EP2419635A1 - Piston pump having cam drive, particularly a fuel pump - Google Patents

Piston pump having cam drive, particularly a fuel pump

Info

Publication number
EP2419635A1
EP2419635A1 EP10704561A EP10704561A EP2419635A1 EP 2419635 A1 EP2419635 A1 EP 2419635A1 EP 10704561 A EP10704561 A EP 10704561A EP 10704561 A EP10704561 A EP 10704561A EP 2419635 A1 EP2419635 A1 EP 2419635A1
Authority
EP
European Patent Office
Prior art keywords
cam
piston
free
piston pump
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10704561A
Other languages
German (de)
French (fr)
Other versions
EP2419635B1 (en
Inventor
Friedrich Boecking
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2419635A1 publication Critical patent/EP2419635A1/en
Application granted granted Critical
Publication of EP2419635B1 publication Critical patent/EP2419635B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B1/0439—Supporting or guiding means for the pistons
    • 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
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams

Definitions

  • the invention relates to a piston pump, in particular fuel pump according to the preamble of claim 1.
  • Fuel pumps of internal combustion engines which are designed as piston pumps and are actuated via a cam drive, are known from the market. In some internal combustion engines of motor vehicles, they are also designed as so-called "plug-in pumps". As such, a pump module is inserted into an opening, for example in the engine block of the internal combustion engine.
  • DE10 2006 045 933 describes an embodiment in which a roller which produces the connection between the cam and the piston is mounted in a roller shoe. To compensate for tolerances of the roller leading roller shoe is easily tilted, so that edge support, that is, excessive compressive stress on the edge of the lateral surface and end face of a cam can be avoided.
  • the object of the invention is to improve the operation of a fuel pump, in particular to extend its life.
  • the elasticity of the metallic materials used, in particular steel is used to produce a reduction in stiffness in the lateral edge region of the cam.
  • a certain "elastic resilience" in the area of the cam edge relative to the roller can be produced. It is therefore not necessary to widen the cam to avoid edge beams. In this way, production-related inaccuracies in the interaction of roller and cam are largely harmless to the fatigue strength of a piston pump. This increases the service life of the piston pump and improves its operation.
  • the free-cutting recess extends radially inward to the radially outer surface of the shaft. As a result, mass is saved, and it can be the production of the free-cutting recess simplified.
  • a further embodiment consists in that the free-slot-like recess has a rectangular, trapezoidal or round cross-section.
  • the stiffness reduction of the lateral edge region of the cam generated by the slot-like recess can be optimally adapted to the specific load case of the piston pump.
  • a rectangular cross section of the free-cutting recess is particularly easy to manufacture.
  • a trapezoidal cross-section of Freistichartigen recess changes the stiffness reduction substantially linearly in the longitudinal direction of the shaft so that voltage peaks can be reduced while still easy manufacturability.
  • the best fatigue strength is achieved with a round (for example circular or elliptical) or strongly rounded cross-section, because high compressive or tensile stresses in the region of the free-hole-like recess are avoided, in particular under strong dynamic loading.
  • the invention provides that the cam is designed as a single cam, a double cam or a triple cam, whereby piston pumps with high flow rate can still be realized with good life.
  • a further embodiment consists in that the free-slot recess is present only in a partial area of the end face. This can take into account that - depending on a rotation angle of the cam - different forces and stresses act on the cam or the roller. With this configuration, the geometry of the free-cutting recess can be optimally adapted to the load corresponding to the angle of rotation of the cam and the working phase of the driven piston pump.
  • plug-in pumps which can be plugged into an opening in a drive housing, for example an internal combustion engine.
  • Such plug-in pumps find use in internal combustion engines of motor vehicles and represent a cost-effective and flexible solution.
  • Figure 1 shows a partial section through a portion of a first embodiment of a piston pump with a single cam
  • Figure 2 is a partial section through a portion of a second embodiment of a piston pump with a double cam
  • FIG. 3 shows a section through a drive shaft of a third embodiment of a piston pump with a single cam
  • FIG. 4 shows a partial longitudinal section through a shaft with a single cam and a free-slot recess with a rectangular cross section in an end face of the single cam;
  • Figure 5 is a view similar to Figure 4 with a free-cutting recess with trapezoidal cross-section in a front side of the single cam;
  • Figure 6 is a view similar to Figure 4 with a free-cutting recess with a round cross-section in a front side of the single cam.
  • Figure 1 shows a part of a piston pump 10, as used in internal combustion engines of motor vehicles, in a partial sectional view. Shown in the lower part of the figure is an axially cut shaft 12, on which a cam 14, which has an approximately circular cross-section, is arranged eccentrically.
  • a free-cutting In the observer of Figure 1 facing the front side of the cam 14 is a free-cutting and seen in the axial direction of the shaft 12 has a relatively small depth recess 16 incorporated through in the region of the transition between the end face and the radially outer surface of the cam 14 an axially extending ridge 18 is formed.
  • the opposite end face is identical.
  • the cam 14 is a cylindrical roller 20 which contacts the cam 14 along a common surface line.
  • the roller 20 has an axial length which corresponds approximately to the width of the cam 14, and it is guided in a roller shoe 22 about half of its circumference.
  • the roller shoe 22 is held by a guide sleeve 24, which has substantially the shape of a hollow cylinder open on both sides.
  • a helical spring 26 engages via a radially extending web attached to the lower end of the guide sleeve 24 in FIG.
  • a piston 28 is supported, which is guided displaceably in a housing 30, in which the other end of the Coil spring 26 is supported.
  • the guide sleeve 24 is guided on a cylindrical and concentric with the piston 28 extension (without reference numeral) of the housing 30.
  • a bore 32 in the housing 30 allows pressure equalization between the roller shoe 22, guide sleeve 24, housing 30 and piston 28 enclosed space during the piston movement.
  • the eccentric movement of the cam 14 provides for a periodic drive of the piston 28.
  • the roller 20 causes a low-wear power transmission from the cam 14 to the roller shoe 22.
  • the roller 20 rolls continuously and with low friction on the radially outer surface of the cam 14th from, while the roller 20 is slidably mounted in the roller shoe 22.
  • the coil spring 26 is compressed. After reversal of a top dead center, not shown, the expanding coil spring 26 during the downward movement causes a non-positive cohesion of roller shoe 22, roller 20 and cam 14th
  • Figure 2 shows a sectional view of a portion of a second embodiment of a piston pump 10 with an elliptical double cam 14.
  • a free-slot recess 16 and a web formed thereby 18 can be seen in the observer facing end face of the cam 14 .
  • the free-cutting recess 16 has a dimension 34 dependent on the angle Phi.
  • a measure 36 of the web 18 may be dependent on the angle Phi.
  • FIG. 3 shows a section through a drive shaft 12 of a third embodiment of a piston pump 10 with a non-circular in contrast to Figure 1 but approximately elliptical single cam 14.
  • the cam 14 is in its lower part in Figure 3 in the circular shape of the shaft 12 on ,
  • the upper part of the cam 14 in turn contains a free-form recess 16 and a web 18 formed thereby.
  • Figure 4 shows a partially sectioned side view of a shaft 12 together with a cam 14, which is designed as a single cam and in the present case with the shaft 12 forms an integral unit.
  • a roller 20 is drawn, which has a radially symmetrical, convex shape (without reference numerals) on both end faces. It can be seen that both the free-slot recess 16 and the web 18 formed by the free-cutting recess 16 have a rectangular cross-section.
  • FIG. 5 shows, similar to FIG. 4, a partially sectioned side view of a shaft 12 together with a cam 14 arranged thereon and a roller 20 resting on the cam 14.
  • the free-slot recess 16 and the web 18 each have a trapezoidal cross section.
  • FIGS. 4 and 5 shows, similar to FIGS. 4 and 5, a partially sectioned side view of a shaft 12 together with a cam 14 arranged thereon and a roller 20 lying on the cam 14.
  • the free-slot recess 16 and the web 18 formed therefrom have a strongly rounded cross section on.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Transmission Devices (AREA)

Abstract

The invention relates to a piston pump (10), particularly a fuel pump, having a shaft (12), at least one cam (14) arranged thereon, a piston, and a roller (20) arranged between the piston and the cam (14) for rolling on the cam (14), wherein on at least one face of the cam (14), an undercut-like recess (16) is provided.

Description

Beschreibung description
Titeltitle
KOLBENPUMPE MIT NOCKENANTRIEB, INSBESONDERE KRAFTSTOFFPUMPEPISTON PUMP WITH CAM DRIVE, ESPECIALLY FUEL PUMP
Stand der TechnikState of the art
Die Erfindung betrifft eine Kolbenpumpe, insbesondere Kraftstoffpumpe nach dem Oberbegriff des Anspruchs 1.The invention relates to a piston pump, in particular fuel pump according to the preamble of claim 1.
Kraftstoffpumpen von Brennkraftmaschinen, die als Kolbenpumpen ausgeführt sind und über einen Nockenantrieb betätigt werden, sind vom Markt her bekannt. In einigen Brennkraftmaschinen von Kraftfahrzeugen werden sie auch als sogenannte "Steckpumpen" ausgeführt. Als solche wird ein Pumpenmodul in eine Öffnung beispielsweise im Motorblock der Brennkraftmaschine eingesteckt. In DE10 2006 045 933 wird eine Ausführung beschrieben, bei der eine die Verbindung zwischen Nocke und Kolben herstellende Laufrolle in einem Rollenschuh gelagert ist. Zum Ausgleich von Toleranzen wird der die Laufrolle führende Rollenschuh leicht kippbar gelagert, so dass Kantenträger, das heißt, eine übermäßige Druckbeanspruchung an der Kante von Mantelfläche und Stirnseite einer Nocke vermieden werden.Fuel pumps of internal combustion engines, which are designed as piston pumps and are actuated via a cam drive, are known from the market. In some internal combustion engines of motor vehicles, they are also designed as so-called "plug-in pumps". As such, a pump module is inserted into an opening, for example in the engine block of the internal combustion engine. DE10 2006 045 933 describes an embodiment in which a roller which produces the connection between the cam and the piston is mounted in a roller shoe. To compensate for tolerances of the roller leading roller shoe is easily tilted, so that edge support, that is, excessive compressive stress on the edge of the lateral surface and end face of a cam can be avoided.
Offenbarung der ErfindungDisclosure of the invention
Die Aufgabe der Erfindung ist es, den Betrieb einer Kraftstoffpumpe zu verbessern, insbesondere deren Lebensdauer zu verlängern.The object of the invention is to improve the operation of a fuel pump, in particular to extend its life.
Diese Aufgabe wird durch eine Vorrichtung nach Anspruch 1 gelöst. Vorteilhafte Weiterbildungen sind in den Unteransprüchen angegeben. Für die Erfindung wichtige Merkmale finden sich ferner in der nachfolgenden Beschreibung und in den Zeichnungen, wobei die Merkmale sowohl in Alleinstellung als auch in unterschiedlichen Kombinationen für die Erfindung wichtig sein können, ohne dass hierauf nochmals explizit hingewiesen wird.This object is achieved by a device according to claim 1. Advantageous developments are specified in the subclaims. For the invention important features can be further found in the following description and in the drawings, the features both alone and in different combinations may be important for the invention, without being explicitly referred to again.
Als Folge von Herstellungenauigkeiten der Laufrolle oder der Nocke, oder von nicht genau parallelen Drehachsen der Laufrolle und der die Nocke tragenden Welle können vor allem am Rand der Nocke hohe Druckspannungen im Bereich der radialen Außenfläche der Nocke entstehen, die - ohne Gegenmaßnahmen - zu sogenannten "Kantenträgern" führen können, also kerbartigen oder kantigen Unebenheiten in der Außenfläche der Nocke. Die Entstehung solcher Kantenträger wird durch die erfindungsgemäßen Maßnahmen verhindert oder zumindest erheblich reduziert. Weil die für die Kantenträger ursächlichen Toleranzen zumeist sehr klein sind, genügen zum Ausgleich entsprechend kleine und lokal wirkende Anpassungen in Form der erfindungsgemäß vorgesehenen freistichartigen Ausnehmungen an mindestens einer Stirnseite der Nocke. Dabei wird die Elastizität der verwendeten metallischen Werkstoffe, insbesondere von Stahl, genutzt, um eine Steifigkeitsreduktion im seitlichen Randbereich der Nocke zu erzeugen. Man kann sogar sagen, dass erfindungsgemäß eine gewisse "federelastische Nachgiebigkeit" im Bereich der Nockenkante gegenüber der Laufrolle erzeugt werden kann. Es ist daher nicht nötig, die Nocke zur Vermeidung von Kantenträgern breiter zu machen. Auf diese Weise sind herstellbedingte Ungenauigkeiten im Zusammenspiel von Laufrolle und Nocke weitgehend unschädlich für die Dauerfestigkeit einer Kolbenpumpe. Damit wird die Lebensdauer der Kolbenpumpe erhöht und ihr Betrieb verbessert.As a result of manufacturing inaccuracies of the roller or the cam, or of not exactly parallel axes of rotation of the roller and the cam bearing shaft, especially at the edge of the cam high compressive stresses in the region of the radial outer surface of the cam may arise, which - without countermeasures - to so-called " Edge bearers ", ie notches or angular unevenness in the outer surface of the cam. The formation of such edge supports is prevented or at least considerably reduced by the measures according to the invention. Because the tolerances causative for the edge supports are usually very small, correspondingly small and locally acting adjustments in the form of the recess-like recesses provided according to the invention on at least one end face of the cam suffice for compensation. In this case, the elasticity of the metallic materials used, in particular steel, is used to produce a reduction in stiffness in the lateral edge region of the cam. One can even say that, according to the invention, a certain "elastic resilience" in the area of the cam edge relative to the roller can be produced. It is therefore not necessary to widen the cam to avoid edge beams. In this way, production-related inaccuracies in the interaction of roller and cam are largely harmless to the fatigue strength of a piston pump. This increases the service life of the piston pump and improves its operation.
Weiterhin wird vorgeschlagen, dass die freistichartige Ausnehmung nach radial einwärts bis zur radial äußeren Oberfläche der Welle reicht. Hierdurch wird Masse gespart, und es kann die Herstellung der freistichartigen Ausnehmung vereinfacht werden.Furthermore, it is proposed that the free-cutting recess extends radially inward to the radially outer surface of the shaft. As a result, mass is saved, and it can be the production of the free-cutting recess simplified.
Eine weitere Ausgestaltung besteht darin, dass die freistichartige Ausnehmung einen rechteckigen, trapezförmigen oder runden Querschnitt aufweist. Durch verschieden geformte Querschnitte kann die durch die freistichartige Ausnehmung erzeugte Steifigkeitsreduktion des seitlichen Randbereichs der Nocke optimal an den spezifischen Lastfall der Kolbenpumpe angepasst werden. Eine rechteckiger Querschnitt der freistichartigen Ausnehmung ist dabei besonders einfach herzustellen. Bei einem trapezförmigen Querschnitt der freistichartigen Ausnehmung verändert sich die Steifigkeitsreduktion im Wesentlichen linear in Längsrichtung der Welle, so dass Spannungsspitzen reduziert werden können bei dennoch einfacher Herstellbarkeit. Die beste Dauerfestigkeit wird mit einem runden (bspw. kreisrunden oder elliptischen) oder stark abgerundeten Querschnitt erreicht, weil insbesondere bei starker dynamischer Belastung hohe Druck- oder Zugspannungen im Bereich der freistichartigen Ausnehmung vermieden werden.A further embodiment consists in that the free-slot-like recess has a rectangular, trapezoidal or round cross-section. By means of differently shaped cross sections, the stiffness reduction of the lateral edge region of the cam generated by the slot-like recess can be optimally adapted to the specific load case of the piston pump. A rectangular cross section of the free-cutting recess is particularly easy to manufacture. In a trapezoidal cross-section of Freistichartigen recess changes the stiffness reduction substantially linearly in the longitudinal direction of the shaft so that voltage peaks can be reduced while still easy manufacturability. The best fatigue strength is achieved with a round (for example circular or elliptical) or strongly rounded cross-section, because high compressive or tensile stresses in the region of the free-hole-like recess are avoided, in particular under strong dynamic loading.
Weiterhin sieht die Erfindung vor, dass die Nocke als eine Einfachnocke, eine Doppelnocke oder eine Dreifachnocke ausgeführt ist, wodurch auch Kolbenpumpen mit hoher Förderleistung bei dennoch guter Lebensdauer realisiert werden können.Furthermore, the invention provides that the cam is designed as a single cam, a double cam or a triple cam, whereby piston pumps with high flow rate can still be realized with good life.
Eine weitere Ausgestaltung besteht darin, dass die freistichartige Ausnehmung nur in einem Teilbereich der Stirnseite vorhanden ist. Dadurch kann berücksichtigt werden, dass - abhängig von einem Drehwinkel der Nocke - unterschiedliche Kräfte und Beanspruchungen auf die Nocke oder die Laufrolle einwirken. Mit dieser Ausgestaltung kann die Geometrie der freistichartigen Ausnehmung an die dem Drehwinkel der Nocke und der Arbeitsphase der angetriebenen Kolbenpumpe entsprechende Belastung optimal angepasst werden.A further embodiment consists in that the free-slot recess is present only in a partial area of the end face. This can take into account that - depending on a rotation angle of the cam - different forces and stresses act on the cam or the roller. With this configuration, the geometry of the free-cutting recess can be optimally adapted to the load corresponding to the angle of rotation of the cam and the working phase of the driven piston pump.
Ein besonders geeigneter Anwendungsfall der Erfindung sind Steckpumpen, die in eine Öffnung eines Antriebsgehäuses, beispielsweise einer Brennkraftmaschine, steckbar sind. Solche Steckpumpen finden in Brennkraftmaschinen von Kraftfahrzeugen Verwendung und stellen eine kostengünstige und flexible Lösung dar.A particularly suitable application of the invention are plug-in pumps, which can be plugged into an opening in a drive housing, for example an internal combustion engine. Such plug-in pumps find use in internal combustion engines of motor vehicles and represent a cost-effective and flexible solution.
Nachfolgend werden beispielhafte Ausführungsformen der Erfindung unter Bezugnahme auf die Zeichnung erläutert. Es werden dabei für funktionsäquivalente Blöcke und Größen die gleichen Bezugszeichen verwendet. In der Zeichnung zeigen:Hereinafter, exemplary embodiments of the invention will be explained with reference to the drawings. The same reference numerals are used for functionally equivalent blocks and sizes. In the drawing show:
Figur 1 einen teilweisen Schnitt durch einen Teilbereich einer ersten Ausführungsform einer Kolbenpumpe mit einer Einfachnocke; Figur 2 eine teilweisen Schnitt durch einen Teilbereich einer zweiten Ausführungsform einer Kolbenpumpe mit einer Doppelnocke;1 shows a partial section through a portion of a first embodiment of a piston pump with a single cam; Figure 2 is a partial section through a portion of a second embodiment of a piston pump with a double cam;
Figur 3 einen Schnitt durch eine Antriebswelle einer dritten Ausführungsform einer Kolbenpumpe mit einer Einfachnocke;3 shows a section through a drive shaft of a third embodiment of a piston pump with a single cam;
Figur 4 einen teilweisen Längsschnitt durch eine Welle mit einer Einfachnocke und einer freistichartigen Ausnehmung mit rechteckigem Querschnitt in einer Stirnseite der Einfachnocke;FIG. 4 shows a partial longitudinal section through a shaft with a single cam and a free-slot recess with a rectangular cross section in an end face of the single cam;
Figur 5 eine Darstellung ähnlich zu Figur 4 mit einer freistichartigen Ausnehmung mit trapezförmigem Querschnitt in einer Stirnseite der Einfachnocke; undFigure 5 is a view similar to Figure 4 with a free-cutting recess with trapezoidal cross-section in a front side of the single cam; and
Figur 6 eine Darstellung ähnlich zu Figur 4 mit einer freistichartigen Ausnehmung mit rundem Querschnitt in einer Stirnseite der Einfachnocke.Figure 6 is a view similar to Figure 4 with a free-cutting recess with a round cross-section in a front side of the single cam.
Figur 1 zeigt einen Teil einer Kolbenpumpe 10, wie sie in Brennkraftmaschinen von Kraftfahrzeugen Verwendung findet, in einer teilweisen Schnittansicht. Dargestellt ist im unteren Teil der Figur eine axial geschnittene Welle 12, auf der eine Nocke 14, die einen in etwa kreisförmigen Querschnitt aufweist, exzentrisch angeordnet ist. In die dem Betrachter der Figur 1 zugewandte Stirnseite der Nocke 14 ist eine freistichartige und in axialer Richtung der Welle 12 gesehen eine relativ geringe Tiefe aufweisende Ausnehmung 16 eingearbeitet, durch im Bereich des Übergangs zwischen der Stirnseite und der radialen Außenfläche der Nocke 14 ein sich axial erstreckender Steg 18 gebildet wird. Die entgegen gesetzt liegende Stirnseite ist identisch ausgebildet. In Figur 1 oberhalb der Nocke 14 befindet sich eine zylindrische Laufrolle 20, welche die Nocke 14 längs einer gemeinsamen Mantellinie berührt. Die Laufrolle 20 hat eine axiale Länge, die in etwa der Breite der Nocke 14 entspricht, und sie ist etwa zur Hälfte ihres Umfangs in einem Rollenschuh 22 geführt. Der Rollenschuh 22 wird von einer Führungshülse 24 gehalten, welche im wesentlichen die Form eines beidseitig offenen Hohlzylinders aufweist. Über einen am in Figur 1 unteren Ende der Führungshülse 24 angebrachten sich radial erstreckenden Steg greift eine Schraubenfeder 26 an. Am Rollenschuh 22 stützt sich ein Kolben 28 ab, der in einem Gehäuse 30 verschiebbar geführt ist, an dem sich das andere Ende der Schraubenfeder 26 abstützt. Die Führungshülse 24 ist auf einem zylindrischen und zum Kolben 28 konzentrischen Fortsatz (ohne Bezugszeichen) des Gehäuses 30 geführt. Eine Bohrung 32 im Gehäuse 30 ermöglicht einen Druckausgleich des zwischen Rollenschuh 22, Führungshülse 24, Gehäuse 30 und Kolben 28 eingeschlossenen Raumes während der Kolbenbewegung.Figure 1 shows a part of a piston pump 10, as used in internal combustion engines of motor vehicles, in a partial sectional view. Shown in the lower part of the figure is an axially cut shaft 12, on which a cam 14, which has an approximately circular cross-section, is arranged eccentrically. In the observer of Figure 1 facing the front side of the cam 14 is a free-cutting and seen in the axial direction of the shaft 12 has a relatively small depth recess 16 incorporated through in the region of the transition between the end face and the radially outer surface of the cam 14 an axially extending ridge 18 is formed. The opposite end face is identical. In Figure 1 above the cam 14 is a cylindrical roller 20 which contacts the cam 14 along a common surface line. The roller 20 has an axial length which corresponds approximately to the width of the cam 14, and it is guided in a roller shoe 22 about half of its circumference. The roller shoe 22 is held by a guide sleeve 24, which has substantially the shape of a hollow cylinder open on both sides. A helical spring 26 engages via a radially extending web attached to the lower end of the guide sleeve 24 in FIG. At the roller shoe 22, a piston 28 is supported, which is guided displaceably in a housing 30, in which the other end of the Coil spring 26 is supported. The guide sleeve 24 is guided on a cylindrical and concentric with the piston 28 extension (without reference numeral) of the housing 30. A bore 32 in the housing 30 allows pressure equalization between the roller shoe 22, guide sleeve 24, housing 30 and piston 28 enclosed space during the piston movement.
Im Betrieb sorgt die exzentrische Bewegung der Nocke 14 für einen periodischen Antrieb des Kolbens 28. Die Laufrolle 20 bewirkt dabei eine verschleißarme Kraftübertragung von der Nocke 14 auf den Rollenschuh 22. Dabei rollt die Laufrolle 20 kontinuierlich und reibungsarm auf der radial äußeren Oberfläche der Nocke 14 ab, wogegen die Laufrolle 20 im Rollenschuh 22 gleitend gelagert ist. Dabei wird, ausgehend von einem in Figur 1 dargestellten unteren Totpunkt zugleich die Schraubenfeder 26 zusammengedrückt. Nach Umkehr von einem nicht dargestellten oberen Totpunkt bewirkt die expandierende Schraubenfeder 26 während der Abwärtsbewegung einen kraftschlüssigen Zusammenhalt von Rollenschuh 22, Laufrolle 20 und Nocke 14.In operation, the eccentric movement of the cam 14 provides for a periodic drive of the piston 28. The roller 20 causes a low-wear power transmission from the cam 14 to the roller shoe 22. The roller 20 rolls continuously and with low friction on the radially outer surface of the cam 14th from, while the roller 20 is slidably mounted in the roller shoe 22. In this case, starting from a bottom dead center shown in Figure 1 at the same time the coil spring 26 is compressed. After reversal of a top dead center, not shown, the expanding coil spring 26 during the downward movement causes a non-positive cohesion of roller shoe 22, roller 20 and cam 14th
Durch die freistichartige Ausnehmung 16 wird eine örtliche Steifigkeitsreduktion erreicht - die Laufrolle 20 wird in diesem seitlichen Randbereich der Nocke 14 nur noch von dem Steg 18 getragen. Durch die verminderte Steifigkeit kann dieser seitliche Randbereich bei Parallelitätsfehlern zwischen Nocke 14 und Laufrolle 20 nachgeben, wodurch das Entstehen sogenannter Kantenträger, also rillen- und/oder kantenartige Unebenheiten in der Oberfläche der Nocke 14 vermieden wird.By the free-slot recess 16, a local stiffness reduction is achieved - the roller 20 is supported in this lateral edge region of the cam 14 only of the web 18. Due to the reduced rigidity, this lateral edge region can yield in the event of parallelism errors between the cam 14 and the roller 20, whereby the emergence of so-called edge supports, ie groove-like and / or edge-like unevennesses in the surface of the cam 14, is avoided.
Figur 2 zeigt eine Schnittansicht eines Teils einer zweiten Ausführungsform einer Kolbenpumpe 10 mit einer elliptischen Doppelnocke 14. Auch hier sind in der dem Betrachter zugewandten Stirnseite der Nocke 14 eine freistichartige Ausnehmung 16 sowie ein dadurch gebildeter Steg 18 zu erkennen. Abhängig von einem in Umfangsrichtung gemessenen und die Geometrie der Nocke 14 kennzeichnenden Winkel Phi wird deutlich, dass die freistichartige Ausnehmung 16 ein vom Winkel Phi abhängiges Maß 34 aufweist. Ebenso kann auch ein Maß 36 des Steges 18 vom Winkel Phi abhängig sein. Während eines Umlaufs der als Doppelnocke ausgeführten Nocke 14 ergeben sich zwei vollständige Arbeitstakte der Kolbenpumpe 10 und verdoppeln somit die Arbeitsfrequenz in Bezug auf einen Betrieb einer Einfachnocke.Figure 2 shows a sectional view of a portion of a second embodiment of a piston pump 10 with an elliptical double cam 14. Again, in the observer facing end face of the cam 14 a free-slot recess 16 and a web formed thereby 18 can be seen. Depending on an angle Phi measured in the circumferential direction and characterizing the geometry of the cam 14, it becomes clear that the free-cutting recess 16 has a dimension 34 dependent on the angle Phi. Likewise, a measure 36 of the web 18 may be dependent on the angle Phi. During one revolution of the cam 14, which is designed as a double cam, two complete working cycles of the piston pump 10 result and thus double the operating frequency with respect to the operation of a single cam.
Figur 3 zeigt einen Schnitt durch eine Antriebswelle 12 einer dritten Ausführungsform einer Kolbenpumpe 10 mit einer im Gegensatz zu Figur 1 nicht kreisrunden sondern in etwa elliptischen Einfachnocke 14. Die Nocke 14 geht in ihrem in Figur 3 unteren Teil in die kreisrunde Form der Welle 12 über. Der obere Teil der Nocke 14 enthält wiederum eine freistichartige Ausnehmung 16 und einen hierdurch gebildeten Steg 18.3 shows a section through a drive shaft 12 of a third embodiment of a piston pump 10 with a non-circular in contrast to Figure 1 but approximately elliptical single cam 14. The cam 14 is in its lower part in Figure 3 in the circular shape of the shaft 12 on , The upper part of the cam 14 in turn contains a free-form recess 16 and a web 18 formed thereby.
Während eines Umlaufs der Nocke 14 ergibt sich ein vollständiger Arbeitstakt der Kolbenpumpe 10.During one revolution of the cam 14, a complete power stroke of the piston pump 10 results.
Figur 4 zeigt eine teilweise geschnittene Seitenansicht einer Welle 12 zusammen mit einer Nocke 14, die als eine Einfachnocke ausgeführt ist und vorliegend mit der Welle 12 eine integrale Einheit bildet. Oberhalb der Nocke 14 ist eine Laufrolle 20 gezeichnet, welche an beiden Stirnseiten eine radial symmetrische, konvexe Ausformung (ohne Bezugszeichen) aufweist. Man erkennt, dass sowohl die freistichartige Ausnehmung 16 als auch der durch die freistichartige Ausnehmung 16 gebildete Steg 18 einen rechteckförmigen Querschnitt besitzen.Figure 4 shows a partially sectioned side view of a shaft 12 together with a cam 14, which is designed as a single cam and in the present case with the shaft 12 forms an integral unit. Above the cam 14, a roller 20 is drawn, which has a radially symmetrical, convex shape (without reference numerals) on both end faces. It can be seen that both the free-slot recess 16 and the web 18 formed by the free-cutting recess 16 have a rectangular cross-section.
Figur 5 zeigt ähnlich zu Figur 4 eine teilweise geschnittene Seitenansicht einer Welle 12 zusammen mit einer darauf angeordneten Nocke 14 und einer auf der Nocke 14 aufliegenden Laufrolle 20. Dabei besitzen die freistichartige Ausnehmung 16 und der Steg 18 jeweils einen trapezförmigen Querschnitt.5 shows, similar to FIG. 4, a partially sectioned side view of a shaft 12 together with a cam 14 arranged thereon and a roller 20 resting on the cam 14. The free-slot recess 16 and the web 18 each have a trapezoidal cross section.
Figur 6 zeigt ähnlich zu den Figuren 4 und 5 eine teilweise geschnittene Seitenansicht einer Welle 12 zusammen mit einer darauf angeordneten Nocke 14 und einer auf der Nocke 14 aufliegenden Laufrolle 20. Dabei weisen die freistichartige Ausnehmung 16 und der daraus gebildete Steg 18 einen stark gerundeten Querschnitt auf.6 shows, similar to FIGS. 4 and 5, a partially sectioned side view of a shaft 12 together with a cam 14 arranged thereon and a roller 20 lying on the cam 14. The free-slot recess 16 and the web 18 formed therefrom have a strongly rounded cross section on.
Weiterhin ist es vorstellbar - unabhängig von einer konkreten Ausführungsform einer Nocke - eine freistichartige Ausnehmung mit einer entsprechenden Wirkung zur Vermeidung von Kantenträgern ergänzend oder alternativ an der Laufrolle 20 vorzusehen. Furthermore, it is conceivable - regardless of a specific embodiment of a cam - a free-slot recess with a corresponding effect to avoid edge supports complementary or alternatively provided on the roller 20.

Claims

Ansprüche claims
1. Kolbenpumpe (10), insbesondere Kraftstoffpumpe, mit einer Welle (12), mindestens einer darauf angeordneten Nocke (14), einem Kolben und einer zwischen Kolben und Nocke (14) angeordneten Laufrolle (20) zum Abrollen auf der Nocke (14), dadurch gekennzeichnet, dass an mindestens einer Stirnseite der Nocke (14) eine freistichartige Ausnehmung (16) vorhanden ist.1. Piston pump (10), in particular fuel pump, with a shaft (12), at least one cam (14) arranged thereon, a piston and between the piston and cam (14) arranged roller (20) for rolling on the cam (14) , characterized in that on at least one end face of the cam (14) a free-slot recess (16) is present.
2. Kolbenpumpe (10) nach Anspruch 1 , dadurch gekennzeichnet, dass die freistichartige Ausnehmung (16) nach radial einwärts bis zur radial äußeren Oberfläche der Welle (12) reicht.Second piston pump (10) according to claim 1, characterized in that the free-cutting recess (16) extends radially inwardly to the radially outer surface of the shaft (12).
3. Kolbenpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die freistichartige Ausnehmung (16) einen rechteckigen, trapezförmigen oder runden Querschnitt aufweist.3. Piston pump (10) according to any one of the preceding claims, characterized in that the free-cutting recess (16) has a rectangular, trapezoidal or round cross-section.
4. Kolbenpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Nocke (14) als eine Einfachnocke, eine Doppelnocke oder eine Dreifachnocke ausgeführt ist.4. Piston pump (10) according to any one of the preceding claims, characterized in that the cam (14) is designed as a single cam, a double cam or a triple cam.
5. Kolbenpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die freistichartige Ausnehmung (16) nur in einem Teilbereich der Stirnseite vorhanden ist.5. Piston pump (10) according to any one of the preceding claims, characterized in that the free-cutting recess (16) is present only in a partial region of the end face.
6. Kolbenpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es sich um eine Steckpumpe handelt, die in eine Öffnung eines Antriebsgehäuses steckbar ist. 6. Piston pump (10) according to one of the preceding claims, characterized in that it is a plug-in pump which can be plugged into an opening of a drive housing.
EP10704561.9A 2009-04-16 2010-02-17 Piston pump having cam drive, particularly a fuel pump Not-in-force EP2419635B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910002434 DE102009002434A1 (en) 2009-04-16 2009-04-16 Piston pump, in particular fuel pump
PCT/EP2010/051955 WO2010118903A1 (en) 2009-04-16 2010-02-17 Piston pump having cam drive, particularly a fuel pump

Publications (2)

Publication Number Publication Date
EP2419635A1 true EP2419635A1 (en) 2012-02-22
EP2419635B1 EP2419635B1 (en) 2013-04-17

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ID=42066334

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10704561.9A Not-in-force EP2419635B1 (en) 2009-04-16 2010-02-17 Piston pump having cam drive, particularly a fuel pump

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Country Link
EP (1) EP2419635B1 (en)
CN (1) CN102395788B (en)
DE (1) DE102009002434A1 (en)
WO (1) WO2010118903A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6102767B2 (en) * 2014-01-24 2017-03-29 株式会社デンソー High pressure fuel pump
DE102014220384B4 (en) * 2014-10-08 2021-02-18 Vitesco Technologies GmbH High pressure fuel pump and drive shaft
GB2557630A (en) * 2016-12-13 2018-06-27 Delphi Int Operations Luxembourg Sarl Cam actuated fuel pump

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Publication number Priority date Publication date Assignee Title
DE3247026A1 (en) * 1982-12-18 1984-06-20 Klöckner-Humboldt-Deutz AG, 5000 Köln Elastic roller tappet
CN2200062Y (en) * 1994-06-03 1995-06-07 孙玉山 Multipurpose air pump for bicycle
GB9615359D0 (en) * 1996-07-22 1996-09-04 Lucas Ind Plc Fuel pump
JP3852756B2 (en) * 2001-02-07 2006-12-06 株式会社デンソー Fuel injection pump
GB0224936D0 (en) * 2002-10-25 2002-12-04 Delphi Tech Inc Fuel pump assembly
DE102005047234A1 (en) * 2005-10-01 2007-04-05 Schaeffler Kg Roller tappet for internal combustion engine, has tappet roller for transverse-force free actuation of pump plunger, where load capacity and life span of tappet are increased with constant outer diameter of roller by broadening roller
DE102006045933A1 (en) 2006-09-28 2008-04-03 Robert Bosch Gmbh Plunger assembly for a high pressure pump and high pressure pump with at least one plunger assembly

Non-Patent Citations (1)

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Title
See references of WO2010118903A1 *

Also Published As

Publication number Publication date
WO2010118903A1 (en) 2010-10-21
DE102009002434A1 (en) 2010-10-21
EP2419635B1 (en) 2013-04-17
CN102395788A (en) 2012-03-28
CN102395788B (en) 2014-10-29

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