EP0606436B1 - Fuel injection nozzle for internal combustion engines - Google Patents
Fuel injection nozzle for internal combustion engines Download PDFInfo
- Publication number
- EP0606436B1 EP0606436B1 EP93915674A EP93915674A EP0606436B1 EP 0606436 B1 EP0606436 B1 EP 0606436B1 EP 93915674 A EP93915674 A EP 93915674A EP 93915674 A EP93915674 A EP 93915674A EP 0606436 B1 EP0606436 B1 EP 0606436B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve needle
- piston
- stroke
- pressure
- injection nozzle
- 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
- 238000002347 injection Methods 0.000 title claims abstract description 25
- 239000007924 injection Substances 0.000 title claims abstract description 25
- 239000000446 fuel Substances 0.000 title claims abstract description 17
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 4
- 230000005540 biological transmission Effects 0.000 claims description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000002679 ablation Methods 0.000 description 1
- 238000000418 atomic force spectrum Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
Definitions
- the invention relates to a fuel injector according to the preamble of claim 1.
- Injectors of this type have a pre-injection and a main injection to reduce the combustion noise by controlling the stroke of the valve needle.
- valve needle In an injection nozzle of this type known from EP-A-240 693, the valve needle abuts the piston of the pressure transmission device at the end of the forward stroke, which stops the further movement of the valve needle until the fuel pressure has risen to such an extent that its force exerted on the valve needle in the opening direction the force of the closing spring and the force exerted by the piston exceeds.
- the known injection nozzle is small, the partition is subject to a complicated manufacturing process due to the design of the pressure chamber and its connecting channel.
- a further injection nozzle is known from GB-A-2 086 473, which forms the closest prior art, in which a pressure space is limited between the rear of the valve needle and an intermediate piston.
- This pressure chamber cannot be relieved during the first stroke phase of the valve member, or can only be relieved via a throttle, so that the forward stroke of the valve member is damped and only a very flat opening stroke curve takes place.
- the pressure chamber is then relieved of pressure over a larger opening cross section, so that the opening stroke movement against the force of the return spring now takes place very quickly in this second stroke phase.
- a two-stage opening stroke profile is thus achieved on this injection nozzle, in which initially a very small opening cross section is slowly released and in a second opening stroke phase the remaining opening stroke path is traveled very quickly.
- the invention has for its object to form a two-stage opening stroke course of the valve member in a structurally simple manner, in which the opening stroke course of the preliminary stroke is relatively steep, while after passing through the preliminary stroke there is a flatter opening of the valve needle.
- the fuel injector according to the invention with the features of claim 1 has the advantage that Achieve a stepped opening stroke of the closing needle down to the piston, the same parts are used as in a single-spring holder, the piston being formed by a special but nevertheless easy to manufacture design of the pressure bolt transmitting the closing force of the closing spring to the valve needle.
- FIG. 1 shows an injection nozzle in longitudinal section
- FIG. 2 shows a detail A from FIG. 1 on an enlarged scale, left in the closed and right in the open position of the valve needle
- FIG. 3 shows an alternative to the exemplary embodiment according to FIG. 2, also left in the closed and right in the open position of the valve needle.
- the injection nozzle has a nozzle body 10 which is clamped together with an intermediate disk 11 with a union nut 13 to a holding body 12.
- a valve needle 15 is slidably mounted in the nozzle body 10 and cooperates with a valve seat 16 which is turned inwards and which is arranged in front of a plurality of spray openings 17 in the nozzle body 10.
- the guide bore 18 of the valve needle 15 is, as usual, expanded at one point to a pressure chamber 19, in the area of which the valve needle 15 has a pressure shoulder 19 and which is connected via a channel 22 and a filter body 23 to a connecting piece 24 on the holding body 12 for connecting a fuel line is.
- the fuel acting on the pressure shoulder 20 of the valve needle 15 pushes the valve needle 15 upward against the graduated force curve of a closing force arrangement described below, the fuel being injected through the injection openings 17 in a pre-injection phase and a main injection phase.
- a spring chamber 26 is formed for receiving a closing spring 27, which is supported on the one hand via a disk 28 on the bottom of the chamber 26 and on the other hand on a pressure piece 29.
- the pressure piece 29 rests on a piston 30 which is tightly guided in a cylindrical through bore 31 in the intermediate plate 11.
- the piston 30 passes through the through hole 31 completely and is supported on the valve needle 15, which loads it in the closing direction.
- a longitudinal groove 35 in the jacket of the piston 30 connects this pressure chamber 33 at times with the spring chamber 26, which is relieved of pressure via a leak channel 38 and a connecting piece 39.
- the longitudinal groove 35 is delimited by a control edge 36 which, in the closed position of the valve needle 15 and piston 30 supported thereon, is at a distance from the annular edge 37 at the transition of the partial surface into the through bore 31 of the intermediate disk 11 h v , which corresponds to the required advance stroke of the valve needle 11.
- a flat ablation for example a surface grinding, can alternatively also be arranged on the piston 30.
- the diameter d K or the hydraulic effective area of the piston 30 is smaller than the diameter D N or the effective area of the valve needle 15.
- the end face 41 of the valve needle 15 delimiting the pressure chamber 33 is flat and the opposite end face 42 of the Piston 30 crowned.
- the valve needle 15 has, as usual, a pressure pin 44 which is offset over a shoulder 43 and which projects with play into a blind bore 45 of the piston 30 and supports it on the base 46 of the blind bore 45.
- the injection nozzle works as follows: When fuel is supplied from an injection pump through the channel 22 into the pressure chamber 19, when a certain opening pressure is reached, the valve needle 15 is counteracted by the action of the closing spring 27, which loads the valve needle 15 indirectly via the piston 30 Valve seat 16 lifted off; injection begins. With increasing pressure, the valve needle 15 continues to lift off the valve seat 16 and thereby moves the piston 30 until its control edge 36 interrupts the connection of the pressure chamber 33 to the spring chamber 26 after a preliminary stroke h v . During this preliminary stroke phase, the valve needle 15 displaces more fuel volume in the pressure chamber 33 due to its large diameter than is released by directly displacing the piston 30, which has a smaller diameter.
- the differential volume is displaced from the pressure chamber 33 through the longitudinal groove 35 in the piston 30 into the pressure-relieved spring chamber 36.
- the closing spring 27 is tensioned with a force that results from the increasing fuel supply pressure in connection with the effective area of the valve needle 15, neglecting the friction losses.
- a control pressure then builds up in the pressure chamber 33 under the pumping action of the valve needle 15, which is still acted upon by the increasing supply pressure. which acts on the piston 30. Since the effective area on the supply side of the valve needle 15 and the effective area on the side delimiting the pressure chamber 33 are of the same size, this control pressure is essentially the same as the supply pressure.
- the volume displaced by the valve needle 15 displaces the piston 30, which is loaded by the closing spring 26 which is further biased by the forward stroke h v .
- the effective area of the piston 30 is smaller than that of the valve needle 15, and thus at the end of the forward stroke h V, the force generated by the piston 30 is smaller than the force generated by the valve needle 15, which is the same as the closing spring force, the piston 30 remains so long in contact with the valve needle 15 until the supply pressure and thus the control pressure in the pressure chamber 33 have risen so far that the force generated by the piston 30 exceeds the biasing force of the closing spring 27 reached at the end of the forward stroke in the preliminary stroke position.
- valve needle 15 also remains in the pre-stroke position. If the supply pressure and thus also the control pressure in the pressure chamber 33 then reach a value on the basis of which the piston 30 is loaded with a force which is equal to and greater than that of the pretensioned closing spring 26, a hydraulic stroke conversion from the valve needle 15 to the piston 30 takes place a, due to which the tensioning of the closing spring 27 is now carried out by the piston 30. Depending on the difference in the diameter of the valve needle 15 and the piston 30, the piston 30 is now displaced by a larger lifting unit as the pressure increases per stroke unit of the valve needle 15.
- the piston 30 thereby lifts off the end face 41 of the valve needle 15 and moves away from it until the valve needle 15 strikes the intermediate disk 11 with its end face 41 or shoulder 43 after passing through the entire stroke h g . Since, as mentioned above, the effective area of the piston 30 is smaller than that of the valve needle 15, the travel of the piston 30 becomes greater than that of the valve needle 15 after the advance stroke h v has been completed. that with the same spring stiffness the closing force exerted by the piston 30 on the hydraulic cushion in the pressure chamber 33 on the valve needle 15 becomes greater, the characteristic of the described injection nozzle thus corresponds to that of a two-spring holder.
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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)
Abstract
Description
Die Erfindung bezieht sich auf eine Kraftstoff-Einspritzdüse nach der Gattung des Anspruchs 1. Einspritzdüsen dieser Gattung haben zum Senken des Verbrennungsgeräusches eine Vor- und eine Haupteinspritzung durch Hubsteuerung der Ventilnadel.The invention relates to a fuel injector according to the preamble of claim 1. Injectors of this type have a pre-injection and a main injection to reduce the combustion noise by controlling the stroke of the valve needle.
Bei einer durch die EP-A-240 693 bekannten Einspritzdüse dieser Art stößt die Ventilnadel am Ende des Vorhubs am Kolben der Druckübertragungseinrichtung an, der die Weiterbewegung der Ventilnadel stoppt, bis der Kraftstoffdruck soweit angestiegen ist, daß seine in Öffnungsrichtung auf die Ventilnadel ausgeübte Kraft die Kraft der Schließfeder und die vom Kolben ausgeübte Kraft übersteigt. Die bekannte Einspritzdüse baut zwar klein, jedoch unterliegt die Zwischenwand wegen der Ausbildung der Druckkammer und deren Anschlußkanal einem komplizierten Fertigungsverfahren.In an injection nozzle of this type known from EP-A-240 693, the valve needle abuts the piston of the pressure transmission device at the end of the forward stroke, which stops the further movement of the valve needle until the fuel pressure has risen to such an extent that its force exerted on the valve needle in the opening direction the force of the closing spring and the force exerted by the piston exceeds. Although the known injection nozzle is small, the partition is subject to a complicated manufacturing process due to the design of the pressure chamber and its connecting channel.
Aus der GB-A-2 086 473, die den nächstkommenden Stand der Technik bildet, ist eine weitere Einspritzdüse bekannt, bei der zwischen der Rückseite der Ventilnadel und einem Zwischenkolben ein Druckraum begrenzt ist. Dieser Druckraum ist dabei während der ersten Hubphase des Ventilgliedes gar nicht oder nur über eine Drossel entlastbar, so daß der Vorhub des Ventilgliedes gedämpft ist und nur ein sehr flacher Öffnungshubverlauf erfolgt. Nach dem Durchlaufen der Vorhubbewegung wird dann der Druckraum über einen größeren Öffnungsquerschnitt druckentlastet, so daß die Öffnungshubbewegung entgegen der Kraft der Rückstellfeder nun in dieser zweiten Hubphase sehr rasch erfolgt. Somit wird an dieser Einspritzdüse ein zweistufiger Öffnungshubverlauf erreicht, bei dem zunächst ein sehr kleiner Öffnungsquerschnitt langsam freigegeben wird und in einer zweiten Öffnungshubphase der restliche Öffnungshubweg sehr rasch durchfahren wird.A further injection nozzle is known from GB-A-2 086 473, which forms the closest prior art, in which a pressure space is limited between the rear of the valve needle and an intermediate piston. This pressure chamber cannot be relieved during the first stroke phase of the valve member, or can only be relieved via a throttle, so that the forward stroke of the valve member is damped and only a very flat opening stroke curve takes place. After the preliminary stroke movement has been completed, the pressure chamber is then relieved of pressure over a larger opening cross section, so that the opening stroke movement against the force of the return spring now takes place very quickly in this second stroke phase. A two-stage opening stroke profile is thus achieved on this injection nozzle, in which initially a very small opening cross section is slowly released and in a second opening stroke phase the remaining opening stroke path is traveled very quickly.
Demgegenüber liegt der Erfindung die Aufgabe zugrunde, einen zweistufigen Öffnungshubverlauf des Ventilgliedes in konstruktiv einfacher Weise zu formen, bei dem der öffnungshubverlauf des Vorhubes relativ steil ist, während nach dem Durchlaufen des Vorhubes ein flacheres Öffnen der Ventilnadel erfolgt.In contrast, the invention has for its object to form a two-stage opening stroke course of the valve member in a structurally simple manner, in which the opening stroke course of the preliminary stroke is relatively steep, while after passing through the preliminary stroke there is a flatter opening of the valve needle.
Die erfindungsgemäße Kraftstoff- Einspritzdüse mit den Merkmalen des Patentanspruchs 1 hat den Vorteil, daß zum Erzielen eines gestuften Öffnungshubes der Schließnadel bis auf den Kolben die gleichen Teile wie bei einem Ein-Federhalter verwendet sind, wobei der Kolben durch besondere, aber dennoch einfach herstellbare Gestaltung des die Schießkraft der Schließfeder auf die Ventilnadel übertragenden Druckbolzens gebildet ist.The fuel injector according to the invention with the features of claim 1 has the advantage that Achieve a stepped opening stroke of the closing needle down to the piston, the same parts are used as in a single-spring holder, the piston being formed by a special but nevertheless easy to manufacture design of the pressure bolt transmitting the closing force of the closing spring to the valve needle.
Durch die in den Unteransprüchen enthaltenen Merkmale sind vorteilhafte Weiterbildungen der Einspritzdüse nach dem Anspruch 1 möglich.Advantageous developments of the injection nozzle according to claim 1 are possible due to the features contained in the subclaims.
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im folgenden näher beschrieben. Es zeigen Figur 1 eine Einspritzdüse im Längsschnitt, Figur 2 einen Ausschnitt A aus Figur 1 in vergrößertem Maßstab, links in Schließ- und rechts in Offenstellung der Ventilnadel, und Figur 3 eine Alternative zu dem Ausführungsbeispiel nach Figur 2, ebenfalls links in Schließ- und rechts in Offenstellung der Ventilnadel.Embodiments of the invention are shown in the drawing and are described in more detail below. 1 shows an injection nozzle in longitudinal section, FIG. 2 shows a detail A from FIG. 1 on an enlarged scale, left in the closed and right in the open position of the valve needle, and FIG. 3 shows an alternative to the exemplary embodiment according to FIG. 2, also left in the closed and right in the open position of the valve needle.
Die Einspritzdüse hat einen Düsenkörper 10, der zusammen mit einer Zwischenscheibe 11 mit einer Überwurfmutter 13 an einem Haltekörper 12 festgespannt ist. Im Düsenkörper 10 ist eine Ventilnadel 15 verschiebbar gelagert, die mit einem nach innen gekehrten Ventilsitz 16 im Düsenkörper 10 zusammenarbeitet, der mehreren Spritzöffnungen 17 vorgelagert ist. Die Führungsbohrung 18 der Ventilnadel 15 ist wie üblich an einer Stelle zu einem Druckraum 19 erweitert, in dessen Bereich die Ventilnadel 15 eine Druckschulter 19 hat und der über einen Kanal 22 und einen Filterkörper 23 mit einem Stutzen 24 am Haltekörper 12 zum Anschließen einer Kraftstoffleitung verbunden ist. Der an der Druckschulter 20 der Ventilnadel 15 angreifende Kraftstoff schiebt die Ventilnadel 15 entgegen dem abgestuften Kraftverlauf einer im folgenden beschriebenen Schließkraftanordnung nach oben, wobei der Kraftstoff in einer Voreinspritzphase und einer Haupteinspritzphase durch die Spritzöffnungen 17 ausgespritzt wird.The injection nozzle has a
Im Haltekörper 12 ist eine Federkammer 26 zur Aufnahme einer Schließfeder 27 gebildet, die sich einerseits über eine Scheibe 28 am Boden der Kammer 26 und andererseits auf einem Druckstück 29 abstützt. Das Druckstück 29 liegt auf einem Kolben 30 auf, der in einer zylindrischen Durchgangsbohrung 31 in der Zwischenscheibe 11 dicht geführt ist. Der Kolben 30 durchsetzt die Durchgangsbohrung 31 vollständig und stützt sich auf der Ventilnadel 15, diese in Schließrichtung belastend, ab.In the
Die einander zugewandten Seiten des Kolbens 30 und der Ventilnadel 15 begrenzen zusammen mit einer Erweiterung 32 der Führungsbohrung 18 im Düsenkörper 10 nahe der Zwischenscheibe 11 und einer naheliegenden Teilfläche der Zwischenscheibe 11 eine Druckkammer 33. Eine Längsnut 35 im Mantel des Kolbens 30 verbindet diese Druckkammer 33 zeitweise mit der Federkammer 26, die über einen Leckkanal 38 und einen Anschlußstutzen 39 druckentlastet ist. Nahe der die Druckkammer 33 begrenzenden Seite des Kolbens 30 ist die Längsnut 35 von einer Steuerkante 36 begrenzt, welche in Schließstellung der Ventilnadel 15 und sich auf dieser abstützendem Kolben 30 von der Ringkante 37 am Übergang der Teilfläche in die Durchgangsbohrung 31 der Zwischenscheibe 11 einen Abstand hv hat, der dem erforderlichen Vorhub der Ventilnadel 11 entspricht. Anstelle einer Längsnut 35 im Umfang des Kolbens 30 kann alternativ auch eine flache Abtragung, beispielsweise ein Flächenanschliff am Kolben 30 angeordnet sein.The mutually facing sides of the
Der Durchmesser dK bzw. die hydraulische Wirkfläche des Kolbens 30 ist kleiner als der Durchmesser DN bzw. die Wirkfläche der Ventilnadel 15. Beim Ausführungsbeispiel nach Figur 2 sind die die Druckkammer 33 begrenzende Stirnseite 41 der Ventilnadel 15 eben und die gegenüberliegende Stirnseite 42 des Kolbens 30 ballig ausgebildet. Alternativ dazu hat beim Ausführungsbeispiel nach Figur 3 die Ventilnadel 15, wie auch üblich, einen über eine Schulter 43 abgesetzten Druckzapfen 44, der mit Spiel in eine Sackbohrung 45 des Kolbens 30 ragt und diesen am Grund 46 der Sackbohrung 45 abstützt.The diameter d K or the hydraulic effective area of the
Die erfindungsgemäße Einspritzdüse arbeitet wie folgt: Beim Zuführen von Kraftstoff von einer Einspritzpumpe durch den Kanal 22 in den Druckraum 19 wird bei Erreichen eines bestimmten Öffnungsdruckes die Ventilnadel 15 entgegen der Wirkung der Schließfeder 27, welche die Ventilnadel 15 mittelbar über den Kolben 30 belastet, vom Ventilsitz 16 abgehoben; die Einspritzung beginnt. Bei steigendem Druck hebt die Ventilnadel 15 weiter vom Ventilsitz 16 ab und verschiebt dabei den Kolben 30, bis dessen Steuerkante 36 nach einem Vorhub hv die Verbindung der Druckkammer 33 mit der Federkammer 26 unterbricht. Während dieser Vorhubphase verdrängt die Ventilnadel 15 aufgrund ihres großen Durchmessers mehr Kraftstoffvolumen in der Druckkammer 33 als durch unmittelbares Verschieben des Kolbens 30 frei wird, der einen kleineren Durchmesser hat. Das Differenzvolumen wird dabei aus der Druckkammer 33 durch die Längsnut 35 im Kolben 30 in die druckentlastete Federkammer 36 verdrängt. Die Schließfeder 27 wird während dieser Vorhubphase mit einer Kraft gespannt, die sich aus dem ansteigenden Kraftstoffzuführdruck in Verbindung mit der Wirkfläche der Ventilnadel 15 unter Vernachlässigung der Reibungsverluste ergibt. Am Ende des Vorhubs hv, wenn die Steuerkante 36 des Kolbens 30 die Druckkammer 33 absperrt, baut sich anschließend unter der Pumpwirkung der Ventilnadel 15, die weiterhin vom steigenden Zuführdruck beaufschlagt ist, in der Druckkammer 33 ein Steuerdruck auf, der den Kolben 30 beaufschlagt. Dieser Steuerdruck ist, da die Wirkfläche an der Zuführseite der Ventilnadel 15 und die Wirkfläche an der die Druckkammer 33 begrenzenden Seite gleich groß sind, im wesentlichen gleich dem Zuführdruck. Ab dem Zeitpunkt aber, wo die Druckkammer 33 abgesperrt worden ist, verdrängt das von der Ventilnadel 15 verdrängte Volumen den Kolben 30, der von der um den Vorhub hv weiter vorgespannten Schließfeder 26 belastet ist. Da aber die Wirkfläche des Kolbens 30 kleiner ist als die der Ventilnadel 15, und damit am Ende des Vorhubs hV die vom Kolben 30 erzeugte Kraft kleiner als die von der Ventilnadel 15 erzeugte Kraft ist, die der Schließfederkraft gleich ist, verbleibt der Kolben 30 so lange in Anlage an der Ventilnadel 15, bis der Zuführdruck und damit auch der Steuerdruck in der Druckkammer 33 so weit gestiegen sind, daß die vom Kolben 30 erzeugte Kraft die am Ende des Vorhubs erreichte Vorspannkraft der Schließfeder 27 in der Vorhubstellung übersteigt. Während dieser Zeit verbleibt auch die Ventilnadel 15 in Vorhubstellung. Erreicht dann der Zuführdruck und damit auch der Steuerdruck in der Druckkammer 33 einen Wert, aufgrund dessen der Kolben 30 mit einer Kraft belastet wird, die der der vorgespannten Schließfeder 26 gleichkommt und größer wird, setzt eine hydraulische Hubumsetzung von der Ventilnadel 15 auf den Kolben 30 ein, aufgrund der das Spannen der Schließfeder 27 nun vom Kolben 30 durchgeführt wird. In Abhängigkeit von der Differenz des Durchmessers der Ventilnadel 15 und des Kolbens 30 verschiebt sich nun der Kolben 30 bei weiterem Druckanstieg pro Hubeinheit der Ventilnadel 15 um eine größere Hubeinheit. Der Kolben 30 hebt dadurch von der Stirnseite 41 der Ventilnadel 15 ab und entfernt sich von dieser immer mehr, bis die Ventilnadel 15 mit ihrer Stirnseite 41, bzw. Schulter 43 nach Durchlaufen des Gesamthubes hg an der Zwischenscheibe 11 anschlägt. Da, wie oben erwähnt, die Wirkfläche des Kolbens 30 kleiner ist als die der Ventilnadel 15, wird nach Zurücklegen des Vorhubs hv der Weg des Kolbens 30 größer als der der Ventilnadel 15. Dies hat zur Folge, daß bei gleicher Federsteifigkeit die vom Kolben 30 über das hydraulische Kissen in der Druckkammer 33 auf die Ventilnadel 15 ausgeübte Schließkraft größer wird, die Charakteristik der beschriebenen Einspritzdüse also der eines Zweifederhalters entspricht.The injection nozzle according to the invention works as follows: When fuel is supplied from an injection pump through the channel 22 into the pressure chamber 19, when a certain opening pressure is reached, the
Claims (6)
- Fuel injection nozzle for internal combustion engines with a nozzle body (10) in which an inward-opening valve needle (15) is displaceably mounted, with a holding body (12) which carries the nozzle body (10) by way of an intermediate wall (11) and in which a spring chamber (26) is formed in order to receive a closing spring (27) which loads the valve needle (15) in the closing direction, and with a force transmission device which passes through the intermediate wall (11), transmits the force of the closing spring (27) to the valve needle (15) and has a piston (30) which delimits a pressure space (33) and the hydraulic effective area of which is smaller than that of the valve needle (15), the valve needle (15) delimiting the pressure space (33) with its end remote from the valve end, the piston (30) on the one hand delimiting the pressure space (33) in the direction of the valve needle (15) and on the other hand being loaded by the closing spring (27), characterized in that the piston (30) has a control edge (36) which controls a connection to a pressure-relieved side (26) and to the pressure chamber (33) and via which, in the closed position and during the preliminary stroke of the valve needle (15), during which the piston (30) is pressed against the valve needle (15) by the force of the closing spring (27), there is a connection between the pressure space (33) and the pressure-relieved side (26) and, after the preliminary stroke (vh) has been travelled, this connection is interrupted during the residual stroke of the valve needle (15) and of the piston (30), with the result that the residual stroke of the piston (30) takes place by virtue of hydraulic stroke transfer.
- Fuel injection nozzle according to Claim 1, characterized in that the intermediate wall (11) is formed by an intermediate disc (11) which is clamped between the nozzle body (10) and the holding body (12), and in that the pressure space (33) is situated in the region of the two mutually adjoining end regions of the nozzle body (10) and of the intermediate disc (11).
- Fuel injection nozzle according to Claim 2, characterized in that the pressure space (33) is surrounded by an expanded portion (32) of the guide hole (18) for the valve needle (15) at that end of the nozzle body (10) which is close to the intermediate disc (11).
- Fuel injection nozzle according to one of Claims 1 to 3, characterized in that a longitudinal groove (35) or cut leading into the spring chamber (26) of the holding body (12) adjoins the control edge (36) of the piston (30).
- Fuel injection nozzle according to Claim 4, characterized in that the piston (30) is of spherical design at its end facing the valve needle (15), and the opposing end (41) of the valve needle (15) is flat.
- Fuel injection nozzle according to Claim 4, characterized in that the piston (30) has a blind hole (45) into which a pressure stud (44) of the valve needle (15) engages.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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DE4225805 | 1992-08-05 | ||
DE4225805A DE4225805A1 (en) | 1992-08-05 | 1992-08-05 | Fuel injection nozzle for internal combustion engines |
PCT/DE1993/000669 WO1994003720A1 (en) | 1992-08-05 | 1993-07-29 | Fuel injection nozzle for internal combustion engines |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0606436A1 EP0606436A1 (en) | 1994-07-20 |
EP0606436B1 true EP0606436B1 (en) | 1996-10-02 |
Family
ID=6464844
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP93915674A Expired - Lifetime EP0606436B1 (en) | 1992-08-05 | 1993-07-29 | Fuel injection nozzle for internal combustion engines |
Country Status (5)
Country | Link |
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US (1) | US5464158A (en) |
EP (1) | EP0606436B1 (en) |
JP (1) | JP3433938B2 (en) |
DE (2) | DE4225805A1 (en) |
WO (1) | WO1994003720A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE4440182C2 (en) * | 1994-11-10 | 2003-09-18 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
US5950931A (en) * | 1998-01-30 | 1999-09-14 | Caterpillar Inc. | Pressure decay passage for a fuel injector having a trapped volume nozzle assembly |
US6543706B1 (en) * | 1999-02-26 | 2003-04-08 | Diesel Technology Company | Fuel injection nozzle for an internal combustion engine |
DE102005054927A1 (en) * | 2005-11-17 | 2007-05-31 | Siemens Ag | Fuel injector for common rail diesel injection for diesel engine, has nozzle needle which has steps in its shaft and damping chamber is formed in area of steps between shaft of nozzle needle and housing wall |
US8637701B2 (en) | 2009-05-15 | 2014-01-28 | Nippon Shokubai Co., Ltd. | Method for producing (meth) acrylic acid |
US9605639B2 (en) | 2012-07-12 | 2017-03-28 | Ford Global Technologies, Llc | Fuel injector |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3041018C2 (en) * | 1980-10-31 | 1986-03-20 | Daimler-Benz Ag, 7000 Stuttgart | Fuel injection device for an air-compressing injection internal combustion engine |
DE3611316A1 (en) * | 1986-04-04 | 1987-10-08 | Bosch Gmbh Robert | FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES |
US5125581A (en) * | 1989-01-12 | 1992-06-30 | Voest-Alpine Automotive Gesellschaft M.B.H. | Fuel injection nozzle |
DE4126698A1 (en) * | 1991-08-13 | 1992-10-15 | Daimler Benz Ag | Fuel injection nozzle for IC engine - has two flow connections between spring and damper chambers, for alternately dampened/non-dampener opening stroke |
-
1992
- 1992-08-05 DE DE4225805A patent/DE4225805A1/en not_active Withdrawn
-
1993
- 1993-07-29 EP EP93915674A patent/EP0606436B1/en not_active Expired - Lifetime
- 1993-07-29 JP JP50489394A patent/JP3433938B2/en not_active Expired - Fee Related
- 1993-07-29 WO PCT/DE1993/000669 patent/WO1994003720A1/en active IP Right Grant
- 1993-07-29 US US08/211,529 patent/US5464158A/en not_active Expired - Lifetime
- 1993-07-29 DE DE59304048T patent/DE59304048D1/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE59304048D1 (en) | 1996-11-07 |
JP3433938B2 (en) | 2003-08-04 |
WO1994003720A1 (en) | 1994-02-17 |
US5464158A (en) | 1995-11-07 |
DE4225805A1 (en) | 1994-02-10 |
JPH07502585A (en) | 1995-03-16 |
EP0606436A1 (en) | 1994-07-20 |
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