EP2823177B1 - Piston pump - Google Patents
Piston pump Download PDFInfo
- Publication number
- EP2823177B1 EP2823177B1 EP13700489.1A EP13700489A EP2823177B1 EP 2823177 B1 EP2823177 B1 EP 2823177B1 EP 13700489 A EP13700489 A EP 13700489A EP 2823177 B1 EP2823177 B1 EP 2823177B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- roller
- rim
- piston pump
- piston
- face surface
- 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.)
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Links
- 239000000446 fuel Substances 0.000 claims description 8
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 3
- 238000004381 surface treatment Methods 0.000 claims description 3
- 229910052742 iron Inorganic materials 0.000 claims description 2
- 238000013461 design Methods 0.000 description 6
- 238000002485 combustion reaction Methods 0.000 description 4
- 239000011248 coating agent Substances 0.000 description 3
- 238000000576 coating method Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000005530 etching Methods 0.000 description 2
- 238000000227 grinding Methods 0.000 description 2
- 230000007257 malfunction Effects 0.000 description 2
- 238000005498 polishing Methods 0.000 description 2
- 238000004904 shortening Methods 0.000 description 2
- 240000001439 Opuntia Species 0.000 description 1
- 235000004727 Opuntia ficus indica Nutrition 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 238000013508 migration Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000012549 training Methods 0.000 description 1
Images
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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
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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
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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
- F04B1/0426—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
- 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
- F04B1/0435—Arrangements for disconnecting the pistons from the actuated cam
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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
- F04B1/0439—Supporting or guiding means for the pistons
Definitions
- the present invention relates to a piston pump, in particular a high-pressure fuel pump, with a housing, a piston and a drive shaft with a cam portion on which the piston is at least indirectly supported via a rotatably mounted in a roller tappet roller, wherein the side of the cam portion on both sides in each case a board is provided, which projects in the radial direction over the cam portion.
- the field of application of the present invention extends to piston pumps, in particular high-pressure fuel pumps, which are used for internal combustion engines in motor vehicles.
- a piston pump which has a housing, a piston and a drive shaft.
- the drive shaft has a cam portion, on which the piston is indirectly supported via a rotatably mounted in a roller tappet roller.
- a board is provided on both sides of the drive shaft, which extends in the radial direction over the cam portion.
- the shelves are conically shaped and the edges facing the Borden the rollers are provided with a conical bevel.
- the roller is mounted on a bolt in a plunger and the axial movement of the roller is limited within the plunger, so that it does not come into contact with the shelves.
- the EP 2 079 923 A1 a piston pump of an internal combustion engine of a motor vehicle, which serves for conveying fuel.
- the piston pump has a piston that can be moved axially back and forth in a cylinder.
- the piston is displaced by the cam of a camshaft against the force of a spring, wherein the spring serves as a return spring and ensures that the roller tappet is always in abutting contact with the cam of the camshaft.
- a roller tappet usually consists of a tappet body on which a roller is rotatably mounted and held. This caster runs on the cam section of the Cam, whereby the friction between the camshaft and the piston is minimized.
- a shelf is arranged projecting beyond the cam portion in the radial direction, so that an axial movement and / or rotation from the ideal position of the roller through the shelves is limited to a defined extent.
- a suitable, tribological mating of the roller and the edges of the wear on the roller and on the board kept so low that it does not lead to malfunction or a shortening of the life of the piston pump.
- the roller is rotated by the friction occurring at the start of one of the ribs in rotation, if they do not already rotate by the rolling friction between the cam portion and roller.
- the board tapers at an end face directed towards the roller towards an outer circumference of the rim and is in particular conically shaped such that an opening inclination results, wherein the roller has a convex curvature, preferably with a face, directed towards the rim Radius has.
- This design of the board and the roller reliably prevents corner contact of the roller with the board. Corner contacts are characterized by high surface pressures and can lead to edge breakage. Edge breakages entail great risks for the operational safety of the piston pump and can lead to undesired operating failures of the piston pump.
- the invention includes the technical teaching that an angle between a perpendicular to a longitudinal axis of the roller and the tapered to an outer periphery of the board end face is 0.1 ° to 10 ° and the radius of a directed to the board end face of the roller between 1 mm and is 40 mm tall. To promote line contact and prevent point contact on a sharp edge, it is proposed to maintain the specified angle for the board and specified radius for the roller. In addition, there is another advantage in that the point of contact between the roller and the board on the shelf between the top edge and the lower edge of the vehicle is located.
- the board on a directed to the roller end face a convex curvature, preferably with a radius and the roller tapers on an end face directed to the board to the front side of the roller, the end face is in particular conically shaped so that gives an opening inclination.
- This design of the board and the roller reliably prevents corner contact of the roller with the board. Corner contacts are characterized by high surface pressures and can lead to edge breakage. Edge breakages entail great risks for the operational safety of the piston pump and can lead to operational failures of the piston pump.
- an angle between a perpendicular to an axis longitudinal axis of the roller and the tapered to an outer periphery of the rim end face 0.1 ° to 10 ° and the radius of a directed to the board end face of the roller between 1 mm and 40 mm is large.
- Such a design of the contact surfaces promotes a line contact and thus prevents the punctual contact on a sharp edge.
- the board and the cam section are integrally formed.
- the board and / or the roller made of a hardenable iron material. Manufacturing technology and from the point of view of assembly, the one-piece design allows a safe and easy way of on-board training on the camshaft. Furthermore, the wear resistance at the contact surfaces of the board and the roller can be increased by a surface hardening.
- the board and / or the roller have a surface treatment to minimize friction.
- a surface treatment means a coating or any mechanical or chemical change in the surface finish. Such changes in the surface condition can be realized in particular by grinding, polishing or etching.
- the board has a lower height than half the diameter of the roller.
- a small height of the board is associated with a greater restoring force of the roller and thus also reduces the wear of the contact surfaces of the board and the roller.
- a piston pump which comprises a housing 1, in which a drive shaft 2 via two bearings 7a and 7b are mounted. Furthermore, the drive shaft 2 between the two bearings 7a and 7b has a cross-sectionally oval Nockenabschitt 3.
- the piston pump serves as a high-pressure fuel pump for an internal combustion engine in a motor vehicle. With it, the fuel is compressed to a very high pressure and conveyed to a fuel manifold, not shown here.
- the drive shaft 2 of the piston pump is driven directly by the internal combustion engine. Therefore, the drive shaft 2 has a corresponding coupling portion 8, which is arranged outside of the housing 1.
- the piston of the piston pump is indirectly driven by the cam portion 3 of the drive shaft 2.
- a roller tappet 4 is arranged. This comprises a plunger body 9 and a roller 5.
- the roller tappet 4 is pressed together with the piston against the cam portion 3 to ensure that the roller 5 does not lift off the cam portion 3 of the drive shaft 2 ,
- a respective board 6 a and 6 b is provided on the drive shaft 2.
- the rims 6a and 6b protrude in the radial direction beyond the cam portion 3, so that the roller 5 starts on migration during operation in the axial direction and / or rotation of the ideal position against one of the two shelves 6a or 6b.
- the axial movement and / or rotation is limited from the ideal position of the roller 5 during operation to a defined extent.
- the Indian FIG. 2 shown portion of a cam portion 3 shows the arranged on an end face of the cam portion 3 in the radial direction beyond the cam portion 3 protruding board 6a.
- the board 6a has a directed to the roller 5 at least approximately conical shaped end face. This end face is tilted in such a way that the width of the rim 6a increases from the outer circumference to the inner circumference, resulting in an opening inclination.
- the roller 5 has a convex curvature, in particular with a radius r, on a face directed towards the rim 6a.
- the board 6a is formed such that its height is less than half the diameter of the roller 5.
- Such a design of the board 6a and the roller 5 allows for angular deviations of the direction of the roller 5, high pressure due to edge support or corner contacts between roller. 5 and board 6a to avoid.
- FIG. 3 is a further embodiment of the cam portion 3 together with the board 6a and roller 5 shown.
- the board 6a has a convex curvature, in particular with a radius r, on a face directed towards the roller 5.
- the roller 5 is formed at least approximately conical on an end face directed towards the rim 6a. This end face is tilted in such a way that its diameter decreases towards an end face of the roller 5 and the end face leads away from the rim 6a towards the outer circumference of the roller 5, so that a closing inclination results.
- the board 6a is formed such that its height is less than half the diameter of the roller 5.
- Such a design of the board 6a and the roller 5 allows for angular deviations of the direction of the roller 5, high pressure due to edge support or corner contacts between roller. 5 and board 6a to avoid. Moreover, it is advantageous if the point of contact of the roller 5 is located with the board 6a between the Bordobernote and the underborder. This is achieved according to the invention when the angle w between a perpendicular to an axis longitudinal axis of the roller 5 and the outer circumference of the roller 5 tapered end surface is 0.1 ° to 10 ° and the radius r directed to the roller 5 end face of the rim 6a between 1 mm and 40 mm in size.
- FIG. 4 shows a misalignment of the roller 5 on the cam portion 3. It comes in a touch point B for contact of the roller 5 with the board 6a.
- the distance a indicates the distance of the contact point B from the center M of the caster width. This distance a coincides with the distance between the contact point B and the roller longitudinal axis in a non-twisted state.
- the distance b is the distance between the contact point B and the center M of Roller width.
- the angle c represents the angle of rotation of the roller 5 and can be up to 30 °.
- the roller 5 undergoes a force, which results from the normal force Fn and the frictional force Fr of the roller 5 by contact on board 6a.
- Another way to promote the provision of the roller 5 is an enlargement of the lever arm a and / or a reduction of the lever arm b.
- a ratio of a / b which causes the provision is always achieved at each angular deviation.
- the permissible angular deviation can be specified. This can be realized by changing the dimensions of the roller 5, wherein the roller diameter should be increased and the roller width should be reduced. Further, the distance a is also increased, the smaller the board 6a is. Thus, the height of the rim 6a should have a lower height than half the diameter of the roller 5.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Description
Die vorliegende Erfindung betrifft eine Kolbenpumpe, insbesondere eine Hochdruck-Kraftstoffpumpe, mit einem Gehäuse, einem Kolben und einer Antriebswelle mit einem Nockenabschnitt, an dem sich der Kolben wenigstens mittelbar über eine in einem Rollenstößel drehbar gelagerte Laufrolle abstützt, wobei seitlich des Nockenabschnitts zu beiden Seiten jeweils ein Bord vorgesehen ist, der in radialer Richtung über den Nockenabschnitt hinausragt.The present invention relates to a piston pump, in particular a high-pressure fuel pump, with a housing, a piston and a drive shaft with a cam portion on which the piston is at least indirectly supported via a rotatably mounted in a roller tappet roller, wherein the side of the cam portion on both sides in each case a board is provided, which projects in the radial direction over the cam portion.
Das Einsatzgebiet der vorliegenden Erfindung erstreckt sich auf Kolbenpumpen, insbesondere Hochdruck-Kraftstoffpumpen, die für Brennkraftmaschinen in Kraftfahrzeugen zum Einsatz kommen.The field of application of the present invention extends to piston pumps, in particular high-pressure fuel pumps, which are used for internal combustion engines in motor vehicles.
Aus der
Des Weiteren offenbart die
Ausgehend von dem vorgehend genannten Stand der Technik ist es die Aufgabe der vorliegenden Erfindung eine Kolbenpumpe zu schaffen, bei der die Axialbewegung und/oder Verdrehung der Laufrolle begrenzt ist, die einem Eckkontakt bei Winkelabweichungen der Laufrichtung einer Laufrolle mit einem Bord entgegenwirkt, die Gefahr des Verschleißens und Abbrechens von Kanten und Ecken minimiert und eine Rückführung der Laufrolle in ihre ursprüngliche Position fördert.Based on the above-mentioned prior art, it is the object of the present invention to provide a piston pump in which the axial movement and / or rotation of the roller is limited, which counteracts a corner contact at angular deviations of the direction of a roller with a board, the risk of Minimizing wear and breakage of edges and corners and promotes a return of the roller to its original position.
Die Aufgabe wird ausgehend von einer Kolbenpumpe gemäß dem Oberbegriff von Anspruch 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Vorteilhafte Weiterbildungen der Erfindung gehen aus den nachfolgenden abhängigen Ansprüchen hervor.The object is achieved on the basis of a piston pump according to the preamble of
Entsprechend eines ersten Ausführungsbeispiels verjüngt sich der Bord an einer zur Laufrolle gerichteten Stirnfläche zu einem Außenumfang des Bordes hin und ist insbesondere konisch ausgebildet, so dass sich eine öffnende Neigung ergibt, wobei die Laufrolle an einer zum Bord gerichteten Stirnfläche eine konvexe Wölbung, vorzugsweise mit einem Radius aufweist. Diese Ausbildung des Bordes und der Laufrolle verhindert zuverlässig einen Eckkontakt der Laufrolle mit dem Bord. Eckkontakte sind von hohen Flächenpressungen geprägt und können zu Kantenabbrüchen führen. Kantenabbrüche bringen große Risiken für die Betriebssicherheit der Kolbenpumpe mit sich und können zu ungewünschten Betriebsausfällen der Kolbenpumpe führen.According to a first embodiment, the board tapers at an end face directed towards the roller towards an outer circumference of the rim and is in particular conically shaped such that an opening inclination results, wherein the roller has a convex curvature, preferably with a face, directed towards the rim Radius has. This design of the board and the roller reliably prevents corner contact of the roller with the board. Corner contacts are characterized by high surface pressures and can lead to edge breakage. Edge breakages entail great risks for the operational safety of the piston pump and can lead to undesired operating failures of the piston pump.
Die Erfindung schließt die technische Lehre ein, dass ein Winkel zwischen einer Senkrechten zu einer Achsenlängsachse der Laufrolle und der zu einem Außenumfang des Bordes verjüngenden Stirnfläche 0,1° bis 10° groß ist und der Radius einer zum Bord gerichteten Stirnfläche der Laufrolle zwischen 1 mm und 40 mm groß ist. Um einen Linienkontakt zu fördern und einen punktuellen Kontakt an einer scharfen Kante zu verhindert, wird vorgeschlagen den angegebene Winkel für den Bord und den angegebenen Radius für die Laufrolle einzuhalten. Darüber hinaus besteht ein weiterer Vorteil darin, dass der Berührpunkt zwischen der Laufrolle und dem Bord am Bord zwischen der Bordoberkante und der Bordunterkante liegt.The invention includes the technical teaching that an angle between a perpendicular to a longitudinal axis of the roller and the tapered to an outer periphery of the board end face is 0.1 ° to 10 ° and the radius of a directed to the board end face of the roller between 1 mm and is 40 mm tall. To promote line contact and prevent point contact on a sharp edge, it is proposed to maintain the specified angle for the board and specified radius for the roller. In addition, there is another advantage in that the point of contact between the roller and the board on the shelf between the top edge and the lower edge of the vehicle is located.
Entsprechend eines zweiten Ausführungsbeispiels weist der Bord an einer zur Laufrolle gerichteten Stirnfläche eine konvexe Wölbung, vorzugsweise mit einem Radius auf und die Laufrolle verjüngt sich an einer zum Bord gerichteten Stirnfläche zur Stirnseite der Laufrolle hin, wobei die Stirnfläche insbesondere konisch geformt ist, so dass sich eine öffnende Neigung ergibt. Diese Ausbildung des Bordes und der Laufrolle verhindert zuverlässig einen Eckkontakt der Laufrolle mit dem Bord. Eckkontakte sind von hohen Flächenpressungen geprägt und können zu Kantenabbrüchen führen. Kantenabbrüche bringen große Risiken für die Betriebssicherheit der Kolbenpumpe mit sich und können zu Betriebsausfällen der Kolbenpumpe führen.According to a second embodiment, the board on a directed to the roller end face a convex curvature, preferably with a radius and the roller tapers on an end face directed to the board to the front side of the roller, the end face is in particular conically shaped so that gives an opening inclination. This design of the board and the roller reliably prevents corner contact of the roller with the board. Corner contacts are characterized by high surface pressures and can lead to edge breakage. Edge breakages entail great risks for the operational safety of the piston pump and can lead to operational failures of the piston pump.
Vorzugsweise ist ein Winkel zwischen einer Senkrechten zu einer Achsenlängsachse der Laufrolle und der zu einem Außenumfang des Bordes verjüngenden Stirnfläche 0,1° bis 10° groß und der Radius einer zum Bord gerichteten Stirnfläche der Laufrolle zwischen 1 mm und 40 mm groß ist. Eine derartige Ausbildung der Kontaktflächen fördert einen Linienkontakt und verhindert somit den punktuellen Kontakt an einer scharfen Kante. Ferner liegt der Berührpunkt zwischen der Laufrolle und dem Bord am Bord zwischen der Bordoberkante und der Bordunterkante.Preferably, an angle between a perpendicular to an axis longitudinal axis of the roller and the tapered to an outer periphery of the rim end face 0.1 ° to 10 ° and the radius of a directed to the board end face of the roller between 1 mm and 40 mm is large. Such a design of the contact surfaces promotes a line contact and thus prevents the punctual contact on a sharp edge. Furthermore, the point of contact between the caster and the board on the board between the curb and the lower edge of the board.
Erfindungsgemäß sind der Bord und der Nockenabschnitt einstückig ausgebildet. Darüber hinaus bestehen der Bord und/oder die Laufrolle aus einem härtbarem Eisenwerkstoff. Fertigungstechnisch und unter dem Gesichtspunkt der Montage erlaubt die einstückige Ausbildung eine sichere und einfache Möglichkeit der Bordausbildung an der Nockenwelle. Desweiteren kann die Verschleißbeständigkeit an den Kontaktflächen des Bordes und der Laufrolle durch eine Oberflächenhärtung erhöht werden.According to the invention, the board and the cam section are integrally formed. In addition, the board and / or the roller made of a hardenable iron material. Manufacturing technology and from the point of view of assembly, the one-piece design allows a safe and easy way of on-board training on the camshaft. Furthermore, the wear resistance at the contact surfaces of the board and the roller can be increased by a surface hardening.
Der Bord und/oder die Laufrolle weisen eine Oberflächenbehandlung zur Reibungsminimierung auf. Unter einer Oberflächenbehandlung ist eine Beschichtung oder eine etwaige mechanische oder chemische Veränderung der Oberflächenbeschaffenheit zu verstehen. Solche Veränderungen der Oberflächenbeschaffenheit können insbesondere durch schleifen, polieren oder ätzen realisiert werden.The board and / or the roller have a surface treatment to minimize friction. A surface treatment means a coating or any mechanical or chemical change in the surface finish. Such changes in the surface condition can be realized in particular by grinding, polishing or etching.
Es wird weiterhin vorgeschlagen, dass der Bord eine geringere Höhe aufweist als der halbe Durchmesser der Laufrolle. Eine geringe Höhe des Bordes ist verbunden mit einer größeren Rückstellungskraft der Laufrolle und vermindert somit auch den Verschleiß der Kontaktflächen des Bordes und der Laufrolle.It is further proposed that the board has a lower height than half the diameter of the roller. A small height of the board is associated with a greater restoring force of the roller and thus also reduces the wear of the contact surfaces of the board and the roller.
Weitere, die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung der bevorzugten Ausführungsbeispiele der Erfindung anhand von Figuren näher dargestellt.Further measures improving the invention will be described in more detail below together with the description of the preferred embodiments of the invention with reference to figures.
Es zeigen:
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Fig.1 eine schematische Schnittdarstellung einer erfindungsgemäßen Kolbenpumpe, -
Fig.2 eine vergrößerte schematische Schnittdarstellung des in gekennzeichneten Bereiches, umfassend einen Nockenabschnitt samt Bord und Laufrolle,Figur 1 -
Fig.3 eine schematische Schnittdarstellung des in dargestellten Nockenabschnittes samt Bord und Laufrolle nach einem zweiten Ausführungsbeispiel undFigur 2 -
Fig.4 eine schematische Darstellung der Borde mit der dazwischenliegenden Laufrolle.
-
Fig.1 a schematic sectional view of a piston pump according to the invention, -
Fig.2 an enlarged schematic sectional view of the inFIG. 1 marked area, comprising a cam portion including board and roller, -
Figure 3 a schematic sectional view of the inFIG. 2 illustrated cam portion including board and roller according to a second embodiment and -
Figure 4 a schematic representation of the shelves with the intermediate roller.
In
Der hier nicht dargestellte Kolben der Kolbenpumpe wird von dem Nockenabschnitt 3 der Antriebswelle 2 mittelbar angetrieben. Zwischen dem Kolben und dem Nockenabschnitt 3 ist ein Rollenstößel 4 angeordnet. Dieser umfasst einen Stößelkörper 9 und eine Laufrolle 5. Mittels einer in der Zeichnung nicht dargestellten Kolbenfeder wird der Rollenstößel 4 zusammen mit dem Kolben gegen den Nockenabschnitt 3 gedrückt, um sicher zu stellen, dass die Laufrolle 5 nicht von dem Nockenabschnitt 3 der Antriebswelle 2 abhebt.The piston of the piston pump, not shown here, is indirectly driven by the
Zu beiden Seiten des Nockenabschnitts 3 ist jeweils ein Bord 6a und 6b an der Antriebswelle 2 vorgesehen. Die Borde 6a und 6b ragen in radialer Richtung über den Nockenabschnitt 3 hinaus, so dass die Laufrolle 5 bei Wanderung während des Betriebes in axialer Richtung und/oder Verdrehung aus der idealen Lage, gegen einen der beiden Borde 6a oder 6b anläuft. Dadurch wird die Axialbewegung und/oder Verdrehung aus der idealen Lage der Laufrolle 5 während des Betriebes auf ein definiertes Maß beschränkt. Gleichzeitig kann dafür Sorge getragen werden, dass durch eine geeignete tribologische Paarung der Laufrolle 5 und der Borde 6a und 6b der Verschleiß sowohl an der Laufrolle 5 als auch an den Borden 6a und 6b so gering ist, dass er nicht zu Funktionsstörungen oder einer Verkürzung der Lebensdauer der Kolbenpumpe führt.On both sides of the
Der in der
Ferner ist der Bord 6a derart ausgebildet, dass seine Höhe geringer ist als der halbe Durchmesser der Laufrolle 5. Eine solche Ausbildung des Bordes 6a und der Laufrolle 5 ermöglicht bei Winkelabweichungen der Laufrichtung der Laufrolle 5, hohe Pressungen infolge von Kantenträger oder Eckkontakten zwischen Laufrolle 5 und Bord 6a zu vermeiden. Darüber hinaus ist es von Vorteil, wenn der Berührpunkt der Laufrolle mit dem Bord 6a zwischen der Bordoberkannte und der Bordunterkannte liegt. Dies wird erfindungsgemäß erfüllt, wenn der Winkel w zwischen einer Senkrechten zu einer Achsenlängsachse der Laufrolle 5 und der zu einem Außenumfang des Bordes 6a verjüngenden Stirnfläche zwischen 0,1° und 10°groß ist und der Radius r einer zum Bord 6a gerichteten Stirnfläche der Laufrolle 5 1 mm bis 40 mm groß ist.Further, the
In
Diese beiden Kräfte Fn und Fr bewirken ein Drehmoment, wobei die Kraft Fr den Hebelarm b aufweist und als Reibmoment wirkt, welches den Verdrehwinkel c vergrößert. Die Kraft Fn weist den Hebelarm a auf und wirkt als Rückstellmoment, welches den Verdrehwinkel c verringert. Eine Rückstellung der Laufrolle 5 in ihre ursprüngliche Position wird erreicht, wenn das Rückstellmoment größer ist als das Reibmoment. Dies kann beispielsweise erreicht werden wenn die Kraft Fr besonders klein ist, wobei eine Verringerung von Fr bewerkstelligt wird, indem der Bord 6a und die Laufrolle 5 mit einer reibungsverringernden Beschichtung zumindest an möglichen Berührungsflächen zwischen Laufrolle 5 und Bord 6a versehen werden.These two forces Fn and Fr cause a torque, wherein the force Fr has the lever arm b and acts as a friction torque, which increases the angle of rotation c. The force Fn has the lever arm a and acts as a restoring moment, which reduces the angle of rotation c. A provision of the
Eine andere Möglichkeit die Rückstellung der Laufrolle 5 zu fördern ist eine Vergrößerung des Hebelarmes a und/oder eine Verringerung des Hebelarmes b. Durch das Einstellen der Geometrien Radius an der Laufrolle 5 und Winkel am Bord 6a zueinander, ergibt sich ein Verhältnis von a/b, welches bewirkt, dass die Rückstellung immer bei jeder Winkelabweichung erreicht wird. Die zulässige Winkelabweichung kann dabei festgelegt werden. Dies lässt sich durch eine Änderung der Abmessungen der Laufrolle 5 realisieren, wobei der Laufrollendurchmesser vergrößert werden sollte und die Laufrollenbreite verringert werden sollte. Ferner wird der Abstand a ebenfalls vergrößert, je kleiner der Bord 6a ist. Somit sollte die Höhe des Bordes 6a eine geringere Höhe aufweisen als der halbe Durchmesser der Laufrolle 5.Another way to promote the provision of the
Die Erfindung ist nicht beschränkt auf die vorstehend beschriebenen bevorzugten Ausführungsbeispiele. Es sind vielmehr auch Abwandlungen hiervon denkbar, welche vom Schutzbereich der nachfolgenden Ansprüche mit umfasst sind. So ist es beispielsweise auch möglich, anstelle der Aufbringung einer reibungsverringernden Beschichtung, die Oberfläche durch schleifen, polieren oder ätzen zu glätten, um den Effekt der Reibungsverringerung hervorzurufen. Desweitern ist eine reibungsverringernde Werkstoffpaarung und insbesondere eine Schmierung der Reibflächen der Laufrolle 5 und der Borde 6a und 6b ebenfalls denkbar.The invention is not limited to the preferred embodiments described above. On the contrary, modifications are conceivable which are included within the scope of the following claims. For example, instead of applying a friction-reducing coating, it is also possible to smooth the surface by grinding, polishing or etching to produce the effect of friction reduction. Desweitern is a friction-reducing material pairing and in particular a lubrication of the friction surfaces of the
Ergänzend ist darauf hinzuweisen, dass "umfassend" keine anderen Elemente oder Schritte ausschließt und "eine" oder "ein" keine Vielzahl ausschließt. Ferner sei darauf hingewiesen, dass Merkmale oder Schritte, die mit Verweis auf eines der obigen Ausführungsbeispiele beschrieben worden sind, auch in Kombination mit anderen Merkmalen oder Schritten anderer oben beschriebener Ausführungsbeispiele verwendet werden können. Bezugszeichen in den Ansprüchen sind nicht als Einschränkung anzusehen.In addition, it should be noted that "inclusive" does not exclude other elements or steps, and "a" or "an" does not exclude a multitude. It should also be appreciated that features or steps described with reference to any of the above embodiments may also be used in combination with other features or steps of other embodiments described above. Reference signs in the claims are not to be considered as limiting.
Claims (10)
- Piston pump, in particular high-pressure fuel pump, having a housing (1), having a piston and having a drive shaft (2) with a cam section (3) on which the piston is supported at least indirectly by way of a roller (5) mounted rotatably in a roller tappet (4), wherein, laterally to both sides of the cam section (3), there is provided in each case one rim (6) which projects beyond the cam section (3) in a radial direction,
characterized in that, by way of the rims (6), the axial movement and/or rotational misalignment of the roller (5) during operation is restricted, in that the rim (6), at a face surface directed toward the roller (5), narrows toward an outer circumference of the rim (6), wherein the rim (6) is in particular of conical form so as to give rise to an opening inclination, wherein the roller (5) has, on a face surface directed toward the rim (6), a convex curvature, preferably with a radius (r), such that corner contact is prevented in the event of the roller (5) running against the rim (6). - Piston pump according to Claim 1,
characterized in that an angle (w) between a perpendicular (s) to an axial longitudinal axis of the roller (5) and the face surface which narrows toward an outer circumference of the rim (6) is 0.1° to 10°. - Piston pump according to Claim 1,
characterized in that the radius (r) of a face surface, directed toward the rim (6), of the roller (5) is between 1 mm and 40 mm. - Piston pump, in particular high-pressure fuel pump, having a housing (1), having a piston and having a drive shaft (2) with a cam section (3) on which the piston is supported at least indirectly by way of a roller (5) mounted rotatably in a roller tappet (4), wherein, laterally to both sides of the cam section (3), there is provided in each case one rim (6) which projects beyond the cam section (3) in a radial direction,
characterized in that, by way of the rims (6), the axial movement and/or rotational misalignment of the roller (5) during operation is restricted, in that the rim (6) has, on a face surface directed toward the roller (5), a convex curvature, preferably with a radius (r), and the roller, at a face surface directed toward the rim (6), narrows toward a face side of the roller (5), wherein the face surface is in particular of conical form so as to give rise to a closing inclination, such that corner contact is prevented in the event of the roller (5) running against the rim (6). - Piston pump according to Claim 4,
characterized in that an angle (w) between a perpendicular (s) to an axial longitudinal axis of the roller (5) and the face surface which narrows toward an outer circumference of the roller (5) is 0.1° to 10°. - Piston pump according to Claim 4,
characterized in that the radius (r) of a face surface, directed toward the roller (5), of the rim (6) is between 1 mm and 40 mm. - Piston pump according to Claim 1 or 4, characterized in that the rim (6) and the cam section (3) are of unipartite form.
- Piston pump according to Claim 1 or 4,
characterized in that the rim (6) and/or the roller (5) are/is composed of a hardenable iron material. - Piston pump according to Claim 1 or 4,
characterized in that the rim (6) and/or the roller (5) have/has a surface treatment for minimizing friction. - Piston pump according to Claim 1 or 4,
characterized in that the rim (6) has a height smaller than half of the diameter of the roller (5).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012203428A DE102012203428A1 (en) | 2012-03-05 | 2012-03-05 | piston pump |
PCT/EP2013/050145 WO2013131662A1 (en) | 2012-03-05 | 2013-01-07 | Piston pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2823177A1 EP2823177A1 (en) | 2015-01-14 |
EP2823177B1 true EP2823177B1 (en) | 2016-04-06 |
Family
ID=47563435
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13700489.1A Active EP2823177B1 (en) | 2012-03-05 | 2013-01-07 | Piston pump |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2823177B1 (en) |
CN (1) | CN104145114B (en) |
DE (1) | DE102012203428A1 (en) |
IN (1) | IN2014DN06231A (en) |
WO (1) | WO2013131662A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102022202578A1 (en) * | 2022-03-15 | 2023-09-21 | Thyssenkrupp Ag | Piston-cylinder assembly for a radial piston compressor, as well as radial piston compressors |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0243339B1 (en) * | 1986-04-21 | 1992-06-03 | Robert Bosch Ag | Cam shaft |
US6345597B1 (en) * | 2000-10-24 | 2002-02-12 | John D. Keeler | Non-rotatable valve lifter mechanism |
GB0309699D0 (en) | 2003-04-28 | 2003-06-04 | Delphi Tech Inc | Improvements in cams and cam followers |
DE102006025924B4 (en) * | 2006-06-02 | 2008-04-03 | Siemens Ag | Fluid pump with roller tappet |
DE102006048722A1 (en) | 2006-10-16 | 2008-04-17 | Robert Bosch Gmbh | Piston pump, in particular high-pressure fuel pump, with roller tappet |
DE102008040081A1 (en) * | 2008-07-02 | 2010-01-07 | Robert Bosch Gmbh | high pressure pump |
DE102009002520A1 (en) * | 2009-04-21 | 2010-10-28 | Robert Bosch Gmbh | High-pressure pump, particularly radial piston pump or in-line piston pump for fuel injection systems of air-compressing, self-ignited internal combustion engines, has pump assembly and drive shaft |
-
2012
- 2012-03-05 DE DE102012203428A patent/DE102012203428A1/en not_active Withdrawn
-
2013
- 2013-01-07 WO PCT/EP2013/050145 patent/WO2013131662A1/en active Application Filing
- 2013-01-07 CN CN201380011975.8A patent/CN104145114B/en not_active Expired - Fee Related
- 2013-01-07 IN IN6231DEN2014 patent/IN2014DN06231A/en unknown
- 2013-01-07 EP EP13700489.1A patent/EP2823177B1/en active Active
Also Published As
Publication number | Publication date |
---|---|
IN2014DN06231A (en) | 2015-10-23 |
WO2013131662A1 (en) | 2013-09-12 |
EP2823177A1 (en) | 2015-01-14 |
DE102012203428A1 (en) | 2013-09-05 |
CN104145114A (en) | 2014-11-12 |
CN104145114B (en) | 2017-07-28 |
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