EP1446575B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1446575B1
EP1446575B1 EP02758100A EP02758100A EP1446575B1 EP 1446575 B1 EP1446575 B1 EP 1446575B1 EP 02758100 A EP02758100 A EP 02758100A EP 02758100 A EP02758100 A EP 02758100A EP 1446575 B1 EP1446575 B1 EP 1446575B1
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EP
European Patent Office
Prior art keywords
screw sleeve
outer contour
fuel injection
screw
valve
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
EP02758100A
Other languages
German (de)
French (fr)
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EP1446575A1 (en
Inventor
Sieghart Maier
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1446575A1 publication Critical patent/EP1446575A1/en
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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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B13/00—Spanners; Wrenches
    • B25B13/02—Spanners; Wrenches with rigid jaws
    • B25B13/06—Spanners; Wrenches with rigid jaws of socket type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B13/00—Spanners; Wrenches
    • B25B13/02—Spanners; Wrenches with rigid jaws
    • B25B13/06—Spanners; Wrenches with rigid jaws of socket type
    • B25B13/065—Spanners; Wrenches with rigid jaws of socket type characterised by the cross-section of the socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B13/00—Spanners; Wrenches
    • B25B13/48—Spanners; Wrenches for special purposes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B13/00—Spanners; Wrenches
    • B25B13/48—Spanners; Wrenches for special purposes
    • B25B13/481—Spanners; Wrenches for special purposes for operating in areas having limited access
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8076—Fuel injection apparatus manufacture, repair or assembly involving threaded members
    • 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

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve is for example from the document DE 199 41 930 A1 known.
  • Such a fuel injection valve has a housing which comprises a first and a second body, wherein the first body is designed as a valve holding body and the second body as a valve body. Both bodies have a contact surface, with which they bear against each other directly or with the interposition of an intermediate disc.
  • a threaded sleeve is provided which surrounds the valve body and the valve holding body and possibly also the intermediate disc in the region of the contact surfaces.
  • the screw sleeve has an internal thread with which it engages in an external thread formed on the valve holding body.
  • a pressure surface is formed on the screw, with which this rests against a contact surface of the second body, so the valve body.
  • the screw is formed substantially cylindrical and generates by screwing into the external thread of the valve holding body an axial force, with the valve holding body is pressed against the valve body.
  • a hexagon is ground to the threaded sleeve at its end facing the combustion chamber, so that the rotary tool, such as a wrench, can engage the surfaces of this hexagon to exert a corresponding torque on the screw.
  • the torque is introduced only via individual introduction lines, each with different torques. At higher torques may result in a considerable torsion of the screw and as a result occur fluctuations in the torque on the thread and thus fluctuations in the axial force with which the first body is pressed against the second body.
  • high-pressure fuel is passed through a passage penetrating the contact surfaces, as a result, leaks may occur at the contact surfaces.
  • the DE 42 14 646 A1 shows an injection valve with a nozzle body which is clamped by a clamping nut against a holding body.
  • the clamping nut has on its outer side a contour to which a corresponding tool for tightening the clamping nut can attack.
  • DE 100 17 112 and the DE 100 17 113 show each clamping nuts in a similar arrangement as the DE 42 14 646 A1 in which the outer contour is formed in each case only in a partial section of the clamping nut.
  • the fuel injection valve according to the invention with the characterizing features of claim 1, in contrast, has the advantage that the torque is introduced almost uniformly and independently of friction factors and dimensions in the threaded sleeve.
  • the torque is introduced over a large part of the outer circumferential surface of the threaded sleeve by the rotary tool.
  • the screw can not twist when screwed, and the axial forces are evenly distributed over the circumference.
  • On the contact surfaces of the two bodies acts a uniform surface pressure, so that the tightness is improved at the contact surfaces.
  • the outer circumferential surface of the screw sleeve has a major part of its length on an outer contour into which the corresponding screwing tool can engage. This can be done by the screwing a tangential force are exerted, with which the threaded sleeve can be screwed onto the external thread of the first body.
  • the outer contour of the screw extends both over the portion of the screw, which is located above the first body, as well as over the portion which is located above the second body.
  • the outer contour is formed by mutually parallel longitudinal grooves, which extend substantially parallel to the longitudinal axis of the threaded sleeve.
  • Such grooves can be easily and inexpensively bring into the outer circumferential surface in the screw and also can be appropriate tools that engage in such grooves, easily finished.
  • the outer contour is formed on the outer circumferential surface of the screw by flat contours.
  • FIG. 1 is a longitudinal section through an inventive fuel injection valve shown.
  • the fuel injection valve has a housing 1, which comprises a first body 3 and a second body 7, wherein between the two bodies 3, 7, an intermediate disc 5 is arranged.
  • the first body is formed as a valve holding body 3 and the second body as a valve body 7.
  • the valve holding body 3 rests with a contact surface 103 on the washer 5 and the valve body 7 with a contact surface 107 on the opposite side of the washer 5.
  • a Bore 12 is formed, which is designed as a blind bore and the combustion chamber side end is formed by a substantially conical valve seat 20.
  • a plurality of injection openings 24 are formed in the valve body 7, which establish the connection to the combustion chamber of the internal combustion engine.
  • a piston-shaped valve needle 14 is arranged, which is sealingly guided in a bore away from combustion chamber in the bore 12.
  • the valve needle 14 tapers to the combustion chamber to form a pressure shoulder 15 and merges at its combustion chamber end in a valve sealing surface 22 which cooperates with the valve seat 20.
  • a pressure chamber 17 is formed at the level of the pressure shoulder 15, which is connected via a valve needle 14 surrounding annular channel 19 with the valve seat 20.
  • the pressure chamber 17 is filled with fuel under high pressure via a not running in the sectional plane of the high-pressure passage 21 which extends in the valve body 7 through the washer 5 and the valve holding body 3 to a high-pressure fuel port of the fuel.
  • the intermediate disc 5 has a central opening 23, in which a pressure piece 25 is arranged, which bears against the valve needle 14 and the valve needle 14 faces away into a spring plate 27 passes.
  • the spring plate 27 in this case projects into a valve holder body 3 formed in the spring chamber 29, which is designed as a bore and extends coaxially to the bore 12.
  • a closing spring 30 is arranged under pressure bias, the combustion chamber facing away from the spring plate 27 and away from the combustion chamber is supported on a stationary surface of the valve holding body 3.
  • the pressure bias of the closing spring 30 results in an axial force on the valve needle 14, which presses the valve sealing surface 22 against the valve seat 20.
  • the pressure in the pressure chamber 17 results in a hydraulic force on the pressure shoulder 15 and on parts of the valve sealing surface 22.
  • valve needle 14 moves in the axial direction and lifts with the valve sealing surface 22 from the valve seat 20, so that fuel from the pressure chamber 17 via the annular channel 19 to the injection ports 24 can flow. In reverse force relationships, the valve needle 14 is held in contact with the valve seat 20, and there is no fuel leak from the injection ports 24.
  • a screw 10 is arranged on the housing.
  • the screw 10 is designed substantially hollow cylindrical and has a longitudinal axis 37. At its end remote from the combustion chamber, an internal thread 42 is formed, with which it is screwed into a male thread 8 formed on the valve holding body 3.
  • the threaded sleeve 10 At its end facing the combustion chamber, has an inwardly projecting collar 110, on which an annular pressure surface 32 is formed, which rests against a likewise annular contact surface 34 on the valve body 7.
  • FIG. 2 shows a cross section through the fuel injection valve of FIG. 1 along the line II-II.
  • a knurling 36 is formed in the outer region, which forms the outer contour of the screw 10.
  • the knurling 36 here consists of mutually parallel longitudinal grooves 38 which have a triangular cross section and directly adjacent to each other.
  • the depth of the longitudinal grooves 38 is only a fraction of the shell thickness of the screw 10, so that no significant weakening of the screw 10 occurs.
  • the longitudinal grooves 38 are in this case formed parallel to the longitudinal axis 37 of the threaded sleeve 10.
  • FIG. 3 a further embodiment of the screw sleeve 10 according to the invention is shown.
  • the screw 10 is shown here cut in the lower, ie in the combustion chamber facing area.
  • the outer contour of the screw 10 is formed here by flat polished sections 40, of which six flat sections 40 are distributed uniformly over the circumference of the threaded sleeve 10, so that in cross section results in an outer shape that corresponds to an equilateral, regular hexagon.
  • longitudinal grooves 38 Both in the formation of longitudinal grooves 38 as well as surface grinding 40 is always provided that they extend at least over much of the length of the threaded sleeve 10. It is particularly advantageous if the longitudinal grooves 38 or the flat contours 40 extend at least approximately over the entire length of the threaded sleeve 10 so that the torque can also be introduced correspondingly over the entire length of the threaded sleeve 10.
  • more than six flat poles 40 are distributed over the circumference of the threaded sleeve 10, for example, eight, ten or twelve flat poles. These are preferably evenly distributed over the circumference of the threaded sleeve 10, so that there is a regular polygon in cross-section on the outline.
  • an outer contour is applied, are arranged distributed in the various recesses over a majority of the length of the screw 10 and over its entire circumference.
  • the depressions may in this case be formed as bores, as grooves or other pocket-like depressions.
  • FIG. 4 a suitable screwing tool is shown in its essential parts.
  • the screwing tool has two clamping jaws 45, each corresponding substantially to half a hollow cylinder.
  • the inside of the clamping jaws 45 has a knurling 47, which is such that it can engage in the knurling 36 of the threaded sleeve 10.
  • the two clamping jaws 45 are in this case pressed together by a device not shown in the drawing in the indicated arrow direction, so that the knurling 47 of the clamping jaws 45 can not slip on the knurling 38 of the screw 10.
  • the knurling 47 of the clamping jaws 45 must be adapted accordingly, so that secure toothing between the screwing tool and the clamping sleeve 10 also takes place in this case.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Ein derartiges Kraftstoffeinspritzventil ist beispielsweise aus der Schrift DE 199 41 930 A1 bekannt. Ein solches Kraftstoffeinspritzventil weist ein Gehäuse auf, das einen ersten und einen zweiten Körper umfasst, wobei der erste Körper als Ventilhaltekörper und der zweite Körper als Ventilkörper ausgebildet ist. Beide Körper weisen eine Anlagefläche auf, mit der sie direkt oder unter Zwischenlage einer Zwischenscheibe aneinander anliegen. Um den Ventilhaltekörper gegen den Ventilkörper zu verspannen, ist eine Schraubhülse vorgesehen, die den Ventilkörper und den Ventilhaltekörper und auch gegebenenfalls die Zwischenscheibe im Bereich der Anlageflächen umgibt. Die Schraubhülse weist ein Innengewinde auf, mit der sie in ein am Ventilhaltekörper ausgebildetes Außengewinde eingreift. Darüber hinaus ist an der Schraubhülse eine Druckfläche ausgebildet, mit der diese an einer Anlagefläche des zweiten Körpers, also des Ventilkörpers, anliegt. Die Schraubhülse ist im wesentlichen zylinderförmig ausgebildet und erzeugt durch das Eindrehen in das Außengewinde des Ventilhaltekörpers eine Axialkraft, mit der der Ventilhaltekörper gegen den Ventilkörper gepresst wird.The invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1. Such a fuel injection valve is for example from the document DE 199 41 930 A1 known. Such a fuel injection valve has a housing which comprises a first and a second body, wherein the first body is designed as a valve holding body and the second body as a valve body. Both bodies have a contact surface, with which they bear against each other directly or with the interposition of an intermediate disc. In order to clamp the valve holding body against the valve body, a threaded sleeve is provided which surrounds the valve body and the valve holding body and possibly also the intermediate disc in the region of the contact surfaces. The screw sleeve has an internal thread with which it engages in an external thread formed on the valve holding body. In addition, a pressure surface is formed on the screw, with which this rests against a contact surface of the second body, so the valve body. The screw is formed substantially cylindrical and generates by screwing into the external thread of the valve holding body an axial force, with the valve holding body is pressed against the valve body.

Zur Einleitung eines Drehmoments in die Schraubhülse ist an der Schraubhülse an ihrem dem Brennraum zugewandten Ende ein Sechskant angeschliffen, so dass das Drehwerkzeug, beispielsweise ein Gabelschlüssel, an den Flächen dieses Sechskant angreifen kann, um ein entsprechendes Drehmoment auf die Schraubhülse auszuüben. Dabei wird das Drehmoment jedoch nur über einzelne Einleitungslinien mit jeweils unterschiedlichen Drehmomenten eingeleitet. Bei höheren Drehmomenten ergibt sich unter Umständen eine erhebliche Torsion der Schraubhülse und als Folge treten Schwankungen im Drehmoment am Gewinde und somit auch Schwankungen der Axialkraft auf, mit der der erste Körper gegen den zweiten Körper gepresst wird. Da bei vielen Kraftstoffeinspritzventilen Kraftstoffhochdruck durch einen die Anlageflächen durchdringenden Kanal hindurch geleitet wird, kann es infolgedessen zu Undichtigkeiten an den Anlageflächen kommen.To initiate a torque in the threaded sleeve a hexagon is ground to the threaded sleeve at its end facing the combustion chamber, so that the rotary tool, such as a wrench, can engage the surfaces of this hexagon to exert a corresponding torque on the screw. However, the torque is introduced only via individual introduction lines, each with different torques. At higher torques may result in a considerable torsion of the screw and as a result occur fluctuations in the torque on the thread and thus fluctuations in the axial force with which the first body is pressed against the second body. As in many fuel injection valves, high-pressure fuel is passed through a passage penetrating the contact surfaces, as a result, leaks may occur at the contact surfaces.

Die DE 42 14 646 A1 zeigt ein Einspritzventil mit einem Düsenkörper, der mittels einer Spannmutter gegen einen Haltekörper verspannt ist. Die Spannmutter weist an ihrer Außenseite eine Kontur auf, an die ein entsprechendes Werkzeug zum Anziehen der Spannmutter angreifen kann.The DE 42 14 646 A1 shows an injection valve with a nozzle body which is clamped by a clamping nut against a holding body. The clamping nut has on its outer side a contour to which a corresponding tool for tightening the clamping nut can attack.

Die DE 42 18 943 A1 , DE 199 13 679 A1 , DE 44 32 686 A1 , DE 100 17 112 und die DE 100 17 113 zeigen jeweils Spannmuttern in ähnlicher Anordnung wie die DE 42 14 646 A1 , bei denen die Außenkontur jeweils nur in einem Teilabschnitt der Spannmutter ausgebildet ist.The DE 42 18 943 A1 . DE 199 13 679 A1 . DE 44 32 686 A1 . DE 100 17 112 and the DE 100 17 113 show each clamping nuts in a similar arrangement as the DE 42 14 646 A1 in which the outer contour is formed in each case only in a partial section of the clamping nut.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass das Drehmoment nahezu gleichmäßig und unabhängig von Reibungsfaktoren und Abmessungen in die Schraubhülse eingebracht wird. Hierzu wird das Drehmoment über einen Großteil der Außenmantelfläche der Schraubhülse vom Drehwerkzeug eingeleitet. Die Schraubhülse kann sich beim Einschrauben nicht verdrehen, und die Axialkräfte sind gleichmäßig über den Umfang verteilt. Auf die Anlageflächen der beiden Körper wirkt eine gleichmäßige Flächenpressung, so dass die Dichtheit an den Anlageflächen verbessert wird. Die Außenmantelfläche der Schraubhülse weist auf einem Großteil ihrer Länge eine Außenkontur auf, in die das entsprechende Schraubwerkzeug eingreifen kann. Dadurch kann durch das Schraubwerkzeug eine tangentiale Kraft ausgeübt werden, mit der die Schraubhülse auf das Außengewinde des ersten Körpers geschraubt werden kann.The fuel injection valve according to the invention with the characterizing features of claim 1, in contrast, has the advantage that the torque is introduced almost uniformly and independently of friction factors and dimensions in the threaded sleeve. For this purpose, the torque is introduced over a large part of the outer circumferential surface of the threaded sleeve by the rotary tool. The screw can not twist when screwed, and the axial forces are evenly distributed over the circumference. On the contact surfaces of the two bodies acts a uniform surface pressure, so that the tightness is improved at the contact surfaces. The outer circumferential surface of the screw sleeve has a major part of its length on an outer contour into which the corresponding screwing tool can engage. This can be done by the screwing a tangential force are exerted, with which the threaded sleeve can be screwed onto the external thread of the first body.

In einer vorteilhaften Ausgestaltung des Gegenstandes der Erfindung erstreckt sich die Außenkontur der Schraubhülse sowohl über den Abschnitt der Schraubhülse, der sich über dem ersten Körper befindet, als auch über den Abschnitt, der sich über dem zweiten Körper befindet. Dadurch lässt sich das Drehmoment auf die Schraubhülse aufbringen, ohne dass ein Verdrehen der Schraubhülse zwischen dem ersten und dem zweiten Körper auftritt.In an advantageous embodiment of the subject of the invention, the outer contour of the screw extends both over the portion of the screw, which is located above the first body, as well as over the portion which is located above the second body. As a result, the torque can be applied to the threaded sleeve, without any rotation of the threaded sleeve occurring between the first and the second body.

In einer weiteren vorteilhaften Ausgestaltung wird die Außenkontur durch zueinander parallele Längsnuten gebildet, die im wesentlichen parallel zur Längsachse der Schraubhülse verlaufen. Derartige Nuten lassen sich einfach und kostengünstig in die Außenmantelfläche in der Schraubhülse einbringen und ebenso lassen sich entsprechende Werkzeuge, die in solche Nuten eingreifen, leicht fertigen. Besonders vorteilhaft ist hierbei, die Außenkontur in Form einer Rändelung auszubilden und hier insbesondere, die Rändelung aus parallelen Längsnuten zu fertigen, die einen dreieckförmigen Querschnitt aufweisen und direkt aneinander angrenzen. Es sind so sehr viele Flächen ausgebildet, an denen das entsprechende Schraubwerkzeug angreifen kann, um das Drehmoment möglichst gleichmäßig auf dem gesamten Umfang der Schraubhülse einzubringen.In a further advantageous embodiment, the outer contour is formed by mutually parallel longitudinal grooves, which extend substantially parallel to the longitudinal axis of the threaded sleeve. Such grooves can be easily and inexpensively bring into the outer circumferential surface in the screw and also can be appropriate tools that engage in such grooves, easily finished. It is particularly advantageous in this case to form the outer contour in the form of a knurling and, in particular, to manufacture the knurling from parallel longitudinal grooves which have a triangular cross section and adjoin one another directly. There are so many surfaces formed on which the corresponding screwing can attack to bring the torque as evenly as possible over the entire circumference of the screw.

In einer weiteren vorteilhaften Ausgestaltung ist die Außenkontur an der Außenmantelfläche der Schraubhülse durch flächige Anschliffe ausgebildet. Hierbei ist insbesondere vorteilhaft, sechs flächige Anschliffe so auszubilden, dass sich im Querschnitt der Schraubhülse ein regelmäßiges Sechseck an der Außenlinie ergibt. Ebenso vorteilhaft ist es, mehr als sechs flächige Anschliffe an der Außenmantelfläche der Schraubhülse auszubilden, die ebenfalls gleichmäßig über den Umfang verteilt angeordnet sind.In a further advantageous embodiment, the outer contour is formed on the outer circumferential surface of the screw by flat contours. In this case, it is particularly advantageous to design six flat poles in such a way that the cross-section of the screw sleeve results in a regular hexagon on the outer line. It is equally advantageous to have more than six flat poles on the outer circumferential surface form the screw, which are also distributed uniformly over the circumference.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung und der Zeichnung entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention can be taken from the description and the drawing.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt

  • Figur 1 einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil,
  • Figur 2 einen Querschnitt durch Figur 1 entlang der Linie II-II,
  • Figur 3 eine teilweise geschnittene Darstellung einer weiteren erfindungsgemäßen Schraubhülse und
  • Figur 4 eine perspektivische Ansicht eines Schraubwerkzeugs zur Verschraubung einer erfindungsgemäßen Schraubhülse.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
  • FIG. 1 a longitudinal section through a fuel injection valve according to the invention,
  • FIG. 2 a cross section through FIG. 1 along the line II-II,
  • FIG. 3 a partially sectioned view of another screw according to the invention and
  • FIG. 4 a perspective view of a screwing tool for screwing a screw according to the invention.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil dargestellt. Das Kraftstoffeinspritzventil weist ein Gehäuse 1 auf, das einen ersten Körper 3 und einen zweiten Körper 7 umfasst, wobei zwischen den beiden Körpern 3, 7 eine Zwischenscheibe 5 angeordnet ist. Der erste Körper ist als Ventilhaltekörper 3 ausgebildet und der zweite Körper als Ventilkörper 7. Der Ventilhaltekörper 3 liegt mit einer Anlagefläche 103 an der Zwischenscheibe 5 an und der Ventilkörper 7 mit einer Anlagefläche 107 an der gegenüberliegenden Seite der Zwischenscheibe 5. Im Ventilkörper 7 ist eine Bohrung 12 ausgebildet, die als Sackbohrung ausgeführt ist und deren brennraumseitiges Ende durch einen im wesentlichen konischen Ventilsitz 20 gebildet wird.In FIG. 1 is a longitudinal section through an inventive fuel injection valve shown. The fuel injection valve has a housing 1, which comprises a first body 3 and a second body 7, wherein between the two bodies 3, 7, an intermediate disc 5 is arranged. The first body is formed as a valve holding body 3 and the second body as a valve body 7. The valve holding body 3 rests with a contact surface 103 on the washer 5 and the valve body 7 with a contact surface 107 on the opposite side of the washer 5. In the valve body 7 is a Bore 12 is formed, which is designed as a blind bore and the combustion chamber side end is formed by a substantially conical valve seat 20.

Brennraumzugewandt vom Ventilsitz 20 sind im Ventilkörper 7 mehrere Einspritzöffnungen 24 ausgebildet, die die Verbindung zum Brennraum der Brennkraftmaschine herstellen. In der Bohrung 12 ist eine kolbenförmige Ventilnadel 14 angeordnet, die in einem brennraumabgewandten Abschnitt in der Bohrung 12 dichtend geführt ist. Die Ventilnadel 14 verjüngt sich dem Brennraum zu unter Bildung einer Druckschulter 15 und geht an ihrem brennraumseitigen Ende in eine Ventildichtfläche 22 über, die mit dem Ventilsitz 20 zusammenwirkt. Durch eine radiale Erweiterung der Bohrung 12 ist auf Höhe der Druckschulter 15 ein Druckraum 17 gebildet, der über einen die Ventilnadel 14 umgebend Ringkanal 19 mit dem Ventilsitz 20 verbunden ist. Der Druckraum 17 ist über einen nicht in der Schnittebene verlaufenden Hochdruckkanal 21, der im Ventilkörper 7, durch die Zwischenscheibe 5 und den Ventilhaltekörper 3 bis zu einem Kraftstoffhochdruckanschluss des Kraftstoff einspritzventils verläuft, mit Kraftstoff unter hohem Druck befüllbar.Combustion chamber facing from the valve seat 20 a plurality of injection openings 24 are formed in the valve body 7, which establish the connection to the combustion chamber of the internal combustion engine. In the bore 12, a piston-shaped valve needle 14 is arranged, which is sealingly guided in a bore away from combustion chamber in the bore 12. The valve needle 14 tapers to the combustion chamber to form a pressure shoulder 15 and merges at its combustion chamber end in a valve sealing surface 22 which cooperates with the valve seat 20. By a radial extension of the bore 12, a pressure chamber 17 is formed at the level of the pressure shoulder 15, which is connected via a valve needle 14 surrounding annular channel 19 with the valve seat 20. The pressure chamber 17 is filled with fuel under high pressure via a not running in the sectional plane of the high-pressure passage 21 which extends in the valve body 7 through the washer 5 and the valve holding body 3 to a high-pressure fuel port of the fuel.

Die Zwischenscheibe 5 weist eine zentrale Öffnung 23 auf, in der ein Druckstück 25 angeordnet ist, das an der Ventilnadel 14 anliegt und der Ventilnadel 14 abgewandt in einen Federteller 27 übergeht. Der Federteller 27 ragt hierbei bis in einen im Ventilhaltekörper 3 ausgebildeten Federraum 29, der als Bohrung ausgeführt ist und koaxial zur Bohrung 12 verläuft. Im Federraum 29 ist eine Schließfeder 30 unter Druckvorspannung angeordnet, die sich brennraumzugewandt am Federteller 27 und brennraumabgewandt an einer ortsfesten Fläche des Ventilhaltekörpers 3 abstützt. Durch die Druckvorspannung der Schließfeder 30 ergibt sich eine axiale Kraft auf die Ventilnadel 14, die die Ventildichtfläche 22 gegen den Ventilsitz 20 drückt. Durch den Druck im Druckraum 17 ergibt sich eine hydraulische Kraft auf die Druckschulter 15 und auf Teile der Ventildichtfläche 22. Übersteigen diese hydraulischen Kräfte die Kraft der Schließfeder 30, so bewegt sich die Ventilnadel 14 in axialer Richtung und hebt mit der Ventildichtfläche 22 vom Ventilsitz 20 ab, so dass Kraftstoff aus dem Druckraum 17 über den Ringkanal 19 zu den Einspritzöffnungen 24 strömen kann. Bei umgekehrten Kraftverhältnissen wird die Ventilnadel 14 in Anlage am Ventilsitz 20 gehalten, und es kann kein Kraftstoff aus den Einspritzöffnungen 24 austreten.The intermediate disc 5 has a central opening 23, in which a pressure piece 25 is arranged, which bears against the valve needle 14 and the valve needle 14 faces away into a spring plate 27 passes. The spring plate 27 in this case projects into a valve holder body 3 formed in the spring chamber 29, which is designed as a bore and extends coaxially to the bore 12. In the spring chamber 29, a closing spring 30 is arranged under pressure bias, the combustion chamber facing away from the spring plate 27 and away from the combustion chamber is supported on a stationary surface of the valve holding body 3. The pressure bias of the closing spring 30 results in an axial force on the valve needle 14, which presses the valve sealing surface 22 against the valve seat 20. The pressure in the pressure chamber 17 results in a hydraulic force on the pressure shoulder 15 and on parts of the valve sealing surface 22. If these hydraulic forces exceed the force of the closing spring 30, then the valve needle 14 moves in the axial direction and lifts with the valve sealing surface 22 from the valve seat 20, so that fuel from the pressure chamber 17 via the annular channel 19 to the injection ports 24 can flow. In reverse force relationships, the valve needle 14 is held in contact with the valve seat 20, and there is no fuel leak from the injection ports 24.

Um den Ventilhaltekörper 3, die Zwischenscheibe 5 und den Ventilkörper 7 in definierter Position zueinander zu halten und gegeneinander zu pressen, damit am Durchtritt des Hochdruckkanals 21 durch die Anlageflächen 103, 107 keine Undichtigkeiten auftreten, ist am Gehäuse 1 eine Schraubhülse 10 angeordnet. Die Schraubhülse 10 ist im wesentlichen hohlzylinderförmig ausgeführt und weist eine Längsachse 37 auf. An ihrem brennraumabgewandten Endbereich ist ein Innengewinde 42 ausgebildet, mit dem sie in ein am Ventilhaltekörper 3 ausgebildetes Außengewinde 8 eingeschraubt ist. An ihrem brennraumzugewandten Ende weist die Schraubhülse 10 einen nach innen ragenden Kragen 110 auf, an dem eine ringförmige Druckfläche 32 ausgebildet ist, die an einer ebenfalls ringförmigen Anlagefläche 34 am Ventilkörper 7 anliegt. Durch das Drehen der Schraubhülse 10 bewegt sich die Schraubhülse 10 bedingt durch die Gewinde 42 bzw. 8 in axialer Richtung, wobei die Druckfläche 32 gegen die Anlagefläche 34 gepresst wird. Dadurch wird der Ventilkörper 7 mit der Anlagefläche 107 gegen die Zwischenscheibe 5 gepresst und die Zwischenscheibe 5 wiederum gegen die Anlagefläche 103 des Ventilhaltekörpers 3.In order to keep the valve holding body 3, the intermediate disc 5 and the valve body 7 in a defined position to each other and to press against each other so that no leaks occur at the passage of the high pressure passage 21 through the contact surfaces 103, 107, a screw 10 is arranged on the housing. The screw 10 is designed substantially hollow cylindrical and has a longitudinal axis 37. At its end remote from the combustion chamber, an internal thread 42 is formed, with which it is screwed into a male thread 8 formed on the valve holding body 3. At its end facing the combustion chamber, the threaded sleeve 10 has an inwardly projecting collar 110, on which an annular pressure surface 32 is formed, which rests against a likewise annular contact surface 34 on the valve body 7. By rotating the screw 10, the screw sleeve 10 moves due to the threads 42 and 8 in the axial direction, wherein the pressure surface 32 is pressed against the contact surface 34. Characterized the valve body 7 is pressed with the contact surface 107 against the washer 5 and the washer 5 in turn against the contact surface 103 of the valve holding body. 3

Figur 2 zeigt einen Querschnitt durch das Kraftstoffeinspritzventil von Figur 1 entlang der Linie II-II. An der Schraubhülse 10 ist im Außenbereich eine Rändelung 36 ausgebildet, die die Außenkontur der Schraubhülse 10 bildet. Die Rändelung 36 besteht hierbei aus zueinander parallelen Längsnuten 38, die einen dreieckförmigen Querschnitt aufweisen und direkt aneinander angrenzen. Die Tiefe der Längsnuten 38 ist nur ein Bruchteil der Manteldicke der Schraubhülse 10, so dass keine wesentliche Schwächung der Schraubhülse 10 auftritt. Die Längsnuten 38 sind hierbei parallel zur Längsachse 37 der Schraubhülse 10 ausgebildet. FIG. 2 shows a cross section through the fuel injection valve of FIG. 1 along the line II-II. On the screw 10, a knurling 36 is formed in the outer region, which forms the outer contour of the screw 10. The knurling 36 here consists of mutually parallel longitudinal grooves 38 which have a triangular cross section and directly adjacent to each other. The depth of the longitudinal grooves 38 is only a fraction of the shell thickness of the screw 10, so that no significant weakening of the screw 10 occurs. The longitudinal grooves 38 are in this case formed parallel to the longitudinal axis 37 of the threaded sleeve 10.

In Figur 3 ist ein weiteres Ausführungsbeispiel der erfindungsgemäßen Schraubhülse 10 dargestellt. Die Schraubhülse 10 ist hierbei im unteren, d. h. im brennraumzugewandten Bereich geschnitten dargestellt. Die Außenkontur der Schraubhülse 10 ist hier durch flächige Anschliffe 40 ausgebildet, von denen sechs flächige Anschliffe 40 gleichmäßig über den Umfang der Schraubhülse 10 verteilt angeordnet sind, so dass sich im Querschnitt eine Außenform ergibt, die einem gleichseitigen, regelmäßigen Sechseck entspricht. Mit einem geeigneten Schraubwerkzeug, das die Schraubhülse 10 auf ihrer gesamten Länge umfasst und entsprechend an allen flächigen Anschliffen 40 anliegt, lässt sich das Drehmoment über die gesamte Länge der Schraubhülse 10 einbringen.In FIG. 3 a further embodiment of the screw sleeve 10 according to the invention is shown. The screw 10 is shown here cut in the lower, ie in the combustion chamber facing area. The outer contour of the screw 10 is formed here by flat polished sections 40, of which six flat sections 40 are distributed uniformly over the circumference of the threaded sleeve 10, so that in cross section results in an outer shape that corresponds to an equilateral, regular hexagon. With a suitable screwing tool which comprises the screw sleeve 10 over its entire length and abuts correspondingly on all planar cuts 40, the torque can be introduced over the entire length of the screw sleeve 10.

Sowohl bei der Ausbildung von Längsnuten 38 als auch von flächigen Anschliffen 40 ist stets vorgesehen, dass diese sich zumindest über einen Großteil der Länge der Schraubhülse 10 erstrecken. Besonders vorteilhaft ist es, wenn sich die Längsnuten 38 bzw. die flächigen Anschliffe 40 zumindest annähernd über die gesamte Länge der Schraubhülse 10 erstrecken, damit das Drehmoment auch entsprechend über die gesamte Länge der Schraubhülse 10 eingeleitet werden kann.Both in the formation of longitudinal grooves 38 as well as surface grinding 40 is always provided that they extend at least over much of the length of the threaded sleeve 10. It is particularly advantageous if the longitudinal grooves 38 or the flat contours 40 extend at least approximately over the entire length of the threaded sleeve 10 so that the torque can also be introduced correspondingly over the entire length of the threaded sleeve 10.

Es kann auch vorgesehen sein, dass analog zu dem in Figur 3 dargestellten Ausführungsbeispiel mehr als sechs flächige Anschliffe 40 über den Umfang der Schraubhülse 10 verteilt angeordnet sind, beispielsweise acht, zehn oder zwölf flächige Anschliffe. Diese werden vorzugsweise gleichmäßig verteilt über den Umfang der Schraubhülse 10, so dass sich im Querschnitt an der Außenlinie ein regelmäßiges Vieleck ergibt.It can also be provided that analogous to that in FIG. 3 illustrated embodiment, more than six flat poles 40 are distributed over the circumference of the threaded sleeve 10, for example, eight, ten or twelve flat poles. These are preferably evenly distributed over the circumference of the threaded sleeve 10, so that there is a regular polygon in cross-section on the outline.

Es kann auch vorgesehen sein, dass an der Außenmantelfläche der Schraubhülse 10 eine Außenkontur aufgebracht ist, bei der verschiedene Vertiefungen über einen Großteil der Länge der Schraubhülse 10 und über ihren gesamten Umfang verteilt angeordnet sind. Mit einem geeigneten Schraubwerkzeug, das in diese Vertiefungen eingreift, lässt sich so ein entsprechendes Drehmoment einleiten. Die Vertiefungen können hierbei als Bohrungen ausgebildet sein, als Nuten oder sonstige taschenartige Vertiefungen.It can also be provided that on the outer circumferential surface of the screw 10 an outer contour is applied, are arranged distributed in the various recesses over a majority of the length of the screw 10 and over its entire circumference. With a suitable screwing tool, which engages in these recesses, so can initiate a corresponding torque. The depressions may in this case be formed as bores, as grooves or other pocket-like depressions.

In Figur 4 ist ein geeignetes Schraubwerkzeug in seinen wesentlichen Teilen gezeigt. Das Schraubwerkzeug weist zwei Spannbacken 45 auf, die jeweils im wesentlichen einem halben Hohlzylinder entsprechen. Die Innenseite der Spannbacken 45 weist eine Rändelung 47 auf, die so beschaffen ist, dass sie in die Rändelung 36 der Schraubhülse 10 eingreifen kann. Die beiden Spannbacken 45 werden hierbei durch eine in der Zeichnung nicht dargestellte Vorrichtung in der angegebenen Pfeilrichtung aneinander gepresst, so dass die Rändelung 47 der Spannbacken 45 nicht auf der Rändelung 38 der Schraubhülse 10 abrutschen kann. Bei einer anders geformten Rändelung 36 an der Spannhülse 10 muss die Rändelung 47 der Spannbacken 45 entsprechend angepasst werden, damit auch in diesem Fall eine sichere Verzahnung zwischen Schraubwerkzeug und Spannhülse 10 erfolgt.In FIG. 4 a suitable screwing tool is shown in its essential parts. The screwing tool has two clamping jaws 45, each corresponding substantially to half a hollow cylinder. The inside of the clamping jaws 45 has a knurling 47, which is such that it can engage in the knurling 36 of the threaded sleeve 10. The two clamping jaws 45 are in this case pressed together by a device not shown in the drawing in the indicated arrow direction, so that the knurling 47 of the clamping jaws 45 can not slip on the knurling 38 of the screw 10. In the case of a differently shaped knurling 36 on the clamping sleeve 10, the knurling 47 of the clamping jaws 45 must be adapted accordingly, so that secure toothing between the screwing tool and the clamping sleeve 10 also takes place in this case.

Claims (5)

  1. Fuel injection valve for internal combustion engines having a housing (1) which has a first body (3) and a second body (7) which bear at least indirectly against one another with in each case one contact face (103; 107) and which are pressed against one another by means of a screw sleeve (10), with the screw sleeve (10) engaging with an internal thread (42) into an external thread (8) on the first body (3) and bearing with a pressure face (32) against a contact face (34) of the second body (7), with the screw sleeve (10) being at least approximately of cylindrical design and surrounding the two bodies (3; 7) in the region of the contact faces (103; 107), with the screw sleeve (10) having, on its outer lateral surface over the majority of its length, an outer contour on which a screwing tool can engage such that a tangential force can be exerted on the screw sleeve (10) by means of the screwing tool, with the outer contour being formed both in that section of the screw sleeve (10) which is situated over the first body (3) and also on that section of the screw sleeve (10) which is situated over the second body (7), and with the outer contour extending at least approximately over the entire length of the screw sleeve (10), characterized in that the outer contour has longitudinal grooves (38) which are parallel to one another and run at least approximately parallel to the longitudinal axis (37) of the screw sleeve (10).
  2. Fuel injection valve according to Claim 1, characterized in that the outer contour is a knurling (36).
  3. Fuel injection valve according to Claim 2, characterized in that the knurling (36) is composed of parallel longitudinal grooves (38) which have a triangular cross section and which directly adjoin one another.
  4. Screwing tool for screwing a screw sleeve (10) according to one of Claims 1 to 3, characterized in that the screwing tool has two clamping jaws (45) which substantially correspond to a longitudinally split hollow cylinder and which, on their inner side, have a contour which can engage into the outer contour of the screw sleeve (10).
  5. Screwing tool according to Claim 4, characterized in that the contour on the inner side of the clamping jaws (45) is a knurling (47).
EP02758100A 2001-11-13 2002-07-17 Fuel injection valve for internal combustion engines Expired - Lifetime EP1446575B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10155679A DE10155679A1 (en) 2001-11-13 2001-11-13 Fuel injection valve has external outline of screw shell suitable for screw tool exerting tangential force on shell
DE10155679 2001-11-13
PCT/DE2002/002611 WO2003046366A1 (en) 2001-11-13 2002-07-17 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1446575A1 EP1446575A1 (en) 2004-08-18
EP1446575B1 true EP1446575B1 (en) 2008-03-19

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ID=7705572

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02758100A Expired - Lifetime EP1446575B1 (en) 2001-11-13 2002-07-17 Fuel injection valve for internal combustion engines

Country Status (5)

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US (1) US6895938B2 (en)
EP (1) EP1446575B1 (en)
JP (1) JP4160903B2 (en)
DE (2) DE10155679A1 (en)
WO (1) WO2003046366A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010039980A1 (en) * 2010-08-31 2012-03-01 Man Diesel & Turbo Se Centering device for a fuel injector

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4565320A (en) * 1982-03-15 1986-01-21 Yanmar Diesel Engine Co. Ltd. Unit injector of internal combustion engine
US5160178A (en) * 1991-12-17 1992-11-03 Kabushiki Kaisha Com Direct sealing coupling
DE4214646A1 (en) * 1992-05-02 1993-11-04 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR PRIME AND MAIN INJECTION
DE4218943A1 (en) * 1992-06-10 1993-12-16 Bosch Gmbh Robert Fuel injection nozzle for IC engine - has swirl chamber, and injected fuel and hot air form swirl flow in chamber
DE4432686C2 (en) * 1994-09-14 1996-09-05 Man B & W Diesel Ag Cross-section controlled injection nozzle
KR100190875B1 (en) * 1996-12-06 1999-06-01 정몽규 High pressure injector of a diesel engine
US6286768B1 (en) * 1998-03-27 2001-09-11 Cummins Engine Company, Inc. Pinned injector assembly
US6085991A (en) * 1998-05-14 2000-07-11 Sturman; Oded E. Intensified fuel injector having a lateral drain passage
DE10017113B4 (en) * 2000-04-06 2006-02-09 Ina-Schaeffler Kg locknut
DE10017112B4 (en) * 2000-04-06 2006-06-01 Schaeffler Kg locknut

Also Published As

Publication number Publication date
US20040104284A1 (en) 2004-06-03
JP4160903B2 (en) 2008-10-08
DE10155679A1 (en) 2003-05-28
US6895938B2 (en) 2005-05-24
WO2003046366A1 (en) 2003-06-05
EP1446575A1 (en) 2004-08-18
DE50211930D1 (en) 2008-04-30
JP2005510657A (en) 2005-04-21

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