EP1296054A1 - Injection valve for a combustion engine - Google Patents

Injection valve for a combustion engine Download PDF

Info

Publication number
EP1296054A1
EP1296054A1 EP02017581A EP02017581A EP1296054A1 EP 1296054 A1 EP1296054 A1 EP 1296054A1 EP 02017581 A EP02017581 A EP 02017581A EP 02017581 A EP02017581 A EP 02017581A EP 1296054 A1 EP1296054 A1 EP 1296054A1
Authority
EP
European Patent Office
Prior art keywords
valve
inner recess
housing part
injection
valve housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP02017581A
Other languages
German (de)
French (fr)
Other versions
EP1296054B1 (en
Inventor
Martin Grieb
Stefan Haug
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
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1296054A1 publication Critical patent/EP1296054A1/en
Application granted granted Critical
Publication of EP1296054B1 publication Critical patent/EP1296054B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors
    • 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
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure

Definitions

  • the invention relates to an injection valve with the features the preamble of claim 1.
  • Such an injection valve is from DE 198 32 826 A1 known.
  • the injector shown there is an injector trained and is in a common rail injection system used for internal combustion engines, which have a high-pressure fuel reservoir has that with a high pressure pump in Connection is established.
  • the injector has one with the High-pressure fuel reservoir connected high-pressure fuel connection, a fuel low pressure port for connection to a fuel return device and an electrical Connection on which for the electrical control of a electrically actuated control valve of the injection valve, for example a solenoid valve.
  • the injection valve becomes a valve needle via a valve piston of fuel pressure prevailing in a control pressure chamber loaded in the closing direction.
  • the control pressure room is arranged in a valve piece inserted into the valve housing and via an inlet duct provided with an inlet throttle and an outlet duct provided with an outlet throttle with the high pressure fuel connection respectively connected to the fuel low pressure connection.
  • a Valve member of a control valve which, for example, as a drive has a magnetic actuator or a piezo actuator, the drain channel can be closed and opened and the fuel pressure in the control pressure chamber for the individual Actuating processes of the valve needle can be controlled.
  • the opening speed of the valve needle is opened Drain channel through the flow difference between inlet throttle and outlet throttle and thus ultimately through the fixed Set size ratio of inlet and outlet throttle certainly.
  • the inlet channel is for High-pressure fuel formed in several parts and includes one introduced into a valve housing part of the injection valve Inlet bore, which in a surrounding the valve piece Annulus in an inner recess of the valve housing part opens.
  • the inlet bore opens out with all of it Inner cross section in the inner recess.
  • the injection valve according to the invention with the characteristic Features of claim 1 has the advantage that the notch stresses in the intersection area between the inner recess and the access hole can be significantly reduced and thereby the strength of the injection valve is greatly increased.
  • the inner recess of the valve housing part of the injection valve only with part of their internal cross section. Reduce by changing the shape of the transition edge the advantage of high pressure material stresses acting in the circumferential direction. Without major ones The lifespan can be increased in manufacturing and reliability of the injection valves can be increased.
  • the inner recess extending part of the inlet bore with a Connect supply hole, which with the injection opening of the injector is connected.
  • About the Inlet bore is thus advantageous to both the valve piece surrounding inner recess of the valve housing part as also the supply hole connected to the injection opening supplied with high pressure fuel, so that the structure of the Injector can be simplified. Since no more Bores from the high pressure connection can start from High-pressure fuel accumulator incoming connection line directly be screwed onto the valve housing part and for example the fuel filter is integrated in the valve housing part become.
  • transition edge between the at least one inlet bore and the inner recess is particularly advantageous to define the transition edge between the at least one inlet bore and the inner recess to round off the valve housing part.
  • the rounding of the edge structure caused by the changed shape of the Transition edge an improved high pressure resistance in the intersection area. It is also advantageous that the transition edge during electrochemical or other processes, where a material processing tool in the Inner recess of the valve body part is inserted in Shaped differently and better than the state of the art is accessible.
  • Fig. 1a and Fig. 1b show a known from the prior art Fuel injector 1, which is for use in a fuel injection system is determined with a High-pressure fuel storage is equipped by a High pressure feed pump continuously with high pressure fuel is supplied.
  • the fuel injector 1 shown has a valve housing part 4 with an inner recess 20 which forms a longitudinal bore 5 over part of its length, in which a valve piston 6 is arranged, with its one end to one arranged in a nozzle body 65 Valve needle 60 acts.
  • the valve needle 60 is in one Pressure chamber 61 arranged via a supply bore 8 is supplied with fuel under high pressure.
  • valve piston 6 At a Opening stroke movement of the valve piston 6 becomes the valve needle 60 through the constantly on a pressure shoulder 68 of the valve needle attacking high fuel pressure in the pressure chamber the closing force of a spring 63 is raised. Then with one the injection opening 7 connected to the pressure chamber is injected of the fuel in the combustion chamber of the internal combustion engine. By lowering the valve piston 6, the valve needle in the closing direction in the valve seat 62 of the injection valve pressed and the injection process ends.
  • valve piston 6 is on its end facing away from the valve needle in a cylinder bore 11 out, which is introduced into a valve piece 12 is, which in a continuing the longitudinal bore 5 coaxial Hole 15 is used with a wider diameter.
  • the Valve piece 12 is fixed in a flange region 22 Screw member 23 clamped to the valve housing part 4.
  • the Inner recess 20 of the valve housing part 4 also has a further bore adjoining the bore 15 with an even wider diameter so that between the outer jacket of the valve piece 12 and the cylindrical Inner wall 35 of the further bore an annular space in the inner recess 20 arises.
  • a control pressure chamber 14 with a via an inlet channel a high-pressure fuel connection 3 is connected.
  • the inlet channel is essentially made up of three parts. A Radially through the wall of the valve member 12 leading bore 26, the inner walls of an inlet throttle over part of their length train with which the valve piece 12 is circumferential surrounding annulus constantly connected, which annulus sealed to the longitudinal bore 5 via a sealing ring 39 is and via an inlet bore 16 and a fuel filter 42 in constant connection with the high-pressure fuel connection 3 one screwable into the valve housing part 4 Connection piece 9 stands.
  • the inlet bore 16 opens the injection valves known in the prior art with their entire inner cross section in the inner recess 20 of the Valve housing part 4 a.
  • Via the inlet channel with inlet throttle is the control pressure chamber 14 that in the high-pressure fuel accumulator exposed to high fuel pressure.
  • the control pressure chamber 14 Coaxial with the valve piston 6 branches out of the control pressure chamber 14 continue from a bore in the valve piece 12, the a fuel drain channel provided with an outlet throttle 18 17 forms, which opens into a relief space 19, which is connected to a fuel low pressure connection 10 is, which in turn in a manner not shown is connected to a fuel return.
  • a valve seat 24 is formed with the a control valve member 25 which controls the injection valve Solenoid valve 30 cooperates.
  • the control valve member 25 is coupled to an anchor 27, which anchor with a Electromagnet of the solenoid valve 30 cooperates.
  • the anchor 27 and the control valve member 25 coupled to the armature are constantly supported by a housing-fixed Closing spring 31 acted in the closing direction, so that Control valve member 25 normally in the closed position on Valve seat 24 is present.
  • the opening and closing of the injection valve is as follows described controlled by the solenoid valve 30.
  • the Armature 27 is constantly in the closing direction by the closing spring 31 acts so that the control valve member 25 at electromagnet not energized in the closed position on the valve seat 24 is present and the control pressure chamber 14 to the discharge side 19 is closed so that there is over the inlet channel the high pressure builds up very quickly, which High-pressure fuel accumulator pending.
  • About the area of the The end face 13 generates the pressure in the control pressure chamber 14 Closing force on the valve piston 6 and in connection therewith standing valve needle 60, which is larger than that on the other hand in the opening direction as a result of the high pressure acting forces.
  • the control pressure chamber 14 through Opening the solenoid valve to the relief side 19, the pressure builds up in the small volume of the control pressure chamber 14 very quickly, since this is via the inlet throttle is decoupled from the high pressure side. Consequently predominates on the valve needle in the opening direction acting force from the high fuel pressure applied to the valve needle, so that the valve needle 60 moves upward and the at least one injection opening 7 for injection is opened.
  • solenoid valve 30 closes the fuel drain channel 17, the pressure in the control pressure chamber 14 by the fuel flowing in via the inlet channel be rebuilt so that the original Closing force is applied and the valve needle of the fuel injector closes.
  • Fig. 2 and Fig. 3 each show a cross section through the Injection valve according to the invention. Same reference numbers as 1a and 1b mean the same parts.
  • 2 is the Upper part of the valve housing part 4 shown, the continuous Inner recess 20 through the longitudinal bore 5 and bores 15 and 35 formed coaxially thereto becomes.
  • the holes 15 and 35 serve to accommodate the Valve piece 12, wherein the outer jacket of the valve piece with the inner wall of the bore 35 forms an annular space.
  • the High-pressure connection 3 is formed on a nozzle 9, which For example, in one piece with forging the valve housing part 4 is connected.
  • the high pressure connection 3 has a receiving bore 33 for a fuel filter from which location hole an access hole is located 16 extends into the valve housing part 4.
  • the access hole 16 cuts the inner recess 20 of the valve housing part 4 only with part of its internal cross section 44, as can best be seen in FIGS. 3 and 4.
  • the Access bore 16 cuts the inner recess 20 in the area the cylinder jacket-shaped wall 35 only with part 45 of its inner cross section 44, but not with part 46 of the Inner cross section 44. This changes the shape of the Transition edge 38 between the inlet bore 16 and the inner wall 35 of the inner recess 20 to form an elongated, narrow contour.
  • the distance is d the central axis 50 of the access bore 16 from the The central axis 51 of the inner recess 20 is equal to the radius R. the inner recess 20 in the region of the cylindrical shell Inner wall 35.
  • the distance d can also be larger or smaller than the radius R of the inner recess 20.
  • the access hole only the inner recess cuts with part of its inner cross section 44.
  • the access hole is 16 from the receptacle 33 of the high-pressure connection 3 so far introduced into the tubular base body 1 that they are a portion 36 a little way over the inner recess 20 out into the high-pressure connection 3 facing portion of the valve body part 4 extends where it is connected to the supply bore 8.
  • the embodiment shown is the end of the access hole connected to the supply bore.
  • the supply well 8 can also be T-shaped from section 36 of FIG Branch off access hole 16. The from the high pressure fuel connection 3 outgoing access bore 16 thus supplied advantageously the inner recess 20 and the supply bore 8 with high pressure fuel.
  • central axis 50 of the access bore 16 in the here shown preferred embodiment perpendicular to the central axis 51 of the inner recess 20 of the valve body part 4 runs, it is also possible that the central axis 50 of the Access hole 16 at an angle other than 90 ° runs to the central axis 51 of the inner recess.
  • transition edge 38 in the intersection area to increase the inner wall 35 and the access bore 16
  • the invention shown here is in no way based on injection valves limited and can for common rail systems applied to all injectors for internal combustion engines be where an access hole for high pressure fuel with an inner recess of the valve body part communicates.

Landscapes

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

Abstract

The injection valve for an internal combustion engine is particularly for a common rail fuel injection system and comprises a valve housing part (4) with an inner recess which has a circular cross-section, high pressure fuel issuing through a feed hole (16) into the recess. The feed hole with a part of its inner cross-section intersects the recess of the valve housing part. The feed hole with a section (36) which extends over the valve housing part (5) turned away from the connection (3) is connected with a supply hole (8), which is connected with the injection aperture of the injection valve.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Einspritzventil mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to an injection valve with the features the preamble of claim 1.

Ein derartiges Einspritzventil ist aus der DE 198 32 826 A1 bekannt. Das dort gezeigte Einspritzventil ist als Injektor ausgebildet und wird in einer Common-Rail-Einspritzanlage für Brennkraftmaschinen eingesetzt, welche einen Kraftstoffhochdruckspeicher aufweist, der mit einer Hochdruckpumpe in Verbindung steht. Das Einspritzventil weist einen mit dem Kraftstoffhochdruckspeicher verbundenen Kraftstoffhochdruckanschluß, einen Kraftstoffniederdruckanschluß zum Anschluß an eine Kraftstoffrücklaufeinrichtung und einen elektrischen Anschluß auf, welcher zur elektrischen Ansteuerung eines elektrisch betätigbaren Steuerventils des Einspritzventils, beispielsweise eines Magnetventils dient. Bei dem bekannten Einspritzventil wird eine Ventilnadel über einen Ventilkolben von in einem Steuerdruckraum herrschenden Kraftstoffdruck in Schließrichtung belastet. Der Steuerdruckraum ist in einem in das Ventilgehäuse eingesetzten Ventilstück angeordnet und über einen mit einer Zulaufdrossel versehenen Zulaufkanal und einen mit einer Ablaufdrossel versehenen Ablaufkanal mit dem Kraftstoffhochdruckanschluß beziehungsweise dem Kraftstoffniederdruckanschluß verbunden. Mit einem Ventilglied eines Steuerventils, welches als Antrieb beispielsweise einen Magnetsteller oder einen Piezosteller aufweist, kann der Ablaufkanal geschlossen und geöffnet werden und der Kraftstoffdruck im Steuerdruckraum für die einzelnen Betätigungsvorgänge der Ventilnadel gesteuert werden. Die Öffnungsgeschwindigkeit der Ventilnadel wird bei geöffnetem Ablaufkanal durch den Durchflußunterschied zwischen Zulaufdrossel und Ablaufdrossel und damit letztlich durch das fest eingestellte Größenverhältnis von Zulauf- und Ablaufdrossel bestimmt.Such an injection valve is from DE 198 32 826 A1 known. The injector shown there is an injector trained and is in a common rail injection system used for internal combustion engines, which have a high-pressure fuel reservoir has that with a high pressure pump in Connection is established. The injector has one with the High-pressure fuel reservoir connected high-pressure fuel connection, a fuel low pressure port for connection to a fuel return device and an electrical Connection on which for the electrical control of a electrically actuated control valve of the injection valve, for example a solenoid valve. With the known The injection valve becomes a valve needle via a valve piston of fuel pressure prevailing in a control pressure chamber loaded in the closing direction. The control pressure room is arranged in a valve piece inserted into the valve housing and via an inlet duct provided with an inlet throttle and an outlet duct provided with an outlet throttle with the high pressure fuel connection respectively connected to the fuel low pressure connection. With a Valve member of a control valve, which, for example, as a drive has a magnetic actuator or a piezo actuator, the drain channel can be closed and opened and the fuel pressure in the control pressure chamber for the individual Actuating processes of the valve needle can be controlled. The The opening speed of the valve needle is opened Drain channel through the flow difference between inlet throttle and outlet throttle and thus ultimately through the fixed Set size ratio of inlet and outlet throttle certainly.

Bei dem bekannten Einspritzventil ist der Zulaufkanal für Hochdruckkraftstoff mehrteilig ausgebildet und umfaßt eine in ein Ventilgehäuseteil des Einspritzventils eingebrachte Zulaufbohrung, welche in einen das Ventilstück umgebenden Ringraum in einer Innenausnehmung des Ventilgehäuseteils einmündet. Die Zulaufbohrung mündet dabei mit ihrem gesamten Innenquerschnitt in die Innenausnehmung ein. In der Praxis hat sich gezeigt, daß im Verschneidungsbereich von Zulaufbohrung und Innenausnehmung bedingt durch den hohen Kraftstoffdruck und die Kerbwirkung der Zulaufbohrung starke Zugspannungen in Umfangsrichtung auftreten, welche zu Brüchen und Rißbildungen führen können.In the known injection valve, the inlet channel is for High-pressure fuel formed in several parts and includes one introduced into a valve housing part of the injection valve Inlet bore, which in a surrounding the valve piece Annulus in an inner recess of the valve housing part opens. The inlet bore opens out with all of it Inner cross section in the inner recess. In practice has been shown that in the intersection of the inlet bore and internal recess due to the high fuel pressure and the notch effect of the inlet bore strong Tensile stresses occur in the circumferential direction, which lead to breaks and can cause cracks.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Einspritzventil mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, daß die Kerbspannungen im Verschneidungsbereich zwischen der Innenausnehmung und der Zugangsbohrung deutlich reduziert werden und dadurch die Festigkeit des Einspritzventils stark erhöht wird. Bei dem erfindungsgemäßen Einspritzventil schneidet die Zulaufbohrung die Innenausnehmung des Ventilgehäuseteils des Einspritzventils nur mit einem Teil ihres Innenquerschnitts. Durch die veränderte Formgebung der Übergangskante reduzieren sich vorteilhaft die bei einer Hochdruckbeaufschlagung in Umfangsrichtung wirkenden Materialspannungen. Ohne größeren Mehraufwand bei der Herstellung kann so die Lebensdauer und Zuverlässigkeit der Einspritzventile erhöht werden.The injection valve according to the invention with the characteristic Features of claim 1 has the advantage that the notch stresses in the intersection area between the inner recess and the access hole can be significantly reduced and thereby the strength of the injection valve is greatly increased. at the inlet bore intersects the injection valve according to the invention the inner recess of the valve housing part of the injection valve only with part of their internal cross section. Reduce by changing the shape of the transition edge the advantage of high pressure material stresses acting in the circumferential direction. Without major ones The lifespan can be increased in manufacturing and reliability of the injection valves can be increased.

Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung werden durch die in den Unteransprüchen enthaltenen Merkmale ermöglicht.Advantageous refinements and developments of the invention are covered by those in the subclaims Features.

Vorteilhaft ist es, die Zulaufbohrung von einem Anschluß des Ventilgehäuseteils aus so weit in das Ventilgehäuseteil einzubringen, daß sich die Zulaufbohrung über die Innenausnehmung hinaus in den von dem Anschluß abgewandten Teil des Ventilgehäuseteils erstreckt. Hierdurch wird eine symmetrische Formgebung der Übergangskante von Zulaufbohrung und Innenausnehmung erreicht, wodurch die Kerbspannungen besonders stark reduziert werden.It is advantageous to the inlet bore from a connection of the Valve housing part from so far into the valve housing part, that the inlet hole over the inner recess out into the part of the Valve housing part extends. This creates a symmetrical Shape of the transition edge of the inlet bore and inner recess achieved, making the notch tensions particularly be greatly reduced.

Besonders vorteilhaft ist es, den sich über die Innenausnehmung hinaus erstreckenden Teil der Zulaufbohrung mit einer Versorgungsbohrung zu verbinden, welche mit der Einspritzöffnung des Einspritzventils in Verbindung steht. Über die Zulaufbohrung wird somit vorteilhaft sowohl die das Ventilstück umgebende Innenausnehmung des Ventilgehäuseteils als auch die mit der Einspritzöffnung verbundene Versorgungsbohrung mit Hochdruckkraftstoff versorgt, so daß der Aufbau des Einspritzventils vereinfacht werden kann. Da keine weiteren Bohrungen von dem Hochdruckanschluß ausgehen, kann die vom Kraftstoffhochdruckspeicher kommende Anschlußleitung direkt auf das Ventilgehäuseteil aufgeschraubt werden und zum Beispiel der Kraftstoffilter in das Ventilgehäuseteil integriert werden.It is particularly advantageous to use the inner recess extending part of the inlet bore with a Connect supply hole, which with the injection opening of the injector is connected. About the Inlet bore is thus advantageous to both the valve piece surrounding inner recess of the valve housing part as also the supply hole connected to the injection opening supplied with high pressure fuel, so that the structure of the Injector can be simplified. Since no more Bores from the high pressure connection can start from High-pressure fuel accumulator incoming connection line directly be screwed onto the valve housing part and for example the fuel filter is integrated in the valve housing part become.

Besonders vorteilhaft ist es, die Übergangskante zwischen der wenigstens einen Zulaufbohrung und der Innenausnehmung des Ventilgehäuseteils zu verrunden. Die Verrundung der Kantenstruktur bewirkt durch die veränderte Formgebung der Übergangskante eine verbesserte Hochdruckfestigkeit im Verschneidungsbereich. Weiterhin ist vorteilhaft, daß die Übergangskante während der elektrochemischen oder anderen Verfahren, bei denen ein materialbearbeitendes Werkzeug in die Innenausnehmung des Ventilkörperteils eingeführt wird, im Vergleich zum Stand der Technik anders geformt und besser zugänglich ist.It is particularly advantageous to define the transition edge between the at least one inlet bore and the inner recess to round off the valve housing part. The rounding of the edge structure caused by the changed shape of the Transition edge an improved high pressure resistance in the intersection area. It is also advantageous that the transition edge during electrochemical or other processes, where a material processing tool in the Inner recess of the valve body part is inserted in Shaped differently and better than the state of the art is accessible.

Zeichnungendrawings

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung erläutert. Es zeigt

  • Fig. 1a einen Querschnitt durch den oberen Teil eines aus dem Stand der Technik bekannten Einspritzventils,
  • Fig. 1b den unteren Teil des Einspritzventils aus Fig. 1a,
  • Fig. 2 einen vereinfachten Querschnitt durch ein Gehäuseteil des erfindungsgemäßen Einspritzventils längs der Linie II-II in Fig. 3,
  • Fig. 3 einen weiteren Querschnitt durch das erfindungsgemäße Einspritzventil,
  • Fig. 4 einen vergrößerten Teilquerschnitt durch das Einspritzventil senkrecht zur Zugangsbohrung.
    • Exemplary embodiments of the invention are illustrated in the drawings and are explained in the description below. It shows
  • 1a shows a cross section through the upper part of an injection valve known from the prior art,
  • 1b, the lower part of the injection valve from Fig. 1a,
  • 2 shows a simplified cross section through a housing part of the injection valve according to the invention along the line II-II in FIG. 3,
  • 3 shows a further cross section through the injection valve according to the invention,
  • Fig. 4 is an enlarged partial cross section through the injection valve perpendicular to the access hole.

    • Beschreibung eines AusführungsbeispielsDescription of an embodiment

    Fig. 1a und Fig. 1b zeigen ein aus dem Stand der Technik bekanntes Kraftstoffeinspritzventil 1, welches zur Verwendung in einer Kraftstoffeinspritzanlage bestimmt ist, die mit einem Kraftstoffhochdruckspeicher ausgerüstet ist, der durch eine Hochdruckförderpumpe kontinuierlich mit Hochdruckkraftstoff versorgt wird. Das dargestellte Kraftstoffeinspritzventil 1 weist ein Ventilgehäuseteil 4 mit einer Innenausnehmung 20 auf, die auf einem Teil ihrer Länge eine Längsbohrung 5 ausbildet, in der ein Ventilkolben 6 angeordnet ist, der mit seinem einen Ende auf eine in einem Düsenkörper 65 angeordnete Ventilnadel 60 einwirkt. Die Ventilnadel 60 ist in einem Druckraum 61 angeordnet, der über eine Versorgungsbohrung 8 mit unter Hochdruck stehendem Kraftstoff versorgt ist. Bei einer Öffnungshubbewegung des Ventilkolbens 6 wird die Ventilnadel 60 durch den ständig an einer Druckschulter 68 der Ventilnadel angreifenden Kraftstoffhochdruck im Druckraum entgegen der Schließkraft einer Feder 63 angehoben. Durch eine dann mit dem Druckraum verbundene Einspritzöffnung 7 erfolgt die Einspritzung des Kraftstoffs in den Brennraum der Brennkraftmaschine. Durch Absenken des Ventilkolbens 6 wird die Ventilnadel in Schließrichtung in den Ventilsitz 62 des Einspritzventils gedrückt und der Einspritzvorgang beendet.Fig. 1a and Fig. 1b show a known from the prior art Fuel injector 1, which is for use in a fuel injection system is determined with a High-pressure fuel storage is equipped by a High pressure feed pump continuously with high pressure fuel is supplied. The fuel injector 1 shown has a valve housing part 4 with an inner recess 20 which forms a longitudinal bore 5 over part of its length, in which a valve piston 6 is arranged, with its one end to one arranged in a nozzle body 65 Valve needle 60 acts. The valve needle 60 is in one Pressure chamber 61 arranged via a supply bore 8 is supplied with fuel under high pressure. At a Opening stroke movement of the valve piston 6 becomes the valve needle 60 through the constantly on a pressure shoulder 68 of the valve needle attacking high fuel pressure in the pressure chamber the closing force of a spring 63 is raised. Then with one the injection opening 7 connected to the pressure chamber is injected of the fuel in the combustion chamber of the internal combustion engine. By lowering the valve piston 6, the valve needle in the closing direction in the valve seat 62 of the injection valve pressed and the injection process ends.

    Wie in Fig. 1a zu erkennen ist, wird der Ventilkolben 6 an seinem von der Ventilnadel abgewandten Ende in einer Zylinderbohrung 11 geführt, die in ein Ventilstück 12 eingebracht ist, welches in eine die Längsbohrung 5 fortsetzende koaxiale Bohrung 15 mit breiterem Durchmesser eingesetzt ist. Das Ventilstück 12 ist in einem Flanschbereich 22 fest über ein Schraubglied 23 mit dem Ventilgehäuseteil 4 verspannt. Die Innenausnehmung 20 des Ventilgehäuseteils 4 weist weiterhin eine sich an die Bohrung 15 anschließende weitere Bohrung mit einem noch breiteren Durchmesser auf, so daß zwischen dem Außenmantel des Ventilstücks 12 und der zylindrischen Innenwandung 35 der weiteren Bohrung ein Ringraum in der Innenausnehmung 20 entsteht. In der Zylinderbohrung 11 des Ventilstücks schließt eine Stirnseite 13 des Ventilkolbens 6 einen Steuerdruckraum 14 ein, der über einen Zulaufkanal mit einem Kraftstoffhochdruckanschluß 3 verbunden ist. Der Zulaufkanal ist im wesentlichen dreiteilig ausgebildet. Eine radial durch die Wand des Ventilstücks 12 führende Bohrung 26, deren Innenwände auf einem Teil ihrer Länge eine Zulaufdrossel ausbilden, ist mit dem das Ventilstück 12 umfangsseitig umgebenden Ringraum ständig verbunden, welcher Ringraum über einen Dichtring 39 zur Längsbohrung 5 abgedichtet ist und über eine Zulaufbohrung 16 und einen Kraftstoffilter 42 in ständiger Verbindung mit dem Kraftstoffhochdruckanschluß 3 eines in das Ventilgehäuseteil 4 einschraubbaren Anschlußstutzens 9 steht. Die Zulaufbohrung 16 mündet bei den im Stand der Technik bekannten Einspritzventilen mit ihrem gesamten Innenquerschnitt in die Innenausnehmung 20 des Ventilgehäuseteils 4 ein. Über den Zulaufkanal mit Zulaufdrossel ist der Steuerdruckraum 14 dem im Kraftstoffhochdruckspeicher herrschenden hohen Kraftstoffdruck ausgesetzt. Koaxial zum Ventilkolben 6 zweigt aus dem Steuerdruckraum 14 weiterhin eine im Ventilstück 12 verlaufende Bohrung ab, die einen mit einer Ablaufdrossel 18 versehenen Kraftstoffablaufkanal 17 bildet, der in einen Entlastungsraum 19 einmündet, der mit einem Kraftstoffniederdruckanschluß 10 verbunden ist, welcher wiederum in nicht weiter dargestellter Weise mit einem Kraftstoffrücklauf verbunden ist. Der Austritt des Kraftstoffablaufkanals 17 aus dem Ventilstück 12 erfolgt im Bereich eines kegelförmig angesenkten Teiles 21 der außenliegenden Stirnseite des Ventilstückes 12. In dem kegelförmigen Teil 21 ist ein Ventilsitz 24 ausgebildet, mit dem ein Steuerventilglied 25 eines das Einspritzventil steuernden Magnetventils 30 zusammenwirkt. Das Steuerventilglied 25 ist mit einem Anker 27 gekoppelt, welcher Anker mit einem Elektromagneten des Magnetventils 30 zusammen wirkt. Der Anker 27 und das mit dem Anker gekoppelte Steuerventilglied 25 sind ständig durch eine sich gehäusefest abstützende Schließfeder 31 in Schließrichtung beaufschlagt, so daß das Steuerventilglied 25 normalerweise in Schließstellung am Ventilsitz 24 anliegt. Bei Erregung des Elektromagneten wird der Anker 27 zum Elektromagneten hin bewegt, wodurch der Ablaufkanal 17 zum Entlastungsraum 19 hin geöffnet wird. As can be seen in Fig. 1a, the valve piston 6 is on its end facing away from the valve needle in a cylinder bore 11 out, which is introduced into a valve piece 12 is, which in a continuing the longitudinal bore 5 coaxial Hole 15 is used with a wider diameter. The Valve piece 12 is fixed in a flange region 22 Screw member 23 clamped to the valve housing part 4. The Inner recess 20 of the valve housing part 4 also has a further bore adjoining the bore 15 with an even wider diameter so that between the outer jacket of the valve piece 12 and the cylindrical Inner wall 35 of the further bore an annular space in the inner recess 20 arises. In the cylinder bore 11 of the The valve piece closes an end face 13 of the valve piston 6 a control pressure chamber 14 with a via an inlet channel a high-pressure fuel connection 3 is connected. The inlet channel is essentially made up of three parts. A Radially through the wall of the valve member 12 leading bore 26, the inner walls of an inlet throttle over part of their length train with which the valve piece 12 is circumferential surrounding annulus constantly connected, which annulus sealed to the longitudinal bore 5 via a sealing ring 39 is and via an inlet bore 16 and a fuel filter 42 in constant connection with the high-pressure fuel connection 3 one screwable into the valve housing part 4 Connection piece 9 stands. The inlet bore 16 opens the injection valves known in the prior art with their entire inner cross section in the inner recess 20 of the Valve housing part 4 a. Via the inlet channel with inlet throttle is the control pressure chamber 14 that in the high-pressure fuel accumulator exposed to high fuel pressure. Coaxial with the valve piston 6 branches out of the control pressure chamber 14 continue from a bore in the valve piece 12, the a fuel drain channel provided with an outlet throttle 18 17 forms, which opens into a relief space 19, which is connected to a fuel low pressure connection 10 is, which in turn in a manner not shown is connected to a fuel return. The exit of the fuel drain channel 17 from the valve piece 12 in the area of a conically countersunk part 21 of the outer part Face of the valve piece 12. In the conical Part 21 is a valve seat 24 is formed with the a control valve member 25 which controls the injection valve Solenoid valve 30 cooperates. The control valve member 25 is coupled to an anchor 27, which anchor with a Electromagnet of the solenoid valve 30 cooperates. The anchor 27 and the control valve member 25 coupled to the armature are constantly supported by a housing-fixed Closing spring 31 acted in the closing direction, so that Control valve member 25 normally in the closed position on Valve seat 24 is present. When the electromagnet is excited the armature 27 moves toward the electromagnet, causing the drain channel 17 to the relief chamber 19 is opened.

    Das Öffnen und Schließen des Einspritzventils wird wie nachfolgend beschrieben von dem Magnetventil 30 gesteuert. Der Anker 27 ist ständig durch die Schließfeder 31 in Schließrichtung beaufschlagt, so daß das Steuerventilglied 25 bei nicht erregtem Elektromagneten in Schließstellung am Ventilsitz 24 anliegt und der Steuerdruckraum 14 zur Entlastungsseite 19 hin verschlossen ist, so daß sich dort über den Zulaufkanal sehr schnell der hohe Druck aufbaut, der auch im Kraftstoffhochdruckspeicher ansteht. Über die Fläche der Stirnseite 13 erzeugt der Druck im Steuerdruckraum 14 eine Schließkraft auf den Ventilkolben 6 und die damit in Verbindung stehende Ventilnadel 60, die größer ist als die andererseits in Öffnungsrichtung in Folge des anstehenden Hochdrucks wirkenden Kräfte. Wird der Steuerdruckraum 14 durch Öffnen des Magnetventils zur Entlastungsseite 19 hin geöffnet, baut sich der Druck in dem geringen Volumen des Steuerdruckraumes 14 sehr schnell ab, da dieser über die Zulaufdrossel von der Hochdruckseite abgekoppelt ist. Infolgedessen überwiegt die auf die Ventilnadel in Öffnungsrichtung wirkende Kraft aus dem an der Ventilnadel anstehenden Kraftstoffhochdruck, so daß die Ventilnadel 60 nach oben bewegt und dabei die wenigstens eine Einspritzöffnung 7 zur Einspritzung geöffnet wird. Schließt jedoch das Magnetventil 30 den Kraftstoffablaufkanal 17, kann der Druck im Steuerdruckraum 14 durch den über den Zulaufkanal nachfließenden Kraftstoff wieder aufgebaut werden, so daß die ursprüngliche Schließkraft ansteht und die Ventilnadel des Kraftstoffeinspritzventils schließt.The opening and closing of the injection valve is as follows described controlled by the solenoid valve 30. The Armature 27 is constantly in the closing direction by the closing spring 31 acts so that the control valve member 25 at electromagnet not energized in the closed position on the valve seat 24 is present and the control pressure chamber 14 to the discharge side 19 is closed so that there is over the inlet channel the high pressure builds up very quickly, which High-pressure fuel accumulator pending. About the area of the The end face 13 generates the pressure in the control pressure chamber 14 Closing force on the valve piston 6 and in connection therewith standing valve needle 60, which is larger than that on the other hand in the opening direction as a result of the high pressure acting forces. The control pressure chamber 14 through Opening the solenoid valve to the relief side 19, the pressure builds up in the small volume of the control pressure chamber 14 very quickly, since this is via the inlet throttle is decoupled from the high pressure side. Consequently predominates on the valve needle in the opening direction acting force from the high fuel pressure applied to the valve needle, so that the valve needle 60 moves upward and the at least one injection opening 7 for injection is opened. However, solenoid valve 30 closes the fuel drain channel 17, the pressure in the control pressure chamber 14 by the fuel flowing in via the inlet channel be rebuilt so that the original Closing force is applied and the valve needle of the fuel injector closes.

    Fig. 2 und Fig. 3 zeigen jeweils einen Querschnitt durch das erfindungsgemäße Einspritzventil. Gleiche Bezugsziffern wie in Fig. 1a und 1b bedeuten gleiche Teile. In Fig. 2 ist der obere Teil des Ventilgehäuseteils 4 gezeigt, dessen durchgehende Innenausnehmung 20 durch die Längsbohrung 5 und die sich koaxial daran anschließenden Bohrungen 15 und 35 gebildet wird. Die Bohrungen 15 und 35 dienen der Aufnahme des Ventilstücks 12, wobei der Außenmantel des Ventilstücks mit der Innenwandung der Bohrung 35 einen Ringraum bildet. Der Hochdruckanschluß 3 ist an einem Stutzen 9 ausgebildet, welcher Stutzen beispielsweise durch Schmieden einstückig mit dem Ventilgehäuseteil 4 verbunden ist. Der Hochdruckanschluß 3 weist eine Aufnahmebohrung 33 für einen Kraftstoffilter auf, von welcher Aufnahmebohrung aus sich eine Zugangsbohrung 16 in das Ventilgehäuseteil 4 erstreckt. Die Zugangsbohrung 16 schneidet die Innenausnehmung 20 des Ventilgehäuseteils 4 lediglich mit einem Teil ihres Innenquerschnitts 44, wie am besten in Fig. 3 und Fig. 4 zu erkennen ist. Die Zugangsbohrung 16 schneidet die Innenausnehmung 20 im Bereich der zylindermantelförmigen Wand 35 nur mit dem Teil 45 ihres Innenquerschnitts 44, nicht aber mit dem Teil 46 des Innenquerschnitts 44. Hierdurch verändert sich die Form der Übergangskante 38 zwischen der Zulaufbohrung 16 und der Innenwandung 35 der Innenausnehmung 20 zu einer länglichen, schmalen Kontur. Wenn "r" der Radius der Zugangsbohrung 16 ist, "R" der Radius der zylindermantelförmigen Innenwandung 35 der Innenausnehmung 20 und "d" der Abstand der Mittelachse 50 der Zugangsbohrung 16 von der Mittelachse 51 der Innenausnehmung 20, wird dies erreicht, falls die folgenden beiden geometrischen Bedingungen gleichzeitig erfüllt sind: 1) r + d > R und 2) d - r < R.Fig. 2 and Fig. 3 each show a cross section through the Injection valve according to the invention. Same reference numbers as 1a and 1b mean the same parts. 2 is the Upper part of the valve housing part 4 shown, the continuous Inner recess 20 through the longitudinal bore 5 and bores 15 and 35 formed coaxially thereto becomes. The holes 15 and 35 serve to accommodate the Valve piece 12, wherein the outer jacket of the valve piece with the inner wall of the bore 35 forms an annular space. The High-pressure connection 3 is formed on a nozzle 9, which For example, in one piece with forging the valve housing part 4 is connected. The high pressure connection 3 has a receiving bore 33 for a fuel filter from which location hole an access hole is located 16 extends into the valve housing part 4. The access hole 16 cuts the inner recess 20 of the valve housing part 4 only with part of its internal cross section 44, as can best be seen in FIGS. 3 and 4. The Access bore 16 cuts the inner recess 20 in the area the cylinder jacket-shaped wall 35 only with part 45 of its inner cross section 44, but not with part 46 of the Inner cross section 44. This changes the shape of the Transition edge 38 between the inlet bore 16 and the inner wall 35 of the inner recess 20 to form an elongated, narrow contour. If "r" is the radius of the access hole 16 "R" is the radius of the inner wall of the cylinder jacket 35 of the inner recess 20 and "d" the distance of the central axis 50 of the access bore 16 from the central axis 51 of the inner recess 20, this is achieved if the following both geometric conditions are fulfilled at the same time: 1) r + d> R and 2) d - r <R.

    In dem in Fig. 4 gezeigten Ausführungsbeispiel ist der Abstand d der Mittelachse 50 der Zugangsbohrung 16 von der Mittelachse 51 der Innenausnehmung 20 gleich dem Radius R der Innenausnehmung 20 im Bereich der zylindermantelförmigen Innenwand 35. Der Abstand d kann aber auch größer oder kleiner als der Radius R der Innenausnehmung 20 sein. Wichtig ist, daß die Zugangsbohrung die Innenausnehmung lediglich mit einem Teil ihres Innenquerschnitts 44 schneidet. In the embodiment shown in Fig. 4, the distance is d the central axis 50 of the access bore 16 from the The central axis 51 of the inner recess 20 is equal to the radius R. the inner recess 20 in the region of the cylindrical shell Inner wall 35. The distance d can also be larger or smaller than the radius R of the inner recess 20. Important is that the access hole only the inner recess cuts with part of its inner cross section 44.

    Wie am besten in Fig. 3 zu erkennen ist, ist die Zugangsbohrung 16 von der Aufnahme 33 des Hochdruckanschlusses 3 aus soweit in den rohrförmigen Grundkörper 1 eingebracht, daß sie sich mit einem Abschnitt 36 ein Stück weit über die Innenausnehmung 20 hinaus in den von dem Hochdruckanschluß 3 abgewandten Abschnitt des Ventilkörperteils 4 erstreckt, wo sie mit der Versorgungsbohrung 8 verbunden ist. In dem hier gezeigten Ausführungsbeispiel ist die Zugangsbohrung endseitig mit der Versorgungsbohrung verbunden. Die Versorgungsbohrung 8 kann aber auch T-förmig von dem Abschnitt 36 der Zugangsbohrung 16 abzweigen. Die von dem Kraftstoffhochdruckanschluß 3 ausgehende Zugangsbohrung 16 versorgt somit vorteilhaft die Innenausnehmung 20 und die Versorgungsbohrung 8 mit Hochdruckkraftstoff.As best seen in Figure 3, the access hole is 16 from the receptacle 33 of the high-pressure connection 3 so far introduced into the tubular base body 1 that they are a portion 36 a little way over the inner recess 20 out into the high-pressure connection 3 facing portion of the valve body part 4 extends where it is connected to the supply bore 8. In this one The embodiment shown is the end of the access hole connected to the supply bore. The supply well 8 can also be T-shaped from section 36 of FIG Branch off access hole 16. The from the high pressure fuel connection 3 outgoing access bore 16 thus supplied advantageously the inner recess 20 and the supply bore 8 with high pressure fuel.

    Obwohl die Mittelachse 50 der Zugangsbohrung 16 in dem hier gezeigten bevorzugten Ausführungsbeispiel senkrecht zur Mittelachse 51 der Innenausnehmung 20 des Ventilkörperteils 4 verläuft, ist es auch möglich, daß die Mittelachse 50 der Zugangsbohrung 16 unter einem von 90° abweichenden Winkel zur Mittelachse 51 der Innenausnehmung verläuft.Although the central axis 50 of the access bore 16 in the here shown preferred embodiment perpendicular to the central axis 51 of the inner recess 20 of the valve body part 4 runs, it is also possible that the central axis 50 of the Access hole 16 at an angle other than 90 ° runs to the central axis 51 of the inner recess.

    Um die Festigkeit der Übergangskante 38 im Verschneidungsbereich der Innenwandung 35 und der Zugangsbohrung 16 zu erhöhen, ist es vorteilhaft, die Übergangskante 38 zu verrunden und dabei zu entgraten, was beispielsweise in einem elektrochemischen Verfahren geschehen kann, bei dem ein materialentfernendes Werkstück in die Innenausnehmung 20 eingeführt wird. Aufgrund der guten Zugänglichkeit der Übergangskante 38 können größere Verrundungen hergestellt werden, was sich wiederum positiv auf die Festigkeit des Einspritzventils im Verschneidungsbereich von Innenausnehmung und Zulaufbohrung auswirkt. The strength of the transition edge 38 in the intersection area to increase the inner wall 35 and the access bore 16, it is advantageous to round the transition edge 38 and deburring what, for example, in an electrochemical Process can be done in which a material removing Workpiece inserted into the inner recess 20 becomes. Because of the good accessibility of the transition edge 38 larger fillets can be made, which is again positive for the strength of the injection valve in the Intersection area of inner recess and inlet bore effect.

    Die hier dargestellte Erfindung ist keinesfalls auf Einspritzventile für Common-Rail-Systeme beschränkt und kann bei allen Einspritzventilen für Brennkraftmaschinen angewandt werden, bei denen eine Zugangsbohrung für Hochdruckkraftstoff mit einer Innenausnehmung des Ventilkörperteils in Verbindung steht. Dadurch, daß die Innenausnehmung von der Zulaufbohrung nur angeschnitten wird und die Zugangsbohrung nicht vollständig in die Innenausnehmung einmündet, verändert sich die Struktur der Übergangskante vorteilhaft so, daß Kerbspannungen verringert werden und die Hochdruckfestigkeit des Einspritzventils erhöht wird.The invention shown here is in no way based on injection valves limited and can for common rail systems applied to all injectors for internal combustion engines be where an access hole for high pressure fuel with an inner recess of the valve body part communicates. The fact that the inner recess of the inlet hole is only cut and the access hole does not completely open into the inner recess, the structure of the transition edge changes advantageously so that notch stresses are reduced and the high pressure resistance of the injection valve is increased.

    Claims (6)

    Einspritzventil für eine Brennkraftmaschine, insbesondere Einspritzventil für ein Common-Rail-Kraftstoffeinspritzsystem, umfassend ein Ventilgehäuseteil (4) mit einer Innenausnehmung (20) mit im wesentlichen kreisförmigen Querschnitt und eine in die Innenausnehmung (20) einmündende Zulaufbohrung (16) für Hochdruckkraftstoff, dadurch gekennzeichnet, daß die Zulaufbohrung (16) die Innenausnehmung (20) des Ventilgehäuseteils lediglich mit einem Teil (45) ihres Innenquerschnitts (44) schneidet.Injection valve for an internal combustion engine, in particular injection valve for a common rail fuel injection system, comprising a valve housing part (4) with an inner recess (20) with a substantially circular cross section and an inlet bore (16) for high pressure fuel opening into the inner recess (20), characterized in that that the inlet bore (16) cuts the inner recess (20) of the valve housing part only with part (45) of its inner cross section (44). Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Zulaufbohrung (16) von einem Anschluß (3) des Ventilgehäuseteils (5) aus so weit in das Ventilgehäuseteil eingebracht ist, daß sich die Zulaufbohrung (16) über die Innenausnehmung (20) hinaus in den von dem Anschluß (3) abgewandten Teil des Ventilgehäuseteils (5) erstreckt.Injection valve according to Claim 1, characterized in that the inlet bore (16) is introduced into the valve housing part from a connection (3) of the valve housing part (5) to such an extent that the inlet bore (16) extends beyond the inner recess (20) into the part of the valve housing part (5) facing away from the connection (3). Einspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Zulaufbohrung (16) mit dem Abschnitt (36), der sich über die Innenausnehmung (20) hinaus in den von dem Anschluß (3) abgewandten Teil des Ventilgehäuseteils (5) erstreckt, mit einer Versorgungsbohrung (8) verbunden ist, welche mit der Einspritzöffnung (7) des Einspritzventils in Verbindung steht. Injection valve according to Claim 1 or 2, characterized in that the inlet bore (16) with the section (36) which extends beyond the inner recess (20) into the part of the valve housing part (5) which faces away from the connection (3) a supply hole (8) is connected, which is connected to the injection opening (7) of the injection valve. Einspritzventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Übergangskante (38) zwischen der wenigstens einen Zulaufbohrung (16) und der Innenausnehmung (20) des Ventilgehäuseteils (5) verrundet ist.Injection valve according to one of the preceding claims, characterized in that the transition edge (38) between the at least one inlet bore (16) and the inner recess (20) of the valve housing part (5) is rounded. Einspritzventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Zulaufbohrung (16) die Innenausnehmung (20) des Ventilgehäuseteils im Bereich einer zylindermantelförmigen Innenwandung (35) der Innenausnehmung (20) mit einem Teil ihres Innenquerschnitts (44) schneidet.Injection valve according to one of the preceding claims, characterized in that the inlet bore (16) intersects the inner recess (20) of the valve housing part in the region of a cylinder jacket-shaped inner wall (35) of the inner recess (20) with part of its inner cross section (44). Einspritzventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Mittelachse (50) der Zulaufbohrung (16) senkrecht zur Mittelachse (51) der Innenausnehmung (20) verläuft.Injection valve according to one of the preceding claims, characterized in that the central axis (50) of the inlet bore (16) extends perpendicular to the central axis (51) of the inner recess (20).
    EP02017581A 2001-09-22 2002-08-07 Injection valve for a combustion engine Expired - Lifetime EP1296054B1 (en)

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    DE10146743 2001-09-22
    DE10146743A DE10146743A1 (en) 2001-09-22 2001-09-22 Injection valve for an internal combustion engine

    Publications (2)

    Publication Number Publication Date
    EP1296054A1 true EP1296054A1 (en) 2003-03-26
    EP1296054B1 EP1296054B1 (en) 2005-07-27

    Family

    ID=7699908

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP02017581A Expired - Lifetime EP1296054B1 (en) 2001-09-22 2002-08-07 Injection valve for a combustion engine

    Country Status (3)

    Country Link
    EP (1) EP1296054B1 (en)
    JP (1) JP4184741B2 (en)
    DE (2) DE10146743A1 (en)

    Cited By (4)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    WO2005035970A1 (en) * 2003-10-06 2005-04-21 Robert Bosch Gmbh Injection nozzle
    WO2008128881A1 (en) * 2007-04-19 2008-10-30 Robert Bosch Gmbh Area of intersection between a high-pressure chamber and a high-pressure duct
    DE102007050993A1 (en) 2007-10-25 2009-04-30 Robert Bosch Gmbh Fuel injector i.e. diesel injection device, for internal combustion engine, has pressure chamber formed between ring surface and ring-shaped shoulder, and inlet borehole diverting for control chamber by shoulder
    CN106181236A (en) * 2016-07-13 2016-12-07 无锡派乐科技有限公司 High-pressure co-rail pad and manufacture method thereof

    Families Citing this family (6)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE102005008466A1 (en) * 2005-02-24 2006-08-31 Robert Bosch Gmbh Fuel-injection valve e.g. injector for fuel-injection systems of compression-ignition internal combustion engines has supply channel of fuel-inlet connecting piece, located eccentrically in relation to axis of valve housing
    DE102005016010A1 (en) 2005-04-07 2006-10-12 Robert Bosch Gmbh Valve for controlling an injection valve of an internal combustion engine
    DE102005020360A1 (en) * 2005-05-02 2006-11-09 Robert Bosch Gmbh Valve for controlling an injection valve of an internal combustion engine
    DE102007044357A1 (en) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Control valve for a fuel injection valve
    DE102007043540A1 (en) 2007-09-12 2009-05-07 Robert Bosch Gmbh Leak-free fuel injector with long nozzle needle
    CN104564472A (en) * 2014-12-31 2015-04-29 无锡威孚马山油泵油嘴有限公司 High-pressure common-rail type gasket

    Citations (5)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    EP0844385A1 (en) * 1996-11-21 1998-05-27 Denso Corporation Accumulator fuel injection apparatus for internal combustion engine
    US5890471A (en) * 1996-08-31 1999-04-06 Isuzu Motors Limited Fuel injection device for engines
    DE19827267A1 (en) * 1998-06-18 1999-12-23 Bosch Gmbh Robert Fuel injection valve for high pressure injection with improved control of the fuel supply
    DE19832826A1 (en) 1998-07-21 2000-01-27 Bosch Gmbh Robert Pre-control valve for fuel injection valve, with insert sector fixed in intended position on bath walls parallel to axis
    DE19859592C1 (en) * 1998-12-22 2000-05-04 Bosch Gmbh Robert Fuel injection valve for high pressure injection of fuel into the combustion chambers of internal combustion engines

    Patent Citations (5)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    US5890471A (en) * 1996-08-31 1999-04-06 Isuzu Motors Limited Fuel injection device for engines
    EP0844385A1 (en) * 1996-11-21 1998-05-27 Denso Corporation Accumulator fuel injection apparatus for internal combustion engine
    DE19827267A1 (en) * 1998-06-18 1999-12-23 Bosch Gmbh Robert Fuel injection valve for high pressure injection with improved control of the fuel supply
    DE19832826A1 (en) 1998-07-21 2000-01-27 Bosch Gmbh Robert Pre-control valve for fuel injection valve, with insert sector fixed in intended position on bath walls parallel to axis
    DE19859592C1 (en) * 1998-12-22 2000-05-04 Bosch Gmbh Robert Fuel injection valve for high pressure injection of fuel into the combustion chambers of internal combustion engines

    Cited By (5)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    WO2005035970A1 (en) * 2003-10-06 2005-04-21 Robert Bosch Gmbh Injection nozzle
    WO2008128881A1 (en) * 2007-04-19 2008-10-30 Robert Bosch Gmbh Area of intersection between a high-pressure chamber and a high-pressure duct
    US8245696B2 (en) 2007-04-19 2012-08-21 Robert Bosch Gmbh Area of intersection between a high-pressure chamber and a high-pressure duct
    DE102007050993A1 (en) 2007-10-25 2009-04-30 Robert Bosch Gmbh Fuel injector i.e. diesel injection device, for internal combustion engine, has pressure chamber formed between ring surface and ring-shaped shoulder, and inlet borehole diverting for control chamber by shoulder
    CN106181236A (en) * 2016-07-13 2016-12-07 无锡派乐科技有限公司 High-pressure co-rail pad and manufacture method thereof

    Also Published As

    Publication number Publication date
    DE10146743A1 (en) 2003-04-17
    EP1296054B1 (en) 2005-07-27
    JP2003120459A (en) 2003-04-23
    DE50203729D1 (en) 2005-09-01
    JP4184741B2 (en) 2008-11-19

    Similar Documents

    Publication Publication Date Title
    EP1485609B1 (en) Device for injecting fuel to stationary internal combustion engines
    DE3688753T2 (en) Control device for electro-hydraulically operated fuel injection valves.
    EP1030966B1 (en) Fuel injection valve for high-pressure injection with improved fuel supply control
    DE69636585T2 (en) fuel Injector
    EP0178427A2 (en) Electrically controlled fuel injection pump for internal combustion engines
    DE19709794A1 (en) Valve for controlling liquids
    DE10138756A1 (en) High-pressure fuel storage
    EP0889231B1 (en) Fuel injection system
    DE3523536A1 (en) Electrically controlled fuel injection pump for internal combustion engines
    EP1296054B1 (en) Injection valve for a combustion engine
    EP0910738A1 (en) Distributor fuel injection pump
    EP0688950A1 (en) Fuel injection system
    DE19860397A1 (en) Fuel injection device for internal combustion engines
    DE10131199A1 (en) Solenoid valve for controlling an injection valve of an internal combustion engine
    EP2084391B1 (en) Fuel injection valve device
    CH686845A5 (en) Control arrangement for an injection valve for internal combustion engines.
    EP1574701A1 (en) Common rail injector
    EP1309788B1 (en) Fuel injection valve
    DE102005054437A1 (en) Fuel injector controller with combined control of the initial injection pressure and the injection peak pressure
    EP1599670B1 (en) Blind hole and seat hole injection nozzle for an internal combustion engine, comprising a transition cone between the blind hole and the nozzle needle seat
    EP4077908B1 (en) Injection nozzle for injecting fuel under high pressure
    WO1999056015A1 (en) Fuel injection valve
    DE10254466B4 (en) Fuel injection valve
    EP0826878B1 (en) Fuel injector for internal combustion engines
    DE10147830A1 (en) Fuel injector, for an IC motor, has a high pressure fuel store in the housing between the control valve and the actuator and sealed off from the valve rod guide

    Legal Events

    Date Code Title Description
    PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

    Free format text: ORIGINAL CODE: 0009012

    AK Designated contracting states

    Kind code of ref document: A1

    Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SK TR

    AX Request for extension of the european patent

    Extension state: AL LT LV MK RO SI

    17P Request for examination filed

    Effective date: 20030926

    AKX Designation fees paid

    Designated state(s): DE FR GB

    17Q First examination report despatched

    Effective date: 20040322

    GRAP Despatch of communication of intention to grant a patent

    Free format text: ORIGINAL CODE: EPIDOSNIGR1

    GRAS Grant fee paid

    Free format text: ORIGINAL CODE: EPIDOSNIGR3

    GRAA (expected) grant

    Free format text: ORIGINAL CODE: 0009210

    AK Designated contracting states

    Kind code of ref document: B1

    Designated state(s): DE FR GB

    REG Reference to a national code

    Ref country code: GB

    Ref legal event code: FG4D

    Free format text: NOT ENGLISH

    REF Corresponds to:

    Ref document number: 50203729

    Country of ref document: DE

    Date of ref document: 20050901

    Kind code of ref document: P

    GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

    Effective date: 20051108

    ET Fr: translation filed
    PLBE No opposition filed within time limit

    Free format text: ORIGINAL CODE: 0009261

    STAA Information on the status of an ep patent application or granted ep patent

    Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

    26N No opposition filed

    Effective date: 20060428

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: GB

    Payment date: 20130823

    Year of fee payment: 12

    Ref country code: FR

    Payment date: 20130820

    Year of fee payment: 12

    GBPC Gb: european patent ceased through non-payment of renewal fee

    Effective date: 20140807

    REG Reference to a national code

    Ref country code: FR

    Ref legal event code: ST

    Effective date: 20150430

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: GB

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20140807

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: FR

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20140901

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: DE

    Payment date: 20161027

    Year of fee payment: 15

    REG Reference to a national code

    Ref country code: DE

    Ref legal event code: R119

    Ref document number: 50203729

    Country of ref document: DE

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: DE

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20180301