EP1438505B1 - Pump element and piston pump for generating high fuel pressure - Google Patents
Pump element and piston pump for generating high fuel pressure Download PDFInfo
- Publication number
- EP1438505B1 EP1438505B1 EP02760107A EP02760107A EP1438505B1 EP 1438505 B1 EP1438505 B1 EP 1438505B1 EP 02760107 A EP02760107 A EP 02760107A EP 02760107 A EP02760107 A EP 02760107A EP 1438505 B1 EP1438505 B1 EP 1438505B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- pump
- plate
- pump element
- foot
- 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.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/02—Fuel-injection apparatus having means for reducing wear
Definitions
- the invention relates to a pump element for a piston pump for fuel high pressure generation in fuel injection systems of internal combustion engines according to the preamble of claim 1 and piston pumps according to the independent claim 11th
- a radial piston pump is known in which the piston foot as well as the recess in the Kolbenfußplatte are flat.
- the diameter of the contact surface corresponds to the diameter of the piston foot.
- a high-pressure fuel pump in which a tappet is arranged between a cambered running drive shaft and a piston foot.
- the bottom of the bucket tappet is designed as a resilient element and in the piston foot a concave depression is formed.
- the bottom of the bucket tappet adapts to the drive shaft and the piston base depending on the load.
- the invention has for its object to provide a pump element and a piston pump for high-pressure fuel production, which is simple and has a further increased reliability under all operating conditions.
- the ring tends to carry out the mentioned unwanted rotational movements.
- the inventive design of the pump elements suppresses the rotational movements of the ring so far that no punctual overstressing of the pump element or the ring occur more.
- the life of the pump elements and the piston pump increases overall, without the manufacturing costs increase. Characterized in that the contact zone is greater than or equal to the cross-sectional area of the piston skirt, the unwanted tilting of the plate and the unwanted rotation of the ring are further reduced.
- the support surface of the piston base or the contact surface with the contact surface forming surface of the recess are curved with a radius greater than twenty times the diameter of the piston skirt , This large radius of curvature ensures that manufacturing tolerances can be compensated without tilting the plates or allowing rotational movement of the ring.
- the piston foot and the plate are positively connected to each other by a plate holder, so that the plate always rests on the ring, which prevents damage to these components and facilitates the formation of a viable lubricating film.
- the piston foot on a collar and the plate holder is connected via the Bund.mit the piston, so that on the one hand a large contact zone between the plate and piston base is possible and on the other hand a secure positive connection between the piston and plate holder is guaranteed.
- This solution is also easy to assemble because the number of components is very low.
- the piston foot may also have a groove with a blasting ring and the plate holder connected to the piston via the blasting ring so that the manufacture of the piston is further simplified.
- the plate holder is connected by forming, in particular by crimping or folding, with the plate, so that in a simple and effective way a permanently resilient connection of plate holder and plate is made.
- the plate may have a chamfer on the side facing the piston on the circumference.
- a particularly secure connection between plate holder and plate can be achieved if the plate has a collar and the plate holder encloses the collar.
- the plate can also be connected directly to the piston, in particular by crimping or folding.
- the number of components is further reduced, which has a positive effect on the manufacturing cost.
- a piston pump for fuel production in fuel injection systems of internal combustion engines in particular in a common rail fuel injection system, with at least one pump element, characterized in that the at least one pump element is a pump element according to one of the preceding claims.
- the advantages of the invention come fully into play.
- Fig. 1 is a section through a equipped with inventive pump elements 1 radial piston pump for fuel high pressure generation in injection systems of internal combustion engines.
- radial piston pump In this generally designated 3 radial piston pump three pump elements 1 are arranged at an angle of 120 ° to each other about a drive shaft 5. In the cutting plane of Fig. 1 an eccentric portion of the drive shaft 5 is shown. Above and below the plane of the drawing, the drive shaft 5 is rotatable in one Housing 7 of the radial piston pump 3 stored (not shown).
- a pump element 1 consists of a cylinder bore 9 and a piston 11 which is sealingly guided in the cylinder bore 9.
- the piston 11, in turn, consists of a piston shaft 13 and a piston foot 15.
- a plate 17 is fastened to the piston foot 15.
- a ring 19 is arranged with flats 21.
- This polygonal ring 19 serves to convert the rotational movement of the eccentric portion of the drive shaft 5 in an oscillating motion.
- the polygonal ring 19 should not rotate. This results in a sliding movement between the plate 17 and flattening 21. This sliding movement results in a tilting moment on the plate 17th
- a section of a first embodiment of a pump element 1 according to the invention is shown in cross section.
- a groove 25 is pierced in the piston 15, in the groove 25 a blasting ring 27 is inserted.
- the piston foot has a substantially flat bearing surface 29, which projects into a recess 31 of the plate 17. At the bottom 33 of the recess 31, the support surface 29 of the piston 15 is on. This results in a substantially flat contact zone between support surface 29 and the recess 31 and the bottom 33 of the recess 31st
- the contact zone (not designated in Fig. 2 ) is in the first embodiment as large as the cross section of the piston skirt 13, so that a very good introduction of the transmitted from the plate 17 to the piston 15 in the axial direction of the piston skirt 13 is present.
- the above-described rotary motion of the polygonal ring 19 (see FIG Fig. 1 )
- the radial piston pump 3 effectively prevented and there is always a flat contact zone between the piston 15 and plate 17 on the one hand and plate 17 and the flats 21 of the polygonal ring 19 is present. Therefore, it does not come to punctual overuse of the flats 21, the plate 17 or the piston foot 15. This results an increased life of the radial piston pump 3rd
- a plate holder 35 is provided, which receives the piston skirt 13 in an opening 37.
- a compression spring 39 which at one end is supported on the pump holder 35 and the other end on the housing 7 of the radial piston pump 3 is supported (see Fig. 1 ) presses the plate holder 35 from top dead center to bottom dead center when the eccentric portion of the drive shaft 5 (see FIG Fig. 1 ) performs the corresponding rotational movement.
- this movement is transmitted to the piston shaft 13.
- the plate 17 can not be detached from the piston 15, the plate holder 35 also has a bead 39, which surrounds a collar 41 of the plate 17.
- This in Fig. 2 illustrated embodiment is manufacturing technology very easy to represent, since the piston shaft 13 and the piston 15 have the same diameter and thus can be ground in one setting.
- the plate 17 has on the support surface 29, with the in Fig. 5 not shown ring 19 comes in Konatkt, a chamfer 40.
- the chamfer 40 causes that even with an occurring under unfavorable circumstances rotation of the polygon-shaped ring 19, not shown, the plate holder 35 is not damaged by the resulting tilting movement of the plate 17.
- the chamfer 40 can be provided in all embodiments of the pump element 1 according to the invention.
- a piston 11 of a second embodiment of a pump element according to the invention is shown.
- the adjoining the piston shaft 13 piston 15 has in this embodiment has a significantly larger diameter than the piston shaft 13. It is thereby achieved that the piston 15 has a flange 43.
- the support surface 29 of the piston foot 15 increases.
- the support surface 29 is slightly curved.
- Fig. 4 is one to the piston 11 of Fig. 3 associated plate 17 shown.
- the recess 31 is dimensioned so that the piston foot 15 fits exactly into the recess 31.
- Fig. 5 are the piston 11 and the plate 17 according to Fig. 3 and 4 shown in assembled condition.
- the plate holder 35 transmits the force exerted on it by the spring 38 via the collar 43 on the piston shaft 13.
- the groove 25 and the blasting ring 27 (see Fig. 2 ) accounted for.
- the contact zone between the piston foot 15 and plate 17 is greater than in the first embodiment.
- the surface load between the piston 15 and the base 33 of the recess 31 in the plate 17 is further reduced.
- that can Twisting the polygonal ring 19 see Fig. 1 ) be even more effectively prevented.
- the disc holder 35 has first lugs 36a bent upwardly. In alternation with the first lugs 36a, the plate holder 35 has second lugs 36b which are bent downwards. By the second lugs 36 b, the plate 17 is fixed to the piston 15.
- the plate 17 has on the bearing surface, with the in Fig. 5 not shown ring 19 comes in Konatkt, a chamfer 40.
- the chamfer 40 causes that even with an occurring under unfavorable circumstances rotation of the polygon-shaped ring 19, not shown, the plate holder 35 is not damaged by the resulting tilting movement of the plate 17.
- the chamfer 40 can be provided in all embodiments of the pump element 1 according to the invention.
- FIGS. 6 and 7 a plate 17 of a third embodiment of a pump element according to the invention in cross-section and in plan view is shown.
- no disc holder is provided.
- the necessary form-fitting connection between the piston skirt 13 (not shown) and plate 17 is produced via a flange 45.
- the beaded edge 45 is bent inwardly and pressed into a groove of the piston 11, not shown.
- the groove and the flange 45 must be dimensioned so that in any case the piston 15 (not shown) rests on the base 33 of the recess 31.
- recesses 47 are provided in the crimping edge 45.
- pump elements are not limited to radial piston pumps, but can also be used with in-line or distributor injection pumps.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Fuel-Injection Apparatus (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
Description
Die Erfindung betrifft ein Pumpenelement für eine Kolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1 sowie Kolbenpumpen nach dem nebengeordneten Anspruch 11.The invention relates to a pump element for a piston pump for fuel high pressure generation in fuel injection systems of internal combustion engines according to the preamble of claim 1 and piston pumps according to the independent claim 11th
Bei nahezu allen Bauarten von Kolbenpumpen wird die Drehbewegung einer Antriebswelle in eine oszillierende Bewegung des Kolbens eines Pumpenelements umgewandelt. Bei sog. innen abgestützten Radialkolbenpumpen zur Kraftstoffhochdruckerzeugung in Kraftstoffeinspritzsystemen von Brennkraftmaschinen sind beispielsweise radial zu einer in einem Pumpengehäuse gelagerten Antriebswelle mehrere Pumpenelemente angeordnet. Die Kolben der Pumpenelemente werden von einem exzentrischen Abschnitt der Antriebswelle oder von Nocken der Antriebswelle betätigt. Wegen der hohen Drücke, auf die der Kraftstoff gebracht werden muss, sind die von der Antriebswelle auf die Kolben zu übertragenden Kräfte sehr groß. Bei der Übertragung der Drehbewegung der Antriebswelle in die oszillierende Bewegung der Kolben der Pumpenelemente treten auch in Umfangsrichtung der Antriebswelle wirkende Kräfte zwischen Antriebswelle und Kolben auf. Ähnliche Effekte treten auch zwischen der Antriebswelle und den Kolben von Reiheneinspritzpumpen oder Verteilereinspritzpumpen auf.In almost all types of piston pumps, the rotational movement of a drive shaft is converted into an oscillating movement of the piston of a pump element. In so-called internally supported radial piston pumps for fuel high pressure generation in fuel injection systems of internal combustion engines, for example, a plurality of pump elements are arranged radially to a drive shaft mounted in a pump housing. The pistons of the pump elements are actuated by an eccentric portion of the drive shaft or by cams of the drive shaft. Because of the high pressures to which the fuel must be brought, the forces to be transmitted from the drive shaft to the pistons are very large. In the transmission of the rotational movement of the drive shaft in the oscillating movement of the piston of the pump elements occur in the circumferential direction of the drive shaft acting forces between the drive shaft and piston. Similar effects also occur between the drive shaft and the pistons of in-line injection pumps or distributor injection pumps.
Zur Verringerung des Verschleißes zwischen Kolben und Antriebswelle ist es aus der
Bei der aus der
Aus der
Aus der
From the
Aus der
Aus der
Allen aus dem Stand der Technik bekannten Lösungen ist gemeinsam, dass sie das Verdrehen des Rings mit den Abflachungen nicht unterdrücken und/oder den aus dem Verdrehen des Rings resultierenden Belastungen nicht standhalten.All known from the prior art solutions have in common that they do not suppress the rotation of the ring with the flats and / or not withstand the resulting from the rotation of the ring loads.
Der Erfindung liegt die Aufgabe zugrunde, ein Pumpenelement und eine Kolbenpumpe zur Kraftstoffhochdruckerzeugung bereitzustellen, welche einfach aufgebaut ist und eine weiter gesteigerte Zuverlässigkeit unter allen Betriebszuständen aufweist.The invention has for its object to provide a pump element and a piston pump for high-pressure fuel production, which is simple and has a further increased reliability under all operating conditions.
Diese Aufgabe wird erfindungsgemäß bei einem gattungsgemäßen Pumpenelement für eine Kolbenpumpe zur Kraftstoffhochdruckerzeugung mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst.This object is achieved in a generic pump element for a piston pump for fuel high pressure generation with the characterizing features of claim 1.
Durch die ebene Kontaktzone zwischen der Auflagefläche und der Vertiefung ist es möglich, die in axialer Richtung des Kolbens zu übertragenden Kräfte auf einer großen Fläche gleichmäßig zu übertragen. Außerdem kann durch die ebene Kontaktfläche verhindert werden, dass die Platte eine Kippbewegung ausführt, welche die Hin- und Herbewegungen in tangentialer Richtung des auf der Antriebswelle gelagerten Rings verursachen, bzw. ermöglichen. Dadurch wird erreicht, dass der Ring in allen Betriebszuständen der Kraftstoffhochdruckpumpe keine oder nur eine sehr kleine Drehbewegung ausführt und somit die Biegebeanspruchung der Platte und des Kolbens verringert wird. Dies ist vor allem von Bedeutung, wenn die Pumpenelemente nicht die volle Fördermenge fördern, sondern durch eine entsprechende Drosselung des Kraftstoffzuflusses nur teilweise befällt werden. Bei der teilweisen Befüllung der Pumpenelemente kommt es zur Dampfblasenbildung in den Pumpenelementen, was eine ungleichförmige Drehmomentübertragung von der Antriebswelle auf die Pumpenelemente mit sich bringt. Infolgedessen neigt der Ring dazu die erwähnten unerwünschten Drehbewegungen auszuführen. Die erfindungsgemäße Ausgestaltung der Pumpenelemente unterdrückt die Drehbewegungen des Rings so weit, dass keine punktuellen Überbeanspruchungen des Pumpenelements oder des Rings mehr vorkommen. Dadurch erhöht sich die Lebensdauer der Pumpenelemente und der Kolbenpumpe insgesamt, ohne dass die Herstellungskosten zunehmen. Dadurch, dass die Kontaktzone größer oder gleich der Querschnittsfläche des Kolbenschafts ist, werden das unerwünschte Kippen der Platte und die unerwünschte Drehbewegung des Rings weiter verringert.Due to the flat contact zone between the support surface and the recess, it is possible to transmit the forces to be transmitted in the axial direction of the piston uniformly over a large area. In addition, can be prevented by the flat contact surface that the plate performs a tilting movement, which cause the reciprocating movements in the tangential direction of the mounted on the drive shaft ring, or allow. This ensures that the ring performs no or only a very small rotational movement in all operating states of the high-pressure fuel pump and thus the bending stress of the plate and the piston is reduced. This is particularly important if the pump elements do not promote the full flow, but are only partially affected by a corresponding throttling of the fuel flow. During the partial filling of the pump elements, vapor bubble formation occurs in the pump elements, resulting in nonuniform torque transmission from the drive shaft to the pump elements. As a result, the ring tends to carry out the mentioned unwanted rotational movements. The inventive design of the pump elements suppresses the rotational movements of the ring so far that no punctual overstressing of the pump element or the ring occur more. As a result, the life of the pump elements and the piston pump increases overall, without the manufacturing costs increase. Characterized in that the contact zone is greater than or equal to the cross-sectional area of the piston skirt, the unwanted tilting of the plate and the unwanted rotation of the ring are further reduced.
Um kleine Fertigungsungenauigkeiten oder Schiefstellungen der Längsachse der Kolben relativ zur Längsachse der Antriebswelle ausgleichen zu können, kann außerdem vorgesehen sein, dass die Auflagefläche des Kolbenfußes oder die mit der Auflagefläche die Kontaktzone bildende Fläche der Vertiefung mit einem Radius größer zwanzigmal dem Durchmesser des Kolbenschafts gekrümmt sind. Bei diesem großen Krümmungsradius ist gewährleistet, dass Fertigungstoleranzen ausgeglichen werden können, ohne dass ein Kippen der Platten oder eine Drehbewegung des Rings ermöglicht würde.In order to compensate for small manufacturing inaccuracies or misalignment of the longitudinal axis of the piston relative to the longitudinal axis of the drive shaft, may also be provided that the support surface of the piston base or the contact surface with the contact surface forming surface of the recess are curved with a radius greater than twenty times the diameter of the piston skirt , This large radius of curvature ensures that manufacturing tolerances can be compensated without tilting the plates or allowing rotational movement of the ring.
In weiterer Ausgestaltung der Erfindung ist vorgesehen, dass der Kolbenfuß und die Platte durch einen Plattenhalter formschlüssig miteinander verbunden sind, so dass die Platte stets auf dem Ring anliegt, was Beschädigungen dieser Bauteile verhindert und die Ausbildung eines tragfähigen Schmierfilms erleichtert.In a further embodiment of the invention, it is provided that the piston foot and the plate are positively connected to each other by a plate holder, so that the plate always rests on the ring, which prevents damage to these components and facilitates the formation of a viable lubricating film.
Bei einer weiteren vorteilhaften Ausgestaltung der Erfindung weist der Kolbenfuß einen Bund auf und ist der Plattenhalter über den Bund.mit dem Kolben verbunden, so dass einerseits eine große Kontaktzone zwischen Platte und Kolbenfuß möglich wird und andererseits ein sicherer Formschluss zwischen Kolben und Plattenhalter gewährleistet ist. Diese Lösung ist auch einfach zu montieren, da die Zahl der Bauteile sehr gering ist.In a further advantageous embodiment of the invention, the piston foot on a collar and the plate holder is connected via the Bund.mit the piston, so that on the one hand a large contact zone between the plate and piston base is possible and on the other hand a secure positive connection between the piston and plate holder is guaranteed. This solution is also easy to assemble because the number of components is very low.
Alternativ kann der Kolbenfuß auch eine.Nut mit einem Spreng-Ring aufweisen und der Plattenhalter über den Spreng-Ring mit dem Kolben verbunden sein, so dass die Herstellung des Kolbens weiter vereinfacht wird.Alternatively, the piston foot may also have a groove with a blasting ring and the plate holder connected to the piston via the blasting ring so that the manufacture of the piston is further simplified.
Bei weiteren Ausgestaltungen der Erfindung kann vorgesehen sein, dass der Plattenhalter durch Umformen, insbesondere durch Bördeln oder Falzen, mit der Platte verbunden wird, so dass auf einfache und wirkungsvolle Weise eine dauerhaft belastbare Verbindung von Plattenhalter und Platte hergestellt wird.In further embodiments of the invention can be provided that the plate holder is connected by forming, in particular by crimping or folding, with the plate, so that in a simple and effective way a permanently resilient connection of plate holder and plate is made.
Zur Erleichterung der Montage kann die Platte auf der zu dem Kolben gewandten Seite am Umfang eine Fase aufweisen.To facilitate assembly, the plate may have a chamfer on the side facing the piston on the circumference.
Eine besonders sichere Verbindung zwischen Plattenhalter und Platte kann erreicht werden, wenn die Platte einen Bund aufweist und der Plattenhalter den Bund umschließt.A particularly secure connection between plate holder and plate can be achieved if the plate has a collar and the plate holder encloses the collar.
Alternativ kann die Platte auch direkt mit dem Kolben, insbesondere durch Bördeln oder Falzen, verbunden werden. Bei dieser Ausführungsvariante wird die Zahl der Bauteile nochmals reduziert, was sich positiv auf die Herstellungskosten auswirkt.Alternatively, the plate can also be connected directly to the piston, in particular by crimping or folding. In this embodiment, the number of components is further reduced, which has a positive effect on the manufacturing cost.
Es hat sich auch als vorteilhaft herausgestellt, wenn an der Platte ein Bördelrand ausgebildet ist und der Bördelrand in die Nut des Kolbens eingreift oder den Bund des Kolbens umschließt, da bei diesen Ausführungsbeispielen die o. g. Vorteile ebenfalls zum Tragen kommen.It has also been found to be advantageous if a flanged edge is formed on the plate and the flanged edge engages in the groove of the piston or surrounds the collar of the piston, since in these embodiments, the o. Benefits also come into play.
Die eingangs genannte Aufgabe wird auch bei einer Kolbenpumpe zur Kraftstofferzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail-Kraftstoffeinspritzsystem, mit mindestens einem Pumpenelement, dadurch gelöst, dass das mindestens eine Pumpenelement ein Pumpenelement nach einem der vorhergehenden Ansprüche ist. Bei dieser Kolbenpumpe kommen die erfindungsgemäßen Vorteile voll zum Tragen. Insbesondere hat es sich als vorteilhaft erwiesen, die erfindungsgemäße Kolbenpumpe als Radialkolbenpumpe gemäß den Ansprüchen 13 oder 14 auszuführen.The aforementioned object is also achieved in a piston pump for fuel production in fuel injection systems of internal combustion engines, in particular in a common rail fuel injection system, with at least one pump element, characterized in that the at least one pump element is a pump element according to one of the preceding claims. In this piston pump, the advantages of the invention come fully into play. In particular, it has proved to be advantageous to carry out the piston pump according to the invention as a radial piston pump according to
Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Zeichnung, deren Beschreibung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention are the following drawings, the description and the claims removable.
Es zeigen:
- Figur 1
- einen Querschnitt durch ein als Radialkolbenpumpe ausgeführtes Ausführungsbeispiel einer erfindungsfgemäßen Kraftstoffhochdruckpumpe,
- Figur 2
- eine detaillierte Darstellung des ersten Ausführungsbeispiels eines erfindungsgemäßen Pumpenelements,
- Fig. 3-5
- ein zweites Ausführungsbeispiel eines erfindungsgemäßen Pumpenelements und
- Fig. 6-7
- einen Querschnitt und eine Draufsicht auf ein drittes Ausführungsbeispiel einer erfindungsgemäßen Platte.
- FIG. 1
- a cross section through a designed as a radial piston pump embodiment of a erfindungsfgemäßen high-pressure fuel pump,
- FIG. 2
- a detailed representation of the first embodiment of a pump element according to the invention,
- Fig. 3-5
- A second embodiment of a pump element according to the invention and
- Fig. 6-7
- a cross section and a plan view of a third embodiment of a plate according to the invention.
In
Bei dieser insgesamt mit 3 bezeichneten Radialkolbenpumpe sind drei Pumpenelemente 1 in einem Winkel von jeweils 120° zueinander um eine Antriebswelle 5 angeordnet. In der Schnittebene von
Ein Pumpenelement 1 besteht aus einer Zylinderbohrung 9 und einem Kolben 11, der in der Zylinderbohrung 9 dichtend geführt ist. Der Kolben 11 wiederum besteht aus einem Kolbenschaft 13 und einem Kolbenfuß 15. An dem Kolbenfuß 15 ist eine Platte 17 befestigt.A pump element 1 consists of a
Zwischen dem in
Wenn die oberhalb der Kolben 11 angeordneten Förderräume 23 der Pumpenelemente im Teillastbetrieb der Radialkolbenpumpe 3 nur teilweise mit Kraftstoff befüllt werden (nicht dargestellt), ist die von der Antriebswelle 5 über den Ring 19 auf die Pumpenelemente 1 übertragene Leistung ungleichförmig. Als Folge davon neigt der polygonförmige Ring 19 dazu, sich etwas in der Drehrichtung der Antriebswelle 5 zu verdrehen. Daraus resultiert ein erhebliches Biegemoment auf die Platten 17. Durch die erfindungsgemäße Ausgestaltung der Erfindung von Kolbenfuß 15 und Platten 17 ist es möglich, diese unerwünschte Drehbewegung des polygonförmigen Rings 19 in allen Betriebszuständen zu unterbinden oder so stark zu reduzieren, dass sie sich nicht mehr nachteilig auf die Lebensdauer der Radialkolbenpumpe 3 bzw. ihrer Pumpenelemente 1 auswirkt. In den nachfolgenden Zeichnungen sind Ausführungsbeispiele erfindungsgemäßer Pumpenelemente dargestellt und werden nachfolgend beschrieben.If the
In
Der Kolbenfuß weist eine im Wesentlichen ebene Auflagefläche 29 auf, welche in eine Vertiefung 31 der Platte 17 ragt. Am Grund 33 der Vertiefung 31 liegt die Auflagefläche 29 des Kolbenfußes 15 auf. Dadurch ergibt sich eine im Wesentlichen ebene Kontaktzone zwischen Auflagefläche 29 und der Vertiefung 31 bzw. dem Grund 33 der Vertiefung 31.The piston foot has a substantially
Die Kontaktzone (nicht bezeichnet in
Damit der Kolbenschaft 13 nach dem Erreichen des oberen Totpunkts (nicht dargestellt) wieder zum unteren Totpunkt (nicht dargestellt) bewegt wird, ist ein Plattenhalter 35 vorgesehen, welcher in einer Öffnung 37 den Kolbenschaft 13 aufnimmt. Durch den Spreng-Ring 27 kann eine Kraft vom Plattenhalter 35 in Richtung Kolbenfuß 15 auf den Kolbenschaft 13 übertragen werden. Eine Druckfeder 39, welche sich einenends an dem Pumpenhalter 35 abstützt und anderenends an dem Gehäuse 7 der Radialkolbenpumpe 3 abstützt (siehe
Die Platte 17 weist an der Auflagefläche 29, die mit dem in
In
In
In
Um die Feder 38 zu zentrieren, weist der Plattenhalter 35 erste Nasen 36a auf, die nach oben gebogen sind. Im Wechsel mit den ersten Nasen 36a weist der Plattenhalter 35 zweite Nasen 36b auf, die nach unten gebogen sind. Durch die zweiten Nasen 36b wird die Platte 17 am Kolbenfuß 15 fixiert.To center the
Die Platte 17 weist an der Auflagefläche, die mit dem in
In den
Die vorstehend beschriebenenen Ausführungsbeispiele von Pumpenelementen sind nicht auf Radialkolbenpumpen beschränkt, sondern können auch bei Reihen- oder Verteilereinspritzpumpen eingesetzt werden.The above-described embodiments of pump elements are not limited to radial piston pumps, but can also be used with in-line or distributor injection pumps.
Claims (14)
- Pump element for a piston pump (3) for generating high fuel pressure in fuel injection systems of internal combustion engines, comprising at least one piston (11) arranged in a cylinder bore (9), wherein the piston (11) has a piston foot (15) and a piston shank (13), comprising a plate (17) attached to the piston foot (15) for transmitting the pumping motion from a drive (5) to the piston (11), wherein the piston foot (15) has a bearing surface (29) interacting with a recess (31) in the plate (17), wherein the bearing surface (29) and the recess (31) form a contact zone, characterized in that the piston foot (15) has a larger diameter than the piston shank (13), in that the piston foot (15) fits exactly into the recess (31), and in that the contact zone is larger than the cross-sectional area of the piston shank (13).
- Pump element according to Claim 1, characterized in that the bearing surface (29) is convexly curved, preferably with a radius greater than 20x the diameter of the piston shank (13).
- Pump element according to either of the preceding claims, characterized in that the piston foot (15) and the plate (17) are connected to one another in a positive-locking manner by a plate holder (35).
- Pump element according to Claim 3, characterized in that the piston foot (15) has a collar (43), and in that the plate holder (35) is connected to the piston (11) via the collar (43).
- Pump element according to Claim 4, characterized in that the piston foot (15) has a groove (25) with a snap ring (27), and in that the plate holder (35) is supported on the snap ring (27).
- Pump element according to one of Claims 3 to 5, characterized in that the plate holder (35) is connected to the plate (17) by shaping, in particular by flanging or folding.
- Pump element according to one of Claims 3 to 6, characterized in that the plate (17) has a bevel at the periphery on the side facing the piston (11).
- Pump element according to one of Claims 3 to 7, characterized in that the plate (17) has a collar (41), and in that the plate holder (35) encloses the collar (41).
- Pump element according to one of the preceding claims, characterized in that the plate (17) has a bevel (40) at its bearing surface facing the polygonal ring (19).
- Pump element according to Claim 9, characterized in that a flanged edge (45) is formed on the plate (17), and in that the flanged edge (45) engages in the groove (25) of the piston (11) or encloses the collar (43) of the piston (11).
- Piston pump for generating high fuel pressure in fuel injection systems of internal combustion engines, in particular in a common-rail injection system, comprising at least one pump element (1), characterized in that the at least one pump element (1) is a pump element (1) according to one of the preceding claims.
- Piston pump according to Claim 11, characterized in that the piston pump is designed as a radial piston pump.
- Piston pump according to Claim 12, characterized in that the piston pump is designed as a radial piston pump comprising a drive shaft (5) which is mounted in a pump housing (7) and is of eccentric design and comprising preferably a plurality of pump elements (1) arranged radially with respect to the drive shaft (5), wherein the pistons (11) are movable in a reciprocating manner in the radial direction in the respective cylinder space by rotation of the drive shaft (5), and wherein a ring (27) having flats (21) is arranged between the drive shaft and the plate (17).
- Piston pump according to Claim 11, characterized in that the piston pump is designed as a distributor or in-line pump.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10150351A DE10150351A1 (en) | 2001-10-15 | 2001-10-15 | Pump element and piston pump for high-pressure fuel generation |
DE10150351 | 2001-10-15 | ||
PCT/DE2002/002780 WO2003042534A2 (en) | 2001-10-15 | 2002-07-27 | Pump element and piston pump for generating high fuel pressure |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1438505A2 EP1438505A2 (en) | 2004-07-21 |
EP1438505B1 true EP1438505B1 (en) | 2009-12-16 |
Family
ID=7702265
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02760107A Expired - Lifetime EP1438505B1 (en) | 2001-10-15 | 2002-07-27 | Pump element and piston pump for generating high fuel pressure |
Country Status (6)
Country | Link |
---|---|
US (1) | US7384246B2 (en) |
EP (1) | EP1438505B1 (en) |
JP (1) | JP2005509782A (en) |
AT (1) | ATE452290T1 (en) |
DE (2) | DE10150351A1 (en) |
WO (1) | WO2003042534A2 (en) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10157375A1 (en) * | 2001-11-22 | 2003-06-05 | Daimler Chrysler Ag | high pressure pump |
DE102007019261A1 (en) | 2007-04-17 | 2008-10-23 | Golle Motor Ag | Radial piston pump, esp. For Common Rail (CR) injection systems |
HUE026768T2 (en) * | 2007-10-12 | 2016-07-28 | Delphi Int Operations Luxembourg Sarl | Improvements relating to fuel pumps |
DE102007060772A1 (en) * | 2007-12-17 | 2009-06-18 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump |
DE102008000824A1 (en) * | 2008-03-26 | 2009-10-01 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump |
JP5633387B2 (en) * | 2011-01-24 | 2014-12-03 | 株式会社デンソー | Fuel supply pump |
GB201202221D0 (en) * | 2012-02-09 | 2012-03-28 | Delphi Tech Holding Sarl | Improvements relating to fuel pumps |
CN103726964A (en) * | 2012-10-16 | 2014-04-16 | 北京亚新科天纬油泵油嘴股份有限公司 | Oil absorption control device for high-pressure common rail pump |
US10694995B2 (en) * | 2017-12-05 | 2020-06-30 | Renegade Optophysics, Llc | Diagnostic eye goggle system |
DE102019202336A1 (en) * | 2019-02-21 | 2020-08-27 | Robert Bosch Gmbh | Eccentric drive of an eccentric pump |
DE102020104313B3 (en) * | 2020-02-19 | 2021-01-28 | Schaeffler Technologies AG & Co. KG | Plunger for acting on a pump piston of a high-pressure fuel pump |
CN111336103A (en) * | 2020-04-15 | 2020-06-26 | 四川洪量联创科技有限公司 | Mechanical partition plate double-cam displacement pump |
CN115306670B (en) * | 2022-01-21 | 2023-06-16 | 衢州学院 | Compressor optimizing structure based on TRIZ principle |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2303865A (en) * | 1938-07-25 | 1942-12-01 | Pleasantaire Corp | Air conditioning apparatus |
US2302865A (en) * | 1942-01-16 | 1942-11-24 | Hydraulic Controls Inc | Pump |
US4690620A (en) * | 1980-08-19 | 1987-09-01 | Karl Eickmann | Variable radial piston pump |
DE59102642D1 (en) * | 1991-05-07 | 1994-09-29 | Hauhinco Maschf | High pressure water pump for pure water. |
DE4401074B4 (en) * | 1994-01-15 | 2007-01-18 | Robert Bosch Gmbh | Pump arrangement, in particular for conveying fuel from a reservoir to an internal combustion engine |
IT239879Y1 (en) * | 1996-12-23 | 2001-03-13 | Elasis Sistema Ricerca Fiat | REFINEMENTS TO A PISTON PUMP, IN PARTICULAR TO A RADIAL APISTON PUMP FOR THE FUEL OF AN INTERNAL COMBUSTION ENGINE. |
DE19758485B4 (en) * | 1997-07-11 | 2006-03-09 | Robert Bosch Gmbh | Sealing element for pressure medium lines |
DE19802475A1 (en) * | 1998-01-23 | 1999-07-29 | Bosch Gmbh Robert | Radial piston pump to supply fuel at high pressure for fuel injection system of internal combustion engine |
DE19804275A1 (en) * | 1998-02-04 | 1999-08-12 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel supply |
DE19809315A1 (en) * | 1998-03-05 | 1999-09-09 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel generation |
DE19814506A1 (en) * | 1998-04-01 | 1999-10-14 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel supply |
DE19816044C2 (en) * | 1998-04-09 | 2002-02-28 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel generation |
DE19829546A1 (en) * | 1998-07-02 | 2000-01-13 | Bosch Gmbh Robert | Radial piston pump |
DE19836901C2 (en) * | 1998-08-14 | 2002-08-29 | Bosch Gmbh Robert | Radial piston pump |
DE19943160A1 (en) * | 1998-09-10 | 2000-03-16 | Denso Corp | Fuel injection pump for supplying high pressure fuel to internal combustion engine comprises pump housing, cylinder and cavity arranged concentrically to each other in pump housing |
DE19847044C2 (en) * | 1998-10-13 | 2002-06-27 | Bosch Gmbh Robert | Radial piston pump |
JP4016237B2 (en) * | 1999-04-16 | 2007-12-05 | 株式会社デンソー | Fuel injection pump |
-
2001
- 2001-10-15 DE DE10150351A patent/DE10150351A1/en not_active Withdrawn
-
2002
- 2002-07-27 WO PCT/DE2002/002780 patent/WO2003042534A2/en active Application Filing
- 2002-07-27 EP EP02760107A patent/EP1438505B1/en not_active Expired - Lifetime
- 2002-07-27 DE DE50214103T patent/DE50214103D1/en not_active Expired - Lifetime
- 2002-07-27 US US10/450,175 patent/US7384246B2/en not_active Expired - Lifetime
- 2002-07-27 JP JP2003544334A patent/JP2005509782A/en active Pending
- 2002-07-27 AT AT02760107T patent/ATE452290T1/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
EP1438505A2 (en) | 2004-07-21 |
US20040089146A1 (en) | 2004-05-13 |
WO2003042534A2 (en) | 2003-05-22 |
US7384246B2 (en) | 2008-06-10 |
ATE452290T1 (en) | 2010-01-15 |
WO2003042534A3 (en) | 2003-08-14 |
DE50214103D1 (en) | 2010-01-28 |
DE10150351A1 (en) | 2003-05-08 |
JP2005509782A (en) | 2005-04-14 |
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