EP0293371B1 - Fuel injection nozzle for internal combustion engines - Google Patents

Fuel injection nozzle for internal combustion engines Download PDF

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Publication number
EP0293371B1
EP0293371B1 EP87900644A EP87900644A EP0293371B1 EP 0293371 B1 EP0293371 B1 EP 0293371B1 EP 87900644 A EP87900644 A EP 87900644A EP 87900644 A EP87900644 A EP 87900644A EP 0293371 B1 EP0293371 B1 EP 0293371B1
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EP
European Patent Office
Prior art keywords
flats
nozzle
valve needle
section
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
Application number
EP87900644A
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German (de)
French (fr)
Other versions
EP0293371A1 (en
Inventor
Ewald Eblen
Rolf Jürgen GIERSCH
Karl Hofmann
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP0293371A1 publication Critical patent/EP0293371A1/en
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Publication of EP0293371B1 publication Critical patent/EP0293371B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M61/06—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.
  • Injectors of this type have the advantage. that the passage cross section formed by the flattening of the throttle pin in the nozzle bore tends to coke less than an annular gap between a fully cylindrical throttle pin and the nozzle bore.
  • the throttle pin has a plurality of flats which are distributed symmetrically over the circumference and are all of the same length. i.e., end in the same cross-sectional plane of the throttle pin. Throttle pegs designed in this way do not allow splitting into cold starts, idling, part-load or full-load operation.
  • the arrangement according to the invention with the characterizing features of the main claim has the advantages that the individual operating stages of the engine are covered by the flats of different lengths, that the variable angles of the flats can be injected into the combustion chamber in different directions and that the flats are also can be produced with measures that are easy to control and monitor in production.
  • 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 preferably be arranged offset from one another by an angle of 180 °. 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.
  • one of the flats can also be advantageous to design one of the flats as two flats which are arranged axially one behind the other and have different depths and which merge into one another at a step edge. If necessary, more than two flats, e.g. three, can be provided one behind the other, so that there are two. Furthermore, 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 11-11 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.
  • 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 and 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 that run parallel to the nozzle axis 28. 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 below the ring edge 22 of the nozzle body 10 by an overlap length 1.
  • the diameter of the throttle pin 18 is only smaller by the amount of a necessary movement gap than the diameter of the nozzle bore 20.
  • the distance c of the longer flat 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 ring edge 24 of the throttle pin 18 extends beyond the ring edge 22 on the nozzle body 10, the majority 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 and 40, which is correspondingly lower than the step edge 38 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.
  • the flattening 40 results in the valve needle 14a in the closed position of a further preferred passage cross section 44, which is diametrically opposite 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 at the start of injection.
  • the throttle pin 18a is dimensioned so long that it protrudes a little further into the nozzle bore 20 at full stroke of the valve needle 14a. In this end position, the total passage cross section is given by the sum of the passage cross sections 34 and 36. It is conceivable to provide further flattenings at different angles on the throttle pin 18a, which only contribute to the total passage cross section when the valve needle 14a is fully lifted and thus become effective in full load operation.

Abstract

The nozzle described comprises an inwardly-opening valve-needle (14) and a nozzle bore (20), in which a throttling pin (18) of the valve needle (14) penetrates during forward movement of the needle. The throttling pin (18) is provided with at least two flats (30, 32, or 30, 32, 40, or 30, 40) to provide preferential passage cross-sections in the nozzle bore (20). At least two flats (30, 32, or 32, 40) and at different cross-sectional planes of the throttling pin (18). This enables a progressive increase in the overall cross-section of the nozzle bore (20) during the forward travel of the valve needle (14), while providing precisely controllable production conditions.

Description

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 vollzylindrischen Drosselzapfen und der Düsenbohrung. Bei einer bekannten Einspritzdüse der eingangs genannten Gattung (GB-A-2 133 833) weist der Drosselzapfen mehrere Abflachungen auf, die symmetrisch über den Umfang verteilt und alle gleich lang sind. d.h., in derselben Querschnittsebene des Drosselzapfens enden. Solchermaßen ausgebildete Drosselzapfen lassen eine Aufspaltung in Kaltstart, Leerlauf-, Teillast- oder Vollastbetrieb nicht zu. Ferner ist es bekannt (DE-A1-34 26 951) eine sich über die Länge des Drosselzapfens erstreckende Abflachung vorzusehen, die zwei Abflachstufen enthält. Die Herstellung solcher Stufen hat in der Mengenfertigung jedoch den Nachteil, das man entweder mehrere Arbeitsschritte oder teure Spezialwerkzeuge benötigt.The invention relates to a fuel injection nozzle according to the preamble of the main claim. Injectors of this type have the advantage. that the passage cross section formed by the flattening of the throttle pin in the nozzle bore tends to coke less than an annular gap between a fully cylindrical throttle pin and the nozzle bore. In a known injection nozzle of the type mentioned at the beginning (GB-A-2 133 833), the throttle pin has a plurality of flats which are distributed symmetrically over the circumference and are all of the same length. i.e., end in the same cross-sectional plane of the throttle pin. Throttle pegs designed in this way do not allow splitting into cold starts, idling, part-load or full-load operation. Furthermore, it is known (DE-A1-34 26 951) to provide a flattening which extends over the length of the throttle pin and which contains two flattening stages. However, the production of such stages has the disadvantage in mass production that either several work steps or expensive special tools are required.

Die erfindungsgemäße Anordnung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber die Vorteile, daß durch die unterschiedlich langen Abflachungen die einzelnen Betriebsstufen des Motors abgedeckt sind, daß durch die variablen Winkel der Abflachungen untereinander in verschiedenen Richtungen in den Brennraum eingespritzt werden kann und daß ferner die Abflachungen mit in der Fertigung gut beherrschbaren und überwachbaren Maßnahmen herstellbar sind.The arrangement according to the invention with the characterizing features of the main claim has the advantages that the individual operating stages of the engine are covered by the flats of different lengths, that the variable angles of the flats can be injected into the combustion chamber in different directions and that the flats are also can be produced with measures that are easy to control and monitor in production.

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 vorzugsweise um einen Winkel von 180° zueinander versetzt angeordnet 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 preferably be arranged offset from one another by an angle of 180 °. 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.

In manchen Fällen kann es auch vorteilhaft sein, eine der Abflachungen als zwei axial hintereinander angeordnete und unterschiedlich tiefe Abflachungen auszubilden, die an einer Stufenkante ineinander übergehen. Bei Bedarf können auch mehr als zwei Abflachungen, z.B. drei, hintereinander vorgesehen sein, so daß sich zwei .Übergangsstufen ergeben. Ferner können auch eine oder mehrere Abflachungen schräg zur Düsenachse angeordnet sein.In some cases it can also be advantageous to design one of the flats as two flats which are arranged axially one behind the other and have different depths and which merge into one another at a step edge. If necessary, more than two flats, e.g. three, can be provided one behind the other, so that there are two. Furthermore, one or more flats can be arranged obliquely to the nozzle axis.

Durch die kennzeichnenden Merkmale des Anspruchs 4 erhält man einen von der Düsennadel abhängigen Endquerschnitt auch bei vollem Hub der Ventilnadel. Dadurch ist es möglich bei verschiedenen Motortypen den gleichen Düsenkörper zu verwenden. Auch werden Einstell- und optimierungsaufgaben wesentlich vereinfacht.Due to the characterizing features of claim 4, an end cross-section dependent on the nozzle needle is obtained even with a full stroke of the valve needle. This makes it possible to use the same nozzle body for different engine types. Adjustment and optimization tasks are also significantly simplified.

Zwei Ausführungsbeispiele der Erfindung sind in der zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen vergrößerten Längsschnitt durch das einspritzseitige Ende des ersten Ausführungsbeispiels, Figur 2 einen Schnitt nach der Linie 11-11 in Figur 1, Figur 3 das zweite Ausführungsbeispiel in einer der Figur 1 entsprechenden Darstellung und Figur 4 einen Schnitt nach der Linie IV-IV in Figur 3.Two 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 11-11 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.

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.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 and 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.

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 throttle pin 18 is provided with two diametrically opposite flats 30, 32 that run parallel to the nozzle axis 28. 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 below the ring edge 22 of the nozzle body 10 by an overlap length 1.

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 Kraftstoff gedrosselt durch den Durchlaßquerschnitt 34 in den Brennraum der Maschine.The diameter of the throttle pin 18 is only smaller by the amount of a necessary movement gap than the diameter of the nozzle bore 20. The distance c of the longer flat 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 fuel, throttled, passes through the passage 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.When 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 ring edge 24 of the throttle pin 18 extends beyond the ring edge 22 on the nozzle body 10, the majority of the fuel is injected unthrottled.

Das Ausführungsbeispiel nach den Figuen 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 Abflachungen 32 und 40, die entsprechend niedriger als die Stufenkante 38 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.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 and 40, which is correspondingly lower than the step edge 38 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 14a ein weiterer bevorzugter Druchlaßquerschnitt 44, der dem Durchlaßquerschnitt 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 valve needle 14a in the closed position of a further preferred passage cross section 44, which is diametrically opposite 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 at the start of injection.

Der Drosselzapfen 18a ist so lang bemessen, daß er bei vollem Hub der Ventilnadel 14a noch ein Stück weit in die Düsenbohrung 20 hineinragt. In dieser Endstellung ist der gesamte Durchlaßquerschnitt durch die Summe der Durchlaßquerschnitte 34 und 36 gegeben. Es ist vorstellbar, noch weitere Abflachungen unter verschiedenen Winkeln auf dem Drosselzapfen 18a anzubringen, die erst bei vollem Hub der Ventilnadel 14a zum Gesamtdurchlaßquerschnitt beitragen und somit im Vollastbetrieb wirksam werden.The throttle pin 18a is dimensioned so long that it protrudes a little further into the nozzle bore 20 at full stroke of the valve needle 14a. In this end position, the total passage cross section is given by the sum of the passage cross sections 34 and 36. It is conceivable to provide further flattenings at different angles on the throttle pin 18a, which only contribute to the total passage cross section when the valve needle 14a is fully lifted and thus become effective in full load operation.

Claims (4)

1. Fuel injection nozzle for internal combustion engines, comprising a nozzle body (10) in which a valve seat (12) which is directed against the fuel flow is formed and a valve needle (14), lifting away from the former towards the inside, is displaceably supported which carries a pintle (18) which, in the closed position of the valve needle (14), plunges into a nozzle hole (20) adjoining the valve seat (12) and has on its circumference at least two flats (30, 32) which are arranged offset via an angle with respect to one another and originate from an annular edge section (24) at the combustion space end, for forming a passage section (34, 36) in the nozzle hole (20) which is greater in the open position of the valve needle (14) than in its closed position, characterized in that at least two of the flats (30, 32), which are offset at an angle with respect to one another, are constructed to be of different length originating from the annular edge section (24) and, as a result, end in different cross-sectional planes of the pintle (18).
2. Injection nozzle according to Claim 1 or 2, characterized in that two flats (30, 32) have different distances (c, d) from the nozzle axis (28).
3. Injection nozzle according to Claim 1 or 2, characterized in that two flats (32, 40) having different distances (d, e) from the nozzle axis (28) are arranged axially behind one another and pass into one another at a step edge (42).
4. Injection nozzle according to one of the preceding claims, characterized in that the pintle (18) is dimensioned in such a manner that it plunges by at least a further section into the nozzle hole (20) at full stroke of the valve needle (14) and that the end cross-section in the nozzle hole (20), corresponding to the main injection, is formed and determined by the flats of the pintle (18).
EP87900644A 1986-02-17 1987-01-10 Fuel injection nozzle for internal combustion engines Expired - Lifetime EP0293371B1 (en)

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 EP0293371A1 (en) 1988-12-07
EP0293371B1 true EP0293371B1 (en) 1990-08-08

Family

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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)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
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

Also Published As

Publication number Publication date
JP2557926B2 (en) 1996-11-27
US4909446A (en) 1990-03-20
BR8707588A (en) 1988-12-06
DE3604907A1 (en) 1987-08-20
WO1987005077A1 (en) 1987-08-27
JPH01501644A (en) 1989-06-08
EP0293371A1 (en) 1988-12-07
DE3764270D1 (en) 1990-09-13

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