EP1109998A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1109998A1
EP1109998A1 EP00952881A EP00952881A EP1109998A1 EP 1109998 A1 EP1109998 A1 EP 1109998A1 EP 00952881 A EP00952881 A EP 00952881A EP 00952881 A EP00952881 A EP 00952881A EP 1109998 A1 EP1109998 A1 EP 1109998A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
closing
bore
injection 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.)
Granted
Application number
EP00952881A
Other languages
German (de)
French (fr)
Other versions
EP1109998B1 (en
Inventor
Detlev Potz
Günter LEWENTZ
Uwe Gordon
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 EP1109998A1 publication Critical patent/EP1109998A1/en
Application granted granted Critical
Publication of EP1109998B1 publication Critical patent/EP1109998B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F02M61/045—The valves being provided with fuel discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to a fuel injection valve for internal combustion engine machines, with a valve member which can be displaced axially outward in a bore of a valve body against the force of a closing spring and which has at its combustion-chamber end a valve head closing member projecting from the bore and on its side facing the valve body has a valve sealing surface with which it interacts with a valve seat surface arranged on the combustion-chamber end face of the valve body, and with at least one injection opening on the closing head originating from a pressure chamber, the outlet opening of which is covered by the valve body in the closed position of the valve member and is released during the outward opening stroke.
  • a nozzle that is, an outward opening to the combustion chamber
  • a nozzle that is, an outward opening to the combustion chamber
  • DE 196 18 698 AI Due to the system, the valve member is subjected to tension in the closing movement when the injection ends. Due to the closing spring and the combustion chamber gas pressure, high closing forces act during the closing movement. The high clamping forces can damage the affected components.
  • the object of the invention is to provide a fuel injection valve with an increased service life. In particular, the forces occurring in the closing movement should be reduced.
  • the object is in a fuel injection valve for internal combustion engines, with a valve member which can be displaced axially outwardly in a bore of a valve body against the force of a closing spring and which has at its combustion-chamber end a valve head closing member which projects out of the bore and which on its side faces the valve body Side has a valve sealing surface with which it interacts with a valve seat surface arranged on the combustion chamber end face of the valve body, and with at least one injection opening on the closing head originating from a pressure chamber, the outlet opening of which is covered by the valve body in the closed position of the valve member and is released during the outward opening stroke, solved in that a hydraulic closing damping device is integrated in the fuel injection valve.
  • the high closing forces that occur in the closing movement lead to high valve member speeds.
  • Valve element considerably reduced, since the damping of the valve element speed reduces the impulse and thus the impact that occurs when the valve sealing surface strikes the valve seat surface. This reduces the load on the entire valve seat that occurs during operation. It can also occur at high operating points Valve member closing speed leads to a so-called bouncing of the valve member on the valve seat surface, ie there is a brief reopening of the valve member. This reopening at the end of the spray is very damaging to the exhaust gas emissions. By damping the valve member movement shortly before the end of closing, the bounce tendency can be significantly reduced.
  • Valve member bears against the end face of a piston which is guided to move back and forth in a blind bore provided in a valve holding body, the longitudinal axis of which coincides with the longitudinal axis of the valve member.
  • the piston acts as a damping piston. The damping effect of the piston only occurs in the closing movement of the valve member, since there is no operative connection between the piston and the valve member during the opening stroke.
  • a further special embodiment of the invention is characterized in that the guidance of the piston in the valve holding body is milled to ensure a sealing guidance of the piston. This ensures that the hydraulic pressure builds up in front of the locking piston to dampen the movement.
  • Another particular embodiment of the invention is characterized in that the piston is biased by a return spring arranged in the blind bore. This ensures that the piston follows the valve member movement when opening and closing.
  • Hydraulic fluid especially oil, is filled.
  • Figure 1 shows a first embodiment
  • Figure 2 shows a second embodiment
  • Fuel injection valve has a valve body 1, which projects with its lower free end into the combustion chamber of the internal combustion engine to be supplied. With its upper end surface 3 remote from the combustion chamber, the valve body 1 is axially prestressed against a valve holding body 7 by means of a clamping nut 5.
  • the valve body 1 has an axial through bore 9, in which a piston-shaped valve member 11 is axially displaceably guided.
  • the valve member 11 has a closing head 13 protruding from the bore 9 and forming a valve closing member at its lower end on the combustion chamber side.
  • the closing head 13 On its side facing the valve body 1, the closing head 13 has a valve sealing surface 15, with which it engages with a face on the combustion chamber side
  • Valve body 1 arranged valve seat surface 17 cooperates.
  • An annular pressure chamber 19 is formed between the valve member 11 and the wall of the bore 9.
  • the pressure chamber 19 is delimited on the combustion chamber side by a diameter enlargement of the valve member 11 which forms an annular shoulder 21 and merges into the closing head 13.
  • Injection openings (not shown) lead from the annular shoulder 21, which are initially designed as a longitudinal bore, of which then at the level of the closing head Remove 13 cross holes.
  • the outlet openings of the injection openings on the wall of the valve member 11 are arranged such that they are covered by the bore wall 9 of the valve body 1 in the closed position of the valve member 11 and only when it is directed outwards
  • Opening stroke of the valve member 11 can be controlled by emerging from the bore 9.
  • valve member 11 protrudes with its shaft 27 into a spring chamber 29 provided in the holding body 7. To ensure a tight contact of the valve member 11 with the valve seat 17 when the injection valve is closed and for a return movement of the valve member 11, there is a closing spring 31 against an annular shoulder 33 formed on the valve member shaft 27 biased.
  • Fuel is supplied to the pressure chamber 19 of the injection valve via a pressure line 20 originating from a high-pressure source.
  • a free end 35 of the valve member shaft 27 is formed on the side of the ring shoulder 33 facing away from the combustion chamber.
  • the valve member end 35 is in abutment against a damper piston 37.
  • the damper piston 37 is received in a blind bore 39 such that it can be moved back and forth.
  • the damper piston 37 limited in the
  • the damping chamber 41 is connected to a return line 45 via a throttle bore 43.
  • the return line 45 is in turn connected to a relief space (not shown).
  • a return spring 47 is arranged in the damping space 41. The return spring 47 is biased against the damping piston 37.
  • FIG. 2 The second exemplary embodiment of the invention shown in FIG. 2 is similar to the first shown in FIG.
  • the throttle effect is not achieved by a throttle bore, but by a throttle cross section 49 formed on the damping piston 37. That is, the damping chamber 41 is connected via the throttle cross-section 49 to the return line 45, which in turn is connected to the relief chamber (not shown).
  • the course of movement of the valve member 11 can be controlled during injection.

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 invention relates to a fuel injection valve for internal combustion engines. Said fuel injection valve comprises a valve member (11) that can be axially outwardly displaced against the force of a closing spring (31) within a bore (9) of a valve body (1). At the combustion chamber end of said valve member a closing head (13) is provided that projects from the bore and that represents a valve closing member. On the side facing the valve body (1) the closing head comprises a valve stem surface (15) which it interacts with a valve face (17) that is located on the front face of the valve body (1) on the combustion chamber end. The valve further comprises at least one injection opening on the closing head which extends from the compression chamber (19). The outlet of said injection opening is covered by the valve body (1) in the closed position of the valve member (11) and is released during the outwardly directed opening stroke. In order to increase the service life of the inventive fuel injection valve a hydraulic valve closure dampening device (37, 39, 41, 43, 45, 47) is integrated into the fuel injection valve.

Description

KraftstoffeinspritzventilFuel injection valve
Stand der TechnikState of the art
Die Erfindung betrifft ein Kraftstoffeinspritzventil für Brεnnkrafcraaschinen, mit einem in einer Bohrung eines Ventilkörpers entgegen der Kraft einer Schließfeder axial nach außen verschiebbaren Ventilglied, das an seinem brennraumseitigen Ende einen aus der Bohrung ragenden, ein Ventilschließglied bildenden Schließkopf aufweist, der auf seiner dem Ventilkörpεr zugewandten Seite eine Ventildichtfläche aufweist, mit der er mit einer an der brennraumseitigen Stirnseite des Ventilkörpers angeordneten Ventilsitzflache zusammenwirkt, und mit wenigstens einer von einem Druckraum ausgehenden Einspritzöffnung am Schließkopf, deren Austrittsöffnung in Schließstellung des Ventilgliedes vom Ventilkörper abgedeckt und beim nach außen gerichteten Öffnungshub freigegeben wird.The invention relates to a fuel injection valve for internal combustion engine machines, with a valve member which can be displaced axially outward in a bore of a valve body against the force of a closing spring and which has at its combustion-chamber end a valve head closing member projecting from the bore and on its side facing the valve body has a valve sealing surface with which it interacts with a valve seat surface arranged on the combustion-chamber end face of the valve body, and with at least one injection opening on the closing head originating from a pressure chamber, the outlet opening of which is covered by the valve body in the closed position of the valve member and is released during the outward opening stroke.
Ein derartiges Kraftstoffeinspritzventil mit einer sog. A- Düse, also einer nach außen, zum Brennraum hin öffnenden Düse, ist aus der DE 196 18 698 AI bekannt. Systembedingt wird das Ventilglied bei Beendigung der Einspritzung in der Schließbewegung auf Zug beansprucht. Während der Schließbewegung wirken, bedingt durch die Schließfeder und den Brennraumgasdruck, hohe Schließkräfce . Die hohen Schließkräfte können zu Beschädigungen der betroffenen Bauteile führen. Aufgabe der Erfindung ist es, ein Kraftstoffeinspritzventil mit einer erhöhten Lebensdauer bereitzustellen. Insbesondere sollen die in der Schließbewegung auftretenden Kräfte reduziert werden.Such a fuel injection valve with a so-called. A nozzle, that is, an outward opening to the combustion chamber, is known from DE 196 18 698 AI. Due to the system, the valve member is subjected to tension in the closing movement when the injection ends. Due to the closing spring and the combustion chamber gas pressure, high closing forces act during the closing movement. The high clamping forces can damage the affected components. The object of the invention is to provide a fuel injection valve with an increased service life. In particular, the forces occurring in the closing movement should be reduced.
Die Aufgabe ist bei einem Kraftstoffeinspritzventil für Brennkraftmaschinen, mit einem in einer Bohrung eines Ventilkörpers entgegen der Kraft einer Schließfeder axial nach außen verschiebbaren Ventilglied, das an seinem brennraumseitigen Ende einen aus der Bohrung ragenden, ein Ventilschließglied bildenden Schließkopf aufweist, der auf seiner dem Ventilkörpεr zugewandten Seite eine Ventiidichtflache aufweist, mit der er mit einer an der brennraumseitigen Stirnseite des Ventilkörpers angeordneten Ventilsitzfläche zusammenwirkt, und mit wenigstens einer von einem Druckraum ausgehenden Einspritzöffnung am Schließkopf, deren Austrittsöffnung in Schließstellung des Ventilgliedes vom Ventilkörper abgedeckt und beim nach außen gerichteten Öffnungshub freigegeben wird, dadurch gelöst, dass eine hydraulische Schließdämpfungseinrichtung in das Kraftstoffeinspritzventil integriert ist. Die in der Schließbewegung auftretenden hohen Schließkräfte führen zu hohen Ventilgliedgeschwindigkeiten. Beim Auftreffen der Ventildichtfläche auf die "steife" Ventilsitzfläche werden die bewegten Massen schlagartig verzögert. Die hohen negativen Beschleunigungswerte und die Trägheit der bewegten Massen führen zu sehr großen Zugkräften in dem Vεntilglied. Die Zugkräfte können zu einem Bruch des Ventilgliedes führen. Durch die hydraulische Schließdämpfungseinrichtung wird die Zugbelastung in demThe object is in a fuel injection valve for internal combustion engines, with a valve member which can be displaced axially outwardly in a bore of a valve body against the force of a closing spring and which has at its combustion-chamber end a valve head closing member which projects out of the bore and which on its side faces the valve body Side has a valve sealing surface with which it interacts with a valve seat surface arranged on the combustion chamber end face of the valve body, and with at least one injection opening on the closing head originating from a pressure chamber, the outlet opening of which is covered by the valve body in the closed position of the valve member and is released during the outward opening stroke, solved in that a hydraulic closing damping device is integrated in the fuel injection valve. The high closing forces that occur in the closing movement lead to high valve member speeds. When the valve sealing surface hits the "rigid" valve seat surface, the moving masses are suddenly decelerated. The high negative acceleration values and the inertia of the moving masses lead to very large tensile forces in the valve member. The tensile forces can cause the valve member to break. Through the hydraulic closing damping device, the tensile load in the
Ventilglied erheblich reduziert, da durch die Dämpfung der Ventilgliedgeschwindigkeit der Impuls und somit der beim Auftreffen der Ventildichtfläche auf die Ventilsitzflache auftretende Stoß reduziert werden. Somit wird die im Betrieb auftretende Belastung für den ganzen Ventilsitz geringer. Außerdem kann es bei Betriebspunkten mit hoher Ventilgliedschließgeschwindigkeit zu einem sog. Prellen des Ventilgliedes an der Ventilsitzfläche kommen, d.h. es kommt zu einem kurzzeitigen Wiederöffnen des Ventilgliedes. Dieses Wiederöffnen bei Spritzende ist für die Abgasemissionen sehr schädlich. Durch die Dämpfung der Ventilgliedbewegung kurz vor Schließende kann die Prellerneigung deutlich verringert werden.Valve element considerably reduced, since the damping of the valve element speed reduces the impulse and thus the impact that occurs when the valve sealing surface strikes the valve seat surface. This reduces the load on the entire valve seat that occurs during operation. It can also occur at high operating points Valve member closing speed leads to a so-called bouncing of the valve member on the valve seat surface, ie there is a brief reopening of the valve member. This reopening at the end of the spray is very damaging to the exhaust gas emissions. By damping the valve member movement shortly before the end of closing, the bounce tendency can be significantly reduced.
Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass das brennraumferne Ende desA special embodiment of the invention is characterized in that the end remote from the combustion chamber
Ventilgliedes an der Stirnseite eines Kolbens anliegt, der in einer in einem Ventilhaltekörper vorgesehenen Sackbohrung hin- und herbewegbar geführt ist, deren Längsachse mit der Längsachse des Ventilgliedes zusammenfällt. Der Kolben wirkt als Dämpfungskolben. Die Dämpfungswirkung entfaltet der Kolben aber nur in der Schließbewegung des Ventilgliedes, da beim Öffnungshub keine Wirkverbindung zwischen dem Kolben und dem Ventilglied vorliegt.Valve member bears against the end face of a piston which is guided to move back and forth in a blind bore provided in a valve holding body, the longitudinal axis of which coincides with the longitudinal axis of the valve member. The piston acts as a damping piston. The damping effect of the piston only occurs in the closing movement of the valve member, since there is no operative connection between the piston and the valve member during the opening stroke.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Führung des Kolbens in dem Ventilhaltekörper paarungsgeschliffen ist, um eine dichtende Führung des Kolbens zu gewährleisten. Dadurch wird sichergestellt, dass sich der hydraulische Druck zur Dämpfung der Bewegung vor dem Schließkolben aufbaut.A further special embodiment of the invention is characterized in that the guidance of the piston in the valve holding body is milled to ensure a sealing guidance of the piston. This ensures that the hydraulic pressure builds up in front of the locking piston to dampen the movement.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Kolben durch eine in der Sackbohrung angeordnete Rückstellfeder vorgespannt ist. Dadurch wird erreicht, dass der Kolben beim Öffnen und Schließen der Ventilgliedbewegung folgt.Another particular embodiment of the invention is characterized in that the piston is biased by a return spring arranged in the blind bore. This ensures that the piston follows the valve member movement when opening and closing.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Sackbohrung mitAnother special embodiment of the invention is characterized in that the blind bore with
Hydraulikflüssigkeit , insbesondere Öl, befüllt ist. Das Hydraulic fluid, especially oil, is filled. The
In der Zeichnung zeigen:The drawing shows:
Figur 1 ein erstes Ausführungsbeispiel imFigure 1 shows a first embodiment in
Längsschnitt durch das Einspritzventil ; undLongitudinal section through the injection valve; and
Figur 2 ein zweites Ausführungsbeispiel imFigure 2 shows a second embodiment in
Längsschnitt durch das Einspritzventil.Longitudinal section through the injection valve.
Das in Figur 1 im Längsschnitt dargestellte erste Ausführungsbeispiel des erfindungsgemäßenThe first embodiment of the invention shown in longitudinal section in Figure 1
Kraftstoffeinspritzventils weist einen Ventilkörper 1 auf, der mit seinem unteren freien Ende in den Brennraum der zu versorgenden Brennkraftmaschine ragt. Mit seiner oberen brennraumfernen Stirnfläche 3 ist der Ventilkörper 1 mittels einer Spannmutter 5 axial gegen einen Ventilhaltekörper 7 vorgespannt. Der Ventilkörper 1 weist eine axiale Durchgangsbohrung 9 auf, in der ein kolbenförmiges Ventilglied 11 axial verschiebbar geführt ist. Das Ventilglied 11 weist an seinem brennraumseitigen unteren Ende einen aus der Bohrung 9 ragenden, ein Ventilschließglied bildenden Schließkopf 13 auf. Der Schließkopf 13 weist auf seiner dem Ventilkörper 1 zugewandten Seite eine Ventildichtfläche 15 auf, mit der er mit einer an der brennraumseitigen Stirnseite desFuel injection valve has a valve body 1, which projects with its lower free end into the combustion chamber of the internal combustion engine to be supplied. With its upper end surface 3 remote from the combustion chamber, the valve body 1 is axially prestressed against a valve holding body 7 by means of a clamping nut 5. The valve body 1 has an axial through bore 9, in which a piston-shaped valve member 11 is axially displaceably guided. The valve member 11 has a closing head 13 protruding from the bore 9 and forming a valve closing member at its lower end on the combustion chamber side. On its side facing the valve body 1, the closing head 13 has a valve sealing surface 15, with which it engages with a face on the combustion chamber side
Ventilkörpers 1 angeordneten Ventilsitzfläche 17 zusammenwirkt .Valve body 1 arranged valve seat surface 17 cooperates.
Zwischen dem Ventilglied 11 und der Wand der Bohrung 9 ist ein ringförmiger Druckraum 19 ausgebildet. Der Druckraum 19 ist brennraumseitig von einer eine Ringschulter 21 bildenden Durchmessererweiterung des Ventilglieds 11 begrenzt, die in den Schließkopf 13 übergeht. Dabei führen von der Ringschulter 21 (nicht dargestellte) Einspritzöffnungen ab, die zunächst als Längsbohrung ausgebildet sind, von denen dann in Höhe des Schließkopfes 13 Querbohrungen abführen. Die Austrittsöffnungen der Einspritzöffnungen an der Wand des Ventilgliedes 11 sind dabei so angeordnet, dass sie in Schließstellung des Ventilgliedes 11 von der Bohrungswand 9 des Ventilkörpers 1 abgedeckt sind und erst beim nach außen gerichtetenAn annular pressure chamber 19 is formed between the valve member 11 and the wall of the bore 9. The pressure chamber 19 is delimited on the combustion chamber side by a diameter enlargement of the valve member 11 which forms an annular shoulder 21 and merges into the closing head 13. Injection openings (not shown) lead from the annular shoulder 21, which are initially designed as a longitudinal bore, of which then at the level of the closing head Remove 13 cross holes. The outlet openings of the injection openings on the wall of the valve member 11 are arranged such that they are covered by the bore wall 9 of the valve body 1 in the closed position of the valve member 11 and only when it is directed outwards
Öffnungshub des Ventilgliedes 11 durch Austauchen aus der Bohrung 9 aufgesteuert werden.Opening stroke of the valve member 11 can be controlled by emerging from the bore 9.
Das Ventilglied 11 ragt mit seinem Schaft 27 in einen im Haltekörper 7 vorgesehenen Federraum 29. Zur Gewährleistung einer dichten Anlage des Ventilgliedes 11 am Ventilsitz 17 bei geschlossenem Einspritzventil und für eine Rückstellbewegung des Ventilgliedes 11 ist eine Schließfeder 31 gegen einen am Ventilgliedschaft 27 ausgebildeten Ringabsatz 33 vorgespannt. DieThe valve member 11 protrudes with its shaft 27 into a spring chamber 29 provided in the holding body 7. To ensure a tight contact of the valve member 11 with the valve seat 17 when the injection valve is closed and for a return movement of the valve member 11, there is a closing spring 31 against an annular shoulder 33 formed on the valve member shaft 27 biased. The
Kraftstoffzufuhr in den Druckraum 19 des Einspritzventils erfolgt über eine von einer Hochdruckquelle ausgehende Druckleitung 20.Fuel is supplied to the pressure chamber 19 of the injection valve via a pressure line 20 originating from a high-pressure source.
Auf der dem Brennraum abgewandten Seite des Ringabsatzes 33 ist ein freies Ende 35 des Ventilgliedschaftes 27 ausgebildet. Das Ventilgliedschaftsende 35 befindet sich in Anlage gegen einen Dämpferkolben 37. Der Dämpferkolben 37 ist hin- und herbewegbar in einer Sackbohrung 39 aufgenommen. Der Dämpferkolben 37 begrenzt in derA free end 35 of the valve member shaft 27 is formed on the side of the ring shoulder 33 facing away from the combustion chamber. The valve member end 35 is in abutment against a damper piston 37. The damper piston 37 is received in a blind bore 39 such that it can be moved back and forth. The damper piston 37 limited in the
Sackbohrung 39 einen Dämpfungsraum 41. Der Dämpfungsraum 41 steht über eine Drosselbohrung 43 mit einer Rücklaufleitung 45 in Verbindung. Die Rücklaufleitung 45 wiederum steht mit einem (nicht dargestellten) Entlastungsraum in Verbindung. Außerdem ist in dem Dämpfungsraum 41 eine Rückstellfeder 47 angeordnet. Die Rückstellfeder 47 ist gegen den Dämpfungskolben 37 vorgespannt.Blind bore 39 a damping chamber 41. The damping chamber 41 is connected to a return line 45 via a throttle bore 43. The return line 45 is in turn connected to a relief space (not shown). In addition, a return spring 47 is arranged in the damping space 41. The return spring 47 is biased against the damping piston 37.
Das in Figur 2 dargestellte zweite Ausführungsbeispiel der Erfindung ähnelt dem in Figur 1 dargestellten erstenThe second exemplary embodiment of the invention shown in FIG. 2 is similar to the first shown in FIG
Ausführungsbeispiel . Der Einfachheit halber werden deshalb zur Bezeichnung gleicher Teile dieselben Bezugszeichen verwendet. Um Wiederholungen zu vermeiden, wird zudem auf die vorstehende Beschreibung des erstenEmbodiment. Therefore, for the sake of simplicity the same reference numerals are used to designate the same parts. To avoid repetition, also refer to the description above of the first
Ausführungsbeispiels verwiesen. Im Folgenden wird nur auf die Unterschiede zwischen den beiden Ausführungsbeispielen eingegangen .Reference embodiment. Only the differences between the two exemplary embodiments are discussed below.
Bei dem in Figur 2 dargestellten zweiten Ausführungsbeispiel der Erfindung wird die Drosselwirkung nicht durch eine Drosselbohrung, sondern durch einen am Dämpfungskolben 37 ausgebildeten Drosselquerschnitt 49 erreicht. D.h., der Dämpfungsraum 41 ist über den Drosselquerschnitt 49 mit der Rücklaufleitung 45 verbunden, die wiederum mit dem (nicht dargestellten) Entlastungsraum in Verbindung steht .In the second exemplary embodiment of the invention shown in FIG. 2, the throttle effect is not achieved by a throttle bore, but by a throttle cross section 49 formed on the damping piston 37. That is, the damping chamber 41 is connected via the throttle cross-section 49 to the return line 45, which in turn is connected to the relief chamber (not shown).
Beiden Ausführungsbeispielen ist gemeinsam, dass die Schließbewegung des Ventilgliedes 11 gedämpft wird. Durch die in Figur 2 beispielhaft dargestellte gestufte Ausbildung des Drosselquerschnitts kann derIt is common to both exemplary embodiments that the closing movement of the valve member 11 is damped. Due to the stepped design of the throttle cross section shown as an example in FIG
Bewegungsverlauf des Ventilgliedes 11 beim Einspritzen gesteuert werden. The course of movement of the valve member 11 can be controlled during injection.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzventil für Brennkraftmaschinen, mit einem in einer Bohrung (9) eines Ventilkörpers (1) entgegen der Kraft einer Schließfeder (31) axial nach außen verschiebbaren Ventilglied (11) , das an seinem brennraumseitigen Ende einen aus der Bohrung ragenden, ein Ventilschließglied bildenden Schließkopf (13) aufweist, der auf seiner dem Ventilkörper (1) zugewandten Seite eine Ventildichtfläche (15) aufweist, mit der er mit einer an der brennraumseitigen Stirnseite des Ventilkörpers (1) angeordneten Ventilsitzfläche (17) zusammenwirkt, und mit wenigstens einer von einem Druckraum (19) ausgehenden1. Fuel injection valve for internal combustion engines, with a valve member (11) which can be displaced axially outwards against the force of a closing spring (31) in a bore (9) of a valve body (1) and which, at its end on the combustion chamber side, projects from the bore and forms a valve closing member Closing head (13), which on its side facing the valve body (1) has a valve sealing surface (15) with which it interacts with a valve seat surface (17) arranged on the end face of the valve body (1) on the combustion chamber, and with at least one of one Outgoing pressure chamber (19)
Einspritzöffnung am Schließkopf, deren Austrittsöffnung in Schließstellung des Ventilgliedes (11) vom Ventilkörper (1) abgedeckt und beim nach außen gerichteten Öffnungshub freigegeben wird, dadurch gekennzeichnet, dass eine hydraulische Schließdämpfungseinrichtung (37, 39, 41, 43, 45, 47, 49) in das Kraftstoffeinspritzventil integriert ist.Injection opening on the closing head, the outlet opening of which is covered by the valve body (1) in the closed position of the valve member (11) and is released during the outward opening stroke, characterized in that a hydraulic closing damping device (37, 39, 41, 43, 45, 47, 49) is integrated into the fuel injector.
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass das brennrau ferne Ende (35) des2. Fuel injection valve according to claim 1, characterized in that the distal end of the fusible end (35) of the
Ventilgliedes (11) an der Stirnseite eines Kolbens (37) anliegt, der in einer in einem Ventilhaltekörper (7) vorgesehenen Sackbohrung (39) hin- und herbewegbar geführt ist, deren Längsachse mit der Längsachse des Ventilgliedes (11) zusammenfällt. Valve member (11) abuts the end face of a piston (37) which is guided to and fro in a blind bore (39) provided in a valve holding body (7), the longitudinal axis of which coincides with the longitudinal axis of the valve member (11).
3. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass die Führung des Kolbens (37) in dem Ventilhaltekörper (7) paarungsgeschliffen ist.3. Fuel injection valve according to claim 2, characterized in that the guide of the piston (37) in the valve holding body (7) is mated.
4. Kraftstoffeinspritzventil nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass der Kolben (37) durch eine in der Sackbohrung (39) angeordnete Rückstellfeder (47) vorgespannt ist.4. Fuel injection valve according to claim 2 or 3, characterized in that the piston (37) is biased by a return spring (47) arranged in the blind bore (39).
5. Kraftstoffeinspritzventil nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass die Sackbohrung (39) mit Hydraulikflüssigkeit , insbesondere Öl, gefüllt ist.5. Fuel injection valve according to one of claims 2 to 4, characterized in that the blind bore (39) is filled with hydraulic fluid, in particular oil.
6. Kraftstoffeinspritzventil nach Anspruch 5, dadurch gekennzeichnet, dass der Innenraum der Sackbohrung (39) über eine Drossel (43, 49) mit einem Entlastungsraum in Verbindung steht.6. Fuel injection valve according to claim 5, characterized in that the interior of the blind bore (39) via a throttle (43, 49) is in communication with a relief chamber.
7. Kraftstoffeinspritzventil nach Anspruch 6 , dadurch gekennzeichnet, dass die Drossel von einer Drosselbohrung (39) in dem Ventilhaltekδrper (7) gebildet ist.7. The fuel injection valve according to claim 6, characterized in that the throttle is formed by a throttle bore (39) in the valve holder body (7).
8. Kraftstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, dass die Drossel durch Flächenanschliffe (49) an dem Kolben (37) gebildet ist . 8. Fuel injection valve according to claim 6, characterized in that the throttle is formed by surface grinding (49) on the piston (37).
EP00952881A 1999-07-02 2000-07-01 Fuel injection valve Expired - Lifetime EP1109998B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19930641 1999-07-02
DE19930641A DE19930641A1 (en) 1999-07-02 1999-07-02 Fuel injector
PCT/DE2000/002148 WO2001002717A1 (en) 1999-07-02 2000-07-01 Fuel injection valve

Publications (2)

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EP1109998A1 true EP1109998A1 (en) 2001-06-27
EP1109998B1 EP1109998B1 (en) 2005-08-10

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EP00952881A Expired - Lifetime EP1109998B1 (en) 1999-07-02 2000-07-01 Fuel injection valve

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EP (1) EP1109998B1 (en)
JP (1) JP2003530503A (en)
CN (1) CN1316036A (en)
BR (1) BR0006887A (en)
DE (2) DE19930641A1 (en)
WO (1) WO2001002717A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10240879A1 (en) * 2002-09-04 2004-03-18 Robert Bosch Gmbh Fuel injector for injection system for internal combustion engines has injection valve component guided in central bore of injector body inside pair-ground section, and valve element closing central bore is in disc-form
DE10323562A1 (en) * 2003-05-26 2004-12-30 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
DE102004054589B4 (en) * 2004-11-11 2008-09-11 Continental Automotive Gmbh Control valve and injector
JP2006161563A (en) 2004-12-02 2006-06-22 Honda Motor Co Ltd Piston for internal combustion engine
DE102008032133B4 (en) * 2008-07-08 2015-08-20 Continental Automotive Gmbh Fuel injector
CN101592108B (en) * 2009-04-24 2012-05-23 靳北彪 Valve head outer displacement fuel injector for engine
DE102014200757A1 (en) * 2014-01-17 2015-07-23 Robert Bosch Gmbh Gas injector for direct injection of gaseous fuel into a combustion chamber
CN106391593B (en) * 2016-12-10 2019-04-12 无锡银联齿轮传动机械有限公司 The toilet seat of handle pipe cleaning before copper plating machine
CN109253005B (en) * 2017-07-12 2022-08-05 罗伯特·博世有限公司 Oil inlet valve for high-pressure oil pump and corresponding high-pressure oil pump

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DE19618698A1 (en) * 1996-05-09 1997-11-13 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE19642440A1 (en) * 1996-10-15 1998-04-16 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
GB2339451A (en) * 1998-07-10 2000-01-26 Lucas Ind Plc A fuel injector with control chamber and a damped needle valve

Non-Patent Citations (1)

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Title
See references of WO0102717A1 *

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DE50010916D1 (en) 2005-09-15
JP2003530503A (en) 2003-10-14
BR0006887A (en) 2001-06-12
WO2001002717A1 (en) 2001-01-11
DE19930641A1 (en) 2001-01-11
CN1316036A (en) 2001-10-03
EP1109998B1 (en) 2005-08-10

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