | Fuel injection valve |
WO1987006650A1 (en) | 1986-04-25 | 1987-11-05 | Voest-Alpine Automotive Gesellschaft M.B.H. | Injection nozzle for internal combustion engines |
DE4023223A1 (en) | 1990-07-21 | 1992-01-23 | Bosch Gmbh Robert | FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES |
DE4432686C2 (en) * | 1994-09-14 | 1996-09-05 | Man B & W Diesel Ag | Cross-section controlled injection nozzle |
EP2003323B1 (en) * | 1999-10-06 | 2010-06-30 | Delphi Technologies Holding S.à.r.l. | Fuel injector |
DE10034444A1 (en) * | 2000-07-15 | 2002-01-24 | Bosch Gmbh Robert | Fuel injector |
GB0021296D0 (en) * | 2000-08-30 | 2000-10-18 | Ricardo Consulting Eng | A dual mode fuel injector |
DE10118699A1 (en) * | 2001-04-17 | 2002-10-31 | Bosch Gmbh Robert | Fuel injection device and fuel system for internal combustion engines, and internal combustion engine |
DE10307002A1 (en) * | 2003-02-19 | 2004-09-09 | Volkswagen Mechatronic Gmbh & Co. Kg | Fuel injection nozzle has outer nozzle needle and control element in form of inner nozzle needle with first and second lower and higher fuel outlet cross-section positions |
-
2003
- 2003-10-22 DE DE2003148978 patent/DE10348978A1/en not_active Withdrawn
-
2004
- 2004-09-08 EP EP04021298.7A patent/EP1526274B1/en not_active Expired - Lifetime
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EP1526274A1 (en) | 2005-04-27 |
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