EP0678161B1 - Fuel-injection distributor pump for internal-combustion engines - Google Patents
Fuel-injection distributor pump for internal-combustion engines Download PDFInfo
- Publication number
- EP0678161B1 EP0678161B1 EP95900049A EP95900049A EP0678161B1 EP 0678161 B1 EP0678161 B1 EP 0678161B1 EP 95900049 A EP95900049 A EP 95900049A EP 95900049 A EP95900049 A EP 95900049A EP 0678161 B1 EP0678161 B1 EP 0678161B1
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- EP
- European Patent Office
- Prior art keywords
- pump
- cylinder bore
- pistons
- cylinder
- stop
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
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- 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
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- 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
Definitions
- the invention is based on a distributor fuel injection pump for internal combustion engines according to the preamble of claim 1.
- a drive shaft drives a rotor guided in a housing in which two pump piston pairs, each guided in a cylinder bore, are arranged in a radial plane to the drive shaft are.
- the arranged in a common radial plane of the rotor cylinder bores intersect at right angles, so that the individual pump pistons with their radially inward-facing end faces a common pump working space in the overlapping area of the Limit cylinder bores.
- the pump pistons run with their ends protruding from the cylinder bores by means of a roller tappet on a stationary cam track of a cam ring guided in the housing, so that they are set in a reciprocating stroke movement when the rotor rotates, whereby they move during the radially outward suction stroke movement open the connection of the cylinder bore with a filling line starting from a low-pressure chamber, which is then closed in the subsequent delivery stroke by the pump pistons.
- the fuel compressed in the common pump work space during the delivery stroke then passes via a high-pressure channel in the rotor to a distributor bore radially leading away from it, which overlaps with the individual high-pressure delivery lines to the injection points during the rotary movement of the rotor.
- the pump piston pairs in the two cylinder bores are designed so that a longer pair of pistons guided in a first cylinder bore protrudes into the second cylinder bore with its end facing the pump working space and the shorter piston pair guided there does not reach the first cylinder bore even in its maximum stroke position.
- the known distributor fuel injection pump has the disadvantage that the cam stroke that is the same for all pump pistons must be less than half the diameter of the cylinder bores of the same size. This is necessary to ensure that the long pistons are still immersed in the second cylinder bore, even in their maximum suction stroke position, in order to move the shorter pistons independently between the long pistons when the internal combustion engine is switched off and the pump work chamber is depressurized Avoid safely, as this would otherwise lead to mechanical destruction of the distributor injection pump during operation.
- the distributor fuel injection pump according to the invention with the features of claim 1 has the advantage that a stop at the end protruding from the cylinder bore of the shorter pump pistons, their unwanted sliding into the cylinder bore between the long pump pistons can be safely avoided.
- This increase in the delivery stroke can advantageously be converted into an increase in the injection pressure or a larger delivery amount.
- the stop on the short pump piston is advantageously arranged in such a way that it allows them to be immersed in the cylinder bore leading them until their end face facing the pump work space has approached to a small extent the second cylinder bore, so that large delivery heights are reached to let.
- the stop on the short pump piston can be easily by a collar or in an annular groove Carry out a circlip on the shaft of the short pistons, which then simply interact with the end wall of the cylinder bore.
- FIG. 1 shows a longitudinal section through the part of the distributor fuel injection pump that is essential to the invention
- FIG. 2 shows a first embodiment of the pump piston lock by means of a collar in a section from FIG. 1
- FIG. 3 shows a second embodiment of the pump piston lock by means of a lock ring in an analogous manner to FIG. 2 shown representation.
- a piston-shaped rotor part 1 is mounted rotatably about its axis in a cylinder bore 2 of a cylindrical guide part 5 which is fixedly connected to the pump housing 3.
- the rotor part 1 has at its one end a part 7 with a larger diameter, which is connected in a rotationally fixed manner to a drive shaft 9 which is driven synchronously with the engine speed and in which two through bores 11 intersecting at right angles in a common radial of the axis of the rotor part 1 extending plane are arranged.
- a delivery channel 13 leads off in the axis of the rotor part 1, which contains a check valve 15 and whose end merges into a radially extending distributor bore 17.
- the guide part 5 has injection lines 19 which start from the cylinder bore 2 to the individual injection points of the internal combustion engine.
- the injection lines 19 are distributed according to the number of injection points to be supplied and at a corresponding distance from one another on the circumference of the guide part 5.
- a supply bore 21 in the rotor part 1 which leads radially away from the delivery channel 13 and which can be connected to a fuel supply line 23 in the guide part 5, which in turn leads to a fuel delivery line (not shown), preferably having a feed pump and having a feed pump a fuel reservoir forming a low pressure space is connected.
- the radial through-bores 11 in the diameter-enlarged part 7 of the rotor part 1 are designed as cylinder bores, in which, as can also be seen in FIGS. 2 and 3, two pump pistons lying opposite one another and working against one another are arranged.
- a first cylinder bore 25 receives a first pair of pump pistons 27 with an axial extension, the pump pistons 27 of which are so long that they protrude into the region of a second cylinder bore 29 that intersects the first during the delivery stroke movement.
- this second cylinder bore 29 is a second shorter pump piston pair 31 guided, the pump pistons 31 are dimensioned such that they do not protrude into the region of the first cylinder bore 25 even in the maximum delivery stroke position.
- the pump pistons 27, 31 delimit a common pump working space 33, in the cylinder bores 25, 29, which can be connected to the injection lines 19 and the fuel supply line 23 via the delivery channel 13.
- the pump pistons 27, 31 each abut a roller tappet 35, the roller 37 of which runs on a cam track 39 of a cam ring 41 located in the radial plane and guided in the pump housing 3.
- the pump pistons 27, 31 are held in contact with the roller tappets 35 by the centrifugal force when the distributor fuel injection pump is in operation.
- the pump pistons 27, 31 can move independently in the cylinder bores 25, 29.
- the short pump pistons 31 In order to avoid with certainty that a short pump piston 31 slips between the long pump pistons 27 into the region of the first cylinder bore 25, the short pump pistons 31 have a stop at their ends projecting radially from the second cylinder bore 29, which stops with the respective axial end wall 49 of the cylinder bore 29 cooperates.
- this stop is designed as a collar 43 formed by enlarging the cross section.
- the axial end stop on the short pump piston 31 is formed by a securing ring 45 which protrudes from the cylinder bore 29 in an annular groove 47 End of the short pump piston 31 is guided and also cooperates with the axial end wall 49 of the cylinder bore 29.
- the distributor fuel injection pump according to the invention works in the following manner.
- the pump pistons 27, 31 are in indefinite positions, depending on the position of the rotor part 1, when the pump work chamber 33 is depressurized, which can also be the respective maximum stroke positions.
- the rotor part 1 With the start of operation of the distributor fuel injection pump, the rotor part 1 is set into a rotating movement by the drive shaft 9, as a result of which the pump pistons 27, 31 are brought into contact with the roller tappet 35 by centrifugal force, which in turn run on the cam track 39 and so on set the pump pistons 27, 31 in a reciprocating motion in the cylinder bores 25, 29.
- the fuel compressed in the pump work chamber 33 during the delivery stroke of the pump pistons 27, 31 is guided via the delivery channel 13 and the check valve 15 to the distributor bore 17, from where it is supplied to the respective injection points when the individual injection lines 19 are passed over.
- the feed line 23 from the low-pressure chamber is at the time of the high-pressure delivery closed, this closing can take place via a solenoid valve arranged in the feed line 23 or the immersion of the suction bore 21 from the overlap with the feed bore 23.
- the end of the high-pressure delivery is regulated by reopening the connection between the supply line 21 and the fuel supply line 23.
- the high-pressure residual fuel initially flows back into the low-pressure chamber before the pump pistons 27, 31 are refilled during the suction stroke of the pump work chamber 33, the check valve 15 ensuring a constant stand pressure in the distributor bore 17 and the injection lines 19.
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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
Description
Die Erfindung geht von einer Verteilerkraftstoffeinspritzpumpe für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einer solchen aus der EP-A-0 382 388, die den nächstkommenden Stand der Technik bildet, bekannten Verteilerkraftstoffeinspitzpumpe treibt eine Antriebswelle einen in einem Gehäuse geführten Rotor an, in dem in einer radialen Ebene zur Antriebswelle zwei jeweils in einer Zylinderbohrung geführte Pumpenkolbenpaare angeordnet sind. Die in einer gemeinsamen radialen Ebene des Rotors angeordneten Zylinderbohrungen schneiden sich dabei rechtwinklig, so daß die einzelnen Pumpenkolben mit ihren radial einwärts weisenden Stirnflächen einen gemeinsamen Pumpenarbeitsraum in dem sich überschneidenden Bereich der Zylinderbohrungen begrenzen. Die Pumpenkolben laufen mit ihren aus den Zylinderbohrungen ragenden Enden mittels eines Rollenstößels auf einer ortsfesten Nockenbahn eines im Gehäuse geführten Nockenringes ab, so daß sie bei einer Drehbewegung des Rotors in eine hin- und hergehende Hubbewegung versetzt werden, wobei sie während der radial auswärts gerichteten Saughubbewegung die Verbindung der Zylinderbohrung mit einer von einem Niederdruckraum ausgehenden Fülleitung aufsteuern, die dann im anschließenden Förderhub durch die Pumpenkolben verschlossen wird. Der während des Förderhubs im gemeinsamen Pumpenarbeitsraum komprimierte Kraftstoff gelangt dann über einen Hochdruckkanal im Rotor zu einer radial von diesem abführenden Verteilerbohrung, die während der Drehbewegung des Rotors mit den einzelnen Hochdruckförderleitungen zu den Einspritzstellen in Überdeckung gelangt.The invention is based on a distributor fuel injection pump for internal combustion engines according to the preamble of claim 1. In such a distributor fuel injection pump known from EP-A-0 382 388, which forms the closest prior art, a drive shaft drives a rotor guided in a housing in which two pump piston pairs, each guided in a cylinder bore, are arranged in a radial plane to the drive shaft are. The arranged in a common radial plane of the rotor cylinder bores intersect at right angles, so that the individual pump pistons with their radially inward-facing end faces a common pump working space in the overlapping area of the Limit cylinder bores. The pump pistons run with their ends protruding from the cylinder bores by means of a roller tappet on a stationary cam track of a cam ring guided in the housing, so that they are set in a reciprocating stroke movement when the rotor rotates, whereby they move during the radially outward suction stroke movement open the connection of the cylinder bore with a filling line starting from a low-pressure chamber, which is then closed in the subsequent delivery stroke by the pump pistons. The fuel compressed in the common pump work space during the delivery stroke then passes via a high-pressure channel in the rotor to a distributor bore radially leading away from it, which overlaps with the individual high-pressure delivery lines to the injection points during the rotary movement of the rotor.
Die Pumpenkolbenpaare in den beiden Zylinderbohrungen sind dabei so ausgeführt, daß ein längeres, in einer ersten Zylinderbohrung geführtes Kolbenpaar mit seinem pumpenarbeitsraumzugewandten Ende in die zweite Zylinderbohrung hineinragt und das dort geführte kürzere Kolbenpaar die erste Zylinderbohrung auch in seiner maximalen Forderhublage nicht erreicht.The pump piston pairs in the two cylinder bores are designed so that a longer pair of pistons guided in a first cylinder bore protrudes into the second cylinder bore with its end facing the pump working space and the shorter piston pair guided there does not reach the first cylinder bore even in its maximum stroke position.
Dabei weist die bekannte Verteilerkraftstoffeinspritzpumpe jedoch den Nachteil auf, daß der für alle Pumpenkolben gleiche Nockenhub kleiner als der halbe Durchmesser der jeweils gleich groß ausgeführten Zylinderbohrungen sein muß. Dies ist dort notwendig um sicherzustellen, daß die langen Kolben auch in ihrer maximalen Saughublage noch in die zweite Zylinderbohrung eintaucht um ein selbständiges Verschieben der kürzeren Kolben zwischen die langen Kolben bei abgestellter Brennkraftmaschine und drucklosem Pumpenarbeitsraum sicher zu vermeiden, da dies ansonsten im Betrieb der Verteilereinspritzpumpe zu deren mechanischer Zerstörung führt.However, the known distributor fuel injection pump has the disadvantage that the cam stroke that is the same for all pump pistons must be less than half the diameter of the cylinder bores of the same size. This is necessary to ensure that the long pistons are still immersed in the second cylinder bore, even in their maximum suction stroke position, in order to move the shorter pistons independently between the long pistons when the internal combustion engine is switched off and the pump work chamber is depressurized Avoid safely, as this would otherwise lead to mechanical destruction of the distributor injection pump during operation.
Somit sind jedoch dem Förderhub der Pumpenkolben konstruktive Grenzen gesetzt, die die Leistungsparameter der gesamten Pumpe einschränken.However, the delivery stroke of the pump pistons is therefore subject to design limits which restrict the performance parameters of the entire pump.
Die erfindungsgemäße Verteilerkraftstoffeinspritzpumpe mit den Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß durch einen Anschlag am aus der Zylinderbohrung herausragenden Ende der kürzeren Pumpenkolben deren ungewolltes Hineingleiten in die Zylinderbohrung zwischen die langen Pumpenkolben sicher vermieden werden kann.The distributor fuel injection pump according to the invention with the features of claim 1 has the advantage that a stop at the end protruding from the cylinder bore of the shorter pump pistons, their unwanted sliding into the cylinder bore between the long pump pistons can be safely avoided.
Damit entfällt für die langen Pumpenkolben die Notwendigkeit eines ständigen Eintauchens in die die kurzen Pumpenkolben führende Zylinderbohrung, so daß der Nockenhub für eine größere Förderhubbewegung größer als der halbe Zylinderbohrungsdurchmesser ausgeführt werden kann. Diese Förderhubvergrößerung kann dabei in vorteilhafter Weise in eine Erhöhung des Einspritzdruckes oder eine größere Fördermenge umgesetzt werden.This eliminates the need for the long pump pistons to be constantly immersed in the cylinder bore guiding the short pump pistons, so that the cam stroke can be made larger than half the cylinder bore diameter for a larger delivery stroke movement. This increase in the delivery stroke can advantageously be converted into an increase in the injection pressure or a larger delivery amount.
Der Anschlag an den kurzen Pumpenkolben ist dabei in vorteilhafter Weise so angeordnet, daß er deren Eintauchen in die sie führende Zylinderbohrung so weit erlaubt, bis deren pumpenarbeitsraumzugewandte Stirnseite sich bis auf ein geringes Maß an die zweite Zylinderbohrung angenähert hat, so daß sich große Förderhubhöhen erreichen lassen. Dabei läßt sich der Anschlag an den kurzen Pumpenkolben in einfacher Weise durch einen Bund oder einen in einer Ringnut am Schaft der kurzen Kolben geführten Sicherungsring ausführen, die dann in einfacher Weise mit der Stirnwand der Zylinderbohrung zusammenwirken.The stop on the short pump piston is advantageously arranged in such a way that it allows them to be immersed in the cylinder bore leading them until their end face facing the pump work space has approached to a small extent the second cylinder bore, so that large delivery heights are reached to let. The stop on the short pump piston can be easily by a collar or in an annular groove Carry out a circlip on the shaft of the short pistons, which then simply interact with the end wall of the cylinder bore.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous configurations of the subject matter of the invention can be found in the description, the drawing and the claims.
Zwei Ausführungsbeispiele der erfindungsgemäßen Verteilerkraftstoffeinspritzpumpe sind in der Zeichnung dargestellt und werden im folgenden näher erläuteret.Two exemplary embodiments of the distributor fuel injection pump according to the invention are shown in the drawing and are explained in more detail below.
Es zeigen die Figur 1 einen Längsschnitt durch den erfindungswesentlichen Teil der Verteilerkraftstoffeinspritzpumpe, die Figur 2 ein erstes Ausführungsbeispiel der Pumpenkolbensicherung mittels eines Bundes in einem Schnitt aus der Figur 1 und die Figur 3 ein zweites Ausführungsbeispiel der Pumpenkolbensicherung mittels eines Sicherungsringes in einer analog zur Figur 2 gezeigten Darstellung.1 shows a longitudinal section through the part of the distributor fuel injection pump that is essential to the invention, FIG. 2 shows a first embodiment of the pump piston lock by means of a collar in a section from FIG. 1, and FIG. 3 shows a second embodiment of the pump piston lock by means of a lock ring in an analogous manner to FIG. 2 shown representation.
Bei der in der Figur 1 vereinfacht dargestellten Verteilerkraftstoffeinspritzpumpe ist ein kolbenförmiges Rotorteil 1 um seine Achse drehbar in einer Zylinderbohrung 2 eines zylinderförmigen, fest mit dem Pumpengehäuse 3 verbundenen Führungsteils 5 gelagert. Das Rotorteil 1 weist an seinem einen Ende ein im Durchmesser erweitertes Teil 7 auf, das verdrehfest mit einer synchron zur Brennkraftmaschinendrehzahl angetriebenen Antriebswelle 9 verbunden ist und in dem zwei einander rechtwinklig schneidende Durchgangsbohrungen 11 in einer gemeinsamen, radial zur Achse des Rotorteiles 1 verlaufenden Ebene angeordnet sind.In the distributor fuel injection pump shown in simplified form in FIG. 1, a piston-shaped rotor part 1 is mounted rotatably about its axis in a
Von diesen Durchgangsbohrungen 11 führt in der Achse des Rotorteiles 1 ein Förderkanal 13 ab, der ein Rückschlagventil 15 enthält und dessen Ende in eine radial verlaufende Verteilerbohrung 17 übergeht. In der Radialebene, in der diese Verteilerbohrung 17 angeordnet ist, weist das Führungsteil 5 Einspritzleitungen 19 auf, die ausgehend von der Zylinderbohrung 2 zu den einzelnen Einspritzstellen der Brennkraftmaschine fren. Dabei sind die Einspritzleitungen 19 entsprechend der Zahl der zu versorgenden Einspritzstellen und in einem entsprechenden Abstand zueinander am Umfang des Führungsteils 5 verteilt angeordnet.From these through
Desweiteren ist zwischen dem Rückschlagventil 15 und den Durchgangsbohrungen 11 eine radial vom Förderkanal 13 abführende Versorgungsbohrung 21 im Rotorteil 1 vorgesehen, die mit einer Kraftstoff zuführungsleitung 23 im Führungsteil 5 verbindbar ist, die ihrerseits an eine nicht dargestellte, vorzugsweise magnetventilgesteuerte, eine Förderpumpe aufweisende Kraftstofförderleitung aus einem einen Niederdruckraum bildenden Kraftstoffvorratsbehälter angeschlossen ist.Furthermore, between the
Die radialen Durchgangsbohrungen 11 im im Durchmesser erweiterten Teil 7 des Rotorteils 1 sind als Zylinderbohrungen ausgeführt, in denen, wie auch Figuren 2 und 3 entnehmbar, jeweils zwei einander gegenüberliegende und gegeneinander arbeitende Pumpenkolben angeordnet sind. Dabei nimmt eine erste Zylinderbohrung 25 ein erstes in seiner axialen Erstreckung langes Pumpenkolbenpaar 27 auf, dessen Pumpenkolben 27 so lang ausgeführt sind, daß sie während der radial einwärts gerichteten Förderhubbewegung bis in den Bereich einer zweiten, die erste schneidenden Zylinderbohrung 29 hineinragen. In dieser zweiten Zylinderbohrung 29 ist ein zweites kürzeres Pumpenkolbenpaar 31 geführt, dessen Pumpenkolben 31 so dimensioniert sind, daß sie auch in der maximalen Förderhubstellung nicht bis in den Bereich der ersten Zylinderbohrung 25 ragen. Mit ihren radial einwärts weisenden Stirnseiten begrenzen die Pumpenkolben 27, 31 einen gemeinsamen Pumpenarbeitsraum 33, in den Zylinderbohrungen 25, 29, der über den Förderkanal 13 mit den Einspritzleitungen 19 und der Kraftstoffzuführungsleitung 23 verbindbar ist.The radial through-
Mit ihren radial auswärts weisenden Enden liegen die Pumpenkolben 27, 31 jeweils an einem Rollenstößel 35 an, dessen Rolle 37 auf einer Nockenbahn 39 eines in der Radialebene liegenden, im Pumpengehäuse 3 geführten Nockenringes 41 abläuft. Die Pumpenkolben 27, 31 werden dabei im Betrieb der Verteilerkraftstoffeinspritzpumpe durch die Fliehkraft nach außen in Anlage an den Rollenstößeln 35 gehalten. Bei Stillstand der Pumpe können sich die Pumpenkolben 27, 31 je nach Lage des Rotorteiles 1 selbständig in den Zylinderbohrungen 25, 29 verschieben. Um dabei mit Sicherheit zu vermeiden, daß ein kurzer Pumpenkolben 31 zwischen die langen Pumpenkolben 27 in den Bereich der ersten Zylinderbohrung 25 hineinrutscht weisen die kurzen Pumpenkolben 31 an ihren radial aus der zweiten Zylinderbohrung 29 ragenden Enden einen Anschlag auf, der mit der jeweiligen axialen Stirnwand 49 der Zylinderbohrung 29 zusammenwirkt. Dieser Anschlag ist im in der Figur 2 gezeigten ersten Ausführungsbeispiel als durch eine Querschnittsvergrößerung gebildeter Bund 43 ausgebildet.With their radially outward-pointing ends, the
Bei dem in der Figur 3 dargestellten zweiten Ausführungsbeispiel wird der axiale Endanschlag an den kurzen Pumpenkolben 31 durch einen Sicherungsring 45 gebildet, der in einer Ringnut 47 am aus der Zylinderbohrung 29 herausragenden Ende der kurzen Pumpenkolben 31 geführt ist und ebenfalls mit der axialen Stirnwand 49 der Zylinderbohrung 29 zusammenwirkt.In the second exemplary embodiment shown in FIG. 3, the axial end stop on the
Diese Wegbegrenzung der maximalen Eintauchtiefen, die wenigstens gleich groß dem maximalen Nockenbzw. Förderhub sind, ermöglichen dabei, den Förderhub so groß auszulegen, daß die langen Pumpenkolben 27 mit ihren arbeitsraumseitigen Enden aus der zweiten Zylinderbohrung 29 austauchen können, ohne ein ungewolltes Hineinrutschen der kurzen Pumpenkolben 31 zwischen die langen befürchten zu müssen.This path limitation of the maximum immersion depth, which is at least equal to the maximum cam or. Delivery stroke, allow to design the delivery stroke so large that the
Die erfindungsgemäße Verteilerkraftstoffeinspritzpumpe arbeitet in folgender Weise.The distributor fuel injection pump according to the invention works in the following manner.
Im Stillstand der Pumpe befinden sich die Pumpenkolben 27, 31 bei drucklosem Pumpenarbeitsraum 33 je nach Lage des Rotorteiles 1 in unbestimmten Positionen, die auch die jeweiligen maximalen Hublagen sein können. Mit dem Beginn des Betriebs der Verteilerkraftstoffeinspritzpumpe wird das Rotorteil 1 durch die Antriebswelle 9 in eine rotierende Bewegung versetzt, in deren Folge die Pumpenkolben 27, 31 durch die Fliehkraft in Anlage an die Rollenstoßel 35 gebracht werden, die ihrerseits auf der Nockenbahn 39 ablaufen und so die Pumpenkolben 27, 31 in eine hinund hergehende Bewegung in den Zylinderbohrungen 25, 29 versetzen.When the pump is at a standstill, the
Der während des Förderhubs der Pumpenkolben 27, 31 im Pumpenarbeitsraum 33 komprimierte Kraftstoff wird dabei über den Förderkanal 13 und das Rückschlagventil 15 zu der Verteilerbohrung 17 geführt, von wo aus er beim Überfahren der einzelnen Einspritzleitungen 19 den jeweiligen Einspritzstellen zugeführt wird. Die Zuführungsleitung 23 vom Niederdruckraum ist dabei zum Zeitpunkt der Hochdruckförderung verschlossen, wobei dieses Verschließen über ein in der Zuführungsleitung 23 angeordnetes Magnetventil oder das Austauchen der Versogungsbohrung 21 aus der Überdeckung mit der Zufrungsbohrung 23 erfolgen kann.The fuel compressed in the
Das Ende der Hochdruckförderung wird durch das erneute Aufsteuern der Verbindung zwischen der Versorgungsleitung 21 und der Kraftstoffzufrungsleitung 23 geregelt. Dabei strömt der unter hohem Druck stehende Restkraftstoff zunächst zurück in den Niederdruckraum, bevor während des Saughubes der Pumpenkolben 27, 31 ein erneutes Befüllen des Pumpenarbeitsraumes 33 erfolgt, wobei das Rückschlagventil 15 einen konstanten Standdruck in der Verteilerbohrung 17 und den Einspritzleitungen 19 gewährleistet.The end of the high-pressure delivery is regulated by reopening the connection between the
Dabei ist es mit der erfindungsgemäßen Verteilerkraftstoffeinspritzpumpe somit ohne großen konstruktiven Aufwand möglich, die Größe des Förderhubes der Pumpenkolben in Abhängigkeit von den jeweiligen Anforderungen auf ein Maß zu vergrößern, bei dem das axial längere Pumpenkolbenpaar aus der das kürzere Pumpenkolbenpaar führenden Zylinderbohrung austaucht.It is thus possible with the distributor fuel injection pump according to the invention without great design effort to increase the size of the delivery stroke of the pump pistons depending on the respective requirements to a level at which the axially longer pump piston pair emerges from the cylinder bore that carries the shorter pump piston pair.
Claims (4)
- Distributor-type fuel injection pump for internal combustion engines with a cam drive which is driven in rotation by a drive shaft (9) and during the rotary motion of which a reciprocating motion is imparted to a pump plunger in a cylinder bore arranged radially relative to the drive shaft in a rotor part (1) by means of a roller tappet (35) running along a cam track (39), at least two intersecting cylinder bores being provided in the rotor part in a plane radial relative to the drive shaft, in each of which are arranged two mutually opposite pump plungers which delimit a common pump working space (33) alternately connectable to a low-pressure space (23) and an injection line (19) and which are moved radially inwards during the delivery stroke and the axial length of which is designed such that, during the delivery stroke movement, a first, longer pump-plunger pair (27) guided in a first cylinder bore (25) in each case enters a second cylinder bore (29) which guides a second pump-plunger pair (31) and the shorter pump plungers (31), guided therein, of which do not intersect the first cylinder bore (25) in their maximum deliverystroke position, characterized in that the pump plungers (31) of the second, shorter pump-plunger pair each have a stop at their end projecting out of the second cylinder bore (29), the said stop limiting their maximum depth of penetration into the cylinder bore (29) in the direction of the pump working space (33).
- Distributor-type fuel injection pump according to Claim 1, characterized in that the shorter pump plungers (31) each come to rest by their stop on the axial end wall (49) of the cylinder bore (29) which guides them before their pump working-space end enters the region of the other cylinder bore (25).
- Distributor-type fuel injection pump according to Claim 1, characterized in that the stop at the end of the short pump plungers (31) which projects out of the second cylinder bore (29) is designed as a collar (43) which is formed by an increasing cross section and which interacts with the axial end wall (49) of the second cylinder bore.
- Distributor-type fuel injection pump according to Claim 1, characterized in that the stop at the end of the short pump plungers (31) which projects out of the second cylinder bore (29) is formed by a retaining ring (45) which is guided in an annular groove (47) in the short pump plunger (31) and interacts with the axial end wall (49) of the second cylinder bore.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4338344A DE4338344A1 (en) | 1993-11-10 | 1993-11-10 | Distributor fuel injection pump for internal combustion engines |
| DE4338344 | 1993-11-10 | ||
| PCT/DE1994/001267 WO1995013469A1 (en) | 1993-11-10 | 1994-10-28 | Fuel-injection distributor pump for internal-combustion engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0678161A1 EP0678161A1 (en) | 1995-10-25 |
| EP0678161B1 true EP0678161B1 (en) | 1996-09-04 |
Family
ID=6502237
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP95900049A Expired - Lifetime EP0678161B1 (en) | 1993-11-10 | 1994-10-28 | Fuel-injection distributor pump for internal-combustion engines |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US5592920A (en) |
| EP (1) | EP0678161B1 (en) |
| JP (1) | JPH08505681A (en) |
| KR (1) | KR100333453B1 (en) |
| DE (2) | DE4338344A1 (en) |
| ES (1) | ES2092420T3 (en) |
| RU (1) | RU2133870C1 (en) |
| WO (1) | WO1995013469A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7048516B2 (en) * | 2003-06-09 | 2006-05-23 | Delphi Technologies, Inc. | High pressure fuel pump with multiple radial plungers |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3771506A (en) * | 1972-06-07 | 1973-11-13 | Stanadyne Inc | Fuel injection pump and automatic timing means therefor |
| US3938911A (en) * | 1973-02-28 | 1976-02-17 | Stanadyne, Inc. | Fuel injection pump with metering valve controlled cooling |
| FR2437502A1 (en) * | 1978-09-29 | 1980-04-25 | Cav Roto Diesel | FUEL INJECTION PUMP |
| DE3342993A1 (en) * | 1982-12-06 | 1984-06-07 | Nissan Motor Co., Ltd., Yokohama, Kanagawa | CONTROL DEVICE FOR THE FUEL INJECTION AMOUNT IN AN INTERNAL COMBUSTION ENGINE |
| DE3412834A1 (en) * | 1984-04-05 | 1985-10-24 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION PUMP |
| GB8410280D0 (en) * | 1984-04-19 | 1984-05-31 | Lumber P M P | Rotary distributor pump |
| DE3612942A1 (en) * | 1986-04-17 | 1987-10-22 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
| DE3719831A1 (en) * | 1987-06-13 | 1988-12-22 | Bosch Gmbh Robert | FUEL INJECTION PUMP |
| DE3816508A1 (en) * | 1988-05-14 | 1989-11-23 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINE |
| GB8902860D0 (en) * | 1989-02-09 | 1989-03-30 | Lucas Ind Plc | Fuel injection pump |
| US5215060A (en) * | 1991-07-16 | 1993-06-01 | Stanadyne Automotive Corp. | Fuel system for rotary distributor fuel injection pump |
| GB9315342D0 (en) * | 1993-07-23 | 1993-09-08 | Lucas Ind Plc | Fuel pumping apparatus |
-
1993
- 1993-11-10 DE DE4338344A patent/DE4338344A1/en not_active Withdrawn
-
1994
- 1994-10-28 WO PCT/DE1994/001267 patent/WO1995013469A1/en active IP Right Grant
- 1994-10-28 ES ES95900049T patent/ES2092420T3/en not_active Expired - Lifetime
- 1994-10-28 RU RU95117079A patent/RU2133870C1/en not_active IP Right Cessation
- 1994-10-28 EP EP95900049A patent/EP0678161B1/en not_active Expired - Lifetime
- 1994-10-28 JP JP7513522A patent/JPH08505681A/en active Pending
- 1994-10-28 US US08/464,896 patent/US5592920A/en not_active Expired - Fee Related
- 1994-10-28 KR KR1019950702839A patent/KR100333453B1/en not_active IP Right Cessation
- 1994-10-28 DE DE59400598T patent/DE59400598D1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| KR960700405A (en) | 1996-01-20 |
| DE4338344A1 (en) | 1995-05-11 |
| RU2133870C1 (en) | 1999-07-27 |
| US5592920A (en) | 1997-01-14 |
| WO1995013469A1 (en) | 1995-05-18 |
| DE59400598D1 (en) | 1996-10-10 |
| JPH08505681A (en) | 1996-06-18 |
| ES2092420T3 (en) | 1996-11-16 |
| KR100333453B1 (en) | 2002-09-17 |
| EP0678161A1 (en) | 1995-10-25 |
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