EP1339968A1 - Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines - Google Patents

Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines

Info

Publication number
EP1339968A1
EP1339968A1 EP01997636A EP01997636A EP1339968A1 EP 1339968 A1 EP1339968 A1 EP 1339968A1 EP 01997636 A EP01997636 A EP 01997636A EP 01997636 A EP01997636 A EP 01997636A EP 1339968 A1 EP1339968 A1 EP 1339968A1
Authority
EP
European Patent Office
Prior art keywords
low
solenoid valve
pressure
electromagnetic valve
fuel injection
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
EP01997636A
Other languages
German (de)
French (fr)
Other versions
EP1339968B1 (en
Inventor
Peter Boehland
Andreas Sterr
Andreas Dutt
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 EP1339968A1 publication Critical patent/EP1339968A1/en
Application granted granted Critical
Publication of EP1339968B1 publication Critical patent/EP1339968B1/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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • F02M41/1411—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically

Definitions

  • the invention relates to a solenoid valve-controlled fuel injection pump according to the preamble of claim 1.
  • valve in particular those fuel injection pumps of the distributor type in which a so-called I-solenoid valve is used.
  • This type of valve is characterized by the fact that the flow is directed radially from the outside inwards when the valve is turned off. An opening (positive) force is achieved by the flow deflection in the low pressure range. The force shortens the valve opening times.
  • a basic characteristic of the valve type in question can be seen in the fact that there is a very large low-pressure area in comparison to the pressure step area in the high-pressure area of the solenoid valve. For this reason, relatively large forces occur even with slight pressure fluctuations in the low pressure range. These forces cause opening time fluctuations, which lead to scattered injection quantities (from stroke to stroke).
  • a low-pressure compensation piston is provided in the valve type in question, which cooperates with the solenoid valve.
  • the low-pressure compensation piston therefore has the function of causing the solenoid valve to open in a stable manner.
  • DE 4339948 A1 which relates to a generic fuel injection pump.
  • the low-pressure compensation piston is made in one piece with the solenoid valve needle and is arranged coaxially with it, whereby it practically forms a continuation of the solenoid valve needle beyond the valve seat.
  • the disadvantage is that there is a flow deflection on the low-pressure compensating piston during shutdown. This flow deflection causes an increase in pressure, which results in a closing needle force. The disadvantageous consequence is a delay in the opening of the solenoid valve during shutdown.
  • the object of the present invention is to take suitable measures to avoid undesirable delays in the opening process of the solenoid valve.
  • the invention is illustrated in the drawing using an exemplary embodiment which is described in detail below.
  • the drawing shows - in vertical longitudinal section and partially - an embodiment of a fuel injection pump of the distributor type.
  • a (not shown) pump work space is connected via a pressure channel 11 in the distributor 10 to a distributor groove 12 on the circumference of the distributor 10, from which (not shown) injection lines running in the pump housing take their exit. The injection lines in turn lead to an injection valve (also not shown).
  • a connecting channel 14 extends from the distributor groove 12 in the interior of the distributor 10 and opens into an annular groove 15.
  • the annular groove 15 forms a valve seat 16 for a valve needle 17 of a (only partially shown) solenoid valve designated overall by 18.
  • valve seat 16 Below the valve seat 16 there extends a blind hole, generally numbered 20, which has an extension 21, from which a (further) connecting channel 22 begins.
  • the connecting channel 22 leads to the (not shown) low-pressure part of the fuel injection pump.
  • the valve seat 16 and the solenoid valve needle 17 thus define a high-pressure region 14, 15 and a low-pressure region 21 within the distributor 10.
  • a low-pressure compensating piston is axially movable, which - in each case half - has a total of 24 on the left-hand side of a common longitudinal central axis 23 of the solenoid-valve needle 17 and the low-pressure compensating piston, and a total of 25 on the right-hand side is.
  • the type 25 of the low-pressure compensating piston drawn on the right-hand side by the longitudinal central axis 23 marks the previous state of the art, the low-pressure compensating piston 25 - at 26 - being connected in one piece to the solenoid valve needle 17.
  • the low-pressure compensation piston 24 shown on the left-hand side of the longitudinal central axis 23 (in half) is the type according to the invention.
  • the special feature here is that the solenoid valve needle 17 and the low-pressure compensating piston 24 are designed as two separate and thus independently (axially) movable components.
  • the low-pressure compensation piston 24 has a piston rod 27 with a tapered diameter, which engages in a guide bore 28 made in the solenoid valve needle 17.
  • the guide 27/28 effectively (otherwise possible) tilting of the low-pressure compensating piston 24 is avoided.
  • the guide bore 28 is provided as SA. cklochbohrung formed, with its (upper) end 29 acts as a stop which cooperates with the free end 30 of the piston rod 27 of the low-pressure compensating piston 24.
  • low-pressure compensating spring 32 On a rear end face 31 of the low-pressure compensating piston 24, there is a compression spring (low-pressure compensating spring) 32, which is supported on the rear at the bottom of the blind bore 20, which is numbered 33.
  • the low-pressure compensating piston 24 is pressed against the (upper) stop 29 of the guide bore 28 by the low-pressure compensating spring 32.
  • a rod-shaped counter-stop 34 surrounded by the low-pressure compensating spring 32, is arranged, which at its end 35 with the (lower) stroke stop for the low pressure Compensating piston 24 acting bottom 33 of the blind bore 20 cooperates.
  • the rod-shaped counter stop 34 also serves at the same time to protect the low-pressure compensating spring 32.

Landscapes

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

Abstract

An electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines, comprises an electromagnetic valve (18) whose valve needle (17), via a valve seat (16) located inside the pump body, disconnects a high-pressure area (14, 15) from a low-pressure area (21) or connects the high-pressure and low-pressure areas, whereby the duration of injection is controlled by the opening of the electromagnetic valve (18). In addition, a low-pressure compensating plunger (24), which is arranged inside the low-pressure area (21), is provided for compensating for variations in pressure inside this low-pressure area (21). The invention is characterized in that the low-pressure compensating plunger (24), which is arranged coaxial to the electromagnetic valve needle (17), is provided as a component that is separate from the electromagnetic valve needle (17). This ensures an unimpeded and thus fastest possible opening of the electromagnetic valve (18) by the opening force that the electromagnet exerts upon the electromagnetic valve needle (17).

Description

Maqnetventilqesteuerte Kraftstoffeinspritzpumpe für Brennkraftmaschinen, insbesondere DieselmotorenMagnetic valve controlled fuel injection pump for internal combustion engines, in particular diesel engines
Stand der TechnikState of the art
Die Erfindung bezieht sich auf eine magnetventilgesteuerte Kraftstoffeinsp ritzpumpe nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a solenoid valve-controlled fuel injection pump according to the preamble of claim 1.
Hierbei handelt es sich vornehmlich um eine Kraftstoffeinspritzpumpe der sogenannten Verteilerbauart. Bei derartigen magnetventilgesteuerten Einspritz- pumpen, die bevorzugt in Dieselmotoren eingesetzt werden, wird die Einspritzdauer durch das Öffnen des Magnetventils gesteuert. Damit der Dieselmotor gute Abgaswerte erreicht, muß der Druck in der Leitung möglichst schnell abfallen. Dies kann nur durch ein schnell öffnendes Magnetventil erreicht werden. Eine magnetventilgesteuerte Voreinspritzung ist nur mit einem schnell öffnenden Magnetventil möglich. Das Magnetventil muß daher so ausgeführt werden, dass sich seine Öffnungszeit durch hydraulische Kräfte verringern läßt.This is primarily a so-called distributor type fuel injection pump. In such solenoid valve-controlled injection pumps, which are preferably used in diesel engines, the injection duration is controlled by opening the solenoid valve. In order for the diesel engine to achieve good exhaust gas values, the pressure in the line must drop as quickly as possible. This can only be achieved by a quick opening solenoid valve. Pre-injection controlled by a solenoid valve is only possible with a quick-opening solenoid valve. The solenoid valve must therefore be designed so that its opening time can be reduced by hydraulic forces.
Erfindungsgemäß relevant sind insbesondere solche Kraftstoffeinspritzpumpen der Verteilerbauart, in denen ein sogenanntes I-Magnetventil eingesetzt wird. Diese Ventilbauart zeichnet sich dadurch aus, dass die Strömung beim Absteuern radial von aussen nach innen gerichtet ist. Durch die Strömungsumlenkung im Niederdruckbereich wird eine öffnende (positive) Kraft erzielt. Die Kraft verkürzt die Ventilöffnungszeiten. Ein Grundcharakteristikum der in Rede stehenden Ventilbauart ist darin zu sehen, dass sich eine sehr große Niederdruckfläche im Vergleich zur Druckstufenfläche im Hochdruckbereich des Magnetventils ergibt. Deshalb treten schon bei geringen Druckschwankungen im Niederdruckbereich verhältnismäßig große Kräfte auf. Diese Kräfte verursachen Öffnungszeitschwankungen, die zu Einspritzmengenstreuungen (von Hub zu Hub) führen. Um die genannten Kräfte - wenigstens teilweise - zu kompensieren und damit ihre nachteiligen Auswirkungen weitgehend zu vermeiden, ist bei der in Rede stehenden Ventilbauart ein Niederdruckausgleichskolben vorgesehen, der mit dem Magnetventil zusammenwirkt. Der Nieder- druckausgleichskolben hat also die Funktion, ein stabiles Öffnungsverhalten des Magnetventils zu bewirken.Relevant according to the invention are in particular those fuel injection pumps of the distributor type in which a so-called I-solenoid valve is used. This type of valve is characterized by the fact that the flow is directed radially from the outside inwards when the valve is turned off. An opening (positive) force is achieved by the flow deflection in the low pressure range. The force shortens the valve opening times. A basic characteristic of the valve type in question can be seen in the fact that there is a very large low-pressure area in comparison to the pressure step area in the high-pressure area of the solenoid valve. For this reason, relatively large forces occur even with slight pressure fluctuations in the low pressure range. These forces cause opening time fluctuations, which lead to scattered injection quantities (from stroke to stroke). In order to compensate for the forces mentioned - at least partially - and thus largely avoid their adverse effects, a low-pressure compensation piston is provided in the valve type in question, which cooperates with the solenoid valve. The low-pressure compensation piston therefore has the function of causing the solenoid valve to open in a stable manner.
Zu dem im Vorstehenden geschilderten Stand der Technik wird die DE 4339948 A1 genannt, die eine gattungsmäßige Kraftstoffeinspritzpumpe zum Gegenstand hat. Bei der bekannten Kraftstoffeinspritzpumpe ist der Niederdruck-Ausgleichskolben einteilig mit der Magnetventilnadel ausgeführt und koaxial zu dieser angeordnet, wobei er praktisch eine Fortsetzung der Magnetventilnadel über den Ventilsitz hinaus bildet.Regarding the prior art described above, DE 4339948 A1 is mentioned, which relates to a generic fuel injection pump. In the known fuel injection pump, the low-pressure compensation piston is made in one piece with the solenoid valve needle and is arranged coaxially with it, whereby it practically forms a continuation of the solenoid valve needle beyond the valve seat.
Der Nachteil besteht darin, dass es beim Absteuern zu einer Strömungsumlenkung auf dem Niederdruck-Ausgleichskolben kommt. Diese Strömungsumlenkung bewirkt eine Druckerhöhung, aus der sich eine schließende Nadelkraft ergibt. Die nachteilige Folge ist eine Verzögerung der Öffnung des Magnetventils beim Absteuern.The disadvantage is that there is a flow deflection on the low-pressure compensating piston during shutdown. This flow deflection causes an increase in pressure, which results in a closing needle force. The disadvantageous consequence is a delay in the opening of the solenoid valve during shutdown.
Aufgabe der vorliegenden Erfindung ist es, geeignete Maßnahmen dafür zu treffen, dass unerwünschte Verzögerungen beim Öffnungsvorgang des Magnetventils vermieden werden. Vorteile der ErfindungThe object of the present invention is to take suitable measures to avoid undesirable delays in the opening process of the solenoid valve. Advantages of the invention
Gemäß der Erfindung wird die Aufgabe bei einer Kraftstoffeinspritzpumpe der eingangs bezeichneten Art durch die kennzeichnenden Merkmale des Patent- anspruchs 1 gelöst.According to the invention, the object is achieved in a fuel injection pump of the type described at the outset by the characterizing features of patent claim 1.
Vorteilhafte Weiterbildungen des Grundgedankens der Erfindung sind den Patentansprüchen 2 - 8 zu entnehmen.Advantageous further developments of the basic idea of the invention can be found in patent claims 2-8.
Durch die erfindungsgemäßen Merkmale gelingt es, die für die Funktion des Magnetventils in dessen geschlossenem Zustand wichtigen Vorteile des vorhandenen Niederdruck-Ausgleichskolbens zu erhalten. Zugleich entfallen aber die bisherigen negativen Wirkungen des Niederdruck-Ausgleichskolbens beim Öffnen des Magnetventils.The features of the invention make it possible to obtain the advantages of the existing low-pressure compensating piston which are important for the function of the solenoid valve in its closed state. At the same time, however, the previous negative effects of the low-pressure compensation piston when opening the solenoid valve are no longer present.
Zeichnungdrawing
Die Erfindung ist in der Zeichnung anhand eines Ausführungsbeispiels veranschaulicht, das im Folgenden detailliert beschrieben wird. Die Zeichnung zeigt - im vertikalen Längsschnitt und teilweise - eine Ausführungsform einer Kraftstoffeinspritzpumpe der Verteilerbauart.The invention is illustrated in the drawing using an exemplary embodiment which is described in detail below. The drawing shows - in vertical longitudinal section and partially - an embodiment of a fuel injection pump of the distributor type.
Beschreibung des AusführunqsbeispielsDescription of the execution example
Es bezeichnet 10 einen Verteiler, der in einem (nicht dargestellten) Pumpengehäuse in bekannter und daher nicht näher gezeigter Weise geführt ist. Der Antrieb des Verteilers 10 erfolgt ebenfalls in üblicher weise, weshalb auch diesbezüglich auf eine detaillierte Beschreibung verzichtet werden kann. Ein (nicht dargestellter) Pumpenarbeitsraum ist über einen Druckkanal 11 im Verteiler 10 mit einer Verteilernut 12 am Umfang des Verteilers 10 verbunden, von der (nicht gezeigte) im Pumpengehäuse verlaufende Einspritzleitungen ihren Ausgang nehmen. Die Einspritzleitungen führen wiederum zu einem (eben- falls nicht gezeigten) Einspritzventil.It designates 10 a distributor which is guided in a pump housing (not shown) in a known and therefore not shown manner. The distributor 10 is also driven in a conventional manner, which is why a detailed description can also be dispensed with in this regard. A (not shown) pump work space is connected via a pressure channel 11 in the distributor 10 to a distributor groove 12 on the circumference of the distributor 10, from which (not shown) injection lines running in the pump housing take their exit. The injection lines in turn lead to an injection valve (also not shown).
Des Weiteren geht von der Verteilernut 12 im Inneren des Verteilers 10 ein Verbindungskanal 14 aus, der in eine Ringnut 15 mündet. Die Ringnut 15 bildet einen Ventilsitz 16 für eine Ventilnadel 17 eines (nur teilweise dargestellten) insgesamt mit 18 bezeichneten Magnetventils. Oberhalb der Magnetventilnadel 17, bei 19, schließt sich ein das Magnetventil 18 betätigender Elektromagnet an, der bekannter Stand der Technik ist, weshalb eine detaillierte Darstellung entfallen kann.Furthermore, a connecting channel 14 extends from the distributor groove 12 in the interior of the distributor 10 and opens into an annular groove 15. The annular groove 15 forms a valve seat 16 for a valve needle 17 of a (only partially shown) solenoid valve designated overall by 18. Above the solenoid valve needle 17, at 19, there is an electromagnet which actuates the solenoid valve 18 and which is known prior art, for which reason a detailed illustration can be omitted.
Unterhalb des Ventilsitzes 16 erstreckt sich eine insgesamt mit 20 bezifferte Sacklochbohrung, die eine Erweiterung 21 aufweist, von der ein (weiterer) Verbindungskanal 22 seinen Ausgang nimmt. Der Verbindungskanal 22 führt zum (nicht dargestellten) Niederdruckteil der Kraftstoffeinspritzpumpe. Somit definieren Ventilsitz 16 und Magnetventilnadel 17 innerhalb des Verteilers 10 einen Hochdruckbereich 14, 15 und einen Niederdruckbereich 21.Below the valve seat 16 there extends a blind hole, generally numbered 20, which has an extension 21, from which a (further) connecting channel 22 begins. The connecting channel 22 leads to the (not shown) low-pressure part of the fuel injection pump. The valve seat 16 and the solenoid valve needle 17 thus define a high-pressure region 14, 15 and a low-pressure region 21 within the distributor 10.
Innerhalb der Sacklochbohrung 20 und koaxial zu der Magnetventilnadel 17 ist ein Niederdruck-Ausgleichskolben axial beweglich angeordnet, der - jeweils hälftig - linksseitig einer gemeinsamen Längsmittelachse 23 von Magnetventil- nadel 17 und Niederdruck-Ausgleichskolben insgesamt mit 24 und rechtsseitig der Längsmittelachse 23 insgesamt mit 25 beziffert ist. Die rechtsseitig von der Längsmittelachse 23 gezeichnete Bauart 25 des Niederdruck-Ausgleichskolbens markiert den bisherigen Stand der Technik, wobei der Niederdruck-Ausgleichskolben 25 - bei 26 - einstückig mit der Magnetventilnadel 17 verbunden ist.Within the blind bore 20 and coaxially to the solenoid valve needle 17, a low-pressure compensating piston is axially movable, which - in each case half - has a total of 24 on the left-hand side of a common longitudinal central axis 23 of the solenoid-valve needle 17 and the low-pressure compensating piston, and a total of 25 on the right-hand side is. The type 25 of the low-pressure compensating piston drawn on the right-hand side by the longitudinal central axis 23 marks the previous state of the art, the low-pressure compensating piston 25 - at 26 - being connected in one piece to the solenoid valve needle 17.
Dagegen handelt es sich bei dem linksseitig der Längsmittelachse 23 (hälftig) dargestellten Niederdruck-Ausgleichskolben 24 um die erfindungsgemäße Bauart. Die Besonderheit besteht hier darin, dass Magnetventilnadel 17 und Niederdruck-Ausgleichskolben 24 als zwei getrennte und damit unabhängig voneinander (axial) bewegliche Bauteile ausgebildet sind. Zur Führung des Niederdruck-Ausgleichskolbens 24 weist dieser eine Kolbenstange 27 verjüngten Durchmessers auf, die in eine in die Magnetventilnadel 17 eingebrachte Führungsbohrung 28 eingreift. Durch die Führung 27/28 wird ein (andernfalls mögliches) Kippen des Niederdruck-Ausgleichskolbens 24 wirksam vermieden. Die Führungsbohrung 28 ist als Sa.cklochbohrung ausgebildet, wobei ihr (oberes) Ende 29 als Anschlag fungiert, der mit dem freien Ende 30 der Kolbenstange 27 des Niederdruck-Ausgleichskolbens 24 zusammenwirkt.In contrast, the low-pressure compensation piston 24 shown on the left-hand side of the longitudinal central axis 23 (in half) is the type according to the invention. The special feature here is that the solenoid valve needle 17 and the low-pressure compensating piston 24 are designed as two separate and thus independently (axially) movable components. To guide the low-pressure compensation piston 24, the latter has a piston rod 27 with a tapered diameter, which engages in a guide bore 28 made in the solenoid valve needle 17. The guide 27/28 effectively (otherwise possible) tilting of the low-pressure compensating piston 24 is avoided. The guide bore 28 is provided as SA. cklochbohrung formed, with its (upper) end 29 acts as a stop which cooperates with the free end 30 of the piston rod 27 of the low-pressure compensating piston 24.
An einer rückwärtigen Stirnfläche 31 des Niederdruck-Ausgleichskolbens 24 liegt eine Druckfeder (Niederdruck-Ausgleichsfeder) 32 an, die sich rückwärtig an dem mit 33 bezifferten Boden der Sacklochbohrung 20 abstützt. Durch die Niederdruck-Ausgleichsfeder 32 wird der Niederdruck-Ausgleichskolben 24 gegen den (oberen) Anschlag 29 der Führungsbohrung 28 gedrückt.On a rear end face 31 of the low-pressure compensating piston 24, there is a compression spring (low-pressure compensating spring) 32, which is supported on the rear at the bottom of the blind bore 20, which is numbered 33. The low-pressure compensating piston 24 is pressed against the (upper) stop 29 of the guide bore 28 by the low-pressure compensating spring 32.
Eine weitere Besonderheit besteht darin, dass an der (unteren) Stirnfläche 31 des Niederdruck-Ausgleichskolbens 24 ein stangenförmiger, von der Niederdruck-Ausgleichsfeder 32 umgebener Gegenanschlag 34 angeordnet ist, der an seinem Ende 35 mit dem zugleich als (unterer) Hubanschlag für den Niederdruck-Ausgleichskolben 24 fungierenden Boden 33 der Sackloch- bohrung 20 zusammenwirkt. Der stangenförmige Gegenanschlag 34 dient auch gleichzeitig zum Schutz der Niederdruck-Ausgleichsfeder 32. Die beschriebene Anordnung und Ausbildung des Niederdruck-Ausgleichskolbens 24 wirkt sich im Betrieb der Kraftstoffeinspritzpumpe wie folgt aus.Another special feature is that on the (lower) end face 31 of the low-pressure compensating piston 24 a rod-shaped counter-stop 34, surrounded by the low-pressure compensating spring 32, is arranged, which at its end 35 with the (lower) stroke stop for the low pressure Compensating piston 24 acting bottom 33 of the blind bore 20 cooperates. The rod-shaped counter stop 34 also serves at the same time to protect the low-pressure compensating spring 32. The described arrangement and design of the low-pressure compensating piston 24 has the following effects during operation of the fuel injection pump.
Beim Öffnen des Magnetventils 18 wird der Druck im Hochdruckbereich 14, 15 über den Ventilsitz 16 abgebaut. Es kommt zu einer lokalen Druckerhöhung auf der Magnetventilnadel 17 und dem Niederdruck-Ausgleichskolben 24. Der Niederdruck-Ausgleichskolben 24 trennt sich nun von der Magnetventilnadel 17. Die in Schließrichtung gerichtete Niederdruck-Ausgleichskolbenkraft wird über den Hubanschlag 33, 34, 35 am Verteilergehäuse 10 abgestützt. Die Magnet- Ventilkraft führt zu einem schnellen Öffnen des Magnetventils 18.When the solenoid valve 18 is opened, the pressure in the high-pressure region 14, 15 is reduced via the valve seat 16. There is a local pressure increase on the solenoid valve needle 17 and the low pressure compensating piston 24. The low pressure compensating piston 24 now separates from the solenoid valve needle 17. The low pressure compensating piston force directed in the closing direction is supported on the distributor housing 10 via the stroke stop 33, 34, 35 , The solenoid valve force causes the solenoid valve 18 to open quickly.
Die auf den Niederdruck-Ausgleichskolben 24 aufgeübten hydraulischen Kräfte, welche bei der bisherigen einstückigen Ausbildung von Magnetventilnadel und Niederdruck-Ausgleichskolben nachteiligerweise in Schließrichtung der Magnetventilnadel wirkten, entfallen somit durch die erfindungsgemäße Separatausbildung von Magnetventilnadel 17 einerseits und Niederdruck-Ausgleichskolben 24 andererseits. Die vom Elektromagneten 19 auf die Magnetventilnadel 17 ausgeübte Öffnungskraft hat somit ein ungehindertes und damit schnellstmögliches Öffnen des Magnetventils 18 zur gewünschten Folge. The hydraulic forces exerted on the low-pressure compensating piston 24, which in the previous one-piece design of the solenoid valve needle and low-pressure compensating piston disadvantageously acted in the closing direction of the solenoid valve needle, are thus eliminated by the inventive design of the solenoid valve needle 17 on the one hand and the low-pressure compensating piston 24 on the other hand. The opening force exerted by the electromagnet 19 on the solenoid valve needle 17 thus has the desired result in an unimpeded and thus fastest opening of the solenoid valve 18.

Claims

4. Magnetventilgesteuerte Kraftstoffeinspritzpumpe nach Anspruch 1 , 2 oder 3, dadurch gekennzeichnet, dass der Niederdruck-Ausgleichskolben (24) an seinem dem Magnetventil (18) zugewandten Ende eine Kolbenstange (27) besitzt, die in eine im Bereich des Magnetventilsitzes (16) in die Magnet- ventilnadel (17) eingebrachte Führungsbohrung (28) hineinragt, die zur Führung des Niederdruck-Ausgleichskolbens (24) dient.4. Solenoid valve-controlled fuel injection pump according to claim 1, 2 or 3, characterized in that the low-pressure compensating piston (24) at its end facing the solenoid valve (18) has a piston rod (27) which in one in the region of the solenoid valve seat (16) in the solenoid valve needle (17) protrudes into the guide bore (28) which serves to guide the low-pressure compensation piston (24).
5. Magnetventilgesteuerte Kraftstoffeinspritzpumpe nach Anspruch 4, dadurch gekennzeichnet, dass die Führungsbohrung (28) einen Anschlag (29) für die Kolbenstange (27) und damit für den Niederdruck-Ausgieichskolben (24) aufweist.5. Solenoid valve-controlled fuel injection pump according to claim 4, characterized in that the guide bore (28) has a stop (29) for the piston rod (27) and thus for the low-pressure compensating piston (24).
6. Magnetventilgesteuerte Kraftstoffeinspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, dass der Niederdruck-Ausgleichskolben (24) unabhängig von der Magnetventilnadel (17) im Niederdruck-Ausgleichskolbenraum (20) geführt ist.6. Solenoid valve-controlled fuel injection pump according to claim 2, characterized in that the low-pressure compensation piston (24) is guided independently of the solenoid valve needle (17) in the low-pressure compensation piston chamber (20).
7. Magnetventilgesteuerte Kraftstoffeinspritzpumpe nach Anspruch 6, dadurch gekennzeichnet, dass der Niederdruck-Ausgleichskolben (24) durch Huban- schlag (33) und Gegenanschlag (34) im Pumpenkörper (10) axial geführt ist.7. Solenoid valve-controlled fuel injection pump according to claim 6, characterized in that the low-pressure compensating piston (24) is axially guided by the stroke stop (33) and counter-stop (34) in the pump body (10).
8. Magnetventilgesteuerte Kraftstoffeinspritzpumpe nach einem oder mehreren der Ansprüche 5 - 7, dadurch gekennzeichnet, dass die Niederdruck-Ausgleichsfeder (32) so ausgelegt ist, dass bei geschlossenem Magnetventil (18) die Kolbenstange (27) des Niederdruck-Ausgleichskolbens (24) durch die Kraft der Niederdruck-Ausgleichsfeder (32) am Anschlag (29) in der Führungsbohrung (28) zur Anlage kommt. 8. Solenoid valve-controlled fuel injection pump according to one or more of claims 5-7, characterized in that the low-pressure compensating spring (32) is designed such that when the solenoid valve (18) is closed, the piston rod (27) of the low-pressure compensating piston (24) by the The force of the low pressure compensation spring (32) comes to rest against the stop (29) in the guide bore (28).
EP01997636A 2000-11-23 2001-11-16 Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines Expired - Lifetime EP1339968B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10058011 2000-11-23
DE10058011A DE10058011A1 (en) 2000-11-23 2000-11-23 Solenoid valve controlled fuel injection pump for internal combustion engines, in particular diesel engines
PCT/DE2001/004319 WO2002042634A1 (en) 2000-11-23 2001-11-16 Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines

Publications (2)

Publication Number Publication Date
EP1339968A1 true EP1339968A1 (en) 2003-09-03
EP1339968B1 EP1339968B1 (en) 2005-06-22

Family

ID=7664285

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01997636A Expired - Lifetime EP1339968B1 (en) 2000-11-23 2001-11-16 Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines

Country Status (6)

Country Link
US (1) US6884041B2 (en)
EP (1) EP1339968B1 (en)
JP (1) JP2004514824A (en)
DE (2) DE10058011A1 (en)
ES (1) ES2243599T3 (en)
WO (1) WO2002042634A1 (en)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5215449A (en) * 1991-12-05 1993-06-01 Stanadyne Automotive Corp. Distributor type fuel injection pump
DE4323683A1 (en) * 1993-07-15 1995-01-19 Bosch Gmbh Robert Fuel injection pump
DE4339948A1 (en) * 1993-11-24 1995-06-01 Bosch Gmbh Robert Fuel injection pump
US5954487A (en) * 1995-06-23 1999-09-21 Diesel Technology Company Fuel pump control valve assembly
DE19616084A1 (en) * 1996-04-23 1997-10-30 Bosch Gmbh Robert Fuel injector
DE19717494A1 (en) * 1997-04-25 1998-10-29 Bosch Gmbh Robert Distributor type fuel injection pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0242634A1 *

Also Published As

Publication number Publication date
DE50106595D1 (en) 2005-07-28
US6884041B2 (en) 2005-04-26
JP2004514824A (en) 2004-05-20
WO2002042634A1 (en) 2002-05-30
DE10058011A1 (en) 2002-05-29
ES2243599T3 (en) 2005-12-01
EP1339968B1 (en) 2005-06-22
US20040131486A1 (en) 2004-07-08

Similar Documents

Publication Publication Date Title
EP0686763B1 (en) Fuel injection valve for internal combustion engines
EP1636484B1 (en) Injector for internal combustion engines
DE3834235C2 (en) Fuel injector for two-stage fuel injection
WO1999030028A1 (en) Fuel injector for auto-ignition internal combustion engines
EP1718862B1 (en) Fuel injection valve for internal combustion engines
EP1339966B1 (en) Injection nozzle comprising two separately controllable nozzle needles
EP1656498A1 (en) Fuel injection valve controlled by a pilot valve
DE4440182C2 (en) Fuel injection valve for internal combustion engines
EP1135603B1 (en) Fuel-injection valve for internal combustion engines
DE102006049885A1 (en) Fuel injector i.e. common rail injector, for internal-combustion engine, has valve seat designed as flat seat with even valve seat surface, and casing resting on seat surface with front-sided circulating edge when control valve is closed
DE102005034879B4 (en) Nozzle assembly for an injection valve
EP0262197B1 (en) Injection valve for internal combustion engines
DE19941688C2 (en) Injection device for an internal combustion engine with direct injection
EP1727977A1 (en) Fuel-injection valve
EP1339968B1 (en) Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines
DE102006050033A1 (en) Injector, in particular common rail injector
WO2003004861A1 (en) Fuel injector comprising a force-balanced control valve
WO2005014997A1 (en) Fuel injection device for a combustion engine
DE102008041561B4 (en) Fuel injector and design method for a fuel injector
DE19940290A1 (en) Control valve for a fuel injector
WO2010000528A1 (en) Solenoid valve for a fuel injector, and fuel injector
DE3807965A1 (en) Pump nozzle
EP3184803B1 (en) Fuel injector
WO2006034910A1 (en) Fuel injection device
AT408136B (en) Fuel injection nozzle for internal combustion engines

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

17P Request for examination filed

Effective date: 20030623

AK Designated contracting states

Kind code of ref document: A1

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

RBV Designated contracting states (corrected)

Designated state(s): DE ES FR GB IT

17Q First examination report despatched

Effective date: 20040422

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 ES FR GB IT

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: 50106595

Country of ref document: DE

Date of ref document: 20050728

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20051117

Year of fee payment: 5

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

Ref country code: FR

Payment date: 20051118

Year of fee payment: 5

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

Ref country code: ES

Payment date: 20051122

Year of fee payment: 5

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2243599

Country of ref document: ES

Kind code of ref document: T3

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

Ref country code: DE

Payment date: 20060127

Year of fee payment: 5

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: 20060323

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

Ref country code: IT

Payment date: 20061130

Year of fee payment: 6

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: 20070601

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

Effective date: 20061116

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20070731

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: 20061116

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20061117

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

Ref country code: ES

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

Effective date: 20061117

Ref country code: FR

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

Effective date: 20061130

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

Ref country code: IT

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

Effective date: 20071116