EP0141111B1 - Fuel injection device - Google Patents

Fuel injection device Download PDF

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Publication number
EP0141111B1
EP0141111B1 EP84110009A EP84110009A EP0141111B1 EP 0141111 B1 EP0141111 B1 EP 0141111B1 EP 84110009 A EP84110009 A EP 84110009A EP 84110009 A EP84110009 A EP 84110009A EP 0141111 B1 EP0141111 B1 EP 0141111B1
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EP
European Patent Office
Prior art keywords
transverse groove
spring element
guide member
face
injection device
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
Application number
EP84110009A
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German (de)
French (fr)
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EP0141111A2 (en
EP0141111A3 (en
Inventor
Rolf Prillwitz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LOrange GmbH
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LOrange GmbH
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Publication date
Application filed by LOrange GmbH filed Critical LOrange GmbH
Priority to AT84110009T priority Critical patent/ATE44584T1/en
Publication of EP0141111A2 publication Critical patent/EP0141111A2/en
Publication of EP0141111A3 publication Critical patent/EP0141111A3/en
Application granted granted Critical
Publication of EP0141111B1 publication Critical patent/EP0141111B1/en
Expired 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift

Definitions

  • the invention relates to a fuel injection device with an injection pump, the piston of which is displaceably mounted in a bore in a guide body, and with a nozzle element which is clamped directly against the end face of the guide body and has a valve needle controlling its spray hole, which extends into one of the end faces of the guide body
  • Valve needle adapted bore protrudes into a receiving space machined into the guide body, in which a spring element is arranged which presses the valve needle onto its valve seat, a fuel channel connected to the pump working space running laterally next to this receiving space in the guide body, which runs into the end face of the guide body opens and there communicates with a channel of the nozzle element leading to the nozzle.
  • a fuel injection device of this type is known from DE-OS-1 805 024. It differs from other known constructions essentially in that there is only one high-pressure sealing surface between the guide body and the nozzle element.
  • the receiving space for the spring element is incorporated centrally from the end face of the guide body as a blind hole.
  • the diameter of the bore on the end face of the guide body is therefore at least as large as the diameter of the spring element, which must find space in this receiving space. Since the spring diameter depends on the desired opening pressure of the valve and because a certain wall thickness between the bore leading to the receiving space and the fuel channel must also be required for reasons of strength, the diameter of the guide body on its end face and thus also the diameter of the nozzle element is proportional in the known design large.
  • the present invention has for its object to develop a fuel injection device of the type mentioned with only one high-pressure sealing surface so that it can be made more compact at a high delivery pressure, easy to manufacture and easy to assemble.
  • Feature c) is therefore of particular advantage for the present invention.
  • the stilts and the spring element can namely be inserted into the transverse groove at an angle to the longitudinal direction of the guide body and pivoted into the operating position by lateral pressure, the support bar sliding along the wall delimiting the transverse groove towards the piston side.
  • This assembly process is very simple and can be carried out quickly without special tools, and at the same time the necessary tensioning of the spring elements is effected.
  • a device for adjusting the operating voltage of the spring element or elements, as is necessary in the prior art, can be dispensed with. The advantage of a short overall length is achieved again.
  • a preferred embodiment of the device according to the features of claim 2 is particularly space-saving because in an oblique arrangement with respect to the axis of the guide body of the portion of the fuel channel which runs into the end face of the guide body, it is possible to use standard nozzle elements of small size. Of course, one must ensure according to claim 3 that a sufficient wall thickness to the fuel channel remains at the level of the receiving space of the spring element.
  • the distance from the axis of the guide body on the end face can be further reduced with an oblique arrangement of the fuel channel.
  • end regions can have a trapezoidal cross-section, but a semicircular cross-section is preferred for production-technical reasons, especially since this means uniform material stress without chip peaks at the corners of the transverse groove is guaranteed.
  • the cross section of the support beam at the end region of the transverse groove should correspond so that guide surfaces are formed on the guide body and on the support beam for the lateral insertion of the support beam into the transverse groove.
  • a semicircular cross section of the support beam an otherwise possible pivoting movement of the support beam about an axis in the longitudinal direction of the transverse groove will be prevented by a retaining pin anchored in the guide body and engaging in a groove in the support beam.
  • a coil spring is preferably used as the spring element.
  • several, preferably three, helical compression springs should be inserted into the transverse groove, because then helical compression springs of smaller diameter can be used and the width of the transverse groove can thus also be reduced.
  • FIGS. 1-6 each show two partial longitudinal sections rotated by 90 degrees to one another through different designs of a fuel injection device according to the invention.
  • Fig. 7 again shows a partial longitudinal section during the assembly process.
  • the pump working chamber 13 is supplied with fuel in a known manner via a transverse bore 14 from an annular chamber 15.
  • a nozzle element, generally designated 20, with spray holes 21 is clamped directly against the free end face 23 of the guide body 10 by means of the union nut 22.
  • This fuel injection device therefore has only one high-pressure sealing surface in the region of this end face 23.
  • the fuel is conveyed from the pump work chamber 13 via a channel 24 to the nozzle element 20.
  • This fuel channel 24 opens into this end face 23 and then continues in a channel section 25 in the nozzle element.
  • the spray holes 21 of this nozzle element 20 can be controlled in a known manner by means of a valve needle 26, which has a collar 27 and then an extension 28 of smaller diameter.
  • a receiving space 30 for a spring element 31 is also incorporated, which acts on the extension 28 via a stilt 32 with a conical flange 33 and a shaft 34 and thus presses the valve needle onto its valve seat.
  • the shaft 34 of the stilt 32 and the shoulder 28 on the valve needle 26 protrude from opposite directions into a bore 35 which starts from the receiving space 30 and opens into the end face 23 of the guide body 10.
  • the receiving space 30 is designed as a transverse groove 40 which is open on one side.
  • this transverse groove 40 is machined into this guide body 10 as a continuous slot perpendicular to the plane intersecting the fuel channel 24 and the axis A of the guide body 10.
  • the spring element 31 is inserted transversely to its direction of action into this transverse groove 40 and brought into its central position in which it loads the valve needle.
  • a bore is first machined from the end face 23 into the guide body 10, the diameter D1 of which is adapted to the diameter of the shaft 34 of the stilt 32. Then a section of the bore 35 that runs out to the end face is expanded, into which a guide bush 42 for the attachment 28 on the valve needle is inserted.
  • This guide bush is preferably hardened and also serves as a stop surface for the collar 27 on the valve needle 26.
  • the diameter D of the bore in this bush 42 is adapted to the diameter of the extension 28.
  • the diameter D of the bore 35 on the end face 23 of the guide body is smaller than the width B of the receiving space 30 for the spring element 31.
  • the width B corresponds approximately to the diameter of a helical compression spring, which in the execution 1 and 2 serves as a spring element.
  • the diameter D of the bore 35 is therefore smaller than the width B of the receiving space 30.
  • This also allows the distance E from the axis A of the guide body 10 or the bore 35, which is usually central is arranged, can be reduced compared to the known embodiment without the material thickness of the wall portion 43 between this fuel channel 24 and the bore 35 would be weakened inadmissibly.
  • the portion of the fuel channel 24 which runs into the end face 23 is arranged obliquely to the axis A of the piston, i.e. the distance of this fuel channel from this axis is smaller in the area of the end face 23 of the guide body 10 than at the level of the receiving space 30.
  • the diameter at the end face 23 and thus the only high-pressure sealing surface can be reduced if the guide body 10 is conical towards the end face 23 tapered, as indicated at 44.
  • the cross section of the transverse groove 40 in the central region corresponds approximately to the cross section of the spring element and that the bottom towards the nozzle element 20 and the bottom towards the piston 12 are semicircular in cross section.
  • the transverse groove thus also tapers on the side facing the fuel channel 24, so that the latter moves closer to the axis A. can be feared without an inadmissible weakening of material between this fuel channel 24 and the end regions of the transverse groove 40.
  • other cross-sectional shapes are also conceivable in the end regions of the transverse groove 40, it being pointed out that this end region is designed in such a way that the conical flange 33 on the stilt 32 can be accommodated therein without requiring additional space.
  • the upper end region of the transverse groove 40 which is semicircular in cross section, is filled by a support beam 50, on which the helical compression spring is supported on one side.
  • this helical compression spring is supported directly on the flange 33 of the stilt 32.
  • three helical compression springs 51 are provided as spring elements, which act centrally on the stilt 32 via a support web 52.
  • a comparison of the drawings shows that the width B of the receiving space 30 is smaller and in turn the overall size is reduced or the device can also be used at a higher injection pressure.
  • the support bar 50 fills the end region of the transverse groove 40. It is particularly important that the transverse groove 40 and the support beam have mutually matched guide surfaces 71 and 72, respectively, which allow the support beam 50 to be pushed in and sliding along this wall 70.
  • the shaft 34 of the stilt 32 is inserted into the bore 35 in such a way that the axis of symmetry of the stilt 32 extends obliquely to the longitudinal direction A of the guide body.
  • the longitudinal axis of the compression spring 31 is also initially arranged at an angle to the longitudinal direction A of the guide body.
  • the support beam 50 can be inserted into the position shown in FIG. 7 without any effort, the shaft of the stilt 32 being supported on a shoulder 75 of the bore 35 at the transition between the bore sections of different diameters .
  • the compression spring 31 is not under tension. If a force is now exerted on the compression spring 31 and / or the support bar 50 in the direction of the arrow, the compression spring 31 is slightly pretensioned while the support bar 50 slides along the wall 70 on the guide body 10. You will coordinate the conditions so that the spring is not biased too much during this assembly process, which would complicate the assembly process. On the other hand, there should be a slight preload in the operating position of the spring so that the parts do not accidentally fall out of the transverse groove during further assembly.
  • the nozzle element 20 is attached and screwed onto the guide body 10 by means of the union nut 22.
  • the compression spring 31 is further pretensioned by the extension 28 of the valve needle 26, which dips further and further into the bore 35.
  • the correct valve opening pressure should be given when the nozzle element 20 bears against the free end face 23 of the guide body. For this purpose, it was determined beforehand by experiments how many disks 60 must be placed on the flange of the stilt 32. A subsequent adjustment of the valve opening pressure is not necessary and also not possible because the union nut also covers the transverse groove 40 laterally and thus secures the position of the support beam 50, as shown in the drawings.
  • the thread 80 is provided between the guide body 10 and the union nut in the area of the transverse groove 40. This enables a compact construction in the longitudinal direction of the pump.
  • Fig. 7 is indicated as an additional feature that an anchored in the guide body 10 retaining pin 90 can engage in a groove 91 in the support beam 50 and thus prevents pivoting movement of the support beam 50 about an axis in the longitudinal direction of the transverse groove.
  • This feature is only important if the cross section of the support beam 50 is semicircular. With a trapezoidal cross section, pivoting of the support beam 50 is not possible even without this retaining pin.
  • a central bore 95 in the support beam 50 provides a connection between the receiving space and a ventilation channel 61 which opens into the annular space.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Automatic Assembly (AREA)
  • Springs (AREA)

Abstract

A fuel-injection device in which a nozzle element is directly pressed towards the front face of a guide body for the pump plunger. The guide body is provided with an enlarged slot into which a spring element can be entered from the side, which spring element loads the valve needle of the nozzle element. Thus this injection device can be made more compact than known types and is therefore especially suitable to be used in automotive vehicles.

Description

Die Erfindung bezieht sich auf eine Kraftstoffeinspritzvorrichtung mit einer Einspritzpumpe, deren Kolben in einer Bohrung eines Führungskörpers verschiebbar gelagert ist, sowie mit einem unmittelbar gegen die Stirnfläche des Führungskörpers gespannten Düsenelement mit einer dessen Spritzloch steuernden Ventilnadel, die in eine von der Stirnfläche des Führungskörpers ausgehende der Ventilnadel angepaßte Bohrung zu einem in den Führungskörper eingearbeiteten Aufnahmeraum hineinragt, in dem ein Federelement angeordnet ist, das die Ventilnadel auf ihren Ventilsitz drückt, wobei seitlich neben diesem Aufnahmeraum im Führungskörper ein mit dem Pumpenarbeitsraum in Verbindung stehender Kraftstoffkanal verläuft, der in die Stirnfläche des Führungskörpers mündet und dort mit einem zur Düse führenden Kanal des Düsenelements komuniziert.The invention relates to a fuel injection device with an injection pump, the piston of which is displaceably mounted in a bore in a guide body, and with a nozzle element which is clamped directly against the end face of the guide body and has a valve needle controlling its spray hole, which extends into one of the end faces of the guide body Valve needle adapted bore protrudes into a receiving space machined into the guide body, in which a spring element is arranged which presses the valve needle onto its valve seat, a fuel channel connected to the pump working space running laterally next to this receiving space in the guide body, which runs into the end face of the guide body opens and there communicates with a channel of the nozzle element leading to the nozzle.

Eine Kraftstoffeinspritzvorrichtung dieser Art ist aus der DE-OS-1 805 024 bekannt. Sie unterscheidet sich von anderen bekannten Konstruktionen im wesentlichen dadurch, daß nur eine Hochdruckdichtfläche zwischen dem Führungskörper und dem Düsenelement vorhanden ist.A fuel injection device of this type is known from DE-OS-1 805 024. It differs from other known constructions essentially in that there is only one high-pressure sealing surface between the guide body and the nozzle element.

Bei dieser bekannten Ausführung wird der Aufnahmeraum für das Federelement zentral von der Stirnfläche des Führungskörpers als Sackloch eingearbeitet. Der Durchmesser der Bohrung an der Stirnfläche des Führungskörpers ist daher mindestens so groß wie der Durchmesser des Federelementes, das in diesem Aufnahmeraum Platz finden muß. Da der Federdurchmesser vom gewünschten Öffnungsdruck des Ventils abhängt und da außerdem aus Festigkeitsgründen eine bestimmte Wandstärke zwischen der zum Aufnahmeraum führenden Bohrung und dem Kraftstoffkanal verlangt werden muß, ist bei der bekannten Ausführung der Durchmesser des Führungskörpers an dessen Stirnfläche und damit auch der Durchmesser des Düsenelementes verhältnismäßig groß.In this known embodiment, the receiving space for the spring element is incorporated centrally from the end face of the guide body as a blind hole. The diameter of the bore on the end face of the guide body is therefore at least as large as the diameter of the spring element, which must find space in this receiving space. Since the spring diameter depends on the desired opening pressure of the valve and because a certain wall thickness between the bore leading to the receiving space and the fuel channel must also be required for reasons of strength, the diameter of the guide body on its end face and thus also the diameter of the nozzle element is proportional in the known design large.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine Kraftstoffeinspritzvorrichtung der eingangs erwähnten Art mit nur einer Hochdruckdichtfläche so weiterzubilden, daß sie bei einem hohen Förderdruck kompakter gebaut werden kann, einfach herstellbar und leicht montierbar ist.The present invention has for its object to develop a fuel injection device of the type mentioned with only one high-pressure sealing surface so that it can be made more compact at a high delivery pressure, easy to manufacture and easy to assemble.

Diese Aufgabe wird erfindungsgemäß mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst.This object is achieved with the characterizing features of claim 1.

Zwar ist aus der US-PS-3 777 984 bereits eine Einspritzdüse bekannt, bei der der Aufnahmeraum für das Federelement als Quernut ausgebildet ist, durch die das Federelement seitlich einsetzbar ist. Bei dieser bekannten Ausführung hat jedoch die Bohrung von der Stirnfläche bis zum Aufnahmeraum für das Federelement einen konstanten Durchmesser. Bei einer ersten in dieser Druckschrift gezeigten Ausführung ist dieser Bohrungsdurchmesser dem Durchmesser eines Ansatzes an der Ventilnadel angepaßt, der diese Bohrung durchsetzt und in den Aufnahmeraum für das Federelement hineinragt. Man benötigt dabei also eine verhältnismäßig lange Ventilnadel und die axiale Länge der Düse muß vergrößert werden.An injection nozzle is already known from US Pat. No. 3,777,984, in which the receiving space for the spring element is designed as a transverse groove through which the spring element can be inserted laterally. In this known embodiment, however, the bore has a constant diameter from the end face to the receiving space for the spring element. In a first embodiment shown in this publication, this bore diameter is adapted to the diameter of an extension on the valve needle which passes through this bore and projects into the receiving space for the spring element. So you need a relatively long valve needle and the axial length of the nozzle must be increased.

Bei der aus der US-PS-3 777 984 bekannten Einspritzdüse ist außerdem eine Einstellschraube vorgesehen, die in einer Bohrung geführt ist, welche in die die Quernut auf der der Ventilnadel gegenüberliegenden Seite abgrenzenden Wand eingearbeitet ist. Eine solche Konstruktion mag bei einer Düse möglich sein, bei einer Übertragung dieses Merkmals auf den Führungskörper einer Einspritzpumpe ergeben sich aber Stabilitätsprobleme, denn es muß beachtet werden, daß diese Wand mit dem in dem sich anschließenden Pumpenraum entstehenden hohen Pumpendruck belastet ist. Man kann also die bei einer Düse gegebenen Verhältnisse nicht ohne weiteres auf eine sogenannte Pumpendüse übertragen.In the injection nozzle known from US Pat. No. 3,777,984, an adjusting screw is also provided which is guided in a bore which is machined into the wall delimiting the transverse groove on the side opposite the valve needle. Such a construction may be possible with a nozzle, but when this feature is transferred to the guide body of an injection pump, stability problems arise because it must be borne in mind that this wall is loaded with the high pump pressure which arises in the subsequent pump chamber. It is therefore not easy to transfer the conditions in a nozzle to a so-called pump nozzle.

Für die vorliegende Erfindung ist daher das Merkmal c) von besonderem Vorteil.Feature c) is therefore of particular advantage for the present invention.

Dieses Merkmal c) begründet zusammen mit den Merkmalen d) und e) einfache Herstellung bzw. Montage der erfindungsgemäßen Einspritzvorrichtung. Die Stelze und das Federelement können nämlich im Winkel zur Längsrichtung des Führungskörpers in die Quernut eingesetzt werden und durch seitlichen Druck in die Betriebsstellung verschwenkt werden, wobei der Auflagebalken an der die Quernut zur Kolbenseite hin abgrenzenden Wand entlanggleitet. Dieser Montagevorgang ist sehr einfach und ohne spezielle Werkzeuge rasch durchführbar und es wird dadurch gleichzeitig das notwendige Spannen der Federelemente bewirkt. Hierdurch kann eine Vorrichtung zur Einstellung der Betriebsspannung des bzw. der Federelemente wie sie im Stand der Technik notwendig ist entfallen. Dadurch wird wieder der Vorteil geringer Baulänge erreicht.This feature c) together with features d) and e) justifies simple manufacture or assembly of the injection device according to the invention. The stilts and the spring element can namely be inserted into the transverse groove at an angle to the longitudinal direction of the guide body and pivoted into the operating position by lateral pressure, the support bar sliding along the wall delimiting the transverse groove towards the piston side. This assembly process is very simple and can be carried out quickly without special tools, and at the same time the necessary tensioning of the spring elements is effected. As a result, a device for adjusting the operating voltage of the spring element or elements, as is necessary in the prior art, can be dispensed with. The advantage of a short overall length is achieved again.

Eine bevorzugte Ausführung der erfindungsgemäßen Vorrichtung gemäß den Merkmalen des Anspruchs 2, ist besonders raumsparend weil bei einer gegenüber der Achse des Führungskörpers schrägen Anordnung des in die Stirnfläche des Führungskörpers auslaufenden Abschnittes des Kraftstoffkanales erreicht wird, daß man serienmäßige Düsenelemente kleiner Baugröße verwenden kann. Natürlich muß man gemäß Anspruch 3 dafür sorgen, daß auch in Höhe des Aufnahmeraumes des Federelementes eine ausreichende Wandstärke zu dem Kraftstoffkanal bleibt.A preferred embodiment of the device according to the features of claim 2 is particularly space-saving because in an oblique arrangement with respect to the axis of the guide body of the portion of the fuel channel which runs into the end face of the guide body, it is possible to use standard nozzle elements of small size. Of course, one must ensure according to claim 3 that a sufficient wall thickness to the fuel channel remains at the level of the receiving space of the spring element.

Durch die Verjüngung des Endbereiches der Quernut zum Düsenelement hin kann bei einer schrägen Anordnung des Kraftstoffkanals dessen Abstand von der Achse des Führungskörpers an der Stirnfläche weiter verringert werden.By tapering the end region of the transverse groove towards the nozzle element, the distance from the axis of the guide body on the end face can be further reduced with an oblique arrangement of the fuel channel.

Diese Endbereiche können dabei einen trapezartigen Querschnitt aufweisen, doch wird aus fertigungstechnischen Gründen ein halbrunder Querschnitt bevorzugt, zumal damit eine gleichmäßige Materialbeanspruchung ohne Spannungsspitzen an den Eckbereichen der Quernut gewährleistet wird. Dabei soll der Querschnitt des Auflagebalkens am Endbereich der Quernut entsprechen, so daß also Führungsflächen am Führungskörper und am Auflagebalken zum seitlichen Einschieben des Auflagebalkens in die Quernut gebildet sind. Dabei wird man bei einem halbrunden Querschnitt des Auflagebalkens durch einen im Führungskörper verankerten und in eine Nut im Auflagebalken eingreifenden Haltestift eine sonst mögliche Verschwenkbewegung des Auflagebalkens um eine Achse in Längsrichtung der Quernut verhindern.These end regions can have a trapezoidal cross-section, but a semicircular cross-section is preferred for production-technical reasons, especially since this means uniform material stress without chip peaks at the corners of the transverse groove is guaranteed. The cross section of the support beam at the end region of the transverse groove should correspond so that guide surfaces are formed on the guide body and on the support beam for the lateral insertion of the support beam into the transverse groove. In the case of a semicircular cross section of the support beam, an otherwise possible pivoting movement of the support beam about an axis in the longitudinal direction of the transverse groove will be prevented by a retaining pin anchored in the guide body and engaging in a groove in the support beam.

Als Federelement wird vorzugsweise eine Schraubenfeder verwendet. Bei einem besonders bevorzugten Ausführungsbeispiel sollen mehrere, vorzugsweise drei Schraubendruckfedern in die Quernut eingesetzt werden, weil dann Schraubendruckfedern kleineren Durchmessers verwendet werden können und damit auch die Breite der Quernut reduziert werden kann.A coil spring is preferably used as the spring element. In a particularly preferred embodiment, several, preferably three, helical compression springs should be inserted into the transverse groove, because then helical compression springs of smaller diameter can be used and the width of the transverse groove can thus also be reduced.

Die Erfindung wird nachstehend anhand der in der Zeichnung dargestellten Ausführungsbeispiele näher erläutert. Die Figuren 1 - 6 zeigen jeweils zwei um 90 Grad zueinander gedrehte Teillängsschnitte durch unterschiedliche Ausführungen einer erfindungsgemäßen Kraftstoffeinspritzvorrichtung. Fig. 7 zeigt nochmals einen Teillängsschnitt während des Montagevorganges.The invention is explained below with reference to the embodiments shown in the drawing. FIGS. 1-6 each show two partial longitudinal sections rotated by 90 degrees to one another through different designs of a fuel injection device according to the invention. Fig. 7 again shows a partial longitudinal section during the assembly process.

Mit 10 ist ein Führungskörper bezeichnet, der eine Bohrung 11 aufweist, in dem ein Kolben 12 axial verschiebbar gelagert ist. Diese Bohrung 11 ist als Sackloch in den Führungskörper 10 eingearbeitet. Dem Pumpenarbeitsraum 13 wird in bekannter Weise Kraftstoff über eine Querbohrung 14 aus einem Ringraum 15 zugeführt.10 with a guide body is designated, which has a bore 11 in which a piston 12 is axially displaceably mounted. This bore 11 is incorporated as a blind hole in the guide body 10. The pump working chamber 13 is supplied with fuel in a known manner via a transverse bore 14 from an annular chamber 15.

Ein insgesamt mit 20 bezeichnetes Düsenelement mit Spritzlöchern 21 ist mittels der Überwurfmutter 22 unmittelbar gegen die freie Stirnfläche 23 des Führungskörpers 10 gespannt. Diese Kraftstoffeinspritzvorrichtung hat also nur eine Hochdruckdichtfläche im Bereich dieser Stirnfläche 23. Aus dem Pumpenarbeitsraum 13 wird der Kraftstoff über einen Kanal 24 zu dem Düsenelement 20 gefördert. Dieser Kraftstoffkanal 24 mündet in diese Stirnfläche 23 und setzt sich dann in einem Kanalabschnitt 25 im Düsenelement fort. Die Spritzlöcher 21 dieses Düsenelementes 20 sind in bekannter Weise durch eine Ventilnadel 26 steuerbar, die einen Bund 27 und daran anschließend einen Ansatz 28 kleineren Durchmessers aufweist.A nozzle element, generally designated 20, with spray holes 21 is clamped directly against the free end face 23 of the guide body 10 by means of the union nut 22. This fuel injection device therefore has only one high-pressure sealing surface in the region of this end face 23. The fuel is conveyed from the pump work chamber 13 via a channel 24 to the nozzle element 20. This fuel channel 24 opens into this end face 23 and then continues in a channel section 25 in the nozzle element. The spray holes 21 of this nozzle element 20 can be controlled in a known manner by means of a valve needle 26, which has a collar 27 and then an extension 28 of smaller diameter.

In den Führungskörpern 10 ist außerdem ein Aufnahmeraum 30 für ein Federelement 31 eingearbeitet, das über eine Stelze 32 mit einem konischen Flansch 33 und einem Schaft 34 auf den Ansatz 28 wirkt und damit die Ventilnadel auf ihren Ventilsitz drückt. Der Schaft 34 der Stelze 32 und der Ansatz 28 an der Ventilnadel 26 ragen dabei aus entgegengesetzten Richtungen in eine Bohrung 35 hinein, die von dem Aufnahmeraum 30 ausgeht und in die Stirnfläche 23 des Führungskörpers 10 mündet.In the guide bodies 10, a receiving space 30 for a spring element 31 is also incorporated, which acts on the extension 28 via a stilt 32 with a conical flange 33 and a shaft 34 and thus presses the valve needle onto its valve seat. The shaft 34 of the stilt 32 and the shoulder 28 on the valve needle 26 protrude from opposite directions into a bore 35 which starts from the receiving space 30 and opens into the end face 23 of the guide body 10.

Der Aufnahmeraum 30 ist als Quernut 40 ausgebildet die einseitig offen ist. Bei den in der Zeichnung dargestellten Ausführungsbeispielen ist diese Quernut 40 als durchgehender Schlitz senkrecht zu der den Kraftstoffkanal 24 und die Achse A des Führungskörpers 10 schneidenden Ebene in diesen Führungskörper 10 eingearbeitet. Das Federelement 31 wird quer zu seiner Wirkungsrichtung in diese Quernut 40 eingeschoben und in seine zentrale Position gebracht, in der es die Ventilnadel belastet.The receiving space 30 is designed as a transverse groove 40 which is open on one side. In the exemplary embodiments shown in the drawing, this transverse groove 40 is machined into this guide body 10 as a continuous slot perpendicular to the plane intersecting the fuel channel 24 and the axis A of the guide body 10. The spring element 31 is inserted transversely to its direction of action into this transverse groove 40 and brought into its central position in which it loads the valve needle.

Damit wird es möglich, gegenüber der bekannten Ausführung den Durchmesser D der Bohrung 35 zu verkleinern. Bei der Ausführung nach den Fig. 1 und 2 wird zunächst von der Stirnfläche 23 her in den Führungskörper 10 eine Bohrung eingearbeitet, deren Durchmesser D1 dem Durchmesser des Schaftes 34 der Stelze 32 angepaßt ist. Dann wird ein zur Stirnfläche auslaufender Abschnitt der Bohrung 35 erweitert, in den eine Führungsbuchse 42 für den Ansatz 28 an der Ventilnadel eingesetzt wird. Diese Führungsbuchse ist vorzugsweise gehärtet und dient zugleich als Anschlagfläche für den Bund 27 an der Ventilnadel 26. Der Durchmesser D der Bohrung in dieser Buchse 42 ist dem Durchmesser des Ansatzes 28 angepaßt.This makes it possible to reduce the diameter D of the bore 35 compared to the known design. In the embodiment according to FIGS. 1 and 2, a bore is first machined from the end face 23 into the guide body 10, the diameter D1 of which is adapted to the diameter of the shaft 34 of the stilt 32. Then a section of the bore 35 that runs out to the end face is expanded, into which a guide bush 42 for the attachment 28 on the valve needle is inserted. This guide bush is preferably hardened and also serves as a stop surface for the collar 27 on the valve needle 26. The diameter D of the bore in this bush 42 is adapted to the diameter of the extension 28.

Man erkennt aus Fig. 1, daß der Durchmesser D der Bohrung 35 an der Stirnfläche 23 des Führungskörpers kleiner ist als die Breite B des Aufnahmeraumes 30 für das Federelement 31. Die Breite B entspricht dabei etwa dem Durchmesser der einen Schraubendruckfeder, die bei der Ausführung nach den Fig. 1 und 2 als Federelement dient. In der Schnittebene nach Fig. 1, d.h. in der den Kraftstoffkanal 24 und die Bohrung 35 schneidenden Ebene ist also der Durchmesser D der Bohrung 35 kleiner als die Breite B des Aufnahmeraumes 30. Damit kann auch der Abstand E von der Achse A des Führungskörpers 10 bzw. der Bohrung 35, die üblicherweise zentral angeordnet ist, gegenüber der bekannten Ausführung verkleinert werden, ohne daß die Materialstärke des Wandabschnittes 43 zwischen diesem Kraftstoffkanal 24 und der Bohrung 35 unzulässig geschwächt würde. Der in die Stirnfläche 23 auslaufende Abschnitt des Kraftstoffkanals 24 ist schräg zur Achse A des Kolbens angeordnet, d.h. der Abstand dieses Kraftstoffkanals von dieser Achse ist im Bereich der Stirnfläche 23 des Führungskörper 10 kleiner als in Höhe des Aufnahmeraumes 30. Damit kann der Durchmesser an der Stirnfläche 23 und damit die einzige Hochdruckdichtfläche verkleinert werden, wenn man den Führungskörper 10 zur Stirnfläche 23 hin konisch verjüngt, wie das bei 44 angedeutet ist.From Fig. 1 it can be seen that the diameter D of the bore 35 on the end face 23 of the guide body is smaller than the width B of the receiving space 30 for the spring element 31. The width B corresponds approximately to the diameter of a helical compression spring, which in the execution 1 and 2 serves as a spring element. In the sectional plane of Fig. 1, i.e. in the plane intersecting the fuel channel 24 and the bore 35, the diameter D of the bore 35 is therefore smaller than the width B of the receiving space 30. This also allows the distance E from the axis A of the guide body 10 or the bore 35, which is usually central is arranged, can be reduced compared to the known embodiment without the material thickness of the wall portion 43 between this fuel channel 24 and the bore 35 would be weakened inadmissibly. The portion of the fuel channel 24 which runs into the end face 23 is arranged obliquely to the axis A of the piston, i.e. the distance of this fuel channel from this axis is smaller in the area of the end face 23 of the guide body 10 than at the level of the receiving space 30. Thus, the diameter at the end face 23 and thus the only high-pressure sealing surface can be reduced if the guide body 10 is conical towards the end face 23 tapered, as indicated at 44.

Die Zeichnungen zeigen, daß der Querschnitt der Quernut 40 im mittleren Bereich etwa dem Querschnitt des Federelementes entspricht und daß der Boden zum Düsenelement 20 hin sowie der Boden zum Kolben 12 hin im Querschnitt halbrund ausgebildet ist. In den Endbereichen verjüngt sich also die Quernut auch auf der dem Kraftstoffkanal 24 zugewandten Seite, so daß dieser näher an die Achse A herangerückt werden kann, ohne daß eine unzulässige Materialschwächung zwischen diesem Kraftstoffkanal 24 und den Endbereichen der Quernut 40 zu befürchten wäre. Natürlich sind auch andere Querschnittsformen in den Endbereichen der Quernut 40 denkbar, wobei noch darauf hingewiesen wird, daß dieser Endbereich so ausgestaltet wird, daß ohne zusätzlichen Raumbedarf der konische Flansch 33 an der Stelze 32 darin Platz findet. Der obere im Querschnitt halbrunde Endbereich der Quernut 40 wird durch einen Auflagebalken 50 ausgefüllt, an dem sich die Schraubendruckfeder einseitig abstützt. Bei dem Ausführungsbeispiel nach den Fig. 1 bis 4 stützt sich diese Schraubendruckfeder unmittelbar auf dem Flansch 33 der Stelze 32 ab.The drawings show that the cross section of the transverse groove 40 in the central region corresponds approximately to the cross section of the spring element and that the bottom towards the nozzle element 20 and the bottom towards the piston 12 are semicircular in cross section. In the end regions, the transverse groove thus also tapers on the side facing the fuel channel 24, so that the latter moves closer to the axis A. can be feared without an inadmissible weakening of material between this fuel channel 24 and the end regions of the transverse groove 40. Of course, other cross-sectional shapes are also conceivable in the end regions of the transverse groove 40, it being pointed out that this end region is designed in such a way that the conical flange 33 on the stilt 32 can be accommodated therein without requiring additional space. The upper end region of the transverse groove 40, which is semicircular in cross section, is filled by a support beam 50, on which the helical compression spring is supported on one side. In the embodiment according to FIGS. 1 to 4, this helical compression spring is supported directly on the flange 33 of the stilt 32.

Bei dem Ausführungsbeispiel nach den Fig. 5 und 6 sind als Federelement drei Schraubendruckfedern 51 vorgesehen, die über einen Auflagesteg 52 zentral auf die Stelze 32 wirken. Ein Vergleich der Zeichnungen zeigt, daß die Breite B des Aufnahmeraums 30 kleiner ist und damit wiederum insgesamt die Baugröße verringert oder die Vorrichtung auch bei einem höheren Einspritzdruck verwendet werden kann.In the exemplary embodiment according to FIGS. 5 and 6, three helical compression springs 51 are provided as spring elements, which act centrally on the stilt 32 via a support web 52. A comparison of the drawings shows that the width B of the receiving space 30 is smaller and in turn the overall size is reduced or the device can also be used at a higher injection pressure.

Der Auflagebalken 50 füllt den Endbereich der Quernut 40 aus. Wichtig ist insbesondere, daß die Quernut 40 und der Auflagebalken einander angepaßte Führungsflächen 71 bzw. 72 aufweisen, die ein seitliches Einschieben und Entlanggleiten des Auflagebalkens 50 an dieser Wand 70 ermöglichen.The support bar 50 fills the end region of the transverse groove 40. It is particularly important that the transverse groove 40 and the support beam have mutually matched guide surfaces 71 and 72, respectively, which allow the support beam 50 to be pushed in and sliding along this wall 70.

Anhand von Fig. 7 soll im folgenden der Montagevorgang näher beschrieben werden. Dazu wird der Schaft 34 der Stelze 32 in die Bohrung 35 derart eingesetzt, daß die Symmetrieachse der Stelze 32 schräg zur Längsrichtung A des Führungskörpers verläuft. Dies ist möglich, weil sich die Bohrung 35 zum Aufnahmeraum 30 des Federelements konisch erweitert. Auch die Längsachse der Druckfeder 31 ist zunächst im Winkel zur Längsrichtung A des Führungskörpers angeordnet. Bei dieser schrägen Anordnung von Stelze 32 und Druckfeder 31 kann der Auflagebalken 50 ohne Kraftaufwand in die in Fig. 7 dargestellte Lage eingesetzt werden, wobei sich der Schaft der Stelze 32 an einem Absatz 75 der Bohrung 35 am Übergang zwischen den Bohrungsabschnitten mit unterschiedlichem Durchmesser abstützt. Bei der Lage der Bauteile nach Fig. 7 ist also die Druckfeder 31 nicht gespannt. Wird nun auf die Druckfeder 31 und /oder den Auflagebalken 50 in Pfeilrichtung eine Kraft ausgeübt, wird die Druckfeder 31 geringfügig vorgespannt, während der Auflagebalken 50 an der Wand 70 am Führungskörper 10 entlanggleitet. Man wird dabei die Verhältnisse so aufeinander abstimmen, daß während dieses Montagevorganges die Feder nicht zu sehr vorgespannt wird, was den Montagevorgang erschweren würde. Andererseits sollte eine geringe Vorspannung in der Betriebsstellung der Feder gegeben sein, damit bei der weiteren Montage die Teile nicht unbeabsichtigt aus der Quernut herausfallen.The assembly process will be described in more detail below with reference to FIG. 7. For this purpose, the shaft 34 of the stilt 32 is inserted into the bore 35 in such a way that the axis of symmetry of the stilt 32 extends obliquely to the longitudinal direction A of the guide body. This is possible because the bore 35 widens conically to the receiving space 30 of the spring element. The longitudinal axis of the compression spring 31 is also initially arranged at an angle to the longitudinal direction A of the guide body. In this oblique arrangement of the stilt 32 and the compression spring 31, the support beam 50 can be inserted into the position shown in FIG. 7 without any effort, the shaft of the stilt 32 being supported on a shoulder 75 of the bore 35 at the transition between the bore sections of different diameters . 7, the compression spring 31 is not under tension. If a force is now exerted on the compression spring 31 and / or the support bar 50 in the direction of the arrow, the compression spring 31 is slightly pretensioned while the support bar 50 slides along the wall 70 on the guide body 10. You will coordinate the conditions so that the spring is not biased too much during this assembly process, which would complicate the assembly process. On the other hand, there should be a slight preload in the operating position of the spring so that the parts do not accidentally fall out of the transverse groove during further assembly.

Nach dem Einsetzen der Stelze, der Feder und des Auflagebalkens wird das Düsenelement 20 angesetzt und mittels der Überwurfmutter 22 an dem Führungskörper 10 festgeschraubt. Bei diesem Montagevorgang wird die Druckfeder 31 durch den immer weiter in die Bohrung 35 eintauchenden Ansatz 28 der Ventilnadel 26 weiter vorgespannt. Der richtige Ventilöffnungsdruck soll dabei dann gegeben sein, wenn das Düsenelement 20 an der freien Stirnfläche 23 des Führungskörpers anliegt. Dazu hat man vorher durch Versuche bestimmt, wieviel Scheiben 60 auf den Flansch der Stelze 32 aufgelegt werden müssen. Ein nachträgliches Einstellen des Ventilöffnungsdruckes ist nicht notwendig und auch nicht möglich, weil die Überwurfmutter zugleich auch die Quernut 40 seitlich abdeckt und damit die Lage des Auflagebalkens 50 sichert, wie dies die Zeichnungen zeigen.After inserting the stilts, the spring and the support bar, the nozzle element 20 is attached and screwed onto the guide body 10 by means of the union nut 22. During this assembly process, the compression spring 31 is further pretensioned by the extension 28 of the valve needle 26, which dips further and further into the bore 35. The correct valve opening pressure should be given when the nozzle element 20 bears against the free end face 23 of the guide body. For this purpose, it was determined beforehand by experiments how many disks 60 must be placed on the flange of the stilt 32. A subsequent adjustment of the valve opening pressure is not necessary and also not possible because the union nut also covers the transverse groove 40 laterally and thus secures the position of the support beam 50, as shown in the drawings.

In diesem Zusammenhang wird darauf hingewiesen, daß das Gewinde 80 zwischen Führungskörper 10 und Überwurfmutter im Bereich der Quernut 40 vorgesehen ist. Dies ermöglicht einen kompakten Aufbau in Längsrichtung der Pumpe.In this context, it is pointed out that the thread 80 is provided between the guide body 10 and the union nut in the area of the transverse groove 40. This enables a compact construction in the longitudinal direction of the pump.

Schließlich wird noch darauf hingewiesen, daß in Fig. 7 als zusätzliches Merkmal angedeutet ist, daß ein im Führungskörper 10 verankerter Haltestift 90 in eine Nut 91 im Auflagebalken 50 eingreifen kann und somit eine Verschwenkbewegung des Auflagebalkens 50 um eine Achse in Längsrichtung der Quernut verhindert. Dieses Merkmale ist nur von Bedeutung, wenn der Querschnitt des Auflagebalkens 50 halbrund ausgebildet ist. Bei einem trapezartigen Querschnitt ist auch ohne diesen Haltestift eine Verschwenkung des Auflagebalkens 50 nicht möglich.Finally, it is pointed out that in Fig. 7 is indicated as an additional feature that an anchored in the guide body 10 retaining pin 90 can engage in a groove 91 in the support beam 50 and thus prevents pivoting movement of the support beam 50 about an axis in the longitudinal direction of the transverse groove. This feature is only important if the cross section of the support beam 50 is semicircular. With a trapezoidal cross section, pivoting of the support beam 50 is not possible even without this retaining pin.

Durch eine zentrische Bohrung 95 in dem Auflagebalken 50 ist eine Verbindung zwischen dem Aufnahmeraum und einem Entlüftungskanal 61 gegeben, der in den Ringraum mündet.A central bore 95 in the support beam 50 provides a connection between the receiving space and a ventilation channel 61 which opens into the annular space.

Claims (7)

1. A fuel injection device with an injection pump, the piston (12) of which is movably mounted in a bore (11) of a guide member (10), and with a nozzle element (20) clamped directly against the end face (23) of the guide member (10) and having a valve needle (26) which controls the injection aperture (21) of the nozzle element (20) and penetrates into a bore (35) opening from the end face (23) of the guide member (10) and fitted by the valve needle (26), and leading to a receiving chamber (30) which is worked into the guide member (10) and in which there is arranged a spring element (31) urging the valve needle (26) onto its valve seating, wherein a fuel duct (24) connected to the pump working chamber (13) runs by the side of this receiving chamber (30) in the guide member (10), the fuel duct (24) opening into the end face (23) of the guide member and there communicating with a duct of the nozzle element (20) leading to the nozzle, characterised by the following features:
a) the receiving chamber (30) for the spring element (31) is constructed as a transverse groove (40) which is open at least on one side and issues into the generated surface of the guide member (10), the cross-sectional area of the transverse groove (40) corresponding roughly to the cross-sectional area of the spring element (31).
b) the diameter (D) of the bore (35) at the end face (23) of the guide member (10) is smaller than the width (B) of the receiving chamber (30),
c) the spring element (31) is supported, at its end remote from the nozzle element (20), on a support bar (50) which is movably mounted on the end face (70) of the transverse groove (40) in the longitudinal direction of the transverse groove and brings the spring element (31) from an unloaded rest position into its operating position loading the needle valve (26) by being pushed in the transverse groove (40),
d) a shoe (32) provided with a supporting flange (33) for the spring element (31) is arranged between the needle valve (26) and the spring element (31),
e) the bore (35) widens conically toward the receiving chamber (30) in the longitudinal direction of the transverse groove (40).
2. A fuel injection device according to Claim 1, characterised in that the distance (E) between the fuel duct (24) and the axis (A) of the bore (35) at the end face (23) of the guide member (10) is smaller than the height of the receiving chamber (30) for the spring element (31) and in that the diameter of the guide member (10) tapers inwardly toward the end face (23).
3. A fuel injection device according to one of the preceding claims, characterised in that the cross-section of the transverse groove (40) tapers inwardly in the end region toward the nozzle element (20), at least on the side facing the fuel duct (24).
4. A fuel injection device according to Claim 3, characterised in that the base of the transverse groove is semicircular in cross-section.
5. A fuel injection device according to at least one of the preceding claims, characterised in that a helical compression spring serves as spring element (31).
6. A fuel injection device according to at least one of Claims 1 to 5, characterised in that a plurality of helical compression springs (51) which are inserted into the transverse groove (40) and act centrally upon the shoe (32) via a support web (52) serve as spring element (31).
7. A fuel injection device according to Claim 6, characterised in that pivoting movement of the support bar (50) about an axis in the longitudinal direction of the transverse groove (40) is prevented by a retaining pin (90) which is secured on the guide member (10) and engages in a groove (91) in the support bar (50).
EP84110009A 1983-08-31 1984-08-22 Fuel injection device Expired EP0141111B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84110009T ATE44584T1 (en) 1983-08-31 1984-08-22 FUEL INJECTOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3331336 1983-08-31
DE19833331336 DE3331336A1 (en) 1983-08-31 1983-08-31 FUEL INJECTION DEVICE

Publications (3)

Publication Number Publication Date
EP0141111A2 EP0141111A2 (en) 1985-05-15
EP0141111A3 EP0141111A3 (en) 1987-05-27
EP0141111B1 true EP0141111B1 (en) 1989-07-12

Family

ID=6207855

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84110009A Expired EP0141111B1 (en) 1983-08-31 1984-08-22 Fuel injection device

Country Status (5)

Country Link
US (1) US4650116A (en)
EP (1) EP0141111B1 (en)
JP (1) JPS6073045A (en)
AT (1) ATE44584T1 (en)
DE (1) DE3331336A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19721241C1 (en) * 1997-05-21 1998-11-05 Hatz Motoren Pump nozzle

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2378165A (en) * 1942-02-07 1945-06-12 Sulzer Ag Fuel injection device
US2507355A (en) * 1946-01-17 1950-05-09 Sola Giuseppe Filter for injectors for combustion engines
US2591401A (en) * 1947-03-08 1952-04-01 Atlas Diesel Ab Fuel injection device
DE1638929U (en) * 1951-10-12 1952-05-29 Friedrich Wilhelm Dipl Deckel INJECTION NOZZLE FOR COMBUSTION MACHINES.
US3075707A (en) * 1961-10-12 1963-01-29 Gen Motors Corp Fuel injector pump with hydraulically controlled injection valve
DE1805024C2 (en) * 1968-10-25 1983-06-01 L'Orange GmbH, 7000 Stuttgart A fuel injection device for internal combustion engines consisting of an assembly consisting of an injection pump and an injection valve
DE2028453A1 (en) * 1970-06-10 1971-12-16 Robert Bosch Gmbh, 7000 Stuttgart Fuel injector
US3777984A (en) * 1972-01-20 1973-12-11 Mack Trucks Miniature fuel injection nozzle and holder assembly
US3952711A (en) * 1975-03-04 1976-04-27 Ambac Industries, Inc. Diesel injection nozzle with independent opening and closing control
WO1980002180A1 (en) * 1979-04-09 1980-10-16 Caterpillar Tractor Co Safety check valve for unit fuel pump-injector
JPS55137346A (en) * 1979-04-11 1980-10-27 Toyota Motor Corp Variable choke carburetter
DE2932480A1 (en) * 1979-08-10 1981-02-26 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES
DE3105671A1 (en) * 1981-02-17 1982-09-02 Robert Bosch Gmbh, 7000 Stuttgart "FUEL INJECTION NOZZLE"
US4527738A (en) * 1982-06-18 1985-07-09 Caterpillar Tractor Co. Modular unit fluid pump-injector

Also Published As

Publication number Publication date
EP0141111A2 (en) 1985-05-15
ATE44584T1 (en) 1989-07-15
DE3331336A1 (en) 1985-03-14
DE3331336C2 (en) 1991-02-14
JPH0522068B2 (en) 1993-03-26
US4650116A (en) 1987-03-17
EP0141111A3 (en) 1987-05-27
JPS6073045A (en) 1985-04-25

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