EP1454055B1 - Radial piston pump having force-feed lubrication - Google Patents

Radial piston pump having force-feed lubrication Download PDF

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Publication number
EP1454055B1
EP1454055B1 EP02764536A EP02764536A EP1454055B1 EP 1454055 B1 EP1454055 B1 EP 1454055B1 EP 02764536 A EP02764536 A EP 02764536A EP 02764536 A EP02764536 A EP 02764536A EP 1454055 B1 EP1454055 B1 EP 1454055B1
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EP
European Patent Office
Prior art keywords
radial piston
piston pump
fuel
sliding bearing
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP02764536A
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German (de)
French (fr)
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EP1454055A1 (en
Inventor
Heinz Siegel
Helmut Rembold
Hans-Peter Stiefel
Karl Gmelin
Thomas Fuerst
Thilo Bolz
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
Priority claimed from DE10208574A external-priority patent/DE10208574A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1454055A1 publication Critical patent/EP1454055A1/en
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Publication of EP1454055B1 publication Critical patent/EP1454055B1/en
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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
    • 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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to a radial piston pump for High-pressure fuel production for one Fuel injection system of internal combustion engines, with a drive shaft, wherein the drive shaft a eccentric section and one in a pump housing Stub shaft supported by a first sliding bearing having, preferably with respect to several Drive shaft radially arranged pump elements, with one between the eccentric section and the Pump element arranged ring, and with a Fuel connection in the pump housing.
  • Such an internally supported radial piston pump is, for example. known from DE 197 05 205 A1.
  • the Radial piston pump for conveying fuels with poor lubricating properties, such as or gasoline is to be used, the storage of the Stub shaft in the pump housing and the bearing of the ring on the eccentric portion of the drive shaft a limiting factor for the flow rate and the head represents.
  • This task is in a radial piston pump for High-pressure fuel production for a fuel injection system of internal combustion engines according to the preamble of claim 1, solved by the fact that the first sliding bearing of the entire The fuel port flowing through the fuel port is flowed through.
  • the incoming in the fuel port of the radial piston pump Fuel has a pressure coming from a prefeed pump is provided, from about 4 - 6 bar on. This pressure is regardless of the speed and operating conditions of the Radial piston pump.
  • the invention provides that the first sliding bearing at least one substantially in the direction of the axis of rotation having the drive shaft extending lubrication, so that the from the fuel port in the first sliding bearing flowing fuel 'uniformly over the entire Warehouse distributed and thus the uniform training a lubricant film is favored.
  • a further supplement of the invention provides that the Stub shaft has a center hole, that of the Mittenbohrung a transverse bore branches off, and that the second plain bearing from the transverse bore with fuel is supplied.
  • the fuel can be used for Lubrication of the second sliding bearing in the middle of Bearing surface of the second sliding bearing are introduced and from there flow to the edges of the plain bearing. This favors the formation of a viable lubricating film between ring and eccentric section of the Drive shaft.
  • the second sliding bearing at least one substantially extending in the direction of the axis of rotation of the drive shaft Has lubrication.
  • the eccentric portion or the ring has an annular groove, and that the transverse bore opens into the annular groove, so that the Fuel evenly over the entire circumference of the second Sliding bearing is distributed.
  • Alternative embodiments of the invention provide that the fuel connection in the interior of the housing or opens directly into the first plain bearing. This allows the inventive design of the first and second Plain bearings in different types of Radial piston pumps equally advantageous for use reach.
  • the formation of a stable lubricating film can continue be promoted when the oil groove on the stub shaft and / or the lubrication groove on the eccentric section are performed coiled.
  • Fig. 1 is a first embodiment of a Radial piston pump according to the invention in cross section shown.
  • the radial piston pump consists of a Pump housing 1.
  • the pump housing 1 is a Drive shaft 3 rotatably mounted.
  • the drive shaft 3 is with a stub shaft 5 in a first sliding bearing 7 in Pump housing 1 stored.
  • With her the stub shaft 5 opposite end is the drive shaft 3 in one Lid 9 supported by a ball bearing 11. immediate
  • the drive shaft 3 a eccentric section 13 on.
  • the eccentric portion 13 is of a ring 15, which in a front view (not shown) one polygonal outer contour 19 has surrounded.
  • the ring 15 does not rotate when the drive shaft 3 is rotated, but performs a circular motion.
  • a second one Plain bearing 17 is present, which is pressed with the ring 15.
  • With its polygonal outer contour 19 transmits the Ring 15 giving it from the eccentric section 13 imprinted circular movement on a piston foot plate 21 a pump element 23.
  • the pump element 23 has a cylinder bore 25 and a piston 27 on.
  • About the Kolbenfußplatte 21 is the Plunged piston 27 in an oscillating motion.
  • Fuel is from a fuel connection (not shown) sucked into a working space 29 when the fuel has flowed through the first sliding bearing 7, and subsequently during the so-called delivery stroke with pressure applied.
  • About a high pressure drain (not shown) becomes the high pressure fuel pushed out of the work space 29.
  • the high-pressure fuel pump is supplied via a Fuel connection 31, which in the first sliding bearing. 7 empties.
  • the fuel in the fuel port 31 is from a pre-feed pump, not shown with a Delivery pressure of about 4 - 6 bar in the first sliding bearing. 7 pressed. This results in a very stable training a lubricating film between the pump housing 1 and Stub shaft 5, which is the carrying capacity and life of the first slide bearing 7 significantly increased.
  • Lubrication grooves 33 are over the circumference of the first sliding bearing 7 distributed.
  • the Lubrication grooves 33 can also be designed coiled.
  • the first sliding bearing 7 consists of a in the Housing 1 pressed bushing 37 with pressed Inner ring 36 and the stub shaft 5.
  • the lubrication grooves 33 can either in the inner ring 36 or in the Shaft stump 5 incorporated. When the lubrication grooves 33 are incorporated in the stub shaft 5, the Rotary movement of the stub shaft to promote fuel be exploited in the first sliding bearing 7. This increases the load capacity of the first sliding bearing 7 continues.
  • Fig. 2 is a second embodiment of a Radial piston pump according to the invention in cross section shown. Same components are with the same Reference numerals provided and it applies that concerning the FIG. 1 stated accordingly.
  • the ball bearing 11 is in the Pump housing 1 used.
  • the fuel connection 31 opens into the interior 35. From there flows the fuel via lubrication grooves 33 through the first sliding bearing 7 to the end of the stub shaft 5. From the cross-sectional view of Fig. 2 it can be seen that in the housing 1 a socket 37 is pressed, in which the lubrication grooves 33 are incorporated.
  • the sleeve 37 forms together with the Stub shaft 5, the first sliding bearing. 7
  • the stub shaft 5 has a central bore 39, which of a transverse bore 41 is penetrated.
  • the transverse bore 41 in turn opens into an annular groove 43, which in the eccentric portion 13 of the drive shaft. 3 is incorporated.
  • the annular groove 43 in the ring 15 are incorporated. This alternative is in Fig. 2 not shown.
  • About the center hole 39 and the Transverse bore 41 and the annular groove 43 passes the fuel from the end of the stub shaft 5 to the second sliding bearing 17, which of the eccentric portion 13 and the ring 15th is formed.
  • lubrication grooves 45 incorporated, which is parallel to the axis of rotation 47 of Drive shaft 3 over almost the entire width of the ring 15th extend.
  • the lubrication grooves 45 provide a hydraulic Connection between annular groove 43 and the interior 35 on the the stub shaft 5 side facing away from the ring 15 ago.
  • This measure ensures that always "fresh" fuel from the interior 35 through the first Plain bearing 7 flows and not to a Short circuit flow between the second sliding bearing 17 and first sliding bearing 7 can come.
  • Fig. 3 is a third embodiment of a Radial piston pump according to the invention in cross section shown. Same components are with the same Reference numerals provided and it applies that concerning the FIG. 1 and 2 said accordingly.
  • a coiled lubricating groove 33 available.
  • this Embodiment is characterized by the rotation of the Drive shaft 3 fuel in the first sliding bearing. 7 promoted, which increases its capacity and durability.
  • a coiled lubrication 45th available.
  • the lubrication groove 45 improves the supply of second sliding bearing 17 with fuel and thereby increases its load capacity and service life.
  • Fig. 4 the third shown in Fig. 3 Embodiment in a side view schematically shown. Based on this presentation, the optimal Arrangement of the coiled or straight lubrication grooves 37 and 45 will be explained.
  • FIG. 4 are three um 120 ° offset from one another arranged pump elements 23-I, 23-II and 23-III schematically by their longitudinal axes represented by the eccentric section 13 of the Drive shaft to be actuated.
  • the direction of rotation of Drive shaft is represented by a first arrow 53.
  • the preferred one Space for the arrangement of the lubrication groove 33 is shown in Fig. 4 as second angle range 59 marked. In this way is the carrying capacity of the first sliding bearing 7 in the area their highest stress by the lubrication groove 33 not impaired.
  • the lubrication groove 45 (not shown) in the region of the second sliding bearing 17 has the first angular range 57, the 180 ° to the second Angle range 59 is arranged offset, as advantageous proved.
  • a throttle (not shown) are provided per plain bearing.

Abstract

The invention relates to a radial piston pump for an injection system of internal combustion engines, in which a first plain bearing (7) and a second plain bearing (17) are provided in the form of a hydrostatic plain bearing, whereby the necessary pressure is provided by a pre-feed pump that supplies fuel to the radial piston pump via a fuel connection (31). This increases the bearing capacity of both the first plain bearing (7) and the second plain bearing (17). In addition, the cooling of said plain bearings (7, 17) is improved. As a result, the inventive radial piston pump can be subjected to higher loads with regard to pump capacity and pump head and has a longer serviceable life than that of prior art radial piston pumps.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung für eine Kraftstoffeinspritzanlage von Brennkraftmaschinen, mit einer Antriebswelle, wobei die Antriebswelle einen exzentrischen Abschnitt und einen in einem Pumpengehäuse durch ein erstes Gleitlager gelagerten Wellenstumpf aufweist, mit vorzugsweise mehreren bezüglich der Antriebswelle radial angeordneten Pumpenelementen, mit einem zwischen dem exzentrischen Abschnitt und dem Pumpenelement angeordneten Ring, und mit einem Kraftstoffanschluß im Pumpengehäuse.The invention relates to a radial piston pump for High-pressure fuel production for one Fuel injection system of internal combustion engines, with a drive shaft, wherein the drive shaft a eccentric section and one in a pump housing Stub shaft supported by a first sliding bearing having, preferably with respect to several Drive shaft radially arranged pump elements, with one between the eccentric section and the Pump element arranged ring, and with a Fuel connection in the pump housing.

Eine solche innen abgestützte Radialkolbenpumpe ist bspw. aus der DE 197 05 205 A1 bekannt. Naturgemäß wird die Lagerung der Antriebswelle im Pumpengehäuse und die Lagerung des Rings auf dem exzentrischen Abschnitt der Antriebswelle mit zunehmender Fördermenge und Förderhöhe der Pumpenelemente stärker beansprucht. Vor allem wenn die Radialkolbenpumpe zum Fördern von Kraftstoffen mit schlechten Schmiereigenschaften, wie bzw. Benzin, eingesetzt werden soll, stellt die Lagerung des Wellenstumpfs im Pumpengehäuse sowie die Lagerung des Rings auf dem exzentrischen Abschnitt der Antriebswelle einen limitierenden Faktor für die Fördermenge und die Förderhöhe dar.Such an internally supported radial piston pump is, for example. known from DE 197 05 205 A1. Naturally, the Storage of the drive shaft in the pump housing and the Mounting the ring on the eccentric section of the Drive shaft with increasing delivery and delivery height the pump elements more stressed. Especially if the Radial piston pump for conveying fuels with poor lubricating properties, such as or gasoline, is to be used, the storage of the Stub shaft in the pump housing and the bearing of the ring on the eccentric portion of the drive shaft a limiting factor for the flow rate and the head represents.

Aus der EP 1 101 931 A2 und der der nachveröffentlichten DE 41 26 640 A1 sind Radialkolbenpumpen bekannt bei denen ein Gleitlager zwangsweise von Kraftstoff durchströmt wird. Nachteilig an diesen Radialkolbenpumpen ist, dass entweder nur eine geringe Kraftstoffmenge durch das Geltlager strömt oder das Gleitlager von Kraftstoff hoher Temperatur durchströmt wird, was sich negativ auf die Tragfähigkeit des ersten Gelitlagers auswirkt.From EP 1 101 931 A2 and the post-published DE 41 26 640 A1 are known radial piston pumps where a Slide bearing is forcibly traversed by fuel. A disadvantage of these radial piston pumps is that either only a small amount of fuel flows through the gel bearing or the Slide bearing is traversed by high-temperature fuel, which negatively affects the carrying capacity of the first gel deposit effect.

Der Erfindung liegt die Aufgabe zugrunde, eine an sich bekannte Radialkolbenpumpe so weiterzuentwickeln, dass sie ohne tiefgreifende Änderungen für größere Fördermengen und größere Förderhöhen einsetzbar ist.The invention is based on the object, a known per se Radial piston pump so that they without profound changes for larger volumes and larger ones Delivery heights can be used.

Diese Aufgabe wird bei einer Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung für eine Kraftstoffeinspritzanlage von Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1, dadurch gelöst, dass das erste Gleitlager von dem gesamten durch den Kraftstoffanschluß strömenden Kraftstoff durchströmt wird.This task is in a radial piston pump for High-pressure fuel production for a fuel injection system of internal combustion engines according to the preamble of claim 1, solved by the fact that the first sliding bearing of the entire The fuel port flowing through the fuel port is flowed through.

Der in dem Kraftstoffanschluß der Radialkolbenpumpe zuströmende Kraftstoff weist einen Druck, der von einer Vorförderpumpe bereitgestellt wird, von etwa 4 - 6 bar auf. Dieser Druck ist unabhängig von der Drehzahl und den Betriebsbedingungen der Radialkolbenpumpe. Dadurch, dass der gesamte durch den Kraftstoffanschluß strömende Kraftstoff durch das erste Gleitlager geführt wird, ist das erste Gleitlager als hydrostatisches Gleitlager ausgeführt. Dadurch bildet sich ein Schmierfilm mit großer Zuverlässigkeit aus, so dass die Gefahr von "Fressern" deutlich reduziert wird. Außerdem erhöht sich die Tragfähigkeit des ersten Gleitlagers.The incoming in the fuel port of the radial piston pump Fuel has a pressure coming from a prefeed pump is provided, from about 4 - 6 bar on. This pressure is regardless of the speed and operating conditions of the Radial piston pump. By doing the whole through the Fuel connection pouring fuel through the first slide bearing is guided, is the first sliding bearing as Hydrostatic plain bearing executed. This forms a Lubricating film with great reliability, so the danger significantly reduced by "eaters". In addition, the increased Load capacity of the first plain bearing.

Vorteilhafter Weise ist bei der erfindungsgemäßen Kraftstoffhochdruckpumpe der durch den Kraftstoffanschluss strömende Kraftstoff relativ kühl. Weil die Fördermenge der Vorförderpumpe direkt von der Fördermenge der Kraftstoffhochdruckpumpe abhängt, wird die Tragfähigkeit des ersten Gleitlagers zwangsläufig an die Belastungen der Kraftstoffhochdruckpumpe angepasst. Schließlich ist der konstruktive Aufbau der erfindungsgemäßen Kraftstoffhochdruckpumpe sehr viel einfacher als bei den aus dem Stand der Technik bekannten Kraftstoffhochdruckpumpen und die erfindungsgemäß beanspruchte Maßnahme kann durch geringfügige Modifikationen des ersten Gleitlagers an einer bekannten Radialkolbenpumpe umgesetzt werden, so dass die bereits vorhandenen Fertigungseinrichtungen zum Herstellen der Radialkolbenpumpe nahezu unverändert übernommen werden können.Advantageously, in the inventive High-pressure fuel pump through the fuel connection flowing fuel relatively cool. Because the flow rate of Pre-feed pump directly from the flow rate of High-pressure fuel pump depends on the carrying capacity of the first slide bearing inevitably to the loads of High-pressure fuel pump adapted. Finally, that is constructive structure of the invention High-pressure fuel pump much easier than the out of the The prior art known high-pressure fuel pumps and the claimed according to the invention measure can by minor Modifications of the first plain bearing on a known Radial piston pump can be implemented so that the already existing production facilities for Manufacture of the radial piston pump almost unchanged can be taken over.

Bei einer Variante der Erfindung ist vorgesehen, dass der Ring auf dem exzentrischen Abschnitt durch ein zweites Gleitlager gelagert ist, und dass das zweite Gleitlager zwangsweise von dem durch den Kraftstoffanschluß strömenden Kraftstoff durchströmt wird, so dass auch die Tragfähigkeit des zweiten Gleitlagers auf einfache und wirkungsvolle Weise bei allen Betriebszuständen und Drehzahlen der Kraftstoffhochdruckpumpe erhöht wird.In a variant of the invention it is provided that the Ring on the eccentric section through a second Plain bearing is stored, and that the second plain bearing forcibly from the flowing through the fuel port Fuel is flowed through, so that the load capacity of the second plain bearing on simple and effective Way in all operating conditions and speeds of High-pressure fuel pump is increased.

Eine besonders wirtschaftlich herzustellende Ausgestaltung der Erfindung sieht vor, dass das erste Gleitlager mindestens eine im Wesentlichen in Richtung der Drehachse der Antriebswelle verlaufende Schmiernut aufweist, so dass der aus dem Kraftstoffanschluß in das erste Gleitlager strömende Kraftstoff sich'gleichmäßig über die gesamte Lagerfläche verteilt und somit die gleichmäßige Ausbildung eines Schmierfilms begünstigt wird.A particularly economical to manufacture embodiment The invention provides that the first sliding bearing at least one substantially in the direction of the axis of rotation having the drive shaft extending lubrication, so that the from the fuel port in the first sliding bearing flowing fuel 'uniformly over the entire Warehouse distributed and thus the uniform training a lubricant film is favored.

Eine weitere Ergänzung der Erfindung sieht vor, dass der Wellenstumpf eine Mittenbohrung aufweist, dass von der Mittenbohrung eine Querbohrung abzweigt, und dass das zweite Gleitlager von der Querbohrung mit Kraftstoff versorgt wird. Auf diese Weise kann der Kraftstoff zur Schmierung des zweiten Gleitlagers in die Mitte der Lagerfläche des zweiten Gleitlagers eingebracht werden und von dort aus zu den Rändern des Gleitlagers strömen. Dies begünstigt die Ausbildung eines tragfähigen Schmierfilms zwischen Ring und exzentrischem Abschnitt der Antriebswelle.A further supplement of the invention provides that the Stub shaft has a center hole, that of the Mittenbohrung a transverse bore branches off, and that the second plain bearing from the transverse bore with fuel is supplied. In this way the fuel can be used for Lubrication of the second sliding bearing in the middle of Bearing surface of the second sliding bearing are introduced and from there flow to the edges of the plain bearing. This favors the formation of a viable lubricating film between ring and eccentric section of the Drive shaft.

Zur weiteren Verbesserung des Schmierfilms ist vorgesehen, dass das zweite Gleitlager mindestens eine im Wesentlichen in Richtung der Drehachse der Antriebswelle verlaufende Schmiernut aufweist.To further improve the lubricating film is provided that the second sliding bearing at least one substantially extending in the direction of the axis of rotation of the drive shaft Has lubrication.

Es hat sich als besonders vorteilhaft erwiesen, wenn zwischen der mindestens einen Schmiernut und einem Innenraum des Pumpengehäuses auf der dem Wellenstumpf abgewandten Seite des zweiten Gleitlagers eine hydraulische Verbindung besteht, da dadurch sichergestellt wird, dass das zweite Gleitlager in seiner gesamten Breite von Kraftstoff durchströmt wird und somit eine besonders gute Ausbildung des Schmierfilms erreicht wird.It has proved to be particularly advantageous if between the at least one lubrication groove and a Interior of the pump housing on the stub shaft opposite side of the second sliding bearing a hydraulic Connection, because it ensures that the second sliding bearing in its entire width of Fuel is flowed through and thus a particularly good Training of the lubricating film is achieved.

In einer Ergänzung der Erfindung ist vorgesehen, dass der exzentrische Abschnitt oder der Ring eine Ringnut aufweist, und dass die Querbohrung in die Ringnut mündet, so dass der Kraftstoff gleichmäßig über den gesamten Umfang des zweiten Gleitlagers verteilt wird.In a supplement of the invention it is provided that the eccentric portion or the ring has an annular groove, and that the transverse bore opens into the annular groove, so that the Fuel evenly over the entire circumference of the second Sliding bearing is distributed.

Zur weiteren Erhöhung des hydrostatischen Drucks im zweiten Gleitlager kann in die Mittenbohrung ein Laufrad einer Mikropumpe eingesetzt werden, so dass zusätzlich in Abhängigkeit von der Drehzahl der Radialkolbenpumpe eine Druckerhöhung stattfindet und somit die Tragfähigkeit des zweiten Gleitlagers bei hohen Drehzahlen weiter erhöht wird.To further increase the hydrostatic pressure in the second Slide bearing can be in the center bore an impeller one Micropump be used, so that in addition Dependence on the speed of the radial piston pump a Pressure increase takes place and thus the carrying capacity of the second slide bearing at high speeds further increased becomes.

Alternative Ausgestaltungen der Erfindung sehen vor, dass der Kraftstoffanschluß in den Innenraum des Gehäuses oder direkt in das erste Gleitlager mündet. Dadurch kann die erfindungsgemäße Ausbildung von erstem und zweitem Gleitlager bei verschiedenen Bauarten von Radialkolbenpumpen gleichermaßen vorteilhaft zum Einsatz gelangen. Alternative embodiments of the invention provide that the fuel connection in the interior of the housing or opens directly into the first plain bearing. This allows the inventive design of the first and second Plain bearings in different types of Radial piston pumps equally advantageous for use reach.

Weiter vorteilhafte Ausgestaltungen der Erfindungen sehen vor, dass die Schmiernut an dem Wellenstumpf der Antriebswelle angeordnet ist, dass die Schmiernut an der Buchse des ersten Gleitlagers angeordnet ist, dass die Schmiernut an dem exzentrischen Abschnitt der Antriebswelle angeordnet ist und/oder dass die Schmiernut an einer Buchse des zweiten Gleitlagers angeordnet ist, so dass sich die Tragfähigkeit und Lebensdauer des ersten und zweiten Gleitlagers weiter erhöhen.See further advantageous embodiments of the invention before that the lubrication groove on the stub shaft of Drive shaft is arranged, that the lubrication groove at the Socket of the first sliding bearing is arranged that the Lubricating groove on the eccentric portion of the drive shaft is arranged and / or that the lubrication groove on a socket of the second sliding bearing is arranged, so that the Load capacity and service life of the first and second Increase sliding bearing further.

Besonders vorteilhaft ist es, wenn die Schmiernut am Wellenstumpf und/oder die Schmiernut am exzentrischen Abschnitt um etwa 180° versetzt zu dem resultierenden Kraftvektor angeordnet sind.It is particularly advantageous if the lubrication groove on Stub shaft and / or the lubrication groove on the eccentric Section offset by about 180 ° to the resulting Force vector are arranged.

Die Bildung eines stabilen Schmierfilms kann weiter gefördert werden, wenn die Schmiernut am Wellenstumpf und/oder die Schmiernut am exzentrischen Abschnitt gewendelt ausgeführt sind.The formation of a stable lubricating film can continue be promoted when the oil groove on the stub shaft and / or the lubrication groove on the eccentric section are performed coiled.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Zeichnung, deren Beschreibung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of Invention are the following drawings, whose Description and claims removed.

Zeichnungdrawing

Es zeigen:

Figur 1
eine Darstellung eines ersten Ausführungsbeispiels einer erfindungsgemäßen Radialkolbenpumpe im Schnitt, und
Figur 2
ein zweites Ausführungsbeispiel einer erfindungsgemäßen Radialkolbenpumpe im Querschnitt.
Show it:
FIG. 1
an illustration of a first embodiment of a radial piston pump according to the invention in section, and
FIG. 2
A second embodiment of a radial piston pump according to the invention in cross section.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Fig. 1 ist ein erstes Ausführungsbeispiel einer erfindungsgemäßen Radialkolbenpumpe im Querschnitt dargestellt. Die Radialkolbenpumpe besteht aus einem Pumpengehäuse 1. In dem Pumpengehäuse 1 ist eine Antriebswelle 3 drehbar gelagert. Die Antriebswelle 3 ist mit einem Wellenstumpf 5 in einem ersten Gleitlager 7 im Pumpengehäuse 1 gelagert. Mit ihrem dem Wellenstumpf 5 gegenüberliegenden Ende ist die Antriebswelle 3 in einem Deckel 9 mittels eines Kugellagers 11 gelagert. Unmittelbar neben dem Wellenstumpf 5 weist die Antriebswelle 3 einen exzentrischen Abschnitt 13 auf.In Fig. 1 is a first embodiment of a Radial piston pump according to the invention in cross section shown. The radial piston pump consists of a Pump housing 1. In the pump housing 1 is a Drive shaft 3 rotatably mounted. The drive shaft 3 is with a stub shaft 5 in a first sliding bearing 7 in Pump housing 1 stored. With her the stub shaft 5 opposite end is the drive shaft 3 in one Lid 9 supported by a ball bearing 11. immediate In addition to the stub shaft 5, the drive shaft 3 a eccentric section 13 on.

Der exzentrische Abschnitt 13 ist von einem Ring 15, der in einer Ansicht von vorne (nicht dargestellt) eine polygonförmige Außenkontur 19 hat, umgeben. Der Ring 15 dreht sich nicht, wenn die Antriebswelle 3 gedreht wird, sondern führt eine kreisende Bewegung aus. Zwischen dem Ring 15 und dem exzentrischen Abschnitt 13 ist ein zweites Gleitlager 17 vorhanden, das mit dem Ring 15 verpresst ist. Mit seiner polygonförmigen Außenkontur 19 überträgt der Ring 15 die ihm von dem exzentrischen Abschnitt 13 aufgeprägte kreisende Bewegung auf eine Kolbenfußplatte 21 eines Pumpenelements 23.The eccentric portion 13 is of a ring 15, which in a front view (not shown) one polygonal outer contour 19 has surrounded. The ring 15 does not rotate when the drive shaft 3 is rotated, but performs a circular motion. Between the Ring 15 and the eccentric portion 13 is a second one Plain bearing 17 is present, which is pressed with the ring 15. With its polygonal outer contour 19 transmits the Ring 15 giving it from the eccentric section 13 imprinted circular movement on a piston foot plate 21 a pump element 23.

Das Pumpenelement 23 weist eine Zylinderbohrung 25 und einen Kolben 27 auf. Über die Kolbenfußplatte 21 wird der Kolben 27 in eine oszillierende Bewegung versetzt. Dadurch wird Kraftstoff aus einem Kraftstoffanschluß (nicht dargestellt) in einen Arbeitsraum 29 angesaugt, wenn der Kraftstoff durch das erste Gleitlager 7 geströmt ist, und anschließend während des sog. Förderhubs mit Druck beaufschlagt. Über einen Hochdruckablauf (nicht dargestellt) wird der unter hohem Druck stehende Kraftstoff aus dem Arbeitsraum 29 ausgeschoben.The pump element 23 has a cylinder bore 25 and a piston 27 on. About the Kolbenfußplatte 21 is the Plunged piston 27 in an oscillating motion. Thereby Fuel is from a fuel connection (not shown) sucked into a working space 29 when the fuel has flowed through the first sliding bearing 7, and subsequently during the so-called delivery stroke with pressure applied. About a high pressure drain (not shown) becomes the high pressure fuel pushed out of the work space 29.

Versorgt wird die Kraftstoffhochdruckpumpe über einen Kraftstoffanschluß 31, welcher in das erste Gleitlager 7 mündet. Der Kraftstoff im Kraftstoffanschluß 31 wird von einer nicht dargestellten Vorförderpumpe mit einem Förderdruck von etwa 4 - 6 bar in das erste Gleitlager 7 gepresst. Dadurch ergibt sich eine sehr stabile Ausbildung eines Schmierfilms zwischen Pumpengehäuse 1 und Wellenstumpf 5, was die Tragfähigkeit und Lebensdauer des ersten Gleitlagers 7 deutlich erhöht.The high-pressure fuel pump is supplied via a Fuel connection 31, which in the first sliding bearing. 7 empties. The fuel in the fuel port 31 is from a pre-feed pump, not shown with a Delivery pressure of about 4 - 6 bar in the first sliding bearing. 7 pressed. This results in a very stable training a lubricating film between the pump housing 1 and Stub shaft 5, which is the carrying capacity and life of the first slide bearing 7 significantly increased.

Um den Durchsatz von Kraftstoff durch das erste Gleitlager 7 zu erhöhen und die Ausbildung eines Schmierfilms zu begünstigen, sind mehrere Schmiernuten 33 über den Umfang des ersten Gleitlagers 7 verteilt angeordnet. Die Schmiernuten 33 können auch gewendelt ausgeführt sein.To the flow rate of fuel through the first sliding bearing 7 to increase and the formation of a lubricating film too favor, several lubrication grooves 33 are over the circumference of the first sliding bearing 7 distributed. The Lubrication grooves 33 can also be designed coiled.

Wenn der Kraftstoff durch das erste Gleitlager 7 geströmt ist, gelangt er in einen Innenraum 35 des Pumpengehäuses. Von dort aus wird der Kraftstoff über eine in Fig. 1 nicht sichtbare Verlängerung des Kraftstoffanschlusses 31 während des Saughubs des Pumpenelements 23 in den Arbeitsraum 29 angesaugt. Das erste Gleitlager 7 besteht aus einer in das Gehäuse 1 eingepressten Buchse 37 mit eingepresstem Innenring 36 und dem Wellenstumpf 5. Die Schmiernuten 33 können entweder in den Innenring 36 oder in den Wellenstumpf 5 eingearbeitet sein. Wenn die Schmiernuten 33 in den Wellenstumpf 5 eingearbeitet sind, kann die Drehbewegung des Wellenstumpfs zur Förderung von Kraftstoff in das erste Gleitlager 7 ausgenutzt werden. Dadurch erhöht sich die Belastbarkeit des ersten Gleitlagers 7 weiter.When the fuel has flowed through the first sliding bearing 7 is, it enters an interior 35 of the pump housing. From there, the fuel does not over one in Fig. 1 visible extension of the fuel port 31 during the suction stroke of the pump element 23 in the working space 29th sucked. The first sliding bearing 7 consists of a in the Housing 1 pressed bushing 37 with pressed Inner ring 36 and the stub shaft 5. The lubrication grooves 33 can either in the inner ring 36 or in the Shaft stump 5 incorporated. When the lubrication grooves 33 are incorporated in the stub shaft 5, the Rotary movement of the stub shaft to promote fuel be exploited in the first sliding bearing 7. This increases the load capacity of the first sliding bearing 7 continues.

In Fig. 2 ist ein zweites Ausführungsbeispiel einer erfindungsgemäßen Radialkolbenpumpe im Querschnitt dargestellt. Gleiche Bauteile werden mit gleichem Bezugszeichen versehen und es gilt das betreffend der Fig. 1 Gesagte entsprechend.In Fig. 2 is a second embodiment of a Radial piston pump according to the invention in cross section shown. Same components are with the same Reference numerals provided and it applies that concerning the FIG. 1 stated accordingly.

Bei diesem Ausführungsbeispiel ist das Kugellager 11 in das Pumpengehäuse 1 eingesetzt. Der Kraftstoffanschluß 31 mündet in den Innenraum 35. Von dort strömt der Kraftstoff über Schmiernuten 33 durch das erste Gleitlager 7 zum Ende des Wellenstumpfs 5. Aus der Querschnittsdarstellung von Fig. 2 ist zu erkennen, dass in dem Gehäuse 1 eine Buchse 37 eingepresst ist, in welche die Schmiernuten 33 eingearbeitet sind. Die Buchse 37 bildet zusammen mit dem Wellenstumpf 5 das erste Gleitlager 7.In this embodiment, the ball bearing 11 is in the Pump housing 1 used. The fuel connection 31 opens into the interior 35. From there flows the fuel via lubrication grooves 33 through the first sliding bearing 7 to the end of the stub shaft 5. From the cross-sectional view of Fig. 2 it can be seen that in the housing 1 a socket 37 is pressed, in which the lubrication grooves 33 are incorporated. The sleeve 37 forms together with the Stub shaft 5, the first sliding bearing. 7

Der Wellenstumpf 5 weist eine Mittenbohrung 39 auf, die von einer Querbohrung 41 durchdrungen wird. Die Querbohrung 41 wiederum mündet in eine Ringnut 43, welche in den exzentrischen Abschnitt 13 der Antriebswelle 3 eingearbeitet ist. Alternativ kann die Ringnut 43 auch in den Ring 15 eingearbeitet werden. Diese Alternative ist in Fig. 2 nicht dargestellt. Über die Mittenbohrung 39 und die Querbohrung 41 sowie die Ringnut 43 gelangt der Kraftstoff vom Ende des Wellenstumpfs 5 zum zweiten Gleitlager 17, welches von dem exzentrischen Abschnitt 13 und dem Ring 15 gebildet wird. Im exzentrischen Ring 15 sind Schmiernuten 45 eingearbeitet, welche sich parallel zur Drehachse 47 der Antriebswelle 3 über nahezu die gesamte Breite des Rings 15 erstrecken. Die Schmiernuten 45 stellen eine hydraulische Verbindung zwischen Ringnut 43 und dem Innenraum 35 auf der dem Wellenstumpf 5 abgewandten Seite des Rings 15 her. Auf der dem Wellenstumpf 5 zugewandten Seite des Rings 15 enden die Schmiernuten 45 im Ring 15, so dass auf dieser Seite des Rings 15 nur sehr wenig Kraftstoff durch den Spalt (nicht sichtbar in Fig. 2) zwischen Ring 15 und exzentrischem Abschnitt 13 in den Innenraum 35 auftreten kann. Durch diese Maßnahme wird gewährleistet, dass stets "frischer" Kraftstoff aus dem Innenraum 35 durch das erste Gleitlager 7 strömt und es nicht zu einer Kurzschlussströmung zwischen zweitem Gleitlager 17 und erstem Gleitlager 7 kommen kann.The stub shaft 5 has a central bore 39, which of a transverse bore 41 is penetrated. The transverse bore 41 in turn opens into an annular groove 43, which in the eccentric portion 13 of the drive shaft. 3 is incorporated. Alternatively, the annular groove 43 in the ring 15 are incorporated. This alternative is in Fig. 2 not shown. About the center hole 39 and the Transverse bore 41 and the annular groove 43 passes the fuel from the end of the stub shaft 5 to the second sliding bearing 17, which of the eccentric portion 13 and the ring 15th is formed. In the eccentric ring 15 are lubrication grooves 45 incorporated, which is parallel to the axis of rotation 47 of Drive shaft 3 over almost the entire width of the ring 15th extend. The lubrication grooves 45 provide a hydraulic Connection between annular groove 43 and the interior 35 on the the stub shaft 5 side facing away from the ring 15 ago. On the stub shaft 5 facing side of the ring 15 ends the lubrication grooves 45 in the ring 15, so that on this page of the ring 15 only very little fuel through the gap (not visible in Fig. 2) between ring 15 and eccentric portion 13 in the interior 35 occur can. This measure ensures that always "fresh" fuel from the interior 35 through the first Plain bearing 7 flows and not to a Short circuit flow between the second sliding bearing 17 and first sliding bearing 7 can come.

In die Mittenbohrung 39 ist am Ende des Wellenstumpfs ein Laufrad 49 einer Mikropumpe eingepresst. Dieses Laufrad dreht sich mit der Antriebswelle 3 und erzeugt einen Kraftstofffluß, wobei Kraftstoff durch das erste Gleitlager 7 angesaugt wird und anschließend aufgrund der Druckerhöhung der Mikropumpe durch das zweite Gleitlager 17 strömt. Der Kraftstoff gelangt über die Ringnut 43 in das zweite Gleitlager 17, wobei die Druckerhöhung durch die Mikropumpe in Abhängigkeit von der Drehzahl der Antriebswelle 3 zunimmt. In Folge dessen nimmt mit zunehmender Drehzahl der Antriebswelle 3 auch die Tragfähigkeit des zweiten Gleitlagers zu. Durch die Zentrifugalkraft, welche auf den in der Querbohrung 41 befindlichen Kraftstoff (nicht dargestellt) wirkt, wird der hydrostatische Druck im zweiten Gleitlager 17 weiter erhöht. Auch dies führt zu einer Zunahme der Tragfähigkeit des zweiten Gleitlagers 17 mit höheren Drehzahlen.In the center hole 39 is at the end of the stub shaft Impeller 49 of a micropump pressed. This wheel turns with the drive shaft 3 and generates a Fuel flow, taking fuel through the first sliding bearing 7 is sucked in and then due to the Pressure increase of the micropump through the second sliding bearing 17th flows. The fuel passes through the annular groove 43 in the second sliding bearing 17, wherein the pressure increase by the Micropump depending on the speed of the Drive shaft 3 increases. As a result, participates increasing speed of the drive shaft 3 and the Load capacity of the second sliding bearing to. By the Centrifugal force, which on the in the transverse bore 41st located fuel (not shown) acts, is the hydrostatic pressure in the second sliding bearing 17 on elevated. This too leads to an increase in the carrying capacity of the second sliding bearing 17 at higher speeds.

In Fig. 3 ist ein drittes Ausführungsbeispiel einer erfindungsgemäßen Radialkolbenpumpe im Querschnitt dargestellt. Gleiche Bauteile werden mit gleichem Bezugszeichen versehen und es gilt das betreffend der Fig. 1 und 2 Gesagte entsprechend. Bei dem dritten Ausführungsbeispiel ist in dem Wellenstumpf 5 eine gewendelte Schmiernut 33 vorhanden. Bei diesem Ausführungsbeispiel wird durch die Drehung der Antriebswelle 3 Kraftstoff in das erste Gleitlager 7 gefördert, was dessen Belastbarkeit und Lebensdauer erhöht. In gleicher Weise ist auch in dem exzentrischen Abschnitt 13 der Antriebswelle 3 eine gewendelte Schmiernut 45 vorhanden. Die Schmiernut 45 verbessert die Versorgung des zweiten Gleitlagers 17 mit Kraftstoff und erhöht dadurch dessen Belastbarkeit und Lebensdauer.In Fig. 3 is a third embodiment of a Radial piston pump according to the invention in cross section shown. Same components are with the same Reference numerals provided and it applies that concerning the FIG. 1 and 2 said accordingly. At the third Embodiment is in the stub shaft 5 a coiled lubricating groove 33 available. In this Embodiment is characterized by the rotation of the Drive shaft 3 fuel in the first sliding bearing. 7 promoted, which increases its capacity and durability. In the same way is also in the eccentric section 13 of the drive shaft 3 a coiled lubrication 45th available. The lubrication groove 45 improves the supply of second sliding bearing 17 with fuel and thereby increases its load capacity and service life.

In Fig. 4 ist das in Fig. 3 dargestellte dritte Ausführungsbeispiel in einer Seitenansicht schematisch dargestellt. Anhand dieser Darstellung soll die optimale Anordnung der gewendelten oder geraden Schmiernuten 37 und 45 erläutert werden. In dieser Darstellung sind drei um 120° zueinander versetzt angeordnete Pumpenelemente 23-I, 23-II und 23-III schematisch durch ihre Längsachsen dargestellt, die über den exzentrischen Abschnitt 13 der Antriebswelle betätigt werden. Die Drehrichtung der Antriebswelle ist durch einen ersten Pfeil 53 dargestellt. Die Richtung des resultierenden Kraftvektors 55, der auf den Wellenstumpf 5 der Antriebswelle wirkt und mit diesem rotiert, liegt innerhalb des mit 57 bezeichneten ersten Winkelbereichs, der vorzugsweise etwa 60° beträgt und dessen Mittelachse ca. 90° zum Maximalpunkt des Exzenterabschnitts 13 versetzt ist (Achse 23-I). Es empfiehlt sich deshalb, die Schmiernut 33 um 180° versetzt zu dem ersten Winkelbereich 57 anzuordnen. Der bevorzugte Platz zur Anordnung der Schmiernut 33 ist in Fig. 4 als zweiter Winkelbereich 59 gekennzeichnet. Auf diese Weise wird die Tragfähigkeit des ersten Gleitlagers 7 im Bereich ihrer höchsten Beanspruchung durch die Schmiernut 33 nicht beeinträchtigt. Für die Anordnung der Schmiernut 45 (nicht dargestellt) im Bereich des zweiten Gleitlagers 17 hat sich der erste Winkelbereich 57, der 180° zum zweiten Winkelbereich 59 versetzt angeordnet ist, als vorteilhaft erwiesen. Zur Steuerung der in die Gleitlager strömenden Kraftstoffmenge kann eine Drossel (nicht dargestellt) je Gleitlager vorgesehen werden.In Fig. 4, the third shown in Fig. 3 Embodiment in a side view schematically shown. Based on this presentation, the optimal Arrangement of the coiled or straight lubrication grooves 37 and 45 will be explained. In this illustration are three um 120 ° offset from one another arranged pump elements 23-I, 23-II and 23-III schematically by their longitudinal axes represented by the eccentric section 13 of the Drive shaft to be actuated. The direction of rotation of Drive shaft is represented by a first arrow 53. The direction of the resulting force vector 55, the on the stub shaft 5 of the drive shaft acts and with this rotates, lies within the designated 57 first Angular range, which is preferably about 60 ° and whose central axis is about 90 ° to the maximum point of Eccentric 13 is offset (axis 23-I). It It is therefore advisable to offset the lubrication groove 33 by 180 ° to arrange to the first angular range 57. The preferred one Space for the arrangement of the lubrication groove 33 is shown in Fig. 4 as second angle range 59 marked. In this way is the carrying capacity of the first sliding bearing 7 in the area their highest stress by the lubrication groove 33 not impaired. For the arrangement of the lubrication groove 45 (not shown) in the region of the second sliding bearing 17 has the first angular range 57, the 180 ° to the second Angle range 59 is arranged offset, as advantageous proved. To control in the Slide bearing flowing fuel quantity can be a throttle (not shown) are provided per plain bearing.

Claims (18)

  1. Radial piston pump for producing a high fuel pressure for a fuel injection assembly of internal combustion engines, having a pump housing (1), having a drive shaft (3), the drive shaft (3) having an eccentric section (13) and a shaft butt (5) which is mounted in the pump housing (1) by a first sliding bearing (7), preferably having a plurality of pump elements (23) which are arranged radially with regard to the drive shaft (1), and having a fuel connection (31) in the pump housing (1), fuel flowing forcibly through the first sliding bearing (7), characterized in that all the fuel which flows through the fuel connection (31) flows through the first sliding bearing.
  2. Radial piston pump according to Claim 1, characterized in that a ring (15) is arranged between the eccentric section (13) and the pump elements (23), in that the ring (15) is mounted on the eccentric section (13) by a second sliding bearing (17), and in that fuel flows forcibly through the second sliding bearing (17) downstream.
  3. Radial piston pump according to Claim 1 or 2, characterized in that the fuel which flows through the fuel connection (31) flows downstream through the second sliding bearing (17).
  4. Radial piston pump according to one of the preceding claims, characterized in that the first sliding bearing (7) has at least one lubricating groove (33) which extends substantially in the direction of the rotational axis (47) of the drive shaft (3).
  5. Radial piston pump according to one of Claims 2 to 4, characterized in that the shaft butt (5) has a central hole (39), in that a transverse hole (41) branches off from the central hole (39), and in that the second sliding bearing (17) is supplied with fuel by the transverse hole (41).
  6. Radial piston pump according to one of Claims 2 to 5, characterized in that the second sliding bearing (17) has at least one lubricating groove (45) which extends substantially in the direction of the rotational axis (47) of the drive shaft (3).
  7. Radial piston pump according to Claim 6, characterized in that, on that side of the second sliding bearing (17) which faces away from the shaft butt (5), there is a hydraulic connection between the at least one lubricating groove (45) and an inner space (35) of the pump housing (1).
  8. Radial piston pump according to one of Claims 1 to 6, characterized in that the fuel connection (31) opens into the inner space (35) of the pump housing (1).
  9. Radial piston pump according to one of Claims 2 to 8, characterized in that the eccentric section (13) or the ring (15) has an annular groove (43), and in that the transverse hole (41) opens into the annular groove (43).
  10. Radial piston pump according to one of Claims 5 to 9, characterized in that a rotor (49) of a micropump is inserted into the central hole (39).
  11. Radial piston pump according to one of the preceding claims, characterized in that the fuel connection (31) opens into the first sliding bearing (7).
  12. Radial piston pump according to one of Claims 4 to 11, characterized in that the lubricating groove (33) is arranged on the shaft butt (5) of the drive shaft (3).
  13. Radial piston pump according to one of Claims 4 to 11, characterized in that the lubricating groove (33) is arranged on the bush (37) of the first sliding bearing (7).
  14. Radial piston pump according to one of Claims 6 to 13, characterized in that the lubricating groove (45) is arranged on the eccentric section (13) of the drive shaft (3).
  15. Radial piston pump according to one of Claims 6 to 14, characterized in that the lubricating groove (45) is arranged on the eccentric section (13) and extends over a first angle range (57) of approximately 60°.
  16. Radial piston pump according to Claim 15, characterized in that the centre axis (23-I) of the first angle range extends offset by approximately 90° from the point of maximum eccentricity of the eccentric section (13).
  17. Radial piston pump according to either of Claims 15 and 16, characterized in that the lubricating groove (33) on the shaft butt (5) is arranged in a second angle range (59), and in that the second angle range (59) is arranged offset by about 180° from the first angle range (57).
  18. Radial piston pump according to one of Claims 12 to 17, characterized in that the lubricating groove (33) on the shaft butt (5) and/or the lubricating groove (45) on the eccentric section (13) are/is of helical configuration.
EP02764536A 2001-12-01 2002-08-06 Radial piston pump having force-feed lubrication Expired - Lifetime EP1454055B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10159099 2001-12-01
DE10159099 2001-12-01
DE10208574 2002-02-21
DE10208574A DE10208574A1 (en) 2001-12-01 2002-02-21 Radial piston pump
PCT/DE2002/002879 WO2003048564A1 (en) 2001-12-01 2002-08-06 Radial piston pump having force-feed lubrication

Publications (2)

Publication Number Publication Date
EP1454055A1 EP1454055A1 (en) 2004-09-08
EP1454055B1 true EP1454055B1 (en) 2005-11-02

Family

ID=26010700

Family Applications (1)

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EP02764536A Expired - Lifetime EP1454055B1 (en) 2001-12-01 2002-08-06 Radial piston pump having force-feed lubrication

Country Status (4)

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EP (1) EP1454055B1 (en)
AT (1) ATE308676T1 (en)
DE (1) DE50204804D1 (en)
WO (1) WO2003048564A1 (en)

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Publication number Priority date Publication date Assignee Title
CN101529082B (en) * 2006-10-16 2012-01-11 罗伯特·博世有限公司 Piston pump, in particular fuel pump, having roller tappet

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Publication number Priority date Publication date Assignee Title
US7273036B2 (en) 2002-10-31 2007-09-25 Robert Bosch Gmbh High-pressure fuel pump with a ball valve in the low-pressure inlet
DE102007012704A1 (en) * 2007-03-16 2008-09-18 Robert Bosch Gmbh High pressure pump for delivering fuel with an improved design of the bearing assembly for supporting the camshaft
ITMI20072259A1 (en) * 2007-11-30 2009-06-01 Bosch Gmbh Robert HIGH PRESSURE PUMP
IT1398728B1 (en) * 2009-04-17 2013-03-18 Bosch Gmbh Robert LUBRICATION CIRCUIT FOR A HIGH PRESSURE COMMON RAIL PUMP AND HIGH PRESSURE COMMON RAIL PUMP
EP2660456B1 (en) * 2012-05-01 2017-12-06 Delphi International Operations Luxembourg S.à r.l. Fuel pump
GB201412187D0 (en) * 2014-07-09 2014-08-20 Delphi International Operations Luxembourg S.�.R.L. Pump assembly

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Publication number Priority date Publication date Assignee Title
DE4126640B4 (en) * 1991-08-12 2005-06-16 Robert Bosch Gmbh Pump arrangement with a prefeed pump and a radial piston pump
DE19705205A1 (en) * 1997-02-12 1998-08-13 Bosch Gmbh Robert Piston pump, esp. high pressure fuel injection pump for IC engine
DE50013384D1 (en) * 1999-11-19 2006-10-12 Crt Common Rail Tech Ag High-pressure injection system with common rail
DE10012306C2 (en) * 2000-03-14 2003-12-24 Bosch Gmbh Robert Distributor injection pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101529082B (en) * 2006-10-16 2012-01-11 罗伯特·博世有限公司 Piston pump, in particular fuel pump, having roller tappet

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ATE308676T1 (en) 2005-11-15
WO2003048564A1 (en) 2003-06-12
EP1454055A1 (en) 2004-09-08
DE50204804D1 (en) 2005-12-08

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