EP0610641A1 - Fuel injection pump for an internal combustion engine - Google Patents

Fuel injection pump for an internal combustion engine Download PDF

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Publication number
EP0610641A1
EP0610641A1 EP93810077A EP93810077A EP0610641A1 EP 0610641 A1 EP0610641 A1 EP 0610641A1 EP 93810077 A EP93810077 A EP 93810077A EP 93810077 A EP93810077 A EP 93810077A EP 0610641 A1 EP0610641 A1 EP 0610641A1
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EP
European Patent Office
Prior art keywords
cylinder
pump
piston
end position
delivery
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
EP93810077A
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German (de)
French (fr)
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EP0610641B1 (en
Inventor
Patrick Genier
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.)
Wartsila Finland Oy
Original Assignee
Winterthur Gas and Diesel AG
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 Winterthur Gas and Diesel AG filed Critical Winterthur Gas and Diesel AG
Priority to DK93810077.3T priority Critical patent/DK0610641T3/en
Priority to EP93810077A priority patent/EP0610641B1/en
Priority to DE59307709T priority patent/DE59307709D1/en
Priority to KR1019940001826A priority patent/KR100283932B1/en
Priority to CN94101418A priority patent/CN1096568A/en
Priority to FI940546A priority patent/FI106397B/en
Priority to JP6014700A priority patent/JPH10205411A/en
Publication of EP0610641A1 publication Critical patent/EP0610641A1/en
Application granted granted Critical
Publication of EP0610641B1 publication Critical patent/EP0610641B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons

Definitions

  • the invention relates to a fuel injection pump for reciprocating piston internal combustion engines, with at least one cylinder containing a delivery chamber and a piston which is axially movable therein and has a first control edge which determines the start of delivery of the pump and a second control edge which determines the delivery end of the pump, both control edges interact with an opening in the wall of the cylinder, which is connected to a suction channel and an overflow channel.
  • the opening interacting with the two control edges is arranged in the cylinder such that the start of injection is relatively early in the reciprocating piston internal combustion engine before top dead center of the working piston.
  • An earlier start of injection results in economical operation, ie low fuel consumption, when the internal combustion engine is in continuous operation.
  • the nitrogen oxide content (NO x ) of the exhaust gases is slightly above the limit value that is specified in the environmental protection regulations of some countries. This is accepted when the reciprocating piston internal combustion engine serves as the drive motor in a ship and the ship is on a long voyage.
  • the NO x content of the exhaust gases can be reduced if the start of injection is moved closer to top dead center.
  • the object of the invention is to improve an injection pump of the type mentioned at the outset in such a way that it can be used to selectively adjust the early start of injection, which is set for economical operation, to a later start of injection.
  • this object is achieved in that the cylinder is arranged in an axially movable manner in a pump housing between two end positions, that a hydraulic force acts on the cylinder in its one end position and that this force can be released when the cylinder is in its other end position should.
  • the cylinder which is movable between two end positions, means that the injection pump can be quickly and easily switched to either an early or late start of injection, depending on whether the reciprocating internal combustion engine has low fuel consumption and a slightly higher NO x content on the open sea or in low-pollutant conditions Operation with correspondingly less NO x in the exhaust gas for a trip near the coast.
  • An injection pump with an axially adjustable cylinder is indeed known, the cylinder being displaced within its adjustment range during operation and then being fixed.
  • the displacement of the cylinder is done with the help of a thread and a lever linkage, which is structurally very complex.
  • the fuel injection pump has a housing 1, which is sealed at its upper end in FIG. 1 by a cover 2.
  • a cylinder 3 is arranged in the housing 1, into which an axially movable piston 4 projects in FIG. 1 from below.
  • the lower end of the piston 4 in FIG. 1 is operatively connected to a camshaft drive in a known, not shown manner.
  • the upper front end of the piston 4 in FIG. 1 forms a first control edge 5, which cooperates with a bore 6 extending transversely through the cylinder 3 and which determines the start of delivery of the pump.
  • the piston 4 has a second control edge 7, which extends obliquely to the piston axis, which also interacts with the bore 6 and determines the delivery end of the injection pump.
  • the delivery chamber 8 of the pump which is delimited by the cylinder 3 and a central extension 9 of the cover 2 which projects into the bore of the cylinder.
  • a central channel 10 which is connected at its upper end to a pressure line, not shown, which leads to the injection nozzle of a reciprocating internal combustion engine of the diesel type and is injected into the working cylinder of the machine via the cyclical fuel.
  • the reciprocating piston internal combustion engine is installed as a drive motor in a sea-going ship.
  • the cylinder 3 In the area of the delivery chamber 8, the cylinder 3 is surrounded on the outside by an annular space 11, into which the transverse bore 6 of the cylinder 3 opens.
  • a channel 12 which is provided in the housing 1 and through which fuel (arrow A) is supplied in a known, not shown manner, opens into the annular space 11. Excess fuel is returned from the annular space 11 via a channel 13 in the housing 1 and a line (not shown) to a collecting container (arrow B).
  • annular pressure chamber 15 is provided in the pump housing 1 below the annular space 11, separated from the latter, and is connected to a supply line 17 for a hydraulic pressure medium via a channel 16 provided in the housing 1.
  • the outer diameter D of the cylinder 3 is reduced to the diameter d, a shoulder 18 being formed, which in FIG. 1 rests on a flat annular surface 19 of the pressure chamber 15.
  • the annular surface 19 has an outer diameter D 'which is larger than the diameter d, but smaller than the outer diameter D of the cylinder.
  • a line 20 branches off, which contains a two-way switch valve 21 and which opens into a channel 22 which is located in the housing 1 in the region of the upper end of the cylinder 3 and opens into a pressure chamber 25.
  • the pressure chamber 25 is located between the top face of the cylinder 3 in FIG. 1 and the cover 2.
  • the pressure chamber 25 is in the form of an annular disk and has an outside diameter equal to the outer diameter D of the cylinder 3 and an inner diameter which is equal to the outer diameter d 'of the extension 9 of the cover 2 projecting into the cylinder.
  • the injection pump described functions as follows: In the position of the changeover valve 21 shown in FIG. 1, hydraulic pressure medium is introduced both into the pressure chamber 15 and into the pressure chamber 25. Since the differential area (D - D ') acted upon by the pressure medium on the shoulder 18 is smaller than the end face of the cylinder 3 (D - d') in the upper pressure chamber 25, the cylinder is pressed onto the annular surface 19 because the pressure force in the upper pressure chamber 25 predominates. When the piston 4 moves upward, the fuel enclosed in the delivery chamber 8 is brought to a higher pressure from the moment in which the first control edge 5 passes the upper limit of the transverse bore 6.
  • the fuel is conveyed via the central channel 10 to the injection nozzle already mentioned, via which the fuel is then injected into the working cylinder when the injection pressure is reached.
  • the injection is interrupted when the second control edge 7 passes the lower limit of the transverse bore 6.
  • the pressure in the fuel in the delivery chamber 8 is relieved and the fuel can escape via the transverse bore 6, the annular chamber 11 and the channel 13.
  • the injection described occurs when the ship is sailing on the open sea, the operation of the drive motor being based on the good efficiency and the NO x content being relatively high.
  • the changeover valve 21 is moved to the right, for example by hand or pneumatically or by an electrical signal, into that shown in position shown moved.
  • the upper pressure chamber 25 is relieved, and the hydraulic Pressure medium escapes from this room into a collection container.
  • the pressure medium still supplied via the line 17 then acts only on the shoulder 18 in the lower pressure chamber 15.
  • the cylinder 3 moves upwards until the upper end face of the cylinder rests on the cover 2.
  • the transverse channel 6 is also shifted upward and, when the piston 4 moves upward, the delivery and injection also begin later than before, because it takes longer for the first control edge 5 to pass the upper limit of the transverse bore 6.
  • the NO x content of the exhaust gases leaving the drive motor is thus lower.
  • This position of the cylinder 3 is maintained until the ship leaves the coastal waters. Then, by resetting the changeover valve 21 to the position shown in FIG. 1, the cylinder 3 is moved back to its lower end position, and the operation takes place again with an earlier start of injection.
  • the lower pressure chamber is included in the annular space 11, so that the shoulder 18 is acted upon by the pressure of the fuel in the annular space.
  • a line 31 is connected, which contains a two-way switch valve 32. Via the changeover valve 32, the line 31 and thus the pressure chamber 25 can be connected to a line 33 for the supply of a hydraulic pressure medium.
  • the pressure medium connection exists in the drawn position of the changeover valve 32, so that the pressure medium in the pressure chamber 25 holds the cylinder 3 in the lower end position against the fuel pressure acting on the shoulder 18.
  • the injection pump works as described in Fig.1, ie the injection takes place with an earlier start of injection and the ship is in the open sea. Drives the ship into coastal waters, the changeover valve 32 is shifted to the right in FIG. 2, so that the line 31 and thus the pressure chamber 25 are relieved of pressure.
  • the pressure force of the fuel on the shoulder 18 now shifts the cylinder 3 into its upper end position, which corresponds to that shown in Fig.1a.
  • the transverse bore 6 in the cylinder 3 is now higher than that shown in FIG. 2, that is to say the delivery of the injection pump takes place later and the formation of NO x is reduced.
  • the hydraulic pressure medium supplied via lines 17 and 33 can be diesel fuel, but the supply thereof is independent of the fuel supplied via channel 12 of the injection pump.
  • fuel is branched off as the hydraulic pressure medium from the diesel fuel supplied to the pump.
  • a channel 36 is provided in the housing 1 in the area of the annular space 11, to which a line 37 is connected which opens into the channel 22 via a two-way switch valve 38, which is connected to the upper pressure chamber 25.
  • a channel 39 is provided in the housing 1, which also communicates with the pressure chamber 25 and to which a line 40 is connected, which opens into a line 13 'which is connected to the outlet channel 13 for the fuel.
  • Throttles 41 and 42 are located in lines 13 'and 40, respectively.
  • the exemplary embodiment according to FIG. 4 largely corresponds to the example according to FIG. 2, but the hydraulic force acting on the shoulder 18 in FIG. 2 is replaced by a helical spring 30.
  • the spring 30 surrounds the lower end of the piston 4 and presses on the lower end face of the cylinder 3 in FIG. 4. In this embodiment, there is therefore no need to form a special annular surface in the housing 1 below the shoulder 18.
  • the cylinder 3 In the operation of the pump, the cylinder 3 is held in the lower end position by the hydraulic force in the pressure chamber 25 in the drawn position of the changeover valve 32, and this corresponds to an early start of injection.
  • the changeover valve 32 When the ship is traveling near the coast, the changeover valve 32 is shifted to the right in FIG. 4, as a result of which the pressure chamber 25 is relieved of the pressure. The compressive force of the coil spring 30 then presses the cylinder 3 into its upper end position, so that the start of injection takes place later.

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

Abstract

The fuel injection pump has at least one cylinder (3) and a piston (4) axially movable therein. The piston has a first control edge (5), determining the start of delivery of the pump, and a second control edge (7), determining the end of delivery of the pump, the two control edges interacting with an orifice (6) situated in the wall of the cylinder (3), which orifice is connected to an intake port (12) and a transfer port (13). The cylinder (3) is arranged axially movable between two limit positions in a pump housing (1). For holding the cylinder in its one limit position, a hydraulic force (chamber 25) acts on it, which can be cancelled when the cylinder is to assume its other limit position. <IMAGE>

Description

Die Erfindung bezieht sich auf eine Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen, mit mindestens einem einen Förderraum enthaltenden Zylinder und einem in diesem axial beweglichen Kolben, der eine den Förderbeginn der Pumpe bestimmende, erste Steuerkante und eine das Förderende der Pumpe bestimmende, zweite Steuerkante aufweist, wobei beide Steuerkanten mit einer in der Wand des Zylinders befindlichen Oeffnung zusammenwirken, die mit einem Saugkanal und einem Ueberströmkanal in Verbindung steht.The invention relates to a fuel injection pump for reciprocating piston internal combustion engines, with at least one cylinder containing a delivery chamber and a piston which is axially movable therein and has a first control edge which determines the start of delivery of the pump and a second control edge which determines the delivery end of the pump, both control edges interact with an opening in the wall of the cylinder, which is connected to a suction channel and an overflow channel.

Bei bekannten Brennstoffeinspritzpumpen dieser Art wird die mit den beiden Steuerkanten zusammenwirkende Oeffnung so im Zylinder angeordnet, dass der Einspritzbeginn verhältnismässig früh vor dem oberen Totpunkt des Arbeitskolbens in der Hubkolbenbrennkraftmaschine liegt. Früher Einspritzbeginn ergibt bei Dauerbetrieb der Brennkraftmaschine einen sparsamen Betrieb, d.h. geringen Brennstoffverbrauch. Der Stickstoffoxyd-Gehalt (NOx) der Auspuffgase liegt dabei leicht über dem Grenzwert, der in den Umweltschutzvorschriften mancher Länder angegeben ist. Man nimmt dies in Kauf, wenn die Hubkolbenbrennkraftmaschine als Antriebsmotor in einem Schiff dient und das Schiff sich auf grosser Fahrt befindet. Der NOx-Gehalt der Auspuffgase lässt sich verringern, wenn der Einspritzbeginn näher an den oberen Totpunkt verlegt wird.In known fuel injection pumps of this type, the opening interacting with the two control edges is arranged in the cylinder such that the start of injection is relatively early in the reciprocating piston internal combustion engine before top dead center of the working piston. An earlier start of injection results in economical operation, ie low fuel consumption, when the internal combustion engine is in continuous operation. The nitrogen oxide content (NO x ) of the exhaust gases is slightly above the limit value that is specified in the environmental protection regulations of some countries. This is accepted when the reciprocating piston internal combustion engine serves as the drive motor in a ship and the ship is on a long voyage. The NO x content of the exhaust gases can be reduced if the start of injection is moved closer to top dead center.

Der Erfindung liegt die Aufgabe zugrunde, eine Einspritzpumpe der eingangs genannten Art dahingehend zu verbessern, dass sich mit ihr auf konstruktiv einfache Art der für sparsamen Betrieb festgelegte frühe Einspritzbeginn wahlweise auf einen späteren Einspritzbeginn verstellen lässt.The object of the invention is to improve an injection pump of the type mentioned at the outset in such a way that it can be used to selectively adjust the early start of injection, which is set for economical operation, to a later start of injection.

Erfindungsgemäss wird diese Aufgabe dadurch gelöst, dass der Zylinder in einem Pumpengehäuse zwischen zwei Endstellungen axial beweglich angeordnet ist, dass zum Halten des Zylinders in seiner einen Endstellung eine hydraulische Kraft auf ihn wirkt und dass diese Kraft aufhebbar ist, wenn der Zylinder seine andere Endstellung einnehmen soll. Durch den zwischen zwei Endstellungen beweglichen Zylinder lässt sich erreichen, dass die Einspritzpumpe rasch und einfach entweder auf einen frühen oder späten Einspritzbeginn umgeschaltet werden kann, je nachdem ob die Hubkolbenbrennkraftmaschine mit niedrigem Brennstoffverbrauch und etwas höherem NOx-Gehalt auf dem offenen Meer oder im schadstoffarmen Betrieb mit entsprechend weniger NOx im Aufpuffgas für eine Fahrt in Küstennähe gefahren werden soll.According to the invention, this object is achieved in that the cylinder is arranged in an axially movable manner in a pump housing between two end positions, that a hydraulic force acts on the cylinder in its one end position and that this force can be released when the cylinder is in its other end position should. The cylinder, which is movable between two end positions, means that the injection pump can be quickly and easily switched to either an early or late start of injection, depending on whether the reciprocating internal combustion engine has low fuel consumption and a slightly higher NO x content on the open sea or in low-pollutant conditions Operation with correspondingly less NO x in the exhaust gas for a trip near the coast.

Eine Einspritzpumpe mit axial verstellbarem Zylinder ist zwar bekannt, wobei der Zylinder im Betrieb innerhalb seines Verstellbereichs verschoben und dann fixiert wird. Das Verschieben des Zylinders geschieht mit Hilfe eines Gewindes und eines Hebelgestänges, was konstruktiv sehr aufwendig ist.An injection pump with an axially adjustable cylinder is indeed known, the cylinder being displaced within its adjustment range during operation and then being fixed. The displacement of the cylinder is done with the help of a thread and a lever linkage, which is structurally very complex.

Einige Ausführungsbeispiele der Erfindung sind in der folgenden Beschreibung anhand der Zeichnung näher erläutert. Es zeigen:

Fig.1
einen Axialschnitt durch eine Brennstoffeinspritzpumpe, wobei der Zylinder die eine Endstellung innehat,
Fig.1a
einen Axialschnitt durch einen Teil der Einspritzpumpe, wobei der Zylinder die andere Endstellung innehat,
Fig.2
einen der Fig.1 entsprechenden Axialschnitt durch eine abgewandelte Einspritzpumpe,
Fig.3
einen der Fig.1 entsprechenden Axialschnitt durch eine weitere Abwandlung der Einspritzpumpe und
Fig.4
einen der Fig.2 entsprechenden Axialschnitt durch eine weiter abgewandelte Einspritzpumpe.
Some embodiments of the invention are explained in more detail in the following description with reference to the drawing. Show it:
Fig. 1
an axial section through a fuel injection pump, the cylinder having one end position,
Fig.1a
an axial section through part of the injection pump, the cylinder being in the other end position,
Fig. 2
1 shows an axial section corresponding to FIG. 1 through a modified injection pump,
Fig. 3
an axial section corresponding to FIG. 1 through a further modification of the injection pump and
Fig. 4
an axial section corresponding to FIG. 2 through a further modified injection pump.

Gemäss Fig.1 weist die Brennstoffeinspritzpumpe ein Gehäuse 1 auf, das an seinem in Fig.1 oberen Ende durch einen Deckel 2 dicht verschlossen ist. Im Gehäuse 1 ist ein Zylinder 3 angeordnet, in den in Fig.1 von unten ein axial beweglicher Kolben 4 ragt. Das in Fig.1 untere Ende des Kolbens 4 ist in bekannter, nicht näher dargestellter Weise mit einem Nockenwellenantrieb in Wirkungsverbindung. Das in Fig.1 obere Stirnende des Kolbens 4 bildet eine erste Steuerkante 5, die mit einer sich quer durch den Zylinder 3 erstreckenden Bohrung 6 zusammenwirkt und die den Förderbeginn der Pumpe bestimmt. In Fig.1 unterhalb der ersten Steuerkante 5 weist der Kolben 4 eine zweite, schräg zur Kolbenachse verlaufende Steuerkante 7 auf, die ebenfalls mit der Bohrung 6 zusammenwirkt und das Förderende der Einspritzpumpe bestimmt. In Fig.1 oberhalb der die Steuerkante 5 bildenden Stirnfläche des Kolbens 4 befindet sich der Förderraum 8 der Pumpe, der vom Zylinder 3 und einem zentralen, in die Bohrung des Zylinders ragenden Fortsatz 9 des Deckels 2 begrenzt ist. Vom Förderraum 8 aus erstreckt sich durch den Deckel 2 ein zentraler Kanal 10, der an seinem oberen Ende mit einer nicht dargestellten Druckleitung verbunden ist, die zur Einspritzdüse einer Hubkolbenbrennkraftmaschine der Dieselbauart führt und über die taktweise Brennstoff in den Arbeitszylinder der Maschine gespritzt wird. Die Hubkolbenbrennkraftmaschine ist als Antriebsmotor in ein seegängiges Schiff eingebaut.According to FIG. 1, the fuel injection pump has a housing 1, which is sealed at its upper end in FIG. 1 by a cover 2. A cylinder 3 is arranged in the housing 1, into which an axially movable piston 4 projects in FIG. 1 from below. The lower end of the piston 4 in FIG. 1 is operatively connected to a camshaft drive in a known, not shown manner. The upper front end of the piston 4 in FIG. 1 forms a first control edge 5, which cooperates with a bore 6 extending transversely through the cylinder 3 and which determines the start of delivery of the pump. In FIG. 1 below the first control edge 5, the piston 4 has a second control edge 7, which extends obliquely to the piston axis, which also interacts with the bore 6 and determines the delivery end of the injection pump. In FIG. 1, above the end face of the piston 4 forming the control edge 5, there is the delivery chamber 8 of the pump, which is delimited by the cylinder 3 and a central extension 9 of the cover 2 which projects into the bore of the cylinder. From the funding room 8 extends through the cover 2, a central channel 10, which is connected at its upper end to a pressure line, not shown, which leads to the injection nozzle of a reciprocating internal combustion engine of the diesel type and is injected into the working cylinder of the machine via the cyclical fuel. The reciprocating piston internal combustion engine is installed as a drive motor in a sea-going ship.

Im Bereich des Förderraums 8 ist der Zylinder 3 aussen von einem Ringraum 11 umgeben, in den die Querbohrung 6 des Zylinders 3 mündet. In den Ringraum 11 mündet ausserdem ein im Gehäuse 1 angebrachter Kanal 12, über den in bekannter, nicht näher dargestellter Weise Brennstoff (Pfeil A) zugeführt wird. Ueberschüssiger Brennstoff wird aus dem Ringraum 11 über einen im Gehäuse 1 angebrachten Kanal 13 und eine nicht dargestellte Leitung zu einem Sammelbehälter zurückgeführt (Pfeil B).In the area of the delivery chamber 8, the cylinder 3 is surrounded on the outside by an annular space 11, into which the transverse bore 6 of the cylinder 3 opens. In addition, a channel 12, which is provided in the housing 1 and through which fuel (arrow A) is supplied in a known, not shown manner, opens into the annular space 11. Excess fuel is returned from the annular space 11 via a channel 13 in the housing 1 and a line (not shown) to a collecting container (arrow B).

Im Pumpengehäuse 1 ist in Fig.1 unterhalb des Ringraums 11 - getrennt von diesem - eine ringförmige Druckkammer 15 vorgesehen, die über einen im Gehäuse 1 angebrachten Kanal 16 mit einer Zufuhrleitung 17 für ein hydraulisches Druckmittel verbunden ist. Im Bereich der Druckkammer 15 ist der Aussendurchmesser D des Zylinders 3 auf den Durchmesser d verringert, wobei eine Schulter 18 gebildet wird, die in Fig.1 auf einer ebenen Ringfläche 19 der Druckkammer 15 ruht. Die Ringfläche 19 weist einen Aussendurchmesser D' auf, der grösser ist als der Durchmesser d, aber kleiner als der Aussendurchmesser D des Zylinders. Von der Zufuhrleitung 17 zweigt eine Leitung 20 ab, die ein Zweiwege-Umschaltventil 21 enthält und die in einen Kanal 22 mündet, der sich im Gehäuse 1 im Bereich des oberen Endes des Zylinders 3 befindet und in einen Druckraum 25 mündet. Der Druckraum 25 befindet sich zwischen der in Fig.1 oberen Stirnfläche des Zylinders 3 und dem Deckel 2. Der Druckraum 25 ist ringscheibenförmig und hat einen Aussendurchmesser gleich dem Aussendurchmesser D des Zylinders 3 und einen Innendurchmesser, der gleich dem Aussendurchmesser d' des in den Zylinder ragenden Fortsatzes 9 des Deckels 2 ist.In FIG. 1, an annular pressure chamber 15 is provided in the pump housing 1 below the annular space 11, separated from the latter, and is connected to a supply line 17 for a hydraulic pressure medium via a channel 16 provided in the housing 1. In the area of the pressure chamber 15, the outer diameter D of the cylinder 3 is reduced to the diameter d, a shoulder 18 being formed, which in FIG. 1 rests on a flat annular surface 19 of the pressure chamber 15. The annular surface 19 has an outer diameter D 'which is larger than the diameter d, but smaller than the outer diameter D of the cylinder. From the supply line 17, a line 20 branches off, which contains a two-way switch valve 21 and which opens into a channel 22 which is located in the housing 1 in the region of the upper end of the cylinder 3 and opens into a pressure chamber 25. The pressure chamber 25 is located between the top face of the cylinder 3 in FIG. 1 and the cover 2. The pressure chamber 25 is in the form of an annular disk and has an outside diameter equal to the outer diameter D of the cylinder 3 and an inner diameter which is equal to the outer diameter d 'of the extension 9 of the cover 2 projecting into the cylinder.

Die beschriebene Einspritzpumpe funktioniert wie folgt: Bei der in Fig.1 gezeichneten Stellung des Umschaltventils 21 wird hydraulisches Druckmittel sowohl in die Druckkammer 15 als auch in den Druckraum 25 eingeführt. Da die vom Druckmittel beaufschlagte Differenzfläche (D - D') an der Schulter 18 kleiner ist als die Stirnfläche des Zylinders 3 (D - d') im oberen Druckraum 25, wird der Zylinder auf die Ringfläche 19 gedrückt, denn die Druckkraft im oberen Druckraum 25 überwiegt. Bei einer Aufwärtsbewegung des Kolbens 4 wird der im Förderraum 8 eingeschlossene Brennstoff von dem Moment an auf einen höheren Druck gebracht, in dem die erste Steuerkante 5 die obere Begrenzung der Querbohrung 6 passiert. Gleichzeitig wird der Brennstoff über den zentralen Kanal 10 zur schon erwähnten Einspritzdüse gefördert, über die der Brennstoff dann in den Arbeitszylinder eingespritzt wird, wenn der Einspritzdruck erreicht wird. Die Einspritzung wird unterbrochen, wenn die zweite Steuerkante 7 die untere Begrenzung der Querbohrung 6 passiert. In diesem Moment findet eine Druckentlastung des Brennstoffs im Förderraum 8 statt und der Brennstoff kann über die Querbohrung 6, den Ringraum 11 und den Kanal 13 entweichen. Die beschriebene Einspritzung geschieht bei einer Fahrt des Schiffes auf offener See, wobei der Betrieb des Antriebsmotors sich nach dem guten Wirkungsgrad richtet und der NOx-Gehalt relativ hoch liegt. Kommt das Schiff in die Nähe der Küste, wo für den Betrieb der Antriebsmaschine die Umweltschutzvorschriften massgebend sind, d.h. möglichst niedriger NOx-Gehalt, wird z.B. von Hand oder pneumatisch oder durch ein elektrisches Signal das Umschaltventil 21 nach rechts in die in Fig.1a gezeichnete Stellung verschoben. In dieser Stellung wird der obere Druckraum 25 entlastet, und das hydraulische Druckmittel entweicht aus diesem Raum in einen Sammelbehälter. Das weiterhin über die Leitung 17 zugeführte Druckmittel wirkt dann nur in der unteren Druckkammer 15 auf die Schulter 18. Als Folge davon verschiebt sich der Zylinder 3 nach oben, bis die obere Stirnfläche des Zylinders am Deckel 2 anliegt. Dadurch wird der Querkanal 6 ebenfalls nach oben verschoben und bei einer Aufwärtsbewegung des Kolbens 4 beginnt auch die Förderung und die Einspritzung später als zuvor, weil es länger dauert, bis die erste Steuerkante 5 die obere Begrenzung der Querbohrung 6 passiert hat. Der NOx-Gehalt der den Antriebsmotor verlassenden Auspuffgase ist damit niedriger. Diese Stellung des Zylinders 3 bleibt so lange erhalten, bis das Schiff das Küstengewässer wieder verlässt. Dann wird durch Zurückstellen des Umschaltventils 21 in die in Fig.1 gezeigte Stellung der Zylinder 3 wieder in seine untere Endstellung bewegt, und es findet wieder der Betrieb mit früherem Einspritzbeginn statt.The injection pump described functions as follows: In the position of the changeover valve 21 shown in FIG. 1, hydraulic pressure medium is introduced both into the pressure chamber 15 and into the pressure chamber 25. Since the differential area (D - D ') acted upon by the pressure medium on the shoulder 18 is smaller than the end face of the cylinder 3 (D - d') in the upper pressure chamber 25, the cylinder is pressed onto the annular surface 19 because the pressure force in the upper pressure chamber 25 predominates. When the piston 4 moves upward, the fuel enclosed in the delivery chamber 8 is brought to a higher pressure from the moment in which the first control edge 5 passes the upper limit of the transverse bore 6. At the same time, the fuel is conveyed via the central channel 10 to the injection nozzle already mentioned, via which the fuel is then injected into the working cylinder when the injection pressure is reached. The injection is interrupted when the second control edge 7 passes the lower limit of the transverse bore 6. At this moment, the pressure in the fuel in the delivery chamber 8 is relieved and the fuel can escape via the transverse bore 6, the annular chamber 11 and the channel 13. The injection described occurs when the ship is sailing on the open sea, the operation of the drive motor being based on the good efficiency and the NO x content being relatively high. If the ship comes close to the coast, where the environmental protection regulations are decisive for the operation of the drive machine, ie the lowest possible NO x content, the changeover valve 21 is moved to the right, for example by hand or pneumatically or by an electrical signal, into that shown in position shown moved. In this position, the upper pressure chamber 25 is relieved, and the hydraulic Pressure medium escapes from this room into a collection container. The pressure medium still supplied via the line 17 then acts only on the shoulder 18 in the lower pressure chamber 15. As a result, the cylinder 3 moves upwards until the upper end face of the cylinder rests on the cover 2. As a result, the transverse channel 6 is also shifted upward and, when the piston 4 moves upward, the delivery and injection also begin later than before, because it takes longer for the first control edge 5 to pass the upper limit of the transverse bore 6. The NO x content of the exhaust gases leaving the drive motor is thus lower. This position of the cylinder 3 is maintained until the ship leaves the coastal waters. Then, by resetting the changeover valve 21 to the position shown in FIG. 1, the cylinder 3 is moved back to its lower end position, and the operation takes place again with an earlier start of injection.

Beim Ausführungsbeispiel gemäss Fig.2 ist die untere Druckkammer in den Ringraum 11 einbezogen, so dass die Schulter 18 vom Druck des Brennstoffs im Ringraum beaufschlagt ist. Am Kanal 22 des Gehäuses 1, der zum oberen Druckraum 25 führt, ist eine Leitung 31 angeschlossen, die ein Zweiwege-Umschaltventil 32 enthält. Ueber das Umschaltventil 32 kann die Leitung 31 und damit die Druckkammer 25 mit einer Leitung 33 für die Zufuhr eines hydraulischen Druckmittels verbunden werden.In the exemplary embodiment according to FIG. 2, the lower pressure chamber is included in the annular space 11, so that the shoulder 18 is acted upon by the pressure of the fuel in the annular space. At the channel 22 of the housing 1, which leads to the upper pressure chamber 25, a line 31 is connected, which contains a two-way switch valve 32. Via the changeover valve 32, the line 31 and thus the pressure chamber 25 can be connected to a line 33 for the supply of a hydraulic pressure medium.

Wie aus Fig.2 ersichtlich, besteht in der gezeichneten Stellung des Umschaltventils 32 die Druckmittelverbindung, so dass das in der Druckkammer 25 befindliche Druckmittel den Zylinder 3 - gegen den auf die Schulter 18 wirkenden Brennstoffdruck - in der unteren Endstellung hält. Die Einspritzpumpe arbeitet wie zu Fig.1 beschrieben, d.h. die Einspritzung findet mit früherem Einspritzbeginn statt und das Schiff befindet sich auf offener See. Fährt das Schiff in Küstengewässer ein, so wird das Umschaltventil 32 in Fig.2 nach rechts verschoben, so dass die Leitung 31 und damit die Druckkammer 25 druckentlastet werden. Die Druckkraft des Brennstoffs auf der Schulter 18 verschiebt nunmehr den Zylinder 3 in seine obere Endstellung, die also der in Fig.1a gezeichneten entspricht. Die Querbohrung 6 im Zylinder 3 liegt nun höher als in Fig.2 gezeichnet, d.h. der Förderbeginn der Einspritzpumpe findet später statt und die NOx-Bildung ist reduziert.As can be seen from FIG. 2, the pressure medium connection exists in the drawn position of the changeover valve 32, so that the pressure medium in the pressure chamber 25 holds the cylinder 3 in the lower end position against the fuel pressure acting on the shoulder 18. The injection pump works as described in Fig.1, ie the injection takes place with an earlier start of injection and the ship is in the open sea. Drives the ship into coastal waters, the changeover valve 32 is shifted to the right in FIG. 2, so that the line 31 and thus the pressure chamber 25 are relieved of pressure. The pressure force of the fuel on the shoulder 18 now shifts the cylinder 3 into its upper end position, which corresponds to that shown in Fig.1a. The transverse bore 6 in the cylinder 3 is now higher than that shown in FIG. 2, that is to say the delivery of the injection pump takes place later and the formation of NO x is reduced.

Bei den Ausführungsbeispielen gemäss Fig.1 und 2 kann das über die Leitungen 17 und 33 zugeführte hydraulische Druckmittel Diesel-Brennstoff sein, dessen Zufuhr jedoch unabhängig von dem über den Kanal 12 der Einspritzpumpe zugeführten Brennstoff ist. Beim Ausführungsbeispiel gemäss Fig.3 wird als hydraulisches Druckmittel Brennstoff aus dem der Pumpe zugeführten Dieselbrennstoff abgezweigt. Zu diesem Zweck ist im Gehäuse 1 im Bereich des Ringraums 11 ein Kanal 36 vorgesehen, an den eine Leitung 37 angeschlossen ist, die über ein Zweiwege-Umschaltventil 38 in den Kanal 22 mündet, der mit der oberen Druckkammer 25 in Verbindung steht. Dem Kanal 22 gegenüberliegend ist im Gehäuse 1 ein Kanal 39 vorgesehen, der ebenfalls mit der Druckkammer 25 kommuniziert und an den eine Leitung 40 angeschlossen ist, die in eine Leitung 13' mündet, die an Ablaufkanal 13 für den Brennstoff angeschlossen ist. In den Leitungen 13' und 40 befindet sich je eine Drosselstelle 41 bzw. 42.In the exemplary embodiments according to FIGS. 1 and 2, the hydraulic pressure medium supplied via lines 17 and 33 can be diesel fuel, but the supply thereof is independent of the fuel supplied via channel 12 of the injection pump. In the exemplary embodiment according to FIG. 3, fuel is branched off as the hydraulic pressure medium from the diesel fuel supplied to the pump. For this purpose, a channel 36 is provided in the housing 1 in the area of the annular space 11, to which a line 37 is connected which opens into the channel 22 via a two-way switch valve 38, which is connected to the upper pressure chamber 25. Opposite the channel 22, a channel 39 is provided in the housing 1, which also communicates with the pressure chamber 25 and to which a line 40 is connected, which opens into a line 13 'which is connected to the outlet channel 13 for the fuel. Throttles 41 and 42 are located in lines 13 'and 40, respectively.

Bei der in Fig.3 gezeichneten Stellung des Umschaltventils 38 wird ein Teil des über den Kanal 12 der Einspritzpumpe zugeführten Brennstoffs über die Leitung 37 der oberen Druckkammer 25 zugeführt. Der in dieser Druckkammer wirkende Brennstoffdruck drückt den Zylinder 3 in seine untere Endstellung, die dem früheren Einspritzbeginn entspricht, bei dem das Schiff auf offener See fährt. Beim Einfahren des Schiffes in Küstengewässer wird das Umschaltventil 38 in Fig.3 nach rechts verschoben, wodurch der Druckraum 25 entlastet wird und nunmehr der auf die Schulter 18 wirkende Brennstoffdruck den Zylinder 3 in seine obere Endstellung bewegt, wie in Fig.1a dargestellt. Durch das Vorsehen des Kanals 39, der Leitung 40 und der beiden Drosseln 41 und 42 wird erreicht, dass der Druckraum 25 bei der in Fig.3 dargestellten Stellung des Zylinders 3 ständig von Brennstoff durchströmt wird.In the position of the changeover valve 38 shown in FIG. 3, part of the fuel supplied via the channel 12 to the injection pump is supplied to the upper pressure chamber 25 via the line 37. The fuel pressure acting in this pressure chamber pushes the cylinder 3 into its lower end position, which corresponds to the earlier start of injection, when the ship is sailing on the open sea. When the ship enters coastal waters, the changeover valve 38 shifted to the right in FIG. 3, whereby the pressure chamber 25 is relieved and the fuel pressure acting on the shoulder 18 now moves the cylinder 3 into its upper end position, as shown in FIG. 1a. Providing the channel 39, the line 40 and the two throttles 41 and 42 ensures that the pressure chamber 25 is continuously flowed through by fuel when the cylinder 3 is shown in FIG.

Das Ausführungsbeispiel gemäss Fig.4 entspricht weitgehend dem Beispiel gemäss Fig.2, wobei jedoch die in Fig.2 auf die Schulter 18 wirkende hydraulische Kraft durch eine Schraubenfeder 30 ersetzt ist. Die Feder 30 umgibt das untere Ende des Kolbens 4 und drückt auf die in Fig.4 untere Stirnfläche des Zylinders 3. Bei dieser Ausführungsform entfällt also die Ausbildung einer besonderen Ringfläche im Gehäuse 1 unterhalb der Schulter 18.The exemplary embodiment according to FIG. 4 largely corresponds to the example according to FIG. 2, but the hydraulic force acting on the shoulder 18 in FIG. 2 is replaced by a helical spring 30. The spring 30 surrounds the lower end of the piston 4 and presses on the lower end face of the cylinder 3 in FIG. 4. In this embodiment, there is therefore no need to form a special annular surface in the housing 1 below the shoulder 18.

Im Betrieb der Pumpe wird bei der gezeichneten Stellung des Umschaltventils 32 der Zylinder 3 durch die hydraulische Kraft in der Druckkammer 25 in der unteren Endstellung gehalten und dies entspricht also frühem Einspritzbeginn. Bei einer Fahrt des Schiffes in Küstennähe wird das Umschaltventil 32 in Fig.4 nach rechts verschoben, wodurch die Druckkammer 25 vom Druck entlastet wird. Die Druckkraft der Schraubenfeder 30 drückt dann den Zylinder 3 in seine obere Endstellung, so dass späterer Einspritzbeginn stattfindet.In the operation of the pump, the cylinder 3 is held in the lower end position by the hydraulic force in the pressure chamber 25 in the drawn position of the changeover valve 32, and this corresponds to an early start of injection. When the ship is traveling near the coast, the changeover valve 32 is shifted to the right in FIG. 4, as a result of which the pressure chamber 25 is relieved of the pressure. The compressive force of the coil spring 30 then presses the cylinder 3 into its upper end position, so that the start of injection takes place later.

Claims (6)

Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen, mit mindestens einem einen Förderraum enthaltenden Zylinder und einem in diesem axial beweglichen Kolben, der eine den Förderbeginn der Pumpe bestimmende, erste Steuerkante und eine das Förderende der Pumpe bestimmende, zweite Steuerkante aufweist, wobei beide Steuerkanten mit einer in der Wand des Zylinders befindlichen Oeffnung zusammenwirken, die mit einem Saugkanal und einem Ueberströmkanal in Verbindung steht,
dadurch gekennzeichnet, dass der Zylinder in einem Pumpengehäuse zwischen zwei Endstellungen axial beweglich angeordnet ist, dass zum Halten des Zylinders in seiner einen Endstellung eine hydraulische Kraft auf ihn wirkt und dass diese Kraft aufhebbar ist, wenn der Zylinder seine andere Endstellung einnehmen soll.Fuel injection pump for reciprocating piston internal combustion engines, with at least one cylinder containing a delivery chamber and a piston which is axially movable therein and has a first control edge which determines the start of delivery of the pump and a second control edge which determines the delivery end of the pump, both control edges having one in the wall of the Interact with the cylinder located opening, which is connected to a suction channel and an overflow channel,
characterized in that the cylinder is axially movable in a pump housing between two end positions, that a hydraulic force acts on it to hold the cylinder in its one end position and that this force can be canceled if the cylinder is to assume its other end position. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass die eine Endstellung des Zylinders diejenige ist, bei der ein früherer Einspritzbeginn stattfindet.Pump according to claim 1, characterized in that the one end position of the cylinder is the one at which an earlier start of injection takes place. Pumpe nach Anspruch 2, dadurch gekennzeichnet, dass die hydraulische Kraft auf die der Antriebsseite des Kolbens abgewendete Stirnfläche des Zylinders wirkt.Pump according to claim 2, characterized in that the hydraulic force acts on the end face of the cylinder facing away from the drive side of the piston. Pumpe nach Anspruch 3, dadurch gekennzeichnet, dass zum Halten des Zylinders in der anderen Endstellung ebenfalls eine hydraulische Kraft vorgesehen ist, die auf eine der Antriebsseite des Kolbens zugewendeten Fläche des Zylinders wirkt, die kleiner bemessen ist als die der Antriebsseite des Kolbens abgewendete Stirnfläche.Pump according to claim 3, characterized in that a hydraulic force is also provided for holding the cylinder in the other end position, which acts on a surface of the cylinder which faces the drive side of the piston and which is of smaller dimensions than the end face facing away from the drive side of the piston. Pumpe nach Anspruch 4, dadurch gekennzeichnet, dass als hydraulische Kraft der Druck des der Pumpe zugeführten Brennstoffs dient.Pump according to claim 4, characterized in that the pressure of the fuel supplied to the pump is used as the hydraulic force. Pumpe nach Anspruch 3, dadurch gekennzeichnet, dass zum Halten des Zylinders in der anderen Endstellung eine Federkraft vorgesehen ist, die auf eine der Antriebsseite des Kolbens zugewendeten Fläche des Zylinders wirkt.Pump according to claim 3, characterized in that a spring force is provided for holding the cylinder in the other end position, which acts on a surface of the cylinder facing the drive side of the piston.
EP93810077A 1993-02-08 1993-02-08 Fuel injection pump for an internal combustion engine Expired - Lifetime EP0610641B1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
DK93810077.3T DK0610641T3 (en) 1993-02-08 1993-02-08 Fuel Injection Pump for Piston Fuel Machines
EP93810077A EP0610641B1 (en) 1993-02-08 1993-02-08 Fuel injection pump for an internal combustion engine
DE59307709T DE59307709D1 (en) 1993-02-08 1993-02-08 Fuel injection pump for reciprocating internal combustion engines
KR1019940001826A KR100283932B1 (en) 1993-02-08 1994-02-01 Fuel injection pump of reciprocating internal combustion engine
CN94101418A CN1096568A (en) 1993-02-08 1994-02-07 A kind of fuel oil injectionpump that is used for reciprocating internal combustion engine
FI940546A FI106397B (en) 1993-02-08 1994-02-07 Fuel injection pump for internal combustion engines with piston
JP6014700A JPH10205411A (en) 1993-02-08 1994-02-08 Fuel injection pump for reciprocating internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP93810077A EP0610641B1 (en) 1993-02-08 1993-02-08 Fuel injection pump for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP0610641A1 true EP0610641A1 (en) 1994-08-17
EP0610641B1 EP0610641B1 (en) 1997-11-19

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EP93810077A Expired - Lifetime EP0610641B1 (en) 1993-02-08 1993-02-08 Fuel injection pump for an internal combustion engine

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EP (1) EP0610641B1 (en)
JP (1) JPH10205411A (en)
KR (1) KR100283932B1 (en)
CN (1) CN1096568A (en)
DE (1) DE59307709D1 (en)
DK (1) DK0610641T3 (en)
FI (1) FI106397B (en)

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Publication number Priority date Publication date Assignee Title
DE19719800C1 (en) * 1997-05-10 1998-12-17 Kurt Wilhelm Injector for free piston engine

Families Citing this family (4)

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Publication number Priority date Publication date Assignee Title
US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump
JP3814245B2 (en) * 2002-11-21 2006-08-23 ヤンマー株式会社 Fuel injection pump
CN1312395C (en) * 2003-12-12 2007-04-25 上海交通大学 Sealing device for common rail Injector of diesel engine
GB2549141A (en) * 2016-04-08 2017-10-11 Delphi Int Operations Luxembourg Sarl Fuel pump

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EP0095026A1 (en) * 1982-03-25 1983-11-30 Deere & Company Injector pump unit with a sleeve-valve controlled floating piston for internal-combustion engines
EP0267894A1 (en) * 1986-10-30 1988-05-18 VOEST-ALPINE AUTOMOTIVE Gesellschaft m.b.H. Pump nozzle unit for fuel injection into an internal-combustion engine
EP0499741A1 (en) * 1991-02-22 1992-08-26 The Cessna Aircraft Company Fuel injection systems for internal combustion engines

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EP0095026A1 (en) * 1982-03-25 1983-11-30 Deere & Company Injector pump unit with a sleeve-valve controlled floating piston for internal-combustion engines
EP0267894A1 (en) * 1986-10-30 1988-05-18 VOEST-ALPINE AUTOMOTIVE Gesellschaft m.b.H. Pump nozzle unit for fuel injection into an internal-combustion engine
EP0499741A1 (en) * 1991-02-22 1992-08-26 The Cessna Aircraft Company Fuel injection systems for internal combustion engines

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19719800C1 (en) * 1997-05-10 1998-12-17 Kurt Wilhelm Injector for free piston engine

Also Published As

Publication number Publication date
FI940546A (en) 1994-08-09
FI940546A0 (en) 1994-02-07
KR940019984A (en) 1994-09-15
DE59307709D1 (en) 1998-01-02
DK0610641T3 (en) 1997-12-22
CN1096568A (en) 1994-12-21
KR100283932B1 (en) 2001-10-22
EP0610641B1 (en) 1997-11-19
FI106397B (en) 2001-01-31
JPH10205411A (en) 1998-08-04

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