EP0293371A1 - Fuel injection nozzle for internal combustion engines. - Google Patents
Fuel injection nozzle for internal combustion engines.Info
- Publication number
- EP0293371A1 EP0293371A1 EP87900644A EP87900644A EP0293371A1 EP 0293371 A1 EP0293371 A1 EP 0293371A1 EP 87900644 A EP87900644 A EP 87900644A EP 87900644 A EP87900644 A EP 87900644A EP 0293371 A1 EP0293371 A1 EP 0293371A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- nozzle
- flats
- throttle pin
- injection nozzle
- valve needle
- 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.)
- Granted
Links
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
- 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
- F02M61/06—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 the valves being furnished at seated ends with pintle or plug shaped extensions
Definitions
- the invention relates to a fuel injection nozzle according to the preamble of the main claim.
- Injection nozzles of this type have the advantage that the passage cross section formed by the flattening of the throttle pin in the nozzle bore is less. Coking tends as an annular gap between a fully cylindrical throttle pin and. the nozzle bore.
- the flattening of the throttle pin is arranged obliquely to the nozzle axis, which results in the desired effect of an increasing passage cross section until the throttle pin emerges from the nozzle bore.
- the correct angular position of such a flattening is difficult to maintain in mass production and can only be checked with increased effort because the reference points must be adhered to extremely precisely.
- the arrangement according to the invention with the characterizing features of the main claim has the advantage that an enlargement of the preferred passage cross section in the nozzle bore during the forward stroke of the valve needle can be achieved with measures that are easy to control and monitor in manufacture.
- the two flats of the throttle pin can have different distances from the nozzle axis, i.e. be ground to different depths, which means that the injection characteristics can also vary or can be optimally adapted to certain engine types.
- the two flats can be arranged at an angle, preferably 180 °, offset from one another and can be of different lengths. This has the advantage that the radial forces exerted by the fuel on the throttle pin largely compensate for each other in the stroke range in which both flattenings are effective.
- the two flats can also be advantageous to arrange the two flats axially one behind the other and to allow them to merge into one another at a stepped channel.
- more than two flattenings for example three, can be provided in succession, so that two transition stages result.
- the axially behind other arranged flats may be provided on their own.
- one or more flats can be arranged obliquely to the nozzle axis.
- FIG. 1 shows an enlarged longitudinal section through the injection-side end of the first embodiment
- FIG. 2 shows a section along the line II-II in FIG. 1
- FIG. 3 shows the second embodiment in a representation corresponding to FIG. 1
- FIG. 4 shows a section along the line IV-IV in Figure 3 and Figure 5 is a partial longitudinal section through the third embodiment.
- the injection nozzle according to FIGS. 1 and 2 has a nozzle body 10, in which a valve seat 12 opposed to the fuel flow is formed and a valve needle 14 is displaceably mounted. This forms a sealing cone 16 which cooperates with the valve seat 12, to which a throttle pin 18 adjoins, which projects into a nozzle bore 20 which adjoins the valve seat 12. At the transition between the valve seat 12 and the nozzle bore 20, an annular edge 22 is formed on the nozzle body 10. An injection molding pin 26 is formed on the throttle pin 18, starting at an annular edge 24.
- the valve needle 14 is pressed against the valve seat 12 by a closing spring and is lifted from the valve seat 12 by the increasing fuel pressure at the start of injection.
- the throttle pin 18 is provided with two diametrically opposite flats 30, 32 which run parallel to the nozzle axis 28 and through which two preferred passage cross sections 34 and 36 are formed in the nozzle bore 20.
- the two flats 30, 32 start from the front ring edge 24 of the throttle pin 18 and have different lengths a, b, and different distances c, d from the nozzle axis 28.
- the length a of the flat 30 is dimensioned such that the valve needle is already in the closed position 14 the passage cross section 34 is present.
- the length b of the flat 32 is dimensioned such that, in the closed position of the valve needle 14, the step edge 38 formed at the end of the flat 32 lies by an overlap length 1 below the ring edge 22 of the nozzle body 10.
- the diameter of the throttle pin 18 is only smaller by the dimension of a necessary movement gap than the diameter of the nozzle bore 20.
- the distance c of the longer flattening 30 from the nozzle axis 28 is chosen so that the size of the preferred passage cross section 34 corresponds approximately to the size of the initial throttle gap of a conventional injection nozzle without surfaces on the throttle pin.
- the second preferred passage cross section 36 is opened and the throttling of the escaping fuel is considerably reduced. If, during the further course of the opening stroke of the valve needle 14, the annular edge 24 of the throttle pin 18 extends beyond the annular edge 22 on the nozzle body 10, the main amount of the fuel is injected unthrottled.
- the exemplary embodiment according to FIGS. 3 and 4 corresponds in its basic structure to the previously described exemplary embodiment, so that the same parts are provided with the same reference numbers.
- Only the throttle pin 18a of the valve needle 14a is provided with a further flat 40, which adjoins the flat 36 axially.
- the flat 40 has a distance e from the nozzle axis 28, which corresponds approximately to the distance c of the opposite flat 30. This results in a step edge 42 between the flats
- the length f of the flat 40 is dimensioned such that it ends approximately in the same cross-sectional plane of the throttle pin 18a as the flat 30.
- the flattening 40 results in the closed position of the valve needle lUa a further preferred passage cross section 44, which is diametrically opposed to the passage cross section 34. It is thereby achieved that the radial forces exerted by the fuel on the valve needle 14a largely cancel each other out at the start of injection.
- a valve seat 52 and a cylindrical nozzle bore 5 4 are formed in a nozzle body 50, so that a valve is adequately connected to the nozzle bore 50 54 protruding throttle pin 58 has. This is dimensioned so long that it protrudes a little further into the nozzle bore 54 when the valve needle 56 is at full stroke.
- the throttle pin 56 is provided with two flats 60, 62 lying axially one behind the other, one of which, 60, a throttle cross-section 64 and the other, 62, an end cross-section 66 in the nozzle bore 54.
- the transition 68 between the two flats 60, 62 can be designed as a fillet or as a flat surface.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
La buse comprend une aiguille de soupape (14) s'ouvrant vers l'intérieur et un alésage de buse (20), dans lequel un téton (18) de l'aiguille (14) entre lors de l'avance de l'aiguille. Le téton (18) comprend au moins deux méplats (30, 32 ou 30, 32, 40 ou 32, 40) qui délimitent des sections de passage préférées dans l'alésage (20). Au moins deux méplats (30, 32 ou 32, 40) se terminent dans des sections différentes du téton (18). Ceci permet d'obtenir une augmentation graduelle de la section de passage totale de l'alésage pendant l'avance de l'aiguille de soupape (14) tout en assurant de bonnes conditions de fabrication de la buse.The nozzle includes an inwardly opening valve needle (14) and a nozzle bore (20), into which a stud (18) of the needle (14) enters as the needle is advanced. . The stud (18) comprises at least two flats (30, 32 or 30, 32, 40 or 32, 40) which define preferred passage sections in the bore (20). At least two flats (30, 32 or 32, 40) terminate in different sections of the stud (18). This makes it possible to obtain a gradual increase in the total passage section of the bore during the advance of the valve needle (14) while ensuring good manufacturing conditions of the nozzle.
Description
Kraftstoff-Einspritzdüse für BrennkraftmaschinenFuel injection nozzle for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht aus von einer Kraftstoff-Einspritzdüse nach der Gattung des Hauptanspruchs. Einspritzdüsen dieser Gattung haben den Vorteil, daß der durch die Abflachung am Drosselzapfen gebildete Durchgangsquerschnitt in der Düsenbohrung weniger zum. Verkoken neigt als ein Ringspalt zwischen einem vollzylindris cheiu Drosselzapfen und. der Düsenbohrung. Bei einer bekannten Einspritzdüse der eingangs genannten Gattung (DE-A1 33 26 468 ) ist die Abflachung am Drosselzapfen zur Düsenachse schräg angeordnet, wodurch sich der erwünschte Effekt eines sich vergrößernden Durchlaßquerschnittes bis zum Austreten des Drosselzapfens aus der Düsenbohrung ergibt. Die vorschriftsmäßige Winkellage einer solchen Abflachung ist jedoch in der Mengenfertigung schwer einzuhalten und auch nur mit erhöhtem Aufwand nachprüfbar, weil dabei die Bezugspunkte äußerst genau eingehalten werden müssen.
Vorteile der ErfindungThe invention relates to a fuel injection nozzle according to the preamble of the main claim. Injection nozzles of this type have the advantage that the passage cross section formed by the flattening of the throttle pin in the nozzle bore is less. Coking tends as an annular gap between a fully cylindrical throttle pin and. the nozzle bore. In a known injection nozzle of the type mentioned (DE-A1 33 26 468), the flattening of the throttle pin is arranged obliquely to the nozzle axis, which results in the desired effect of an increasing passage cross section until the throttle pin emerges from the nozzle bore. However, the correct angular position of such a flattening is difficult to maintain in mass production and can only be checked with increased effort because the reference points must be adhered to extremely precisely. Advantages of the invention
Die erfindungsgemäße Anordnung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß eine Vergrößerung des bevorzugten Durchlaßquerschnittes in der Düsenbohrung beim Vorhub der Ventilnadel mit in der Fertigung gut beherrschbaren und überwachbaren Maßnahmen erzielbar ist .The arrangement according to the invention with the characterizing features of the main claim has the advantage that an enlargement of the preferred passage cross section in the nozzle bore during the forward stroke of the valve needle can be achieved with measures that are easy to control and monitor in manufacture.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des Gegenstandes des Hauptanspruchs möglich.Advantageous further developments of the subject matter of the main claim are possible through the measures listed in the subclaims.
Die beiden Abflachungen des Drosselzapfens können unterschiedliche Abstände zur Düsenachse haben, d.h. unterschiedlich tief angeschliffen sein, wodurch sich die Einspritzcharakteristik ebenfalls variieren bzw. optimal an bestimmte Motortypen anpassen läßt. In diesem Fall können die beiden Abflachungen um einen Winkel, vorzugsweise um 180º , zue inander ver s et z t angeordnet und unter s chiedli ch lang aus ge führt sein. Das hat den Vorteil, daß sich in dem Hubbereich, in welchem beide Abflachungen wirksam sind, die vom Kraftstoff auf den Drosselzapfen ausgeübten Radialkräfte weitgehend ausgleichen.The two flats of the throttle pin can have different distances from the nozzle axis, i.e. be ground to different depths, which means that the injection characteristics can also vary or can be optimally adapted to certain engine types. In this case, the two flats can be arranged at an angle, preferably 180 °, offset from one another and can be of different lengths. This has the advantage that the radial forces exerted by the fuel on the throttle pin largely compensate for each other in the stroke range in which both flattenings are effective.
Im manchen Fällen kann es auch vorteilhaft sein, die beiden Abflachungen axial hintereinander anzuordnen und an einer Stufenkanöe ineinander übergehen zu lassen. Bei Bedarf können auch mehr als zwei Abflachungen, z.B. drei, hintereinander vorgesehen sein, so daß sich zwei Übergangsstufen ergeben. Um iuch in diesem Fall einen Ausgleich der Radialkräfte zu haben wird weiter vorgeschlagen, zusätzlich zu den axial hintereinander angeordneten Abflachungen eine weitere, vorzugsweise um 180º zu diesen versetzte Abflachung anzuordnen. Selbstverständlich können jedoch auch die axial hinterein
ander angeordneten Abflachungen für sich allein vorgesehen sein. Ferner können auch eine oder mehrere Abflachungen schräg zur Düsenachse angeordnet sein.In some cases it can also be advantageous to arrange the two flats axially one behind the other and to allow them to merge into one another at a stepped channel. If necessary, more than two flattenings, for example three, can be provided in succession, so that two transition stages result. In order to have a balance of the radial forces in this case as well, it is further proposed to arrange a further flattening, preferably offset by 180 °, in addition to the flats arranged axially one behind the other. Of course, however, the axially behind other arranged flats may be provided on their own. Furthermore, one or more flats can be arranged obliquely to the nozzle axis.
Zeichnungdrawing
Drei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen vergrößerten Längsschnitt durch das einsprit zseitige Ende des ersten Ausführungsbeispiels, Figur 2 einen Schnitt nach der Linie II-II in Figur 1, Figur 3 das zweite Ausführungsbeispiel in einer der Figur 1 entsprechenden Darstellung, Figur 4 einen Schnitt nach der Linie IV-IV in Figur 3 und Figur 5 einen Teil-Längsschnitt durch das dritte Ausführungsbeispiel.Three embodiments of the invention are shown in the drawing and explained in more detail in the following description. 1 shows an enlarged longitudinal section through the injection-side end of the first embodiment, FIG. 2 shows a section along the line II-II in FIG. 1, FIG. 3 shows the second embodiment in a representation corresponding to FIG. 1, and FIG. 4 shows a section along the line IV-IV in Figure 3 and Figure 5 is a partial longitudinal section through the third embodiment.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Die Einspritzdüse nach den Figuren 1 und 2 hat einen Düsenkörper 10, in welchem ein der Kraftstoffströmung entgegengerichteter Ventilsitz 12 gebildet und eine Ventilnadel 14 verschiebbar gelagert ist. Diese bildet einen mit dem Ventilsitz 12 zusammenarbeitenden Dichtkonus 16, an den sich ein Drosselzapfen 18 anschließt, der in eine Düsenbohrung 20 ragt, welche sich an dem Ventilsitz 12 anschließt. Am Übergang zwischen dem Ventilsitz 12 und der Düsenbohrung 20 ist eine Ringkante 22 am Düsenkörper 10 gebildet. An den Drosselzapfen 18 ist, an einer Ringkante 24 beginnend, ein Spritzformungszapfen 26 angeformt. Die Ventilnadel 14 wird von einer Schließfeder gegen den Ventilsitz 12 gedrückt und von dem bei Einspritzbeginn ansteigenden Kraftstoffdruck vom Ventilsitz 12 abgehoben.
Der Drosselzapfen 18 ist mit zwei parallel zur Düsenachse 28 verlaufenden, sich diametral gegenüberliegenden Abflachungen 30, 32 versehen, durch welche in der Düsenbohrung 20 zwei bevorzugte Durchlaßquerschnitte 34 und 36 gebildet sind. Die beiden Abflachungen 30, 32 gehen von der vorderen Ringkante 24 des Drosselzapfens 18 aus und haben unterschiedliche Längen a, b, sowie unterschiedliche Abstände c, d zur Düsenachse 28. Die Länge a der Abflachung 30 ist so bemessen, daß bereits in Schließstellung der Ventilnadel 14 der Durchlaßquerschnitt 34 vorhanden ist. Die Länge b der Abflachung 32 ist so bemessen, daß in Schließstellung der Ventilnadel 14 die am Ende der Abflachung 32 gebildete Stufenkante 38 um eine Überdeckungslänge 1 unterhalb der Ringkante 22 des Düsenkörpers 10 liegt.The injection nozzle according to FIGS. 1 and 2 has a nozzle body 10, in which a valve seat 12 opposed to the fuel flow is formed and a valve needle 14 is displaceably mounted. This forms a sealing cone 16 which cooperates with the valve seat 12, to which a throttle pin 18 adjoins, which projects into a nozzle bore 20 which adjoins the valve seat 12. At the transition between the valve seat 12 and the nozzle bore 20, an annular edge 22 is formed on the nozzle body 10. An injection molding pin 26 is formed on the throttle pin 18, starting at an annular edge 24. The valve needle 14 is pressed against the valve seat 12 by a closing spring and is lifted from the valve seat 12 by the increasing fuel pressure at the start of injection. The throttle pin 18 is provided with two diametrically opposite flats 30, 32 which run parallel to the nozzle axis 28 and through which two preferred passage cross sections 34 and 36 are formed in the nozzle bore 20. The two flats 30, 32 start from the front ring edge 24 of the throttle pin 18 and have different lengths a, b, and different distances c, d from the nozzle axis 28. The length a of the flat 30 is dimensioned such that the valve needle is already in the closed position 14 the passage cross section 34 is present. The length b of the flat 32 is dimensioned such that, in the closed position of the valve needle 14, the step edge 38 formed at the end of the flat 32 lies by an overlap length 1 below the ring edge 22 of the nozzle body 10.
Der Durchmesser des Drosselzapfens 18 ist lediglich um das Maß eines notwendigen Bewegungsspaltes kleiner als der Durchmesser der Düsenbohrung 20 bemessen. Der Abstand c der längeren Abflachung 30 von der Düsenachse 28 ist so gewählt, daß die Größe des bevorzugten Durchlaßquerschnittes 34 in etwa der Größe des anfänglichen Drosselspaltes einer herkömmlichen Einspritzdüse ohne Flächen am Drosselzapfen entspricht. Während eines der Überdeckung 1 entsprechenden Vorhubes der Ventilnadel 14 gelangt der Kraft st of f gedro s s elt durc h den Durc hlaßquer s c hnit t 34 in den Brennraum der MaschineThe diameter of the throttle pin 18 is only smaller by the dimension of a necessary movement gap than the diameter of the nozzle bore 20. The distance c of the longer flattening 30 from the nozzle axis 28 is chosen so that the size of the preferred passage cross section 34 corresponds approximately to the size of the initial throttle gap of a conventional injection nozzle without surfaces on the throttle pin. During a preliminary stroke of the valve needle 14 corresponding to the overlap 1, the force of the throttle passes through the cross-section 34 into the combustion chamber of the engine
Wenn sich die Ventilnadel 14 um den Weg 1 nach oben bewegt hat, wird der zweite bevorzugte Durchlaßquerschnitt 36 geöffnet und die Drosselung des austretenden Kraftstoffs erheblich gemindert. Wenn im weiteren Verlauf des Öffnungshubes der Ventilnadel 14 die Ringkante 24 des Drosselzapfens 18 über die Ringkante 22 am Düsenkörper 10 hinausgelangt, wird die Hauptmenge des Kraftstoffs ungedrosselt eingespritzt.
Das Ausführungsbeispiel nach den Figuren 3 und 4 stimmt im grundsätzlichen Aufbau mit dem vorher beschriebenen Ausführungsbeispiel überein, so daß gleiche Teile mit den gleichen Bezugszahlen versehen sind. Lediglich der Drosselzapfen 18a der Ventilnadel 14a ist mit einer weiteren Abflachung 40 versehen, die sich axial an die Abflachung 36 anschließt. Die Abflachung 40 hat einen Abstand e von der Düsenachse 28, der etwa dem Abstand c der gegenüberliegenden Abflachung 30 entspricht. Dadurch ergibt sich eine Stufenkante 42 zwischen den AbflachungenWhen the valve needle 14 has moved up the path 1, the second preferred passage cross section 36 is opened and the throttling of the escaping fuel is considerably reduced. If, during the further course of the opening stroke of the valve needle 14, the annular edge 24 of the throttle pin 18 extends beyond the annular edge 22 on the nozzle body 10, the main amount of the fuel is injected unthrottled. The exemplary embodiment according to FIGS. 3 and 4 corresponds in its basic structure to the previously described exemplary embodiment, so that the same parts are provided with the same reference numbers. Only the throttle pin 18a of the valve needle 14a is provided with a further flat 40, which adjoins the flat 36 axially. The flat 40 has a distance e from the nozzle axis 28, which corresponds approximately to the distance c of the opposite flat 30. This results in a step edge 42 between the flats
32 und 40 , die entsprechend niedriger als die Stufenkante32 and 40, which are correspondingly lower than the step edge
33 des Drosselzapfens 18 ist. Die Länge f der Abflachung 40 ist so bemessen, daß diese etwa in der gleichen Querschnittsebene des Drosselzapfens 18a endet wie die Abflachung 30.33 of the throttle pin 18. The length f of the flat 40 is dimensioned such that it ends approximately in the same cross-sectional plane of the throttle pin 18a as the flat 30.
Durch die Abflachung 40 ergibt sich in der Schließstellung der Ventilnadel lUa ein weiterer bevorzugter Durchlaßquerschnitt 44, der dem Durchlaßquer schnitt 34 diametral gegenüberliegt. Dadurch ist erreicht, daß schon bei Einspritzbeginn die sich vom Kraftstoff auf die Ventilnadel 14a ausgeübten Radialkräfte weitgehend aufheben.The flattening 40 results in the closed position of the valve needle lUa a further preferred passage cross section 44, which is diametrically opposed to the passage cross section 34. It is thereby achieved that the radial forces exerted by the fuel on the valve needle 14a largely cancel each other out at the start of injection.
3ei der Einspritzdüse nach Figur 5 ist in einem Düsenkörper 50 ein Ventilsitz 52 und eine zylindrische Düsenbohrung 5 4 gebildet , s owi e e ine Ve nt i ln ade l 56 v er s c hi eb b ar gel ag ert , di e einen in die Düsenbohrung 54 hineinragenden Drosselzapfen 58 hat. Dieser ist so lang bemessen, daß er bei vollem Hub der Ventilnadel 56 noch ein Stück weit in die Düsenbohrung 54 hineinragt. Der Drosselzapfen 56 ist mit zwei axial hintereinander liegenden Abflachungen 60 , 62 versehen, von denen die eine,
60, einen Drosselquerschnitt 64 und die andere, 62, einen Endquerschnitt 66 in der Düsenbohrung 54 bestimmt. Der Übergang 68 zwischen beiden Abflachungen 60, 62 kann als Hohlkehle oder als ebene Fläche ausgebildet sein.
In the injection nozzle according to FIG. 5, a valve seat 52 and a cylindrical nozzle bore 5 4 are formed in a nozzle body 50, so that a valve is adequately connected to the nozzle bore 50 54 protruding throttle pin 58 has. This is dimensioned so long that it protrudes a little further into the nozzle bore 54 when the valve needle 56 is at full stroke. The throttle pin 56 is provided with two flats 60, 62 lying axially one behind the other, one of which, 60, a throttle cross-section 64 and the other, 62, an end cross-section 66 in the nozzle bore 54. The transition 68 between the two flats 60, 62 can be designed as a fillet or as a flat surface.
Claims
1. Kraftstoff-Einspritzdüse für Brennkraftmaschinen, mit einem Düsenkörper, in welchem ein der Kraftstoffströmung entgegengerichter Ventilsitz gebildet und eine von diesem nach innen abhebende Ventilnadel verschiebbar gelagert ist, die einen Drosselzapfen trägt, der über einen Teil des Öffnungshubes der Ventilnadel in eine an den Ventilsitz anschließende Düsenbohrung taucht und an seinem Umfang mit einer Abflachung zur Bildung eines bevorzugten Durchlaßquerschnitts in der Düsenbohrung versehen ist, der beim Austreten des Dr o sselzapfens aus der Düsenbohrung größer ist als in Schließstellung der Ventilnadel, dadurch gekennzeichnet, daß der Dros selsapfen (18, 18a). mindestens zwei Abflachungen (30,32 bzw. 30,32, 40 bzw. 32, 40) hat, von denen mindestens zwei (30,32 bzw. 32,40) in unterschiedlichen Querschnittsebenen des Drosselzapfens (18, 18a ) enden.1. Fuel injection nozzle for internal combustion engines, with a nozzle body in which a valve seat opposing the fuel flow is formed and a valve needle which is lifted inward from it is displaceably mounted and carries a throttle pin which over part of the opening stroke of the valve needle into a valve seat Subsequent nozzle bore dips and is provided on its circumference with a flattening to form a preferred passage cross section in the nozzle bore, which is larger when the throttle pin emerges from the nozzle bore than in the closed position of the valve needle, characterized in that the throttle pin plug (18, 18a ). has at least two flats (30, 32 or 30, 32, 40 or 32, 40), of which at least two (30, 32 or 32, 40) end in different cross-sectional planes of the throttle pin (18, 18a).
2. Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß die Abflachungen (30, 32 bzw. 32, 40 ) unterschiedliche Abstände (c, d bzw. d, e) zur Düsenachse (23) haben. 2. Injection nozzle according to claim 1, characterized in that the flats (30, 32 or 32, 40) have different distances (c, d or d, e) to the nozzle axis (23).
3. Einspritzdüse nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß zwei Abflachungen (30, 32) um einen Winkel, vorzugsweise um 180º , zueinander versetzt angeordnet und unterschiedlich lang ausgeführt sind.3. Injection nozzle according to claim 1 or 2, characterized in that two flats (30, 32) at an angle, preferably by 180 °, offset from one another and are of different lengths.
4 . Einspritzdüse nach Anspruch 2, dadurch gekennzeichnet, daß zwei Abflachungen (32, 40 ) mit unterschiedlichen Abständen (d, e) zur Düsenachse (28) axial hintereinander angeordnet sind und an einer Stufenkante (42) iπaina,nder übergehen.4th Injection nozzle according to claim 2, characterized in that two flats (32, 40) with different distances (d, e) to the nozzle axis (28) are arranged axially one behind the other and merge at a step edge (42) iπaina, nder.
5. Einspritzdüse nach Anspruch 4 , dadurch gekennzeichnet, daß zusätzlich zu den axial hintereinander angeordneten Abflachungen (32, 40 ) eine weitere, vorzugsweise um 180º zu diesen versetzte Abflachung (30) angeordnet ist.5. Injection nozzle according to claim 4, characterized in that in addition to the axially arranged flats (32, 40) a further, preferably by 180 ° offset to these flats (30) is arranged.
6. Einspritzdüse nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Drosselzapfen (58) so bemessen ist, daß er bei vollem Hub der Ventilnadel (56) mindestens noch ein Stück weit in die Düseabohrung ( 54 ) eintaucht, und daß der der Haupteinspritzung entsprechende Endquerschnitt in der Düsenbohrung durch mindestens eine Abflachung (62) des Drosselzapfens (53) gebildet und bestimmt ist. 6. Injection nozzle according to one of the preceding claims, characterized in that the throttle pin (58) is dimensioned so that it is at least a little further into the nozzle bore (54) at full stroke of the valve needle (56), and that that of the main injection corresponding end cross section in the nozzle bore is formed and determined by at least one flattened portion (62) of the throttle pin (53).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3604907 | 1986-02-17 | ||
| DE19863604907 DE3604907A1 (en) | 1986-02-17 | 1986-02-17 | FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0293371A1 true EP0293371A1 (en) | 1988-12-07 |
| EP0293371B1 EP0293371B1 (en) | 1990-08-08 |
Family
ID=6294229
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP87900644A Expired - Lifetime EP0293371B1 (en) | 1986-02-17 | 1987-01-10 | Fuel injection nozzle for internal combustion engines |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US4909446A (en) |
| EP (1) | EP0293371B1 (en) |
| JP (1) | JP2557926B2 (en) |
| BR (1) | BR8707588A (en) |
| DE (2) | DE3604907A1 (en) |
| WO (1) | WO1987005077A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3725618C2 (en) * | 1987-08-03 | 2002-11-07 | Bosch Gmbh Robert | Fuel injection nozzle for internal combustion engines |
| DE3841324A1 (en) * | 1988-12-08 | 1990-06-13 | Bosch Gmbh Robert | Fuel injection nozzle for internal combustion engines |
| FR2676503B1 (en) * | 1991-05-17 | 1993-09-17 | Chevenet Jean Charles | THERMAL MOTOR. |
| US5186824A (en) * | 1991-09-04 | 1993-02-16 | Large Scale Biology Corporation | System for solid phase reactions |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2263197A (en) * | 1939-03-08 | 1941-11-18 | Eisemann Magneto Corp | Fuel injection nozzle |
| US4082224A (en) * | 1976-10-07 | 1978-04-04 | Caterpillar Tractor Co. | Fuel injection nozzle |
| DE2822675A1 (en) * | 1978-05-24 | 1979-11-29 | Daimler Benz Ag | Compression ignition engine injector - has two symmetrically situated flats on pintle |
| US4540126A (en) * | 1982-04-08 | 1985-09-10 | Nissan Motor Co., Ltd. | Fuel injection nozzle |
| JPS59131764A (en) * | 1983-01-17 | 1984-07-28 | Daihatsu Motor Co Ltd | Fuel injection nozzle |
| JPS59134372A (en) * | 1983-01-22 | 1984-08-02 | Daihatsu Motor Co Ltd | Fuel injection nozzle |
| DE3326468C2 (en) * | 1983-07-22 | 1986-07-24 | Daimler-Benz Ag, 7000 Stuttgart | Throttle pin nozzle for fuel injection into an internal combustion engine designed in particular as an antechamber engine |
| DE3426951A1 (en) * | 1984-07-21 | 1986-01-30 | Daimler-Benz Ag, 7000 Stuttgart | Throttle pintle nozzle for an air-compressing injection internal combustion engine, especially a precombustion chamber engine |
| SU1377441A1 (en) * | 1986-01-23 | 1988-02-28 | Научно-производственное объединение по топливной аппаратуре двигателей "ЦНИТА" | Pintle-type atomizer |
-
1986
- 1986-02-17 DE DE19863604907 patent/DE3604907A1/en not_active Withdrawn
-
1987
- 1987-01-10 BR BR8707588A patent/BR8707588A/en unknown
- 1987-01-10 DE DE8787900644T patent/DE3764270D1/en not_active Expired - Lifetime
- 1987-01-10 US US07/243,299 patent/US4909446A/en not_active Expired - Lifetime
- 1987-01-10 WO PCT/DE1987/000009 patent/WO1987005077A1/en active IP Right Grant
- 1987-01-10 JP JP62500554A patent/JP2557926B2/en not_active Expired - Fee Related
- 1987-01-10 EP EP87900644A patent/EP0293371B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
| Title |
|---|
| See references of WO8705077A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2557926B2 (en) | 1996-11-27 |
| JPH01501644A (en) | 1989-06-08 |
| WO1987005077A1 (en) | 1987-08-27 |
| DE3604907A1 (en) | 1987-08-20 |
| DE3764270D1 (en) | 1990-09-13 |
| BR8707588A (en) | 1988-12-06 |
| US4909446A (en) | 1990-03-20 |
| EP0293371B1 (en) | 1990-08-08 |
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