EP0890735B2 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP0890735B2
EP0890735B2 EP98109048.3A EP98109048A EP0890735B2 EP 0890735 B2 EP0890735 B2 EP 0890735B2 EP 98109048 A EP98109048 A EP 98109048A EP 0890735 B2 EP0890735 B2 EP 0890735B2
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EP
European Patent Office
Prior art keywords
valve
combustion chamber
degree
spray holes
rounding
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EP98109048.3A
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German (de)
French (fr)
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EP0890735B1 (en
EP0890735A3 (en
EP0890735A2 (en
Inventor
Karl Hofmann
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/184—Discharge orifices having non circular sections

Definitions

  • the invention relates to an internal combustion engine having a combustion chamber and a fuel injection valve comprising a displaceable in a valve body against the restoring force of a valve spring valve member having a valve sealing surface which cooperates with a arranged on the valve body valve seat, and having a plurality of valve seat disposed in the valve body spray holes whose Inlet openings are rounded.
  • Such a fuel injection valve for an internal combustion engine is, for example, from the EP 0 370 659 A1 out.
  • the rounding of the inlet openings of the injection holes is made possible that a larger amount of fuel can be injected through the injection holes in the combustion chamber of the internal combustion engine, since a narrowing of the fuel flowing through the injection holes, resulting in a sharp-edged inlet opening does not occur.
  • the shape of the jet sprayed through the spray holes can be changed by the rounded inlet openings.
  • the injection holes on their side facing the valve member have a different degree of rounding than on its side facing away from the valve member.
  • rounding degree is to be understood in each case as the radius of the rounding.
  • a large rounding degree means a rounding with a large radius, a small roundness a rounding with a small radius.
  • the rounding degrees of the inlet opening of the injection hole of the EP 0 370 659 A1 known fuel injection valve are chosen so that the best possible combustion in the combustion chamber can be achieved.
  • an injection valve for internal combustion engines which has a number of injection ports.
  • the injection ports have different rounding radii at the transition to the valve seat.
  • the radius of curvature hereby varies both over the circumference of the individual injection openings and at the angle which the injection openings enclose with the longitudinal axis of the injection valve.
  • the invention is therefore based on the object, an internal combustion engine with a combustion chamber and a fuel injection valve of the generic type such that an easy adjustment of the spray holes on a variety of conditions, in particular to various installation positions in combustion chambers and on a variety of combustion chamber shapes allows so that the combustion process is further improved.
  • the degree of rounding of the inlet openings of the injection holes is adapted to the arrangement of the injection holes in the valve body, to the installation position in a combustion chamber of the internal combustion engine and to the combustion chamber shape of the internal combustion engine.
  • the degree of rounding of the inlet opening of the injection hole which is further removed from a combustion chamber wall in the installed state, a greater degree of rounding than the inlet opening of a less distant from the combustion chamber wall spray hole.
  • injection holes may have the same degree of rounding, but it is also possible that all the injection holes have inlet openings with completely different degrees of rounding. In principle, a wide variety of combinations are conceivable with regard to the degree of rounding of the individual injection holes.
  • the inlet openings of one or more spray holes on their side facing the valve member have a different degree of rounding than on its side facing away from the valve member. It varies the degree of rounding not only from injection hole to injection hole, but also also depending on the position of the inlet openings relative to the valve member at each inlet opening of the individual injection holes.
  • a fuel injection valve for internal combustion engines shown in FIG Fig. 2 , Includes a piston-shaped valve member 41, which is axially displaceably guided in a bore 42 of a valve body 43.
  • the valve member 41 has at its one, the combustion chamber of an internal combustion engine (not shown) facing the end of a conical valve sealing surface 44, with which it cooperates with a conical valve seat 45 at the inwardly projecting closed end of the bore 42.
  • the valve body 43 is clamped with its combustion chamber remote end by means of a clamping nut 46 axially against a valve holding body 47, wherein between the end faces of the valve body 43 and the valve holding body 47 an intermediate disc 48 is clamped with a central opening.
  • valve member 41 At its end facing away from the valve seat 45, the valve member 41 via a pressure piece 49 which projects through the washer 48, of a coil spring 50 designed as a valve spring, which is supported on a stationary stop 51 which is arranged on the valve holding body 47, and on the Valve member 41 exerts a valve seat 45 toward directed force, acted upon by a spring force.
  • spray holes 53, 57 are provided in the wall of the valve body 43, which open into the combustion chamber of the internal combustion engine.
  • the high-pressure fuel supply takes place in a known manner via a formed between the shank of the valve member 41 and the wall of the bore 42 annular channel 54, which expands into a pressure chamber 55 into which a discharging from an injection pump, not shown, discharge line 56.
  • the inlet openings 60 of the injection holes 53, 57 curves 61, 62, 63, 64 with different radii, ie with different degrees of rounding.
  • the inlet opening 60 of the injection hole 57 has, for example, curves 61, 62 with a smaller degree of rounding than the inlet opening 60 of the injection hole 53.
  • the degrees of rounding of the inlet openings of the injection holes differ on their side facing the valve member from the roundness degrees of the inlet openings facing away from the respective valve member Pages.
  • the spray hole 53 shown on the right side 53 whose inlet opening has greater rounding degrees than those of the inlet opening of the injection hole 57 disposed at a position of the combustion chamber of the internal combustion engine, which has a greater distance from the combustion chamber wall than that of the injection port 57th
  • the rounded portions 63, 64 with greater degrees of rounding a stronger bundling of the fuel jet ejected through the injection hole 53 is made possible, which moreover has a greater length than is the case with the fuel jet ejected through the injection hole 57.
  • the formation of the inlet port 60 of the injection ports 53, 57 is selected depending on the installation position in the combustion chamber and the combustion chamber shape. It proves to be particularly advantageous that the curves 61, 62, 63, 64 in a particularly simple manner, for example by so-called HE rounding, i. hydroerosives rounds are produced.
  • HE rounding i. hydroerosives rounds are produced.
  • a fluid containing abrasive particles is forced with pressure through previously made holes in the valve body 43, whereby the edges of the inlet ports are rounded by grinding.
  • spray holes can be drilled and rounded and only then the remaining spray holes drilled and rounded.
  • the first drilled and rounded spray holes are then rounded more rounded in a further HE rounding process than the last drilled injection holes.
  • an optimum quantity distribution of the injected fuel can be adapted to the combustion chamber shape and to the installation position, wherein the beam shape can be selected practically freely by varying the degrees of rounding.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Brennkraftmaschine mit einem Brennraum und einem Kraftstoffeinspritzventil umfassend ein in einem Ventilkörper entgegen der Rückstellkraft einer Ventilfeder verschiebliches Ventilglied mit einer Ventildichtfläche, die mit einem an dem Ventilkörper angeordneten Ventilsitz zusammenwirkt, und mit mehreren unterhalb des Ventilsitzes in dem Ventilkörper angeordneten Spritzlöchern, deren Einlaßöffnungen abgerundet sind.The invention relates to an internal combustion engine having a combustion chamber and a fuel injection valve comprising a displaceable in a valve body against the restoring force of a valve spring valve member having a valve sealing surface which cooperates with a arranged on the valve body valve seat, and having a plurality of valve seat disposed in the valve body spray holes whose Inlet openings are rounded.

Ein derartiges Kraftstoffeinspritzventil für eine Brennkraftmaschine geht beispielsweise aus der EP 0 370 659 A1 hervor. Durch die Abrundung der Einlaßöffnungen der Spritzlöcher wird ermöglicht, daß eine größere Menge Kraftstoffs durch die Spritzlöcher in den Brennraum der Brennkraftmaschine eingespritzt werden kann, da eine Einengung des durch die Spritzlöcher strömenden Kraftstoffes, die sich bei einer scharfkantigen Einlaßöffnung ergibt, nicht auftritt.Such a fuel injection valve for an internal combustion engine is, for example, from the EP 0 370 659 A1 out. The rounding of the inlet openings of the injection holes is made possible that a larger amount of fuel can be injected through the injection holes in the combustion chamber of the internal combustion engine, since a narrowing of the fuel flowing through the injection holes, resulting in a sharp-edged inlet opening does not occur.

Durch die abgerundeten Einlaßöffnungen kann darüber hinaus die Form des durch die Spritzlöcher ausgespritzten Strahls verändert werden. Bei dem aus der EP 0 370 659 A1 bekannten Kraftstoffeinspritzventil ist dabei vorgesehen, daß die Spritzlöcher auf ihrer dem Ventilglied zugewandten Seite einen anderen Rundungsgrad aufweisen als auf ihrer dem Ventilglied abgewandten Seite.In addition, the shape of the jet sprayed through the spray holes can be changed by the rounded inlet openings. In the from the EP 0 370 659 A1 known fuel injection valve is provided that the injection holes on their side facing the valve member have a different degree of rounding than on its side facing away from the valve member.

Hierbei und im folgenden ist unter Rundungsgrad dabei jeweils der Radius der Rundung zu verstehen. Ein großer Rundungsgrad bedeutet eine Rundung mit einem großen Radius, ein kleiner Rundungsgrad eine Rundung mit einem kleinen Radius.In this case and in the following, rounding degree is to be understood in each case as the radius of the rounding. A large rounding degree means a rounding with a large radius, a small roundness a rounding with a small radius.

Die Rundungsgrade der Einlaßöffnung des Spritzlochs des aus der EP 0 370 659 A1 bekannten Kraftstoffeinspritzventils sind so gewählt, daß eine möglichst optimale Verbrennung im Brennraum erzielt werden kann.The rounding degrees of the inlet opening of the injection hole of the EP 0 370 659 A1 known fuel injection valve are chosen so that the best possible combustion in the combustion chamber can be achieved.

Aus der US 4 578 164 ist ein Einspritzventil für Brennkraftmaschinen bekannt, das eine Anzahl von Einspritzöffnung aufweist. Die Einspritzöffnungen weisen verschiedene Rundungsradien am Übergang zum Ventilsitz auf. Der Rundungsradius variiert hierbei sowohl über den Umfang der einzelnen Einspritzöffnungen als auch mit dem Winkel, den die Einspritzöffnungen mit der Längsachse des Einspritzventils einschließen.From the US 4,578,164 For example, an injection valve for internal combustion engines is known which has a number of injection ports. The injection ports have different rounding radii at the transition to the valve seat. The radius of curvature hereby varies both over the circumference of the individual injection openings and at the angle which the injection openings enclose with the longitudinal axis of the injection valve.

Wenn - wie es heute üblich ist - mehrere Spritzlöcher in dem Kraftstoffeinspritzventil vorgesehen sind, können feste, vorgegebene Spritzlöcher und die dadurch hervorgerufenen Strahlformen des ausgespritzten Kraftstoffs je nach Einbauposition im Brennraum einer Brennkraftmaschine wenig vorteilhaft sein.If - as is customary today - several injection holes are provided in the fuel injection valve, fixed, predetermined injection holes and the resulting spray shapes of the ejected fuel depending on the installation position in the combustion chamber of an internal combustion engine may be less advantageous.

Der Erfindung liegt daher die Aufgabe zugrunde, eine Brennkraftmaschine mit einem Brennraum und einem Kraftstoffeinspritzventil der gattungsgemäßen Art derart weiterzubilden, daß auf einfach herzustellende Weise eine Anpassung der Spritzlöcher auf unterschiedlichste Verhältnisse, insbesondere auf unterschiedlichste Einbaupositionen in Brennräumen sowie auf unterschiedlichste Brennraumformen ermöglich wird, so daß der Verbrennungsvorgang weiter verbessert wird.The invention is therefore based on the object, an internal combustion engine with a combustion chamber and a fuel injection valve of the generic type such that an easy adjustment of the spray holes on a variety of conditions, in particular to various installation positions in combustion chambers and on a variety of combustion chamber shapes allows so that the combustion process is further improved.

Vorteile der ErfindungAdvantages of the invention

Diese Aufgabe wird bei Brennkraftmaschine mit einem Brennraum und einem Kraftstoffeinspritzventil der eingangs beschriebenen Art erfindungsgemäß dadurch gelöst, daß ein Teil der Spritzlöcher wenigstens einen von dem Rest der Spritzlöcher unterschiedlichen Rundungsgrad aufweist.This object is achieved in internal combustion engine with a combustion chamber and a fuel injection valve of the type described above according to the invention that a part of the injection holes has at least one of the rest of the injection holes different degree of rounding.

Es ist vorgesehen, daß der Rundungsgrad der Einlaßöffnungen der Spritzlöcher auf die Anordnung der Spritzlöcher in dem Ventilkörper, auf die Einbauposition in einem Brennraum der Brennkraftmaschine und auf die Brennraumform der Brennkraftmaschine angepaßt ist.It is envisaged that the degree of rounding of the inlet openings of the injection holes is adapted to the arrangement of the injection holes in the valve body, to the installation position in a combustion chamber of the internal combustion engine and to the combustion chamber shape of the internal combustion engine.

Dabei weist der Rundungsgrad der Einlaßöffnung des Spritzlochs, das von einer Brennraumwand im eingebauten Zustand weiter entfernt ist, einen größeren Rundungsgrad auf als die Einlaßöffnung eines von der Brennraumwand weniger weit entfernten Spritzlochs. Durch den größeren Rundungsgrad wird nämlich eine schärfere Bündelung und eine größere Länge des durch ein derartiges Spritzloch ausgespritzten Kraftstoff-Strahls erreicht als bei einem Spritzloch, das eine Einlaßöffnung mit kleinerem Rundungsgrad aufweist.In this case, the degree of rounding of the inlet opening of the injection hole, which is further removed from a combustion chamber wall in the installed state, a greater degree of rounding than the inlet opening of a less distant from the combustion chamber wall spray hole. By the greater degree of rounding namely a sharper bundling and a greater length of the ejected through such a spray hole fuel jet is achieved as in a spray hole having an inlet opening with a smaller degree of rounding.

Dadurch, daß wenigstens ein Teil der Spritzlöcher einen von dem Rest der Spritzlöcher unterschiedlichen Rundungsgrad aufweist, wird insbesondere ermöglicht, daß die aus den einzelnen Spritzlöchern eines Kraftstoffeinspritzventils ausströmenden Strahlformen unterschiedlichste, auf die jeweilige Einbausituation und Einbauposition angepaßte Formen aufweisen. Hierdurch wird insbesondere ermöglicht, daß mittels eines einzigen Kraftstoffeinspritzventils mehrere, voneinander verschiedene Strahlformen und damit eine positionsabhängige Mengenverteilung des in einen Brennraum eingespritzten Kraftstoffs erreicht wird.Characterized in that at least a portion of the injection holes has a different degree of rounding from the rest of the injection holes, in particular allows the effluent from the individual spray holes of a fuel injection valve beam shapes have a variety of adapted to the particular installation situation and installation forms. This makes it possible, in particular, that a plurality of mutually different jet shapes and thus a position-dependent quantity distribution of the fuel injected into a combustion chamber are achieved by means of a single fuel injection valve.

Dabei können mehrere Spritzlöcher den gleichen Rundungsgrad aufweisen, es ist aber auch möglich, daß sämtliche Spritzlöcher Einlaßöffnungen mit völlig unterschiedlichen Rundungsgraden aufweisen. Rein prinzipiell sind hinsichtlich der Rundungsgrade der einzelnen Spritzlöcher die unterschiedlichsten Kombinationen denkbar.Several injection holes may have the same degree of rounding, but it is also possible that all the injection holes have inlet openings with completely different degrees of rounding. In principle, a wide variety of combinations are conceivable with regard to the degree of rounding of the individual injection holes.

Weiter ist vorgesehen, daß die Einlaßöffnungen einzelner oder mehrerer Spritzlöcher auf Ihrer dem Ventilglied zugewandten Seite einen anderen Rundungsgrad aufweisen als auf ihrer dem Ventilglied abgewandten Seite. Es variiert der Rundungsgrad nicht nur von Spritzloch zu Spritzloch, sondern darüber hinaus auch noch abhängig von der Position der Einlaßöffnungen relativ zu dem Ventilglied an jeweils einer Einlaßöffnung der einzelnen Spritzlöcher.It is further provided that the inlet openings of one or more spray holes on their side facing the valve member have a different degree of rounding than on its side facing away from the valve member. It varies the degree of rounding not only from injection hole to injection hole, but also also depending on the position of the inlet openings relative to the valve member at each inlet opening of the individual injection holes.

Zeichnungdrawing

Weitere Merkmale und Vorteile der Erfindung sind Gegenstand der nachfolgenden Beschreibung sowie der zeichnerischen Darstellung einiger Ausführungsbeispiele.Further features and advantages of the invention are the subject of the following description and the drawings of some embodiments.

In der Zeichnung zeigen:

Fig. 1
eine teilweise geschnittene Darstellung des unteren Bereichs eines erfindungsgemäßen Kraftstoffeinspritzventils und
Fig. 2
eine geschnittene Darstellung eines Kraftstoffeinspritzventils.
In the drawing show:
Fig. 1
a partially sectioned view of the lower portion of a fuel injection valve according to the invention and
Fig. 2
a sectional view of a fuel injection valve.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Ein Kraftstoffeinspritzventil für Brennkraftmaschinen, dargestellt in Fig. 2, umfaßt ein kolbenförmiges Ventilglied 41, das axialverschieblich in einer Bohrung 42 eines Ventilkörpers 43 geführt ist. Das Ventilglied 41 weist an seinem einen, dem Brennraum einer Brennkraftmaschine (nicht dargestellt) zugewandten Ende eine konische Ventildichtfläche 44 auf, mit der es mit einem konischen Ventilsitz 45 am nach innen ragenden geschlossenen Ende der Bohrung 42 zusammenwirkt. Der Ventilkörper 43 ist dabei mit seinem brennraumfernen Ende mittels einer Spannmutter 46 axial gegen einen Ventilhaltekörper 47 verspannt, wobei zwischen den Stirnflächen des Ventilkörpers 43 und des Ventilhaltekörpers 47 eine Zwischenscheibe 48 mit einer zentralen Öffnung eingespannt ist.A fuel injection valve for internal combustion engines, shown in FIG Fig. 2 , Includes a piston-shaped valve member 41, which is axially displaceably guided in a bore 42 of a valve body 43. The valve member 41 has at its one, the combustion chamber of an internal combustion engine (not shown) facing the end of a conical valve sealing surface 44, with which it cooperates with a conical valve seat 45 at the inwardly projecting closed end of the bore 42. The valve body 43 is clamped with its combustion chamber remote end by means of a clamping nut 46 axially against a valve holding body 47, wherein between the end faces of the valve body 43 and the valve holding body 47 an intermediate disc 48 is clamped with a central opening.

An seinem dem Ventilsitz 45 abgewandten Ende wird das Ventilglied 41 über ein Druckstück 49, das die Zwischenscheibe 48 durchragt, von einer als Schraubenfeder 50 ausgebildeten Ventilfeder, die sich an einem ortsfesten Anschlag 51, der an dem Ventilhaltekörper 47 angeordnet ist, abstützt und auf das Ventilglied 41 eine zum Ventilsitz 45 hin gerichtete Kraft ausübt, mit einer Federkraft beaufschlagt.At its end facing away from the valve seat 45, the valve member 41 via a pressure piece 49 which projects through the washer 48, of a coil spring 50 designed as a valve spring, which is supported on a stationary stop 51 which is arranged on the valve holding body 47, and on the Valve member 41 exerts a valve seat 45 toward directed force, acted upon by a spring force.

Unterhalb der Ventildichtfläche 44 und des Ventilsitzes 45 sind in der Wand des Ventilkörpers 43 Spritzlöcher 53, 57 vorgesehen, die in den Brennraum der Brennkraftmaschine münden.Below the valve sealing surface 44 and the valve seat 45, spray holes 53, 57 are provided in the wall of the valve body 43, which open into the combustion chamber of the internal combustion engine.

Die Kraftstoffhochdruckzufuhr erfolgt in bekannter Weise über einen zwischen dem Schaft des Ventilglieds 41 und der Wand der Bohrung 42 ausgebildeten Ringkanal 54, der sich in einen Druckraum 55 erweitert, in den eine von einer nicht gezeigten Einspritzpumpe abführende Druckleitung 56 mündet.The high-pressure fuel supply takes place in a known manner via a formed between the shank of the valve member 41 and the wall of the bore 42 annular channel 54, which expands into a pressure chamber 55 into which a discharging from an injection pump, not shown, discharge line 56.

Wie in Fig. 1 dargestellt ist, weisen die Einlaßöffnungen 60 der Spritzlöcher 53, 57 Rundungen 61, 62, 63, 64 mit unterschiedlichen Radien, d.h. mit unterschiedlichen Rundungsgraden auf.As in Fig. 1 is shown, the inlet openings 60 of the injection holes 53, 57 curves 61, 62, 63, 64 with different radii, ie with different degrees of rounding.

Die Einlaßöffnung 60 des Spritzlochs 57 weist beispielsweise Rundungen 61, 62 mit kleinerem Rundungsgrad auf als die Einlaßöffnung 60 des Spritzlochs 53. Dabei unterscheiden sich die Rundungsgrade der Einlaßöffnungen der Spritzlöcher auf ihrer dem Ventilglied zugewandten Seite von den Rundungsgraden der Einlaßöffnungen auf ihren jeweils dem Ventilglied abgewandten Seiten.The inlet opening 60 of the injection hole 57 has, for example, curves 61, 62 with a smaller degree of rounding than the inlet opening 60 of the injection hole 53. In this case, the degrees of rounding of the inlet openings of the injection holes differ on their side facing the valve member from the roundness degrees of the inlet openings facing away from the respective valve member Pages.

Bei den in Fig. 1 dargestellten Spritzlöchern 53, 57 ist beispielsweise das auf der rechten Seite dargestellte Spritzloch 53, dessen Einlaßöffnung größere Rundungsgrade aufweist als diejenigen der Einlaßöffnung des Spritzlochs 57 an einer Stelle des Brennraums der Brennkraftmaschine angeordnet, die einen größeren Abstand zur Brennraumwand aufweist als derjenige des Spritzlochs 57. Durch die Rundungen 63, 64 mit größeren Rundungsgraden wird nämlich eine stärkere Bündelung des durch das Spritzloch 53 ausgespritzten Kraftstoff-Strahls ermöglicht, der zudem eine größere Länge aufweist als es bei dem durch das Spritzloch 57 ausgespritzten Kraftstoff-Strahl der Fall ist.At the in Fig. 1 For example, the spray hole 53 shown on the right side 53, whose inlet opening has greater rounding degrees than those of the inlet opening of the injection hole 57 disposed at a position of the combustion chamber of the internal combustion engine, which has a greater distance from the combustion chamber wall than that of the injection port 57th By virtue of the rounded portions 63, 64 with greater degrees of rounding, a stronger bundling of the fuel jet ejected through the injection hole 53 is made possible, which moreover has a greater length than is the case with the fuel jet ejected through the injection hole 57.

Die Ausbildung der Einlaßöffnung 60 der Spritzlöcher 53, 57 wird mit anderen Worten abhängig von der Einbauposition in dem Brennraum und der Brennraumform gewählt. Dabei erweist es sich als besonders vorteilhaft, daß die Rundungen 61, 62, 63, 64 auf besonders einfache Weise beispielsweise durch sogenanntes HE-Runden, d.h. hydroerosives Runden hergestellt werden. Bei diesem hydroerosiven Runden wird ein Schleifkörper enthaltendes Fluid mit Druck durch zuvor hergestellte Bohrungen in dem Ventilkörper 43 gepreßt, wodurch die Kanten der Einlaßöffnungen durch Abschleifen gerundet wurden. Durch Abdecken einzelner Spritzlöcher auf ihrer Einlaßseite und/oder auf ihrer Auslaßseite können unterschiedliche Rundungsgrade hergestellt werden. Statt abgedeckt zu werden, kann zunächst auch nur ein Teil der Spritzlöcher gebohrt und gerundet und erst dann die übrigen Spritzlöcher gebohrt und gerundet werden. Die zuerst gebohrten und gerundeten Spritzlöcher werden sodann bei einem weiteren HE-Rundungsvorgang stärker gerundet als die zuletzt gebohrten Spritzlöcher.In other words, the formation of the inlet port 60 of the injection ports 53, 57 is selected depending on the installation position in the combustion chamber and the combustion chamber shape. It proves to be particularly advantageous that the curves 61, 62, 63, 64 in a particularly simple manner, for example by so-called HE rounding, i. hydroerosives rounds are produced. In this hydroerosive rounding, a fluid containing abrasive particles is forced with pressure through previously made holes in the valve body 43, whereby the edges of the inlet ports are rounded by grinding. By covering individual spray holes on their inlet side and / or on their outlet side different degrees of rounding can be produced. Instead of being covered, at first only a part of the spray holes can be drilled and rounded and only then the remaining spray holes drilled and rounded. The first drilled and rounded spray holes are then rounded more rounded in a further HE rounding process than the last drilled injection holes.

Durch die obenbeschriebenen Kraftstoffeinspritzventile läßt sich eine optimale Mengenverteilung des eingespritzten Kraftstoffes auf die Brennraumform und auf die Einbauposition anpassen, wobei die Strahlform durch Verändern der Rundungsgrade praktisch frei wählbar ist.By means of the above-described fuel injection valves, an optimum quantity distribution of the injected fuel can be adapted to the combustion chamber shape and to the installation position, wherein the beam shape can be selected practically freely by varying the degrees of rounding.

Claims (1)

  1. Internal combustion engine having a combustion chamber and a fuel injection valve, which fuel injection valve comprises a valve body (43) in which a displaceable valve member (41) is arranged counter to the resetting force of a valve spring (50), which valve member (41) interacts, by means of a valve sealing face (44), with a valve seat (45) which is arranged on the valve body, and having a plurality of spray holes arranged below the valve seat (45) in the valve body (43), the inlet openings (60) of which spray holes are rounded, some of the spray holes (53) having at least one degree of curvature which is different to the rest of the spray holes (57), the inlet openings (60) of some spray holes (53, 57) of the fuel injection valve having a different degree of curvature on their side which faces towards the valve member (41) than on their side which faces away from the valve member (41), characterized in that the degree of curvature of the spray holes (53, 57) is matched to the arrangement of the spray holes (53, 57) in the valve body (43), to the installation position in a combustion chamber of the internal combustion engine and to the shape of the combustion chamber of the internal combustion engine, in such a way that the degree of curvature of the inlet opening (60) of that spray hole (53) which, in the installed state, is further away from a combustion chamber wall in the direction of the fuel jet which is sprayed out has a greater degree of curvature than the inlet opening (60) of a spray hole (57) which is closer to the combustion chamber wall.
EP98109048.3A 1997-07-11 1998-05-19 Fuel injection valve Expired - Lifetime EP0890735B2 (en)

Applications Claiming Priority (2)

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DE19729827 1997-07-11
DE19729827A DE19729827A1 (en) 1997-07-11 1997-07-11 Fuel injector

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Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19914719C2 (en) * 1999-03-31 2001-05-03 Siemens Ag Device for hydroerosive rounding of inlet edges of the spray hole channels in a nozzle body
DE19931890A1 (en) * 1999-07-08 2001-01-18 Siemens Ag Edge rounding method for combustion engine fuel injection nozzle injection orifice channel
JP4189714B2 (en) * 2000-08-03 2008-12-03 株式会社デンソー Fuel injection device
DE10156020A1 (en) * 2001-11-15 2003-07-17 Bosch Gmbh Robert Fuel injector
DE10219608A1 (en) * 2002-05-02 2003-11-20 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10330256A1 (en) † 2003-07-04 2005-01-20 Robert Bosch Gmbh Fuel injection valve for internal combustion engine, comprises bulges arranged such that the two connecting lines of points of largest distance to the center form an angle of less than 180 degrees with the mirror plane
DE102004062008A1 (en) * 2004-12-23 2006-07-13 Robert Bosch Gmbh Fuel filter with outlet openings, which are preferably processed by a hydroerosive method
US7572997B2 (en) * 2007-02-28 2009-08-11 Caterpillar Inc. EDM process for manufacturing reverse tapered holes
EP2333307A4 (en) * 2008-09-24 2013-03-13 Toyota Motor Co Ltd Fuel injection valve for internal combustion engine and method of manufacturing the same
WO2019030078A1 (en) * 2017-08-08 2019-02-14 Robert Bosch Gmbh Fuel injector nozzle
DE102019202073A1 (en) 2019-02-15 2020-08-20 Robert Bosch Gmbh Method for producing an injection nozzle for injecting fuel into a combustion chamber of an internal combustion engine and nozzle arrangement with an injection nozzle

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58106167A (en) † 1981-12-21 1983-06-24 Hino Motors Ltd Fuel injection nozzle of internal-combustion engine

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2557772A1 (en) * 1975-12-20 1977-06-23 Kloeckner Humboldt Deutz Ag FUEL INJECTION VALVE
JPS6049262U (en) * 1983-09-14 1985-04-06 日産自動車株式会社 Diesel engine fuel injection valve
US4578164A (en) * 1983-08-24 1986-03-25 Nissan Motor Co., Ltd. Method of electrolytically finishing spray-hole of fuel injection nozzle
JPH0267459A (en) * 1988-08-31 1990-03-07 Nippon Denso Co Ltd Fuel injection nozzle
GB8827107D0 (en) * 1988-11-19 1988-12-21 Lucas Ind Plc Fuel injection nozzle
JPH0494452A (en) * 1990-08-08 1992-03-26 Nissan Motor Co Ltd Fuel injection nozzle
JPH0583367U (en) * 1992-04-20 1993-11-12 日産ディーゼル工業株式会社 Fuel injection nozzle for direct injection diesel engine
DE19507188C1 (en) * 1995-03-02 1996-08-14 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
EP0809017A1 (en) * 1996-05-22 1997-11-26 Steyr-Daimler-Puch Aktiengesellschaft Two-stage fuel injection nozzel for internal combustion engine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58106167A (en) † 1981-12-21 1983-06-24 Hino Motors Ltd Fuel injection nozzle of internal-combustion engine

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
LONG ZHANG, TADASHI TSURUSHIMA, TAKAHIRO UEDA,: "Measurement of Liquid Phase Penetration of Evaporating", SAE 971645, 31 December 1997 (1997-12-31) - 31 December 1997 (1997-12-31), pages 87 - 93 †
S. KAMPMANN, B. DITTUS, P. MATTES, M. KIRNER: "The Influence of Hydro Grinding at VCO Nozzles on the Mixture Preparation in a DI Diesel Engine", SAE 960867, 26 February 1996 (1996-02-26) - 29 February 1996 (1996-02-29) †

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EP0890735B1 (en) 2006-10-18
JP4154033B2 (en) 2008-09-24
EP0890735A3 (en) 2001-10-10
JPH1193806A (en) 1999-04-06
DE59813768D1 (en) 2006-11-30
US5992766A (en) 1999-11-30
EP0890735A2 (en) 1999-01-13
DE19729827A1 (en) 1999-01-14

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