EP1454055A1 - Radial piston pump having force-feed lubrication - Google Patents

Radial piston pump having force-feed lubrication

Info

Publication number
EP1454055A1
EP1454055A1 EP02764536A EP02764536A EP1454055A1 EP 1454055 A1 EP1454055 A1 EP 1454055A1 EP 02764536 A EP02764536 A EP 02764536A EP 02764536 A EP02764536 A EP 02764536A EP 1454055 A1 EP1454055 A1 EP 1454055A1
Authority
EP
European Patent Office
Prior art keywords
radial piston
piston pump
pump according
fuel
slide bearing
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
EP02764536A
Other languages
German (de)
French (fr)
Other versions
EP1454055B1 (en
Inventor
Heinz Siegel
Helmut Rembold
Hans-Peter Stiefel
Karl Gmelin
Thomas Fuerst
Thilo Bolz
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
Priority date (The priority date 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 date listed.)
Filing date
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
Application granted granted Critical
Publication of EP1454055B1 publication Critical patent/EP1454055B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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 generating high fuel pressure for a
  • Fuel injection system of internal combustion engines with a drive shaft, the drive shaft having an eccentric section and a stub shaft supported in a pump housing by a first slide bearing, preferably several with respect to the
  • Such an internally supported radial piston pump is known, for example, from DE 197 05 205 AI.
  • the mounting of the drive shaft in the pump housing and the mounting of the ring on the eccentric section of the drive shaft are subject to greater stress as the delivery volume and delivery head of the pump elements increase.
  • the radial piston pump is to be used to deliver fuels with poor lubrication properties, such as gasoline, the mounting of the stub shaft in the pump housing and the mounting of the ring on the eccentric section of the drive shaft are a limiting factor for the delivery rate and the delivery head - 1
  • the object of the invention is to further develop a known radial piston pump in such a way that it can be used for larger delivery quantities and greater delivery heights without profound changes.
  • a radial piston pump for high-pressure fuel generation for a fuel injection system of internal combustion engines with a drive shaft, the drive shaft having an eccentric section and a stub shaft supported in a pump housing by a first slide bearing, preferably with a plurality of pump elements arranged radially with respect to the drive shaft, with one between the eccentric section and the pump elements arranged ring, and with a fuel connection in the pump housing, solved in that the first sliding bearing is forcibly flowed through by the fuel flowing through the fuel connection.
  • the fuel flowing into the fuel connection of the radial piston pump has a pressure, which is provided by a prefeed pump, of about 4-6 bar. This pressure is independent of the speed and the
  • the first slide bearing is designed as a hydrostatic slide bearing. This creates a lubricating film with great reliability, so that the risk of "eaters" is significantly reduced.
  • the load capacity of the first plain bearing also increases. This measure can be implemented by slight modifications of the first slide bearing on a known radial piston pump, so that the existing production facilities for manufacturing the radial piston pump can be taken over almost unchanged.
  • the ring is supported on the eccentric section by a second slide bearing, and that the fuel flowing through the fuel connection forcibly flows through the second slide bearing, so that the load-bearing capacity of the second slide bearing is simple and effective Way is increased in all operating states and speeds of the high-pressure fuel pump.
  • a particularly economical embodiment of the invention provides that the first slide bearing has at least one lubrication groove running essentially in the direction of the axis of rotation of the drive shaft, so that the fuel flowing out of the fuel connection into the first slide bearing is ' evenly distributed over the entire bearing surface and thus the uniform formation of a lubricating film is favored.
  • the stub shaft has a central bore, that a transverse bore branches off from the central bore, and that the second slide bearing is supplied with fuel by the transverse bore.
  • the fuel for lubrication of the second slide bearing can be introduced into the center of the bearing surface of the second slide bearing and flow from there to the edges of the slide bearing. This favors the formation of a stable lubricating film between the ring and the eccentric section of the drive shaft.
  • the second slide bearing has at least one lubrication groove running essentially in the direction of the axis of rotation of the drive shaft.
  • the eccentric section or the ring has an annular groove, and that the transverse bore opens into the annular groove, so that the fuel is distributed uniformly over the entire circumference of the second slide bearing.
  • an impeller of a micropump can be inserted into the center bore, so that an additional pressure increase takes place depending on the speed of the radial piston pump, thus further increasing the load-bearing capacity of the second slide bearing at high speeds.
  • Alternative embodiments of the invention provide that the fuel connection opens into the interior of the housing or directly into the first slide bearing.
  • the design of the first and second plain bearings according to the invention can be used equally advantageously in different types of radial piston pumps.
  • Further advantageous refinements of the inventions provide that the lubrication groove is arranged on the stub shaft of the drive shaft, that the lubrication groove is arranged on the bushing of the first slide bearing, that the lubrication groove is arranged on the eccentric section of the drive shaft and / or that the lubrication groove on one Bushing of the second plain bearing is arranged so that the load capacity and life of the first and second plain bearings increase further.
  • lubrication groove on the stub shaft and / or the lubrication groove on the eccentric section are arranged offset by approximately 180 ° to the resulting force vector.
  • the formation of a stable lubricating film can be further promoted if the lubricating groove on the shaft end and / or the lubricating groove on the eccentric section are designed to be spiral.
  • Figure 1 is a representation of a first embodiment of an inventive
  • Figure 2 shows a second embodiment of a radial piston pump according to the invention in cross section. Description of the embodiments
  • a first embodiment of a radial piston pump according to the invention is shown in cross section.
  • the radial piston pump consists of a pump housing 1.
  • a drive shaft 3 is rotatably mounted in the pump housing 1.
  • the drive shaft 3 is supported with a stub shaft 5 in a first slide bearing 7 in the pump housing 1. With its end opposite the shaft end 5, the drive shaft 3 is supported in a cover 9 by means of a ball bearing 11.
  • the drive shaft 3 has an eccentric section 13.
  • the eccentric section 13 is surrounded by a ring 15 which, in a view from the front (not shown), has a polygonal outer contour 19.
  • the ring 15 does not rotate when the drive shaft 3 is rotated, but performs a circular movement.
  • a second slide bearing 17 is present, which is pressed with the ring 15. With its polygonal outer contour 19, the ring 15 transmits the circular movement impressed on it by the eccentric section 13 to a piston foot plate 21 of a pump element 23.
  • the pump element 23 has a cylinder bore 25 and a piston 27.
  • the piston 27 is set into an oscillating movement via the piston foot plate 21.
  • fuel is drawn from a fuel connection (not shown) into a working space 29 and then pressurized during the so-called delivery stroke.
  • the fuel which is under high pressure, is fed through a high-pressure outlet (not shown) pushed out of the work space 29.
  • the high-pressure fuel pump is supplied via a fuel connection 31, which opens into the first slide bearing 7.
  • the fuel in the fuel connection 31 is pressed into the first slide bearing 7 by a prefeed pump, not shown, with a delivery pressure of approximately 4-6 bar. This results in a very stable formation of a lubricating film between the pump housing 1 and the shaft end 5, which significantly increases the load-bearing capacity and service life of the first plain bearing 7.
  • a plurality of lubrication grooves 33 are arranged distributed over the circumference of the first slide bearing 7.
  • the lubrication grooves 33 can also be designed helically.
  • the first slide bearing 7 consists of a bush 37 pressed into the housing 1 with a pressed bush
  • the lubrication grooves 33 can be incorporated either in the inner ring 36 or in the stub shaft 5. When the lubrication grooves 33 are machined into the stub shaft 5, the rotary movement of the stub shaft can be used to deliver fuel into the first slide bearing 7. This further increases the load capacity of the first plain bearing 7.
  • Fig. 2 is a second embodiment of an inventive radial piston pump in cross section shown :. Same components will be mine. provided with the same reference number and what has been said regarding FIG. 1 applies accordingly.
  • the ball bearing 11 is inserted into the pump housing 1.
  • the fuel connection 31 opens into the interior 35. From there, the fuel flows via lubrication grooves 33 through the first slide bearing 7 to the end of the stub shaft 5. From the cross-sectional illustration of FIG. 2 it can be seen that a bushing 37 is pressed into the housing 1, in which the lubrication grooves 33 are incorporated. The bush 37 forms, together with the stub shaft 5, the first slide bearing 7.
  • the stub shaft 5 has a central bore 39, which is penetrated by a transverse bore 41.
  • the transverse bore 41 in turn opens into an annular groove 43 which is incorporated in the eccentric section 13 of the drive shaft 3.
  • the annular groove 43 can also be worked into the ring 15. This alternative is not shown in Fig. 2.
  • the fuel passes from the end of the stub shaft 5 to the second slide bearing 17, which is formed by the eccentric section 13 and the ring 15.
  • In the eccentric ring 15 are lubrication grooves
  • the lubrication grooves 45 establish a hydraulic connection between the ring groove 43 and the interior 35 on the side of the ring 15 facing away from the shaft end 5.
  • the lubrication grooves 45 end in the ring 15, so that on this side of the ring 15 only very little fuel passes through the gap (not visible in FIG. 2) between the ring 15 and the eccentric section 13 in FIG Interior 35 occur can. This measure ensures that "fresh" fuel always flows out of the interior 35 through the first slide bearing 7 and that a short-circuit flow cannot occur between the second slide bearing 17 and the first slide bearing 7.
  • An impeller 49 of a micropump is pressed into the center bore 39 at the end of the stub shaft. This impeller rotates with the drive shaft 3 and generates a fuel flow, fuel being sucked in through the first slide bearing 7 and then flowing through the second slide bearing 17 due to the pressure increase of the micropump. The fuel passes through the annular groove 43 into the second slide bearing 17, the pressure increase by the micropump depending on the speed of the
  • a third embodiment of a radial piston pump according to the invention is shown in cross section.
  • the same components are provided with the same reference numerals and what has been said regarding FIGS. 1 and 2 applies accordingly.
  • a coiled lubrication groove 33 is present in the stub shaft 5.
  • fuel is conveyed into the first slide bearing 7 by the rotation of the drive shaft 3, which increases its resilience and service life.
  • a helical lubrication groove 45 is present. The lubrication groove 45 improves the supply of fuel to the second slide bearing 17 and thereby increases its load capacity and service life.
  • Fig. 4 the third embodiment shown in Fig. 3 is shown schematically in a side view.
  • the optimal arrangement of the coiled or straight lubrication grooves 37 and 45 will be explained.
  • three pump elements 23-1, 23-11 and 23-111 which are arranged offset by 120 ° to one another are schematically represented by their longitudinal axes, which are actuated via the eccentric section 13 of the drive shaft.
  • the direction of rotation of the drive shaft is shown by a first arrow 53.
  • the direction of the resulting force vector 55 which acts on the shaft end 5 of the drive shaft and rotates with it, lies within the first angular range designated 57, which is preferably approximately 60 ° and whose central axis is approximately 90 ° to the maximum point of the
  • Eccentric section 13 is offset (axis 23-1). It is therefore advisable to arrange the lubrication groove 33 offset by 180 ° to the first winding area 57.
  • the preferred location for arranging the lubrication groove 33 is identified in FIG. 4 as the second angular range 59. In this way, the load-bearing capacity of the first plain bearing 7 is not impaired by the lubrication groove 33 in the area of its highest stress.
  • the first angular area 57 has 180 ° to the second
  • Angular range 59 is arranged offset, proven to be advantageous.
  • the first and second slide bearings 7 and 17 can also be lubricated with high-pressure fuel from the pump elements 23 (not shown).
  • a throttle (not shown) can be provided for each plain bearing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

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

Radialkolbenpumpe mit ZwanqsschmierunqRadial piston pump with dual lubrication
Stand der TechnikState of the art
Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung für eineThe invention relates to a radial piston pump for generating high fuel pressure for a
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 derFuel injection system of internal combustion engines, with a drive shaft, the drive shaft having an eccentric section and a stub shaft supported in a pump housing by a first slide bearing, preferably several with respect to the
Antriebswelle radial angeordneten Pumpenelementen, mit einem zwischen dem exzentrischen Abschnitt und dem Pumpenelement angeordneten Ring, und mit einem Kraftstoffanschluß im Pumpengehäuse.Drive shaft radially arranged pump elements, with a ring arranged between the eccentric section and the pump element, and with a fuel connection in the pump housing.
Eine solche innen abgestützte Radialkolbenpumpe ist bspw. aus der DE 197 05 205 AI 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 - 1Such an internally supported radial piston pump is known, for example, from DE 197 05 205 AI. Naturally, the mounting of the drive shaft in the pump housing and the mounting of the ring on the eccentric section of the drive shaft are subject to greater stress as the delivery volume and delivery head of the pump elements increase. Especially when the radial piston pump is to be used to deliver fuels with poor lubrication properties, such as gasoline, the mounting of the stub shaft in the pump housing and the mounting of the ring on the eccentric section of the drive shaft are a limiting factor for the delivery rate and the delivery head - 1
dar .represents.
Der Erfindung liegt die Aufgabe zugrunde, eine an sich bekannte Radialkolbenpumpe so weiterzuenrwickeln, dass sie ohne tiefgreifende Änderungen für größere Fördermengen und größere Förderhöhen einsetzbar ist.The object of the invention is to further develop a known radial piston pump in such a way that it can be used for larger delivery quantities and greater delivery heights without profound changes.
Diese Aufgabe wird bei einer 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 den Pumpenelementen angeordneten Ring, und mit einem Kraftstoffanschluß im Pumpengehäuse, dadurch gelöst, dass das erste Gleitlager zwangsweise von dem durch den Kraftstoffanschluß strömenden Kraftstoff durchströmt wird.This object is achieved in a radial piston pump for high-pressure fuel generation for a fuel injection system of internal combustion engines, with a drive shaft, the drive shaft having an eccentric section and a stub shaft supported in a pump housing by a first slide bearing, preferably with a plurality of pump elements arranged radially with respect to the drive shaft, with one between the eccentric section and the pump elements arranged ring, and with a fuel connection in the pump housing, solved in that the first sliding bearing is forcibly flowed through by the fuel flowing through the fuel connection.
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 denThe fuel flowing into the fuel connection of the radial piston pump has a pressure, which is provided by a prefeed pump, of about 4-6 bar. This pressure is independent of the speed and the
Betriebsbedingungen der Radialkolbenpumpe. Dadurch, dass der durch den Kraftstoffanschluß strömende Kraftstoff zwangsweise 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. Diese 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.Operating conditions of the radial piston pump. Because the fuel flowing through the fuel connection is forcibly guided through the first slide bearing, the first slide bearing is designed as a hydrostatic slide bearing. This creates a lubricating film with great reliability, so that the risk of "eaters" is significantly reduced. The load capacity of the first plain bearing also increases. This measure can be implemented by slight modifications of the first slide bearing on a known radial piston pump, so that the existing production facilities for manufacturing the radial piston pump can be taken over almost unchanged.
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 is supported on the eccentric section by a second slide bearing, and that the fuel flowing through the fuel connection forcibly flows through the second slide bearing, so that the load-bearing capacity of the second slide bearing is simple and effective Way is increased in all operating states and speeds of the high-pressure fuel pump.
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 embodiment of the invention provides that the first slide bearing has at least one lubrication groove running essentially in the direction of the axis of rotation of the drive shaft, so that the fuel flowing out of the fuel connection into the first slide bearing is ' evenly distributed over the entire bearing surface and thus the uniform formation of a lubricating 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 .Another addition to the invention provides that the stub shaft has a central bore, that a transverse bore branches off from the central bore, and that the second slide bearing is supplied with fuel by the transverse bore. In this way, the fuel for lubrication of the second slide bearing can be introduced into the center of the bearing surface of the second slide bearing and flow from there to the edges of the slide bearing. This favors the formation of a stable lubricating film between the ring and the 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, that the second slide bearing has at least one lubrication groove running essentially in the direction of the axis of rotation of the drive shaft.
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 vonIt has proven to be particularly advantageous if there is a hydraulic connection between the at least one lubrication groove and an interior of the pump housing on the side of the second slide bearing facing away from the shaft stub, since this ensures that the entire width of the second slide bearing is
Kraftstoff durchströmt wird und somit eine besonders gute Ausbildung des ' Schmierfilms erreicht wird.Fuel flows through and thus a particularly good formation 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 section or the ring has an annular groove, and that the transverse bore opens into the annular groove, so that the fuel is distributed uniformly over the entire circumference of the second slide bearing.
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, an impeller of a micropump can be inserted into the center bore, so that an additional pressure increase takes place depending on the speed of the radial piston pump, thus further increasing the load-bearing capacity of the second slide bearing at high speeds.
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 . 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.Alternative embodiments of the invention provide that the fuel connection opens into the interior of the housing or directly into the first slide bearing. As a result, the design of the first and second plain bearings according to the invention can be used equally advantageously in different types of radial piston pumps. Further advantageous refinements of the inventions provide that the lubrication groove is arranged on the stub shaft of the drive shaft, that the lubrication groove is arranged on the bushing of the first slide bearing, that the lubrication groove is arranged on the eccentric section of the drive shaft and / or that the lubrication groove on one Bushing of the second plain bearing is arranged so that the load capacity and life of the first and second plain bearings increase 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 the stub shaft and / or the lubrication groove on the eccentric section are arranged offset by approximately 180 ° to the resulting force vector.
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 be further promoted if the lubricating groove on the shaft end and / or the lubricating groove on the eccentric section are designed to be spiral.
Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Zeichnung, deren Beschreibung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention can be found in the following drawing, its description and the patent claims.
Zeichnungdrawing
Es zeigen:Show it:
Figur 1 eine Darstellung eines ersten Ausführungsbeispiels einer erfindungsgemäßenFigure 1 is a representation of a first embodiment of an inventive
Radialkolbenpumpe im Schnitt, undRadial piston pump in section, and
Figur 2 ein zweites Ausführungsbeispiel einer erfindungsgemäßen Radialkolbenpumpe im Querschnitt. Beschreibung der AusführungsbeispieleFigure 2 shows a second embodiment of a radial piston pump according to the invention in cross section. Description 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, a first embodiment of a radial piston pump according to the invention is shown in cross section. The radial piston pump consists of a pump housing 1. A drive shaft 3 is rotatably mounted in the pump housing 1. The drive shaft 3 is supported with a stub shaft 5 in a first slide bearing 7 in the pump housing 1. With its end opposite the shaft end 5, the drive shaft 3 is supported in a cover 9 by means of a ball bearing 11. Immediately next to the stub shaft 5, the drive shaft 3 has an eccentric section 13.
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 demThe eccentric section 13 is surrounded by a ring 15 which, in a view from the front (not shown), has a polygonal outer contour 19. The ring 15 does not rotate when the drive shaft 3 is rotated, but performs a circular movement. Between the
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.Ring 15 and the eccentric section 13, a second slide bearing 17 is present, which is pressed with the ring 15. With its polygonal outer contour 19, the ring 15 transmits the circular movement impressed on it by the eccentric section 13 to a piston foot plate 21 of 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 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. The piston 27 is set into an oscillating movement via the piston foot plate 21. As a result, fuel is drawn from a fuel connection (not shown) into a working space 29 and then pressurized during the so-called delivery stroke. The fuel, which is under high pressure, is fed through a high-pressure outlet (not shown) 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 opens into the first slide bearing 7. The fuel in the fuel connection 31 is pressed into the first slide bearing 7 by a prefeed pump, not shown, with a delivery pressure of approximately 4-6 bar. This results in a very stable formation of a lubricating film between the pump housing 1 and the shaft end 5, which significantly increases the load-bearing capacity and service life of the first plain bearing 7.
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.In order to increase the throughput of fuel through the first slide bearing 7 and to promote the formation of a lubricating film, a plurality of lubrication grooves 33 are arranged distributed over the circumference of the first slide bearing 7. The lubrication grooves 33 can also be designed helically.
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 eingepresstemWhen the fuel has flowed through the first slide bearing 7, it reaches an interior 35 of the pump housing. From there, the fuel via a 'in Fig. 1, not visible extension of the fuel port 31 during the suction stroke of the pump element is sucked into the working chamber 29 23. The first slide bearing 7 consists of a bush 37 pressed into the housing 1 with a pressed bush
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.Inner ring 36 and the stub shaft 5. The lubrication grooves 33 can be incorporated either in the inner ring 36 or in the stub shaft 5. When the lubrication grooves 33 are machined into the stub shaft 5, the rotary movement of the stub shaft can be used to deliver fuel into the first slide bearing 7. This further increases the load capacity of the first plain bearing 7.
In Fig. 2 ist ein zweites Ausführungsbeispiel einer er indungsgemäßen Radialkolbenpumpe im Querschnitt dargestellt:. Gleiche Bauteile werden mir. gleichem Bezugszeichen versehen und es gilt das betreffend der Fig. 1 Gesagte entsprechend.In Fig. 2 is a second embodiment of an inventive radial piston pump in cross section shown :. Same components will be mine. provided with the same reference number and what has been said regarding FIG. 1 applies 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 inserted into the pump housing 1. The fuel connection 31 opens into the interior 35. From there, the fuel flows via lubrication grooves 33 through the first slide bearing 7 to the end of the stub shaft 5. From the cross-sectional illustration of FIG. 2 it can be seen that a bushing 37 is pressed into the housing 1, in which the lubrication grooves 33 are incorporated. The bush 37 forms, together with the stub shaft 5, the first slide 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 SchmiernutenThe stub shaft 5 has a central bore 39, which is penetrated by a transverse bore 41. The transverse bore 41 in turn opens into an annular groove 43 which is incorporated in the eccentric section 13 of the drive shaft 3. Alternatively, the annular groove 43 can also be worked into the ring 15. This alternative is not shown in Fig. 2. Via the central bore 39 and the transverse bore 41 and the annular groove 43, the fuel passes from the end of the stub shaft 5 to the second slide bearing 17, which is formed by the eccentric section 13 and the ring 15. In the eccentric ring 15 are lubrication grooves
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.45 incorporated, which extend parallel to the axis of rotation 47 of the drive shaft 3 over almost the entire width of the ring 15. The lubrication grooves 45 establish a hydraulic connection between the ring groove 43 and the interior 35 on the side of the ring 15 facing away from the shaft end 5. On the side of the ring 15 facing the stub shaft 5, the lubrication grooves 45 end in the ring 15, so that on this side of the ring 15 only very little fuel passes through the gap (not visible in FIG. 2) between the ring 15 and the eccentric section 13 in FIG Interior 35 occur can. This measure ensures that "fresh" fuel always flows out of the interior 35 through the first slide bearing 7 and that a short-circuit flow cannot occur between the second slide bearing 17 and the first slide bearing 7.
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 derAn impeller 49 of a micropump is pressed into the center bore 39 at the end of the stub shaft. This impeller rotates with the drive shaft 3 and generates a fuel flow, fuel being sucked in through the first slide bearing 7 and then flowing through the second slide bearing 17 due to the pressure increase of the micropump. The fuel passes through the annular groove 43 into the second slide bearing 17, the pressure increase by the micropump depending on the speed of the
Antriebswelle 3 zunimmt. In Folge dessen nimmt mit zunehmender Drehzahl der Antriebswelle 3 auch die Tragf higkeit 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.Drive shaft 3 increases. As a result, the load capacity of the second plain bearing increases with increasing speed of the drive shaft 3. The hydrostatic pressure in the second slide bearing 17 is further increased by the centrifugal force which acts on the fuel (not shown) located in the transverse bore 41. This also leads to an increase in the load-bearing capacity of the second slide 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, a third embodiment of a radial piston pump according to the invention is shown in cross section. The same components are provided with the same reference numerals and what has been said regarding FIGS. 1 and 2 applies accordingly. In the third exemplary embodiment, a coiled lubrication groove 33 is present in the stub shaft 5. In this exemplary embodiment, fuel is conveyed into the first slide bearing 7 by the rotation of the drive shaft 3, which increases its resilience and service life. In the same way is also in the eccentric section 13 of the drive shaft 3, a helical lubrication groove 45 is present. The lubrication groove 45 improves the supply of fuel to the second slide bearing 17 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 23-1, 23-11 und 23-111 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 desIn Fig. 4, the third embodiment shown in Fig. 3 is shown schematically in a side view. On the basis of this illustration, the optimal arrangement of the coiled or straight lubrication grooves 37 and 45 will be explained. In this illustration, three pump elements 23-1, 23-11 and 23-111 which are arranged offset by 120 ° to one another are schematically represented by their longitudinal axes, which are actuated via the eccentric section 13 of the drive shaft. The direction of rotation of the drive shaft is shown by a first arrow 53. The direction of the resulting force vector 55, which acts on the shaft end 5 of the drive shaft and rotates with it, lies within the first angular range designated 57, which is preferably approximately 60 ° and whose central axis is approximately 90 ° to the maximum point of the
Exzenterabschnitts 13 versetzt ist (Achse 23-1) . Es empfiehlt sich deshalb, die Schmiernut 33 um 180° versetzt zu dem ersten Wiήkelbereich 57 anzuordnen. Der bevorzugte Platz zur Anordnung der Schmiernut 33 ist in Fig. 4 als zweiter Winkelbereich 59 gekennzeichnet. Auf diese Weise wird die Tragf higkeit 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 zweitenEccentric section 13 is offset (axis 23-1). It is therefore advisable to arrange the lubrication groove 33 offset by 180 ° to the first winding area 57. The preferred location for arranging the lubrication groove 33 is identified in FIG. 4 as the second angular range 59. In this way, the load-bearing capacity of the first plain bearing 7 is not impaired by the lubrication groove 33 in the area of its highest stress. For the arrangement of the lubrication groove 45 (not shown) in the area of the second slide bearing 17, the first angular area 57 has 180 ° to the second
Winkelbereich 59 versetzt angeordnet ist, als vorteilhaft erwiesen. Selbstverständlich können bei Bedarf das erste und das zweite Gleitlager 7 und 17 auch mit unter Hochdruck stehendem Kraftstoff aus den Pumpenelementen 23 geschmiert werden (nicht dargestellt) . Zur Steuerung der in die Gleitlager strömenden Kraftstoffmenge kann eine Drossel (nicht dargestellt) je Gleitlager vorgesehen werden. Angular range 59 is arranged offset, proven to be advantageous. Of course, if necessary, the first and second slide bearings 7 and 17 can also be lubricated with high-pressure fuel from the pump elements 23 (not shown). To control the amount of fuel flowing into the plain bearings, a throttle (not shown) can be provided for each plain bearing.

Claims

AnsprücheExpectations
1. Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung für eine Kraftstoffeinspritzanlage von Brennkraftmaschinen, mit einem Pumpengehäuse (1), mit einer Antriebswelle (3), wobei die Antriebswelle (3) einen exzentrischen Abschnitt (13) und einen in dem Pumpengehäuse (1) durch ein erstes1. Radial piston pump for high-pressure fuel generation for a fuel injection system of internal combustion engines, with a pump housing (1), with a drive shaft (3), the drive shaft (3) having an eccentric section (13) and one in the pump housing (1) by a first
Gleitlager (7) gelagerten 'Wellenstumpf (5) aufweist, mit vorzugsweise mehreren bezüglich der Antriebswelle (1) radial angeordneten Pumpenelementen (23) und mit einem Kraftstoffanschluß (31) im Pumpengehäuse (1) , dadurch gekennzeichnet, dass das erste Gleitlager (7) zwangsweise von Kraftstoff durchströmt wird.Sliding bearing (7) having a stub shaft (5), preferably with a plurality of pump elements (23) arranged radially with respect to the drive shaft (1) and with a fuel connection (31) in the pump housing (1), characterized in that the first sliding bearing (7) is forcibly flowed through by fuel.
2. Radial'kolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, dass zwischen zwischen dem exzentrischen Abschnitt (13) und den Pumpenelementen (23) ein Ring (15) angeordnet ist, dass der Ring (15) auf dem exzentrischen Abschnitt (13) durch ein zweites Gleitlager (17) gelagert ist, und dass das zweite Gleitlager (17) zwangsweise von Kraftstoff durchströmt wird.2. Radial ' piston pump according to claim 1, characterized in that between the eccentric section (13) and the pump elements (23) a ring (15) is arranged, that the ring (15) on the eccentric section (13) by a second slide bearing (17) is mounted, and that the second slide bearing (17) is forcibly flowed through by fuel.
3. Radialkolbenpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das erste Gleitlager (7) und/oder das zweite Gleitlager (17) von dem durch den Kraftstoffanschluß (31) strömenden Kraftstoff durchströmt wird. 3. Radial piston pump according to claim 1 or 2, characterized in that the first sliding bearing (7) and / or the second sliding bearing (17) is flowed through by the fuel flowing through the fuel connection (31).
4. Radialkolbenpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das erste Gleitlager (7) und/oder das zweite Gleitlager (17) von dem von den Pumpenelementen (23) geförderten, unter Hochdruck stehendem Kraftstoff durchströmt wird.4. Radial piston pump according to claim 1 or 2, characterized in that the first slide bearing (7) and / or the second slide bearing (17) is flowed through by the pump elements (23) delivered under high pressure fuel.
5. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das erste Gleitlager (7) mindestens eine im wesentlichen in Richtung der Drehachse (47) der Antriebswelle (3) verlaufende Schmiernut (33) aufweist.5. Radial piston pump according to one of the preceding claims, characterized in that the first slide bearing (7) has at least one lubricating groove (33) extending essentially in the direction of the axis of rotation (47) of the drive shaft (3).
6. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Wellenstumpf (5) eine Mittenbohrung (39) aufweist, dass von der Mittenbohrung (39) eine Querbohrung (41) abzweigt, und dass das zweite Gleitlager (17) von der Querbohrung (41) mit Kraftstoff versorgt wird.6. Radial piston pump according to one of the preceding claims, characterized in that the stub shaft (5) has a central bore (39) that branches off from the central bore (39), a transverse bore (41), and that the second plain bearing (17) from the transverse bore (41) is supplied with fuel.
7. Radialkolbenpumpe nach einem der Ansprüche 4 bis 6, dadurch gekennzeichnet, dass das zweite Gleitlager (17) mindestens eine im wesentlichen in Richtung der Drehachse7. Radial piston pump according to one of claims 4 to 6, characterized in that the second slide bearing (17) at least one substantially in the direction of the axis of rotation
(47) der Antriebswelle (3) verlaufende Schmiernut (45) aufweist.(47) of the drive shaft (3) extending lubrication groove (45).
6. Radialkolbenpumpe nach Anspruch 7, dadurch gekennzeichnet, dass zwischen der mindestens einen Schmiernut (45) und einem Innenraum (35) des Pumpengehäuses (1) auf der dem Wellenstumpf (5) abgewandten Seite des zweiten Gleitlagers (17) eine hydraulische Verbindung besteht .6. Radial piston pump according to claim 7, characterized in that there is a hydraulic connection between the at least one lubrication groove (45) and an interior (35) of the pump housing (1) on the side of the second slide bearing (17) facing away from the shaft end (5).
9. Radialkolbenpumpe nach einem der Ansprüche 6 bis 8, dadurch gekennzeichnet, dass der exzentrische Abschnitt (13) oder der Ring (15) eine Ringnut (43) aufweist, und dass die Querbohrung (41) in die Ringnut (43) mündet.9. Radial piston pump according to one of claims 6 to 8, characterized in that the eccentric section (13) or the ring (15) has an annular groove (43), and that the transverse bore (41) opens into the annular groove (43).
10. Radialkolbenpumpe nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, dass in die Mittεnbohrung (39) ein Laufrad (49) einer Mikropumpe eingesetzt ist.10. Radial piston pump according to one of claims 6 to 9, characterized in that an impeller (49) of a micropump is inserted into the central bore (39).
11. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Kraftstoffanschluß (31) in den Innenraum (35) des Pumpengehäuses (1) mündet.11. Radial piston pump according to one of the preceding claims, characterized in that the fuel connection (31) opens into the interior (35) of the pump housing (1).
12. Radialkolbenpumpe nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass der Kraftstoffanschluß (31) in das erste Gleitlager (7) mündet.12. Radial piston pump according to one of claims 1 to 11, characterized in that the fuel connection (31) opens into the first slide bearing (7).
13. Radialkolbenpumpe nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die Schmiernut (33) an dem Wellenstumpf (5) der Antriebswelle (3) angeordnet ist.13. Radial piston pump according to one of claims 1 to 12, characterized in that the lubrication groove (33) on the stub shaft (5) of the drive shaft (3) is arranged.
14. Radialkolbenpumpe nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die Schmiernut (33) an der Buchse (37) des ersten Gleitlagers (7) angeordnet ist.14. Radial piston pump according to one of claims 1 to 12, characterized in that the lubrication groove (33) on the bush (37) of the first plain bearing (7) is arranged.
15. Radialkolbenpumpe nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, dass die Schmiernut (45) an dem exzentrischen Abschnitt (13) der Antriebswelle (3) angeordnet ist. 15. Radial piston pump according to one of claims 1 to 14, characterized in that the lubrication groove (45) on the eccentric section (13) of the drive shaft (3) is arranged.
16. Radialkolbenpumpe nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, dass die Schmiernut (45) an dem exzentrischen Abschnitt angeordnet ist und sich über einen ersten Winkelbereich 57 von ca. 60° erstreckt.16. Radial piston pump according to one of claims 1 to 14, characterized in that the lubrication groove (45) is arranged on the eccentric section and extends over a first angular range 57 of approximately 60 °.
17. Radialkolbenpumpe nach Anspruch 16, dadurch gekennzeichnet, dass die Mittelachse (23-1) des ersten Winkelbereichs um etwa 90° vom Punkt der maximalen Exzentrizität des exzentrischen Abschnitts (13) ) versetzt verläuft.17. Radial piston pump according to claim 16, characterized in that the central axis (23-1) of the first angular range is offset by approximately 90 ° from the point of maximum eccentricity of the eccentric section (13).
18. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Schmiernut (33) am Wellenstumpf (5) in einem zweiten Wiinkelbereich (59) angeordnet ist, und dass der zweite Winkelbereich (59) um etwa 180° zum ersten Winkelbereich (57) versetzt angeordnet ist .18. Radial piston pump according to one of the preceding claims, characterized in that the lubricating groove (33) on the stub shaft (5) is arranged in a second angular region (59), and in that the second angular region (59) is approximately 180 ° to the first angular region (57 ) is arranged offset.
19. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Schmiernut (33) am Wellenstumpf (5) und/oder die Schmiernut (45) am exzentrischen Abschnitt (13) gewendelt ausgeführt sind. 19. Radial piston pump according to one of the preceding claims, characterized in that the lubrication groove (33) on the stub shaft (5) and / or the lubrication groove (45) on the eccentric section (13) are designed helically.
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 true EP1454055A1 (en) 2004-09-08
EP1454055B1 EP1454055B1 (en) 2005-11-02

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ID=26010700

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

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

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EP2660456B1 (en) * 2012-05-01 2017-12-06 Delphi International Operations Luxembourg S.à r.l. Fuel pump

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GB201412187D0 (en) * 2014-07-09 2014-08-20 Delphi International Operations Luxembourg S.�.R.L. Pump assembly
CN115807748A (en) * 2022-12-07 2023-03-17 北京天玛智控科技股份有限公司 Plunger piston shoe assembly and radial plunger pump driven by polygonal wheel disc

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EP2660456B1 (en) * 2012-05-01 2017-12-06 Delphi International Operations Luxembourg S.à r.l. Fuel pump

Also Published As

Publication number Publication date
DE50204804D1 (en) 2005-12-08
EP1454055B1 (en) 2005-11-02
ATE308676T1 (en) 2005-11-15
WO2003048564A1 (en) 2003-06-12

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