EP1738074B1 - Radial piston pump - Google Patents

Radial piston pump Download PDF

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Publication number
EP1738074B1
EP1738074B1 EP04804728A EP04804728A EP1738074B1 EP 1738074 B1 EP1738074 B1 EP 1738074B1 EP 04804728 A EP04804728 A EP 04804728A EP 04804728 A EP04804728 A EP 04804728A EP 1738074 B1 EP1738074 B1 EP 1738074B1
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EP
European Patent Office
Prior art keywords
pump
radial piston
lubrication pockets
lubrication
pockets
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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 - Fee Related
Application number
EP04804728A
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German (de)
French (fr)
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EP1738074A1 (en
Inventor
Uwe Nigrin
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Continental Automotive GmbH
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Continental Automotive GmbH
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Publication of EP1738074A1 publication Critical patent/EP1738074A1/en
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    • 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
    • F04B1/0413—Cams
    • 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
    • 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

Definitions

  • the invention relates to a radial piston pump, in particular a radial piston high-pressure pump for a fuel injection system, according to the preamble of patent claim 1.
  • a generic radial piston pump is from the DE 100 39 210 A1 known.
  • the radial piston pump has a drive shaft with an eccentric portion which is rotatably mounted in a pump housing. On the eccentric shaft portion a cam ring is slidably mounted.
  • the radial piston pump has three at a distance of 120 ° to each other arranged pump units. Each pump unit has a radially in the pump housing longitudinally movably guided pump piston.
  • the pump pistons abut each other on a sliding shoe, which is supported on the lifting ring.
  • the cam ring has a number of flats corresponding to the number of pump pistons.
  • In pump operation there is a relative movement between the sliding surface of the shoe and the flattening of the cam ring. Due to the relative movement, there is a high degree of closure of the components. In addition, the relative movement causes transverse forces are introduced into the pump piston, which can lead to a clamping of the piston.
  • the DE 196 35 164 A1 proposes to reduce the friction to form lubrication grooves in the flats on the cam ring, which are mounted substantially transversely to the relative movement between the piston and cam.
  • the DE 198 36 901 C2 which describes the closest prior art, proposes to form in the flattening of the cam ring lubricating grooves, which are arranged parallel to the direction of movement of the respective flattening relative to the associated piston.
  • the US 6,350,107 B1 discloses a radial piston pump with multiple pistons.
  • the plates each have a recess for reducing stresses in the center of the plate.
  • a disadvantage of such lubrication grooves is that the cross-sectional area of the lubrication grooves is relatively large in relation to the cross-sectional area of the entire flattening. As a result, the bearing surface decreases the flattening, causing increased wear occurs. In addition, the oil can be easily pushed out of the lubrication grooves, so that at high speeds no adequate lubrication of the sliding surfaces is guaranteed.
  • the radial piston pump according to the invention is characterized according to a first aspect in that in the flats of the cam ring and / or in the respective sliding surface of the shoe lubricating pockets are formed, the lubrication pockets are arranged at a regular distance from each other, and the lubrication pockets are arranged like a matrix or checkerboard.
  • a particularly good lubrication can be achieved.
  • the lubrication pockets support the construction of a hydrodynamic lubricating wedge during the relative movement of the slide shoe and the lifting ring.
  • the matrix-like or checkered arrangement allows the construction of a particularly uniform lubrication gap.
  • the radial piston pump according to the invention is characterized according to a second aspect in that in the flats of the cam ring and / or in the respective sliding surface of the shoe lubricating pockets are formed, the lubrication pockets are arranged at a regular distance from each other, and the lubrication pockets are arranged on circular paths, the run concentric to each other. This also makes it possible to achieve a particularly uniform lubrication gap.
  • the lubrication pockets preferably have an oval or triangular cross-section.
  • the lubrication pockets are arranged such that their longitudinal axis is preferably in the direction of the relative movement.
  • the bottom of the lubrication pockets has a constant depth.
  • Lubrication pockets with constant depth are particularly easy and inexpensive to manufacture.
  • the bottom of the lubrication pockets on an inclined surface additionally supports the construction of a hydrodynamic lubricating wedge.
  • the inclined surface is formed to the flattening of the cam ring or the sliding surface of the sliding block.
  • the structure of the hydrodynamic lubricating wedge is further advantageously influenced.
  • the lubrication pockets are dome-shaped or hemispherical in shape. Such training The lubrication pockets are particularly easy to produce.
  • the cross-sectional areas of the individual lubrication pockets are small with respect to the cross-sectional area of the entire flattening of the cam ring or the sliding surface of the slide shoe.
  • the cross-sectional area of the individual lubrication pockets is less than 1% of the cross-sectional area of the entire flattening of the cam ring or the sliding surface. This results in a sufficiently good lubricating wedge and for other a sufficiently large contact surface between the shoe and the cam ring. As a result, the wear of the components is minimized.
  • the lubricating pockets are produced by laser structuring or erosion. These methods allow easy insertion of the lubrication pockets.
  • the introduction can be integrated directly into the existing manufacturing process, whereby the production time and production costs can be kept low.
  • the lubricating pockets according to the invention are thus characterized in that they can be distributed uniformly over the entire cross section of the sliding surface of the sliding shoe or the flattening of the lifting ring and thereby promote the construction of a hydrodynamic locking wedge. Due to the small cross-sectional area of the lubrication pockets in relation to the total area of the sliding shoe or the flattening results in a large footprint between shoe and cam. As a result, the force is transmitted from the piston to the shoe uniformly passed to the cam. By lubricating pockets according to the invention thus the friction between the shoe and the lifting ring can be reduced to a minimum. This increases the life of the surfaces. In addition, the lateral forces are passed from the cam ring on the shoe into the piston, reduced, resulting in an increased life.
  • the radial piston pump 1 consists essentially of a pump housing 2 and a plurality of radially arranged pump units 9.
  • the pump units 9 are preferably arranged at an angular distance of 120 ° to each other.
  • the pump units 9 have a cylinder bore in which a pump piston 8 is movably arranged.
  • the pump piston 6 has at its lower end a sliding shoe 6 which is supported with a sliding surface 7 against a lifting ring 4.
  • the lifting ring 4 has one of the number of pumping pistons 8 corresponding number of flats 5.
  • the cam ring 4 is slidably disposed on an eccentric shaft portion of the drive shaft 3. At each full revolution of the drive shaft 3, the pump piston 8 performs a suction and a compression stroke.
  • FIG. 2a shows a side view of the lifting ring as in the radial piston pump after FIG. 1 is used.
  • the reciprocating piston has three each flattened by 120 ° flats 5.
  • the lubrication pockets 9 are arranged.
  • the lubrication pockets form small recesses in the flattening 5 and thus serve as an oil reservoir and thus ensure a good lubrication of the friction surfaces.
  • FIG. 2b shows a side view of an in FIG. 2a shown lubricating pocket 9.
  • the lubricating pocket 9 is formed hemispherical 14.
  • Such a hemispherical formation 14 can be very easily introduced into the surface.
  • a laser structuring method or an erosion method is preferably used. These processes can be integrated directly into the existing manufacturing process. Thus, only marginally longer production times occur.
  • Figure 2c shows a plan view of the in FIG. 2a shown cam ring 4.
  • the lubrication pockets 9 are distributed matrix-like. This distribution allows a particularly uniform formation of a lubricating wedge.
  • the lubrication pockets 9 can also be arranged at a different regular distance from each other. Also advantageous is a checkerboard-like arrangement of the lubrication pockets 9 or an arrangement on a circular path, which run concentrically with one another ( Fig. 5 ). Of course it is also possible To arrange lubrication pockets 9 at irregular intervals to each other.
  • Figure 3a and 3b show two different configurations of the bottom 12 of the lubrication pockets 9.
  • the in FIG. 4a shown embodiment of the bottom 12 with a constant depth h is particularly easy to produce.
  • the inclined surface 13, the in FIG. 3b extends to the flattening 5 of the cam ring 4, supports particularly advantageous the formation of a hydrodynamic lubricating wedge.
  • FIGS. 4a and 4b show two preferred cross-sectional areas of the lubricating pockets 9.
  • FIG. 4a shows an oval cross-sectional shape 10 in conjunction with the in FIG. 4a shown bottom 12 with constant depth h is particularly simple and inexpensive to produce.
  • triangular formation 11 of the cross-sectional area is particularly in combination with in FIG. 3b shown slope of the surface 13 suitable to form a hydrodynamic lubrication wedge.
  • lubrication pockets 9 are exemplary only, of course, other cross-sectional shapes or other configurations of the bottom of the lubrication pocket can be used.
  • the embodiments each show the formation of the lubrication pockets in the flats of the cam ring as well as it is possible to form the lubrication pockets in the sliding surface of the shoe. Again, the lubrication pockets ensure the formation of a hydrodynamic lubrication wedge.
  • the inventive design of lubrication pockets in the flats of the cam ring and or in the respective sliding surface of the shoe thus provide better lubrication between the contact surfaces and increase the life of the components considerably.
  • the better lubrication will be the Transverse forces transmitted from the cam ring via the slide ring in the pump piston are minimized.
  • the radial piston pump according to the invention is particularly suitable for use in modern common rail injection systems with the prevailing high pressures.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Die Erfindung betrifft eine Radialkolbenpumpe, insbesondere eine Radialkolbenhochdruckpumpe für ein Kraftstoffeinspritzsystem, nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a radial piston pump, in particular a radial piston high-pressure pump for a fuel injection system, according to the preamble of patent claim 1.

Eine gattungsgemäße Radialkolbenpumpe ist aus der DE 100 39 210 A1 bekannt. Die Radialkolbenpumpe weist eine Antriebswelle mit einem Exzenterabschnitt auf, die in einem Pumpengehäuse drehbar gelagert ist. Auf dem exzentrischen Wellenabschnitt ist ein Hubring gleitend gelagert. Die Radialkolbenpumpe weist drei in einem Abstand von je 120° zueinander angeordnete Pumpeneinheiten auf. Jede Pumpeneinheit besitzt einen radial im Pumpengehäuse längs bewegbar geführten Pumpenkolben. Die Pumpenkolben liegen jeweils an einem Gleitschuh an, der sich am Hubring abstützt. Hierzu weist der Hubring eine der Anzahl der Pumpenkolben entsprechende Zahl von Abflachungen auf. Im Pumpenbetrieb kommt es zu einer Relativbewegung zwischen der Gleitfläche des Gleitschuhs und der Abflachung des Hubrings. Aufgrund der Relativbewegung kommt es zu einem hohen Verschluss der Bauteile. Darüber hinaus führt die Relativbewegung dazu, dass Querkräfte in den Pumpenkolben eingebracht werden, die zu einem Klemmen des Kolbens führen können.A generic radial piston pump is from the DE 100 39 210 A1 known. The radial piston pump has a drive shaft with an eccentric portion which is rotatably mounted in a pump housing. On the eccentric shaft portion a cam ring is slidably mounted. The radial piston pump has three at a distance of 120 ° to each other arranged pump units. Each pump unit has a radially in the pump housing longitudinally movably guided pump piston. The pump pistons abut each other on a sliding shoe, which is supported on the lifting ring. For this purpose, the cam ring has a number of flats corresponding to the number of pump pistons. In pump operation, there is a relative movement between the sliding surface of the shoe and the flattening of the cam ring. Due to the relative movement, there is a high degree of closure of the components. In addition, the relative movement causes transverse forces are introduced into the pump piston, which can lead to a clamping of the piston.

Die DE 196 35 164 A1 schlägt zur Reduzierung der Reibung vor, Schmierrillen in die Abflachungen am Hubring auszubilden, die im wesentlichen quer zur Relativbewegung zwischen Kolben und Hubring angebracht sind.The DE 196 35 164 A1 proposes to reduce the friction to form lubrication grooves in the flats on the cam ring, which are mounted substantially transversely to the relative movement between the piston and cam.

Die DE 198 36 901 C2 , die den nächsten Stand der Technik beschreibt, schlägt vor, in der Abflachung des Hubrings Schmiernuten auszubilden, die parallel zur Richtung der Bewegung der jeweiligen Abflachung relativ zu dem zugehörigen Kolben angeordnet sind.The DE 198 36 901 C2 , which describes the closest prior art, proposes to form in the flattening of the cam ring lubricating grooves, which are arranged parallel to the direction of movement of the respective flattening relative to the associated piston.

Die US 6,350,107 B1 offenbart eine Radialkolbenpumpe mit mehreren Kolben. Die Kolben, die in diesen zugeordneten Zylinderkammern angeordnet sind, weisen an einem Ende jeweils eine Platte auf. Die Platten weisen jeweils eine Ausnehmung auf, zur Reduzierung von Spannungen im Zentrum der Platte.The US 6,350,107 B1 discloses a radial piston pump with multiple pistons. The pistons, which are arranged in these associated cylinder chambers, each have a plate at one end. The plates each have a recess for reducing stresses in the center of the plate.

Nachteilig an solchen Schmiernuten ist, dass die Querschnittsfläche der Schmiernuten relativ groß im Verhältnis zur Querschnittsfläche der gesamten Abflachung ist. Hierdurch nimmt die tragende Fläche die Abflachung ab, wodurch ein erhöhter Verschleiß auftritt. Zudem kann das Öl leicht aus den Schmiernuten herausgedrückt werden, so dass bei hohen Drehzahlen keine ausreichende Schmierung der Gleitflächen gewährleistet ist.A disadvantage of such lubrication grooves is that the cross-sectional area of the lubrication grooves is relatively large in relation to the cross-sectional area of the entire flattening. As a result, the bearing surface decreases the flattening, causing increased wear occurs. In addition, the oil can be easily pushed out of the lubrication grooves, so that at high speeds no adequate lubrication of the sliding surfaces is guaranteed.

Hiervon ausgehend ist es Aufgabe der vorliegenden Erfindung eine Radialkolbenpumpe bereitzustellen, bei der die Reibung zwischen der Gleitfläche des Gleitschuhs und den Abflachungen des Hubrings minimiert ist und bei der sich eine große Aufstandsfläche zwischen Gleitschuh und Hubring ergibt.On this basis, it is an object of the present invention to provide a radial piston pump, wherein the friction between the sliding surface of the shoe and the flattenings of the cam ring is minimized and in which there is a large footprint between the shoe and cam.

Die Aufgabe wird gelöst durch den unabhängigen Patentanspruch 1 und den unabhängigen Patentanspruch 2.The object is solved by the independent claim 1 and the independent claim 2.

Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen erläutert.Advantageous embodiments of the invention are explained in the subclaims.

Die erfindungsgemäße Radialkolbenpumpe zeichnet sich gemäß eines ersten Aspekts dadurch aus, dass in den Abflachungen des Hubrings und/oder in der jeweiligen Gleitfläche des Gleitschuhs Schmiertaschen ausgebildet sind, die Schmiertaschen in einem regelmäßigen Abstand zueinander angeordnet sind, und die Schmiertaschen matrixförmig oder schachbrettartig angeordnet sind. Durch eine Vielzahl von Schmiertaschen die über die Gleitfläche des Gleitschuhs bzw. über die Abflachung des Hubrings verteilt sind, lässt sich eine besonders gute Schmierung erreichen. Die Schmiertaschen unterstützen dabei den Aufbau eines hydrodynamischen Schmierkeils bei der Relativbewegung von Gleitschuh und Hubring. Die matrixförmige oder schachbrettartige Anordnung ermöglicht den Aufbau eines besonders gleichmäßigen Schmierspaltes.The radial piston pump according to the invention is characterized according to a first aspect in that in the flats of the cam ring and / or in the respective sliding surface of the shoe lubricating pockets are formed, the lubrication pockets are arranged at a regular distance from each other, and the lubrication pockets are arranged like a matrix or checkerboard. By a variety of lubrication pockets are distributed over the sliding surface of the shoe or on the flattening of the cam, a particularly good lubrication can be achieved. The lubrication pockets support the construction of a hydrodynamic lubricating wedge during the relative movement of the slide shoe and the lifting ring. The matrix-like or checkered arrangement allows the construction of a particularly uniform lubrication gap.

Die erfindungsgemäße Radialkolbenpumpe zeichnet sich gemäß eines zweiten Aspekts dadurch aus, dass in den Abflachungen des Hubrings und/oder in der jeweiligen Gleitfläche des Gleitschuhs Schmiertaschen ausgebildet sind, die Schmiertaschen in einem regelmäßigen Abstand zueinander angeordnet sind, und die Schmiertaschen auf Kreisbahnen angeordnet sind, die zueinander konzentrisch verlaufen. Auch hierdurch lässt sich ein besonders gleichmäßiger Schmierspalt erzielen.The radial piston pump according to the invention is characterized according to a second aspect in that in the flats of the cam ring and / or in the respective sliding surface of the shoe lubricating pockets are formed, the lubrication pockets are arranged at a regular distance from each other, and the lubrication pockets are arranged on circular paths, the run concentric to each other. This also makes it possible to achieve a particularly uniform lubrication gap.

Die Schmiertaschen weisen bevorzugt einen ovalen oder dreieckförmigen Querschnitt auf. Dabei sind die Schmiertaschen derart angeordnet, dass ihre Längsachse vorzugsweise in Richtung der Relativbewegung liegt.The lubrication pockets preferably have an oval or triangular cross-section. The lubrication pockets are arranged such that their longitudinal axis is preferably in the direction of the relative movement.

In einer bevorzugten Ausgestaltung der Erfindung weist der Boden der Schmiertaschen eine konstante Tiefe auf. Schmiertaschen mit konstanter Tiefe sind besonders einfach und preisgünstig zu fertigen.In a preferred embodiment of the invention, the bottom of the lubrication pockets has a constant depth. Lubrication pockets with constant depth are particularly easy and inexpensive to manufacture.

In einer weiteren besonders bevorzugten Ausgestaltung der Erfindung weist der Boden der Schmiertaschen eine geneigte Fläche auf. Die geneigte Oberfläche unterstützt dabei zusätzlich den Aufbau eines hydrodynamischen Schmierkeils.In a further particularly preferred embodiment of the invention, the bottom of the lubrication pockets on an inclined surface. The inclined surface additionally supports the construction of a hydrodynamic lubricating wedge.

Besonders bevorzugt ist die geneigte Fläche bis zur Abflachung des Hubrings bzw. der Gleitfläche des Gleitschuhs ausgebildet. Hierdurch wird der Aufbau des hydrodynamischen Schmierkeils weiter vorteilhaft beeinflusst.Particularly preferably, the inclined surface is formed to the flattening of the cam ring or the sliding surface of the sliding block. As a result, the structure of the hydrodynamic lubricating wedge is further advantageously influenced.

Erfindungsgemäß bevorzugt sind die Schmiertaschen kalottenförmig oder halbkugelförmig ausgebildet. Eine solche Ausbildung der Schmiertaschen lässt sich besonders einfach herstellen.According to the invention, the lubrication pockets are dome-shaped or hemispherical in shape. Such training The lubrication pockets are particularly easy to produce.

Bevorzugt sind die Querschnittsflächen der einzelnen Schmiertaschen klein gegenüber der Querschnittsfläche der gesamten Abflachung des Hubrings bzw. der Gleitfläche des Gleitschuhs. Besonders bevorzugt ist die Querschnittsfläche der einzelnen Schmiertaschen kleiner 1% der Querschnittsfläche der gesamten Abflachung des Hubrings bzw. der Gleitfläche. Hierdurch ergibt sich zum einen ein ausreichend guter Schmierkeil und zum anderen eine ausreichend große Kontaktfläche zwischen dem Gleitschuh und dem Hubring. Hierdurch wird der Verschleiß der Bauteile minimiert.Preferably, the cross-sectional areas of the individual lubrication pockets are small with respect to the cross-sectional area of the entire flattening of the cam ring or the sliding surface of the slide shoe. Particularly preferably, the cross-sectional area of the individual lubrication pockets is less than 1% of the cross-sectional area of the entire flattening of the cam ring or the sliding surface. This results in a sufficiently good lubricating wedge and for other a sufficiently large contact surface between the shoe and the cam ring. As a result, the wear of the components is minimized.

Erfindungsgemäß bevorzugt sind die Schmiertaschen durch Laserstrukturieren oder Erodieren hergestellt. Diese Verfahren ermöglichen eine einfache Einbringung der Schmiertaschen. Das Einbringen kann dabei direkt in den bestehenden Fertigungsprozess integriert werden, wodurch die Fertigungszeit und der Fertigungsaufwand gering gehalten werden können.According to the invention, the lubricating pockets are produced by laser structuring or erosion. These methods allow easy insertion of the lubrication pockets. The introduction can be integrated directly into the existing manufacturing process, whereby the production time and production costs can be kept low.

Die erfindungsgemäßen Schmiertaschen zeichnen sich somit dadurch aus, dass sie gleichmäßig über den gesamten Querschnitt der Gleitfläche des Gleitschuhs bzw. der Abflachung des Hubrings verteilt werden können und dadurch den Aufbau eines hydrodynamischen Sperrkeils begünstigen. Durch die geringe Querschnittsfläche der Schmiertaschen in Bezug auf die Gesamtfläche des Gleitschuhs bzw. der Abflachungen ergibt sich eine große Aufstandsfläche zwischen Gleitschuh und Hubring. Hierdurch wird die Kraft die vom Kolben auf den Gleitschuh übertragen wird gleichmäßig an den Hubring weitergegeben. Durch die erfindungsgemäßen Schmiertaschen kann somit die Reibung zwischen Gleitschuh und Hubring auf ein Minimum reduziert werden. Hierdurch wird die Lebensdauer der Oberflächen erhöht. Zudem werden die Querkräfte die vom Hubring über den Gleitschuh in den Kolben geleitet werden, reduziert, was zu einer erhöhten Lebensdauer führt.The lubricating pockets according to the invention are thus characterized in that they can be distributed uniformly over the entire cross section of the sliding surface of the sliding shoe or the flattening of the lifting ring and thereby promote the construction of a hydrodynamic locking wedge. Due to the small cross-sectional area of the lubrication pockets in relation to the total area of the sliding shoe or the flattening results in a large footprint between shoe and cam. As a result, the force is transmitted from the piston to the shoe uniformly passed to the cam. By lubricating pockets according to the invention thus the friction between the shoe and the lifting ring can be reduced to a minimum. This increases the life of the surfaces. In addition, the lateral forces are passed from the cam ring on the shoe into the piston, reduced, resulting in an increased life.

Die Radialkolbenpumpe eignet sich besonders für den Einsatz bei modernen Common-Rail-Einspritzsystemen. Moderne Common-Rail-Einspritzsysteme erzeugen Drücke bis zu 2000 bar, hierdurch treten extreme Belastungen am Gleitschuh bzw. am Hubring auf. Durch die erfindungsgemäßen Schmiertaschen kann die Radialkolbenpumpe diesen Belastungen standhalten. Ausführungsbeispiele und weitere Vorteile der Erfindung werden im folgenden anhand der Zeichnungen erläutert. Es zeigt schematisch:

Figur 1
einen Querschnitt durch eine Radialkolbenpumpe;
Figur 2a
eine Seitenansicht eines Hubringes wie er in der Radialkolbenpumpe nach Figur 1 verwendet wird;
Figur 2b
einen Teilausschnitt des Hubrings aus Fig. 2a;
Figur 2c
eine Draufsicht auf den in Figur 2a gezeigten Hub- ring mit einer schachbrettartigen Anordnung der er- findungsgemäßen Schmiertasche;
Figur 3a und 3b
einen Längsschnitt durch zwei unterschiedli- che Ausführungsformen der Schmiertaschen, sowie;
Figur 4a und 4b
die jeweilige Draufsicht der in Figur 3a und 3b dargestellten Schmiertaschen, sowie
Figur 5
eine Draufsicht auf einen Hubring, bei dem die Schmiertaschen auf Kreisbahnen angeordnet sind, welche zueinander konzentrisch verlaufen.
The radial piston pump is particularly suitable for use with modern common-rail injection systems. Modern common-rail injection systems produce pressures up to 2000 bar, which causes extreme loads on the sliding shoe or on the lifting ring. The lubricating pockets according to the invention, the radial piston pump can withstand these loads. Embodiments and other advantages of the invention will be explained below with reference to the drawings. It shows schematically:
FIG. 1
a cross section through a radial piston pump;
FIG. 2a
a side view of a lifting ring as in the radial piston pump after FIG. 1 is used;
FIG. 2b
a partial section of the cam ring Fig. 2a ;
Figure 2c
a top view of the in FIG. 2a shown lifting ring with a checkerboard-like arrangement of the inventive lubricating pocket;
Figure 3a and 3b
a longitudinal section through two different embodiments of the lubrication pockets, and;
FIGS. 4a and 4b
the respective top view of in Figure 3a and 3b illustrated lubrication pockets, as well
FIG. 5
a plan view of a cam ring, wherein the lubricating pockets are arranged on circular paths which extend concentric to each other.

Die Radialkolbenpumpe 1 besteht im wesentlichen aus einem Pumpengehäuse 2 sowie mehreren radial angeordneten Pumpeneinheiten 9. Die Pumpeneinheiten 9 sind vorzugsweise in einem Winkelabstand von 120° zueinander angeordnet. Die Pumpeneinheiten 9 weisen eine Zylinderbohrung auf, in denen bewegbar ein Pumpenkolben 8 angeordnet ist. Der Pumpenkolben 6 weist an seinem unteren Ende einen Gleitschuh 6 auf, der mit einer Gleitfläche 7 sich gegen einen Hubring 4 abstützt. Der Hubring 4 weist hierzu einer der Anzahl der Pumpenkolben 8 entsprechende Zahl von Abflachungen 5 auf. Der Hubring 4 ist gleitend auf einem exzentrischen Wellenabschnitt der Antriebswelle 3 angeordnet. Bei jeder vollen Umdrehung der Antriebswelle 3 führt der Pumpenkolben 8 einen Ansaug- sowie einen Kompressionshub durch. Während der Drehung der Antriebswelle 3 kommt es zu einer Relativbewegung der Gleitfläche 7 des Gleitschuhs 6 und der Abflachung 5 des Hubrings 4. Durch die Relativbewegung wird zusätzlich eine Querkraft auf den Gleitschuh 6 und auf den Pumpenkolben 8 übertragen. Die Querkraft kann zu einem Klemmen des Pumpenkolbens 8 führen. Um die Reibung zwischen der Gleitfläche 7 des Gleitschuhs 6 und der Abflachung 5 des Hubrings 4 zu verringern, sind in der Abflachung 5 des Hubrings 4 und/oder in der jeweiligen Gleitfläche 7 des Gleitschuhs 6 Schmiertaschen 9 ausgebildet. Die Schmiertaschen 9 erleichtern den Aufbau eines hydrodynamischen Schmierkeils und sorgen damit für eine Verringerung der Reibkräfte. Dadurch wird die Lebensdauer der Bauteile erheblich erhöht.The radial piston pump 1 consists essentially of a pump housing 2 and a plurality of radially arranged pump units 9. The pump units 9 are preferably arranged at an angular distance of 120 ° to each other. The pump units 9 have a cylinder bore in which a pump piston 8 is movably arranged. The pump piston 6 has at its lower end a sliding shoe 6 which is supported with a sliding surface 7 against a lifting ring 4. For this purpose, the lifting ring 4 has one of the number of pumping pistons 8 corresponding number of flats 5. The cam ring 4 is slidably disposed on an eccentric shaft portion of the drive shaft 3. At each full revolution of the drive shaft 3, the pump piston 8 performs a suction and a compression stroke. During the rotation of the drive shaft 3, there is a relative movement of the sliding surface 7 of the sliding shoe 6 and the flattening 5 of the cam ring 4. The relative movement is additionally a transverse force transmitted to the shoe 6 and the pump piston 8. The Transverse force can lead to a clamping of the pump piston 8. In order to reduce the friction between the sliding surface 7 of the sliding shoe 6 and the flattening 5 of the cam ring 4, 6 lubrication pockets 9 are formed in the flattening 5 of the cam ring 4 and / or in the respective sliding surface 7 of the shoe. The lubricating pockets 9 facilitate the construction of a hydrodynamic lubricating wedge and thus ensure a reduction of the frictional forces. This significantly increases the life of the components.

Figur 2a zeigt eine Seitenansicht des Hubringes wie er bei der Radialkolbenpumpe nach Figur 1 verwendet wird. Der Hubkolben weist dabei drei um je 120° zueinander versetzte Abflachungen 5 auf. In den Abflachungen 5 sind die Schmiertaschen 9 angeordnet. Bei den Schmiertaschen bilden kleine Vertiefungen in der Abflachung 5 und dienen dadurch als Ölreservoir und gewährleisten somit eine gute Schmierung der Reibflächen. FIG. 2a shows a side view of the lifting ring as in the radial piston pump after FIG. 1 is used. The reciprocating piston has three each flattened by 120 ° flats 5. In the flats 5, the lubrication pockets 9 are arranged. In the lubrication pockets form small recesses in the flattening 5 and thus serve as an oil reservoir and thus ensure a good lubrication of the friction surfaces.

Figur 2b zeigt eine Seitenansicht einer in Figur 2a gezeigten Schmiertasche 9. Die Schmiertasche 9 ist dabei halbkugelförmig 14 ausgebildet. Eine solche halbkugelförmige Ausbildung 14 lässt sich sehr einfach in die Oberfläche einbringen. Bevorzugt wird dabei ein Laserstrukturierungsverfahren oder ein Erodierverfahren eingesetzt. Diese Verfahren können direkt in den bestehenden Fertigungsprozess integriert werden. Somit treten nur unwesentlich längere Fertigungszeiten auf. FIG. 2b shows a side view of an in FIG. 2a shown lubricating pocket 9. The lubricating pocket 9 is formed hemispherical 14. Such a hemispherical formation 14 can be very easily introduced into the surface. In this case, a laser structuring method or an erosion method is preferably used. These processes can be integrated directly into the existing manufacturing process. Thus, only marginally longer production times occur.

Figur 2c zeigt eine Draufsicht auf den in Figur 2a gezeigten Hubring 4. Die Schmiertaschen 9 sind dabei matrixförmig verteilt. Diese Verteilung ermöglicht eine besonders gleichmäßige Ausbildung eines Schmierkeils. Selbstverständlich können die Schmiertaschen 9 aber auch in einem anderen regelmäßigen Abstand zueinander angeordnet sein. Vorteilhaft ist auch eine schachbrettartige Anordnung der Schmiertaschen 9 bzw. eine Anordnung auf Kreisbahn, welche zueinander konzentrisch verlaufen (Fig. 5). Es ist selbstverständlich auch möglich die Schmiertaschen 9 in unregelmäßigen Abständen zueinander anzuordnen. Figure 2c shows a plan view of the in FIG. 2a shown cam ring 4. The lubrication pockets 9 are distributed matrix-like. This distribution allows a particularly uniform formation of a lubricating wedge. Of course, the lubrication pockets 9 can also be arranged at a different regular distance from each other. Also advantageous is a checkerboard-like arrangement of the lubrication pockets 9 or an arrangement on a circular path, which run concentrically with one another ( Fig. 5 ). Of course it is also possible To arrange lubrication pockets 9 at irregular intervals to each other.

Figur 3a und 3b zeigen zwei unterschiedliche Ausgestaltungen des Bodens 12 der Schmiertaschen 9. Die in Figur 4a gezeigte Ausgestaltung des Bodens 12 mit einer konstanten Tiefe h ist besonders einfach herstellbar. Bevorzugt ist jedoch eine in Figur 3b gezeigte geneigte Fläche 13. Die geneigte Fläche 13 die in Figur 3b bis zur Abflachung 5 des Hubrings 4 reicht, unterstützt besonders vorteilhaft die Ausbildung eines hydrodynamischen Schmierkeils. Figure 3a and 3b show two different configurations of the bottom 12 of the lubrication pockets 9. The in FIG. 4a shown embodiment of the bottom 12 with a constant depth h is particularly easy to produce. However, preferred is an in FIG. 3b shown inclined surface 13. The inclined surface 13, the in FIG. 3b extends to the flattening 5 of the cam ring 4, supports particularly advantageous the formation of a hydrodynamic lubricating wedge.

Figur 4a und 4b zeigen zwei bevorzugte Querschnittsflächen der Schmiertaschen 9. Figur 4a zeigt eine ovale Querschnittsform 10 die in Verbindung mit dem in Figur 4a gezeigten Boden 12 mit konstanter Tiefe h besonders einfach und preiswert herzustellen ist. Die in Figur 4b gezeigte dreieckförmige Ausbildung 11 der Querschnittsfläche ist besonders in Kombination mit der in Figur 3b gezeigten Neigung der Fläche 13 geeignet um einen hydrodynamischen Schmierkeil auszubilden. FIGS. 4a and 4b show two preferred cross-sectional areas of the lubricating pockets 9. FIG. 4a shows an oval cross-sectional shape 10 in conjunction with the in FIG. 4a shown bottom 12 with constant depth h is particularly simple and inexpensive to produce. In the FIG. 4b shown triangular formation 11 of the cross-sectional area is particularly in combination with in FIG. 3b shown slope of the surface 13 suitable to form a hydrodynamic lubrication wedge.

Die dargestellten Ausbildungen der Schmiertaschen 9 sind nur beispielhaft, selbstverständlich können auch andere Querschnittsformen bzw. andere Ausbildungen des Bodens der Schmiertasche verwendet werden.The illustrated embodiments of the lubrication pockets 9 are exemplary only, of course, other cross-sectional shapes or other configurations of the bottom of the lubrication pocket can be used.

Die Ausführungsbeispiele zeigen jeweils die Ausbildung der Schmiertaschen in den Abflachungen des Hubrings ebenso ist es aber möglich die Schmiertaschen in der Gleitfläche des Gleitschuhs auszubilden. Auch hierbei sorgen die Schmiertaschen für die Ausbildung eines hydrodynamischen Schmierkeils.The embodiments each show the formation of the lubrication pockets in the flats of the cam ring as well as it is possible to form the lubrication pockets in the sliding surface of the shoe. Again, the lubrication pockets ensure the formation of a hydrodynamic lubrication wedge.

Die erfindungsgemäße Ausbildung von Schmiertaschen in den Abflachungen des Hubringes und oder in der jeweiligen Gleitfläche des Gleitschuhs sorgen somit für eine bessere Schmierung zwischen den Kontaktflächen und erhöhen die Lebensdauer der Bauteile erheblich. Durch die bessere Schmierung werden die Querkräfte die vom Hubring über den Gleitring in den Pumpenkolben übertragen werden minimiert. Die erfindungsgemäße Radialkolbenpumpe eignet sich besonders für den Einsatz in modernen Common Rail Einspritzsystemen mit den dort herrschenden hohen Drücken.The inventive design of lubrication pockets in the flats of the cam ring and or in the respective sliding surface of the shoe thus provide better lubrication between the contact surfaces and increase the life of the components considerably. The better lubrication will be the Transverse forces transmitted from the cam ring via the slide ring in the pump piston are minimized. The radial piston pump according to the invention is particularly suitable for use in modern common rail injection systems with the prevailing high pressures.

Claims (9)

  1. Radial piston pump (1), especially a radial piston highpressure pump for a fuel injection system, said pump comprising a drive shaft (3) which is mounted in a pump housing (2) and comprises an eccentric shaft section on which a lifting ring (4) is mounted in a sliding manner, the surface of said ring opposing the eccentric shaft section comprising preferably a plurality of flats (5) on which a sliding block (6) comprising a sliding surface (7) is respectively supported, said block being activated by a pump piston (8) which is radially arranged in relation to the drive shaft (3),
    with lubrication pockets (9) being formed in the flats (5) of the lifting ring (4) and/or in the respective sliding surface (7) of the sliding block (6) and the lubrication pockets (9) being arranged at regular distances from one another, characterised in that the lubrication pockets (9) are arranged in the manner of a matrix or checkered.
  2. Radial piston pump (1), especially a radial piston highpressure pump for a fuel injection system, said pump comprising a drive shaft (3) which is mounted in a pump housing (2) and comprises an eccentric shaft section on which a lifting ring (4) is mounted in a sliding manner, the surface of said ring opposing the eccentric shaft section comprising preferably a plurality of flats (5) on which a sliding block (6) comprising a sliding surface (7) is respectively supported, said block being activated by a pump piston (8) which is radially arranged in relation to the drive shaft (3),
    with lubrication pockets (9) being formed in the flats (5) of the lifting ring (4) and/or in the respective sliding surface (7) of the sliding block (6) and the lubrication pockets (9) being arranged at regular distances from one another, characterised in that the lubrication pockets (9) are arranged on circular paths 15 which run concentrically to one another.
  3. Radial piston pump (1) according to one of the preceding claims,
    characterised in that
    the lubrication pockets (9) have an oval (10) or triangular (11) cross-section.
  4. Radial piston pump (1) according to one o the preceding claims,
    characterised in that
    the base (12) of the lubrication pockets (9) has a constant depth (h).
  5. Radial piston pump (1) according to one of claims 1 to 3,
    characterised in that
    the base (12) of the lubrication pockets (9) has an inclined surface (13).
  6. Radial piston pump (1) according to claim 5,
    characterised in that
    the inclined surface (13) reaches the flat (5) of the lifting ring (4) and/or the sliding surface (7) of the sliding block (6).
  7. Radial piston pump (1) according to one of claims 1 to 2,
    characterised in that
    the lubrication pockets (9) are embodied dome-shaped or hemispherical (14).
  8. Radial piston pump (11) according to one of the preceding claims,
    characterised in that
    the cross-sectional surface (10, 11) of the individual lubrication pockets (9) is small compared with the cross-sectional surface of the entire flat (5) of the lifting ring (4) and/or the sliding surface (7) of the sliding block (6), preferably <1%
  9. Radial piston pump (1) according to one of the preceding claims, characterised in that
    the lubrication pockets (9) are produced by means of laser-structuring or erosion.
EP04804728A 2004-04-14 2004-12-08 Radial piston pump Expired - Fee Related EP1738074B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200410018163 DE102004018163A1 (en) 2004-04-14 2004-04-14 Radial piston pump
PCT/EP2004/053346 WO2005108788A1 (en) 2004-04-14 2004-12-08 Radial piston pump

Publications (2)

Publication Number Publication Date
EP1738074A1 EP1738074A1 (en) 2007-01-03
EP1738074B1 true EP1738074B1 (en) 2010-04-21

Family

ID=34959576

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04804728A Expired - Fee Related EP1738074B1 (en) 2004-04-14 2004-12-08 Radial piston pump

Country Status (3)

Country Link
EP (1) EP1738074B1 (en)
DE (2) DE102004018163A1 (en)
WO (1) WO2005108788A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016106232B3 (en) * 2016-04-06 2017-08-31 L'orange Gmbh Radial piston pump, especially for fuel, with several storage holes in the housing of the radial piston pump

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006010680A1 (en) * 2005-11-21 2007-05-24 Continental Teves Ag & Co. Ohg Radial piston pump
DE102005059031A1 (en) * 2005-12-10 2007-06-14 Schaeffler Kg Radial piston high pressure pump e.g. radial piston distributor type fuel injection pump, for internal combustion engine, has thrust surface of cam ring, guidance slot surface, rolling pickers surface and rolls surface, with micro recesses
DE102008001713A1 (en) * 2008-05-13 2009-11-19 Robert Bosch Gmbh Radial piston pump
DE102011003245A1 (en) * 2011-01-27 2012-08-02 Schaeffler Technologies Gmbh & Co. Kg Cup tappet for acting on a pump piston of a high-pressure fuel pump
DE102011079781A1 (en) * 2011-07-26 2013-01-31 Continental Automotive Gmbh Shaft for high pressure pump i.e. fuel high pressure pump, for delivering fluid i.e. fuel, in internal combustion engine in motor car, has helical-formed or pocket-like recess arranged in exterior wall section for receiving lubricant
DE102014211870A1 (en) * 2014-06-20 2015-12-24 Robert Bosch Gmbh Swash plate machine
CN110671316A (en) * 2019-10-28 2020-01-10 吉林大学 High-abrasion-resistance high-sealing piston

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE564479C (en) * 1928-12-25 1932-11-19 Metallgesellschaft Ag High pressure lubrication device for slide bearings
GB983310A (en) * 1962-01-29 1965-02-17 Hans Thoma Improvements in or relating to swash plate or like pumps or motors
DE2750490A1 (en) * 1977-11-11 1979-05-17 Bosch Gmbh Robert SLIDER FOR HYDROSTATIC PISTON MACHINERY
US5577846A (en) * 1992-03-30 1996-11-26 Koyo Seiko, Co., Ltd. Eccentric rolling bearing device
DE19635164A1 (en) * 1996-08-30 1998-03-05 Bosch Gmbh Robert Piston pump
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.
DE19814506A1 (en) * 1998-04-01 1999-10-14 Bosch Gmbh Robert Radial piston pump for high-pressure fuel supply
DE19836901C2 (en) * 1998-08-14 2002-08-29 Bosch Gmbh Robert Radial piston pump
DE10039210A1 (en) * 2000-08-10 2002-02-28 Siemens Ag Radial piston pump has two-part spring carrier in form of pivoted connecting element between piston and return spring
DE10247645A1 (en) * 2002-10-11 2004-04-22 Robert Bosch Gmbh Radial piston pump for high pressure fuel supply has at least one lubricant pocket in plates

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016106232B3 (en) * 2016-04-06 2017-08-31 L'orange Gmbh Radial piston pump, especially for fuel, with several storage holes in the housing of the radial piston pump

Also Published As

Publication number Publication date
EP1738074A1 (en) 2007-01-03
DE502004011084D1 (en) 2010-06-02
WO2005108788A1 (en) 2005-11-17
DE102004018163A1 (en) 2005-11-10

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