EP0925443B1 - Piston pump for high pressure fuel supply - Google Patents

Piston pump for high pressure fuel supply Download PDF

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Publication number
EP0925443B1
EP0925443B1 EP98936263A EP98936263A EP0925443B1 EP 0925443 B1 EP0925443 B1 EP 0925443B1 EP 98936263 A EP98936263 A EP 98936263A EP 98936263 A EP98936263 A EP 98936263A EP 0925443 B1 EP0925443 B1 EP 0925443B1
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EP
European Patent Office
Prior art keywords
pressure fuel
bolt
fuel pump
pump according
tappet
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
Application number
EP98936263A
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German (de)
French (fr)
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EP0925443A1 (en
Inventor
Horst Klinger
Uwe Kuhn
Bernd Rosenau
Peter Traub
Thomas GÖTTEL
Gerd LÖSCH
Sandro Soccol
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0925443A1 publication Critical patent/EP0925443A1/en
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Classifications

    • 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
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2307/00—Preventing the rotation of tappets

Definitions

  • piston pump preferably several radially arranged plungers are provided, either on their side facing away from the drive shaft there are pistons delimiting the high pressure side or even the Limit the high pressure side and thus immediately displacer or Perform compressor function.
  • the present invention is therefore the object based on the wear of generic piston pumps to reduce without the tappet load (piston force, Piston or ram stroke, relative speed of the roller compared to their storage). Moreover the measures according to the invention are to be cost-effective be feasible.
  • the bearing of the role a particularly aerodynamically favorable and Particularly easy way to lubricate in terms of production technology.
  • the lubricant supply opening, preferably with is connected to a lubricating oil circuit of the engine, according to the invention either flows directly into the area Sliding surfaces or in the so-called role room, which from the end area of the ram receiving the roller and the roller axis is limited.
  • the lubricant guide device is from one in Flattening of the bolt in the longitudinal direction on the bolt jacket be formed, which is particularly easy to manufacture is accomplished.
  • the piston pump can be special in terms of manufacturing technology be designed so that a respective plunger has a role with rigidly attached journals with which the roller is rotatably mounted in the end region of the ram.
  • the lubricant supply opening in the End region of the tappet in at least one hub of the tappet Storage of the journal or the bearing pin of the role opens. It would also be conceivable that the bearing pin or the bolt in the Hub area are formed with an annular groove that with of the lubricant supply opening covers.
  • the bolt and / or the role of ceramic material is therefore characterized in With regard to temperature resistance and wear resistance against metallic sliding pairings.
  • the bolt has a structured lateral surface that preferably has groove-shaped recesses which are in to extend in any shape along the bolt, or it lubrication pockets can be provided.
  • this Surface structuring is on the one hand due to the particular capillary effect of the structure a lubricant transport in the Gap between the journal and the hub or between the roller and in particular fixed bolt and on the other hand a Storage of the lubricating oil in the contaminated zone (Lubrication pocket effect).
  • Preferred dimensions of the Surface structures result from the dependent ones Claims.
  • Figures 1 and 2 show a piston pump with a Pump housing 2, in which a drive shaft 4 and several Roller tappet compression units 6 in the radial direction or are arranged in a star shape to each other.
  • the drive shaft 4 comprises three cam-like elevations 8 in the circumferential direction, the radially outermost points in each case by 120 ° in the circumferential direction is staggered and the apex of one form an even fillet. Furthermore is in one a corresponding plane parallel to the plane of the figure cam-like design 10 of the drive shaft 4 is provided, which, however, is rotated by 60 ° to the former and with a further roller tappet compressor unit 6 '(FIG. 2) interacts.
  • the roller tappet compressor unit 6 comprises a tappet 12 which in the radial direction 14 back and forth in one Cylinder chamber 16 of the pump housing 2 is provided.
  • a roller 20 On his The end section 18 facing the drive shaft 4 is a roller 20 rotatably mounted.
  • the end section 18 forms one Bolt chair 22 ( Figure 3) in which hubs 24 are provided to a pin 26 for the rotatable mounting of the roller 20th take.
  • the roller 20 rolls against the cam-like Elevations 8 of the drive shaft 4 in the circumferential direction and this causes the plunger 12 to move back and forth.
  • the Ram 12 On its side facing away from the drive shaft 4 is the Ram 12 by a spring 28 in the radial direction 14 inwards biased towards the drive shaft 4.
  • the spring 28 supports plunger side against a spring plate 30, which with its outer area 32 is pressed against the plunger 12.
  • a central opening 36 is provided in the inner region 34 which a piston 38 is passed.
  • the piston 38 supports on the ram side against a central extension 40 of the ram 12 and projects with its opposite free end 42 in a cylinder chamber 44 on the high-pressure side, which is surrounded by a flange-shaped section 46 of the pump housing 2 is formed.
  • the piston 38 When the plunger 12 goes back and forth, the piston 38 is in the cylinder chamber 44 on the high-pressure side in the compression direction or Intake direction moved back and forth.
  • the high-pressure side cylinder space 44 is not shown in FIG Way with an intake line and one to a common rail storage leading high pressure line connected.
  • the end section 18 on the drive axle side and the bolt chair 22 of the plunger 12 form a above the longitudinal axis 48 of the bolt Roll room 50.
  • This roll room 50 is over a Vent opening 52 with the side facing away from the drive shaft of the plunger 12 on which the spring 28 is connected to the back and forth of the plunger 12 does not go through To prevent pressure / negative pressure formation.
  • a Lubricant supply channel 54 is provided, which with a Lubricant supply of a motor vehicle engine interacts.
  • a Lubricant feed channel 54 in FIG. 1 Stub 56 not shown, with a throttle device 55 (Figure 2) away and opens into the inner cylinder surface of the Cylinder space 16.
  • a throttle device 55 Figure 2
  • Figure 3 At the corresponding point in the outer lateral surface 56 of the plunger 12 one in the stroke direction extending groove 58 ( Figure 3) is provided. From this groove 58 a lubricant supply opening 60 extends into the plunger and opens in the area of the hub 24, that is in the area of the Bearing point of the pin 26.
  • Figure 4 shows a plunger 90 with roller 92 and fixed Bolt 94.
  • the plunger 90 in turn has a stroke direction extending longitudinal groove 96 on its outer lateral surface 98, from which a lubricant feed opening 100 leads away and in Area of the hub 102 opens.
  • the bolt 94 ' has one Lubricant guide device 104 in the form of an in Flattening 108 extending in the longitudinal direction of the bolt on the Bolt surface on.
  • About the Lubricant guide device 104 will Lubricant feed opening 100 conveyed into the hub area Lubricant in the axial direction (arrow 110) in the area of surfaces of roller 92 and pin 94 sliding against each other brought.
  • the flat 108 is in the axial direction of the bolt completed
  • FIG. 5 shows a plunger 110 corresponding to FIG. 4, in which an anti-rotation device 112 of the pin 114 with respect to the hub 116 is provided.
  • the anti-rotation device 112 is radial to the longitudinal direction of the bolt through the plunger 110 inserted pin 118 formed.
  • Figure 7 shows a plunger, in which between the Roller 154 and bolt 156 one opposite bolt 156 and intermediate bush 158 running relative to the roller 154 Reduction of the relative speed of the friction partners is provided.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Description

Die Erfindung betrifft eine Kolbenpumpe, insbesondere eine Radialkolbenpumpe vom Rollenstößeltyp zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail-Einspritzsystem, mit einer Antriebswelle, die in Umfangsrichtung mehrere nockenartige Erhebungen aufweist, und mit wenigstens einem bezüglich der Antriebswelle radial angeordneten Stößel, der an seinem radial inneren Endbereich eine umdrehbare Rolle aufweist, welche abrollbar gegen die Antriebswelle im Bereich deren Erhebungen in Umfangsrichtung abrollbar abgestützt ist.The invention relates to a piston pump, in particular a Radial piston pump of roller tappet type High-pressure fuel supply in fuel injection systems of internal combustion engines, especially in a common rail injection system, with a drive shaft running in the circumferential direction has several cam-like elevations, and with at least a plunger arranged radially with respect to the drive shaft, which at its radially inner end region has a reversible roller has, which can be rolled against the drive shaft in the area the elevations of which are supported such that they can be rolled up in the circumferential direction.

Es versteht sich, dass bei einer derartigen Kolbenpumpe vorzugsweise mehrere radial angeordnete Stößel vorgesehen sind, die auf ihrer antriebswellenabgewandten Seite entweder gegen eine Hochdruckseite begrenzende Kolben anliegen oder selbst die Hochdruckseite begrenzen und damit unmittelbar Verdränger- oder Verdichterfunktion ausüben.It is understood that with such a piston pump preferably several radially arranged plungers are provided, either on their side facing away from the drive shaft there are pistons delimiting the high pressure side or even the Limit the high pressure side and thus immediately displacer or Perform compressor function.

Insbesondere bei den vorstehend erwähnten Common-Rail-Anwendungen, bei denen die Kolbenpumpe nicht zur direkten Einspritzung in den Motorzylinder sondern zum Fördern in einen Hochdruckspeicher verwendet wird, besteht das Bestreben, aus Funktions- und Kostengründen die Anzahl der separaten Fördereinheiten im Vergleich zu konventionellen Einspritzsystemen (z.B. Reihenpumpe, Steckpumpe) zu reduzieren, indem - wie eingangs bereits angedeutet - die Antriebswelle der Kolbenpumpe mehrere Erhebungen in Umfangsrichtung aufweist, die während einer Antriebswellenumdrehung nacheinander eine Hubbewegung bei einem Radialkolben bzw. -stößel bewirken (Mehrfachnockensystem).Especially in the common rail applications mentioned above, where the piston pump is not for direct Injection into the engine cylinder but for delivery into one High pressure storage is used, the effort is made of Functional and cost reasons the number of separate Conveying units compared to conventional Reduce injection systems (e.g. in-line pumps, plug-in pumps), by - as already indicated at the beginning - the drive shaft of the Piston pump has several elevations in the circumferential direction, the one during a drive shaft revolution Carry out lifting movement with a radial piston or tappet (Multi-cam system).

Dies führt jedoch zu einer erhöhten Belastung der Antriebskomponenten, insbesondere des Stößels und der drehbar gelagerten Rolle. Im Vergleich zu Einfachnockensystemen werden die Förderzeiten des Radialkolbens bzw. -stößels erhöht, während die Entlastungszeiten zwischen den Förderphasen verkürzt werden. Es steht infolgedessen weniger Zeit für einen Schmierfilmaufbau bzw. eine Regenerierung des Schmierfilms im Bereich der Lagerung der Rolle zur Verfügung. Dies führt bei Kolbenpumpen der genannten Art zu erhöhtem Verschleiß in Folge ungenügender Schmierung im Bereich der Lagerung der Rolle. Durch die langen Förderzeiten wird das Schmieröl aus dem Lagerspalt herausgedrückt und kann während der verhältnismäßig kurzen Entlastungszeiten nicht in hinreichendem Maße wieder in die Lagerstelle eindringen.However, this leads to an increased burden on the Drive components, especially the plunger and the rotatable stored role. Compared to single cam systems the delivery times of the radial piston or tappet increases while the relief times between the funding phases are reduced. As a result, there is less time for a lubricating film build-up or a regeneration of the lubricating film in the area of the storage of the role. This leads to the piston pumps mentioned type to increased wear as a result of insufficient Lubrication in the area of the roller bearing. Through the long The lubrication oil is delivered from the bearing gap pressed out and can during the relatively short Relief times are not sufficiently back in the Penetrate the bearing.

Aus der JP 05 180 116 als nächstliegendem Stand der Technik ist eine Kraftstoffhochdruckpumpe nach dem Oberbegriff des Anspruchs 1 bekannt, bei der der Stößel und der Bolzen über eine Schmiermittelzuführöffnung im Stößel geschmiert werden.From JP 05 180 116 as the closest prior art a high-pressure fuel pump according to the preamble of the claim 1 known, in which the plunger and the bolt on a Lubricant feed opening in the tappet must be lubricated.

Aus der AT 307 808 B ist eine Einspritzpumpe bekannt bei der die Ölversorgung der Gleitflächen der Bolzen/Rolle-Paarung über Mittenbohrung und eine mit der Mittenbohrung kommunizierende Querbohrung erfolgt. Der Strömungswiderstand der Mittenbohrung und der Querbohrung ist relativ hoch, wenn der Bolzen nicht zu sehr geschwächt werden soll. Außerdem sind diese Bohrungen fertigungstechnisch ungünstig, da es wegen der kleinen Bohrungsdurchmesser beim Bohren der Querbohrung oft zu Bohrerbrüchen kommt, wenn die Mittenbohrung angebohrt wird. From AT 307 808 B an injection pump is known in which the Oil supply to the sliding surfaces of the pin / roller pairing Center hole and one communicating with the center hole Cross drilling is done. The flow resistance of the center hole and the cross hole is relatively high if the bolt is not too to be weakened very much. In addition, these are holes Technically unfavorable because it is small Hole diameter often increases when drilling the cross hole Drill breaks occur when the center hole is drilled.

Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, den Verschleiß bei gattungsgemäßen Kolbenpumpen zu reduzieren, ohne die Stößelbelastung (Kolbenkraft, Kolben- bzw. Stößelhub, Relativgeschwindigkeit der Rolle gegenüber ihrer Lagerung) verringern zu müssen. Außerdem sollen die erfindungsgemäßen Maßnahmen kostengünstig realisierbar sein.The present invention is therefore the object based on the wear of generic piston pumps to reduce without the tappet load (piston force, Piston or ram stroke, relative speed of the roller compared to their storage). Moreover The measures according to the invention are to be cost-effective be feasible.

Diese Aufgabe wird bei einer Kolbenpumpe der genannten Art erfindungsgemäß durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst.This task is carried out in a piston pump of the type mentioned according to the invention by the characterizing features of Claim 1 solved.

Es wird also erfindungsgemäß vorgeschlagen, die Lagerstelle der Rolle auf eine strömungstechnisch besonders günstigen und fertigungstechnisch besonders einfachen Weg zu schmieren. Die Schmiermittelzuführöffnung, die bevorzugtermaßen mit einem Schmierölkreislauf des Motors in Verbindung steht, mündet nach der Erfindung entweder direkt im Bereich der Gleitflächen oder aber im sogenannten Rollenraum, welcher von dem die Rolle aufnehmenden Endbereich des Stößels und der Rollenachse begrenzt wird. It is therefore proposed according to the invention the bearing of the role a particularly aerodynamically favorable and Particularly easy way to lubricate in terms of production technology. The lubricant supply opening, preferably with is connected to a lubricating oil circuit of the engine, according to the invention either flows directly into the area Sliding surfaces or in the so-called role room, which from the end area of the ram receiving the roller and the roller axis is limited.

Desweiteren hat es sich als vorteilhaft erwiesen, wenn die Abflachung in Bolzenlängsrichtung abgeschlossen ist, d.h. wenn sie nicht an den Stirnseiten des Bolzens mündet, um ein Austreten des Schmiermittels in dieser nicht erwünschten Richtung zu verhindern.Furthermore, it has proven to be advantageous proven if the flattening is in the longitudinal direction of the bolt completed, i.e. if they are not on the front of the Bolzens opens to escape the lubricant in this to prevent unwanted direction.

Die Schmiermittelleiteinrichtung ist von einer in Bolzenlängsrichtung verlaufenden Abflachung am Bolzenmantel gebildet sein, was herstellungstechnisch besonders einfach zu bewerkstelligen ist.The lubricant guide device is from one in Flattening of the bolt in the longitudinal direction on the bolt jacket be formed, which is particularly easy to manufacture is accomplished.

Dadurch, dass über die Schmiermittelzuführöffnung Schmiermittel entweder direkt in die Nabe oder aber in den Rollenraum des Stößels eingeleitet wird, steht eine ausreichende Schmiermittelmenge zur Verfügung. Im ersten Fall wird das Schmiermittel direkt in den Bereich der gegeneinander gleitenden Flächen eingeleitet, und im zweiten Fall steht im Rollenraum stets soviel Schmiermittel zur Verfügung, dass es während der eingangs erwähnten verhältnismäßig kurzen Entlastungszeiten dennoch in ausreichendem Maße in die Lagerstelle eindringen kann.The fact that lubricant through the lubricant supply opening either directly into the hub or into the role space of the Is initiated, there is sufficient Lubricant amount available. In the first case it will Lubricant directly in the area of sliding against each other Areas initiated, and in the second case stands in the role room Always have enough lubricant available that Relatively short relief times mentioned at the beginning nevertheless penetrate the bearing to a sufficient extent can.

Die Kolbenpumpe kann in herstellungstechnisch besonders einfacher Weise so ausgebildet sein, dass ein jeweiliger Stößel eine Rolle mit starr angefügten Lagerzapfen aufweist, mit denen die Rolle drehbar in dem Endbereich des Stößels gelagert ist.The piston pump can be special in terms of manufacturing technology be designed so that a respective plunger has a role with rigidly attached journals with which the roller is rotatably mounted in the end region of the ram.

Die Rolle kann aber auch gegenüber einem parallel zur Umdrehungsachse der Antriebswelle erstreckten Bolzen umdrehbar und über diesen Bolzen an dem Endbereich des Stößels gelagert sein.The role can also be parallel to one Rotation axis of the drive shaft extending pin rotatable and mounted on this pin on the end region of the plunger his.

Wie vorstehend bereits angedeutet erweist es sich als besonders vorteilhaft, wenn die Schmiermittelzuführöffnung in dem Endbereich des Stößels in wenigstens einer Nabe des Stößels zur Lagerung der Lagerzapfen bzw. des Lagerbolzens der Rolle mündet. Es wäre auch denkbar, dass die Lagerzapfen oder der Bolzen im Nabenbereich mit einer Ringnut ausgebildet sind, die sich mit der Schmiermittelzuführöffnung deckt.As already indicated above, it turns out to be special advantageous if the lubricant supply opening in the End region of the tappet in at least one hub of the tappet Storage of the journal or the bearing pin of the role opens. It would also be conceivable that the bearing pin or the bolt in the Hub area are formed with an annular groove that with of the lubricant supply opening covers.

Es hat sich desweiteren als vorteilhaft erwiesen, wenn der Bolzen bezüglich dem Stößel feststehend ist und eine mit der Schmiermittelzuführöffnung sich überdeckende bzw. kommunizierende Schmiermittelleiteinrichtung zu den gegeneinander gleitenden Flächen der Bolzen/Rolle-Paarung aufweist. Bei feststehendem Bolzen befinden sich diese Gleitflächen innen zwischen Rolle und Bolzen. Die Schmiermittelleiteinrichtung dient also dazu, das über die Schmiermittelzuführöffnung in die Naben oder in den Rollenraum geförderte Schmiermittel zu den gegeneinander gleitenden Flächen von Rolle und Bolzen zu transportieren.It has also proven to be advantageous if the Bolt is fixed with respect to the plunger and one with the Lubricant feed opening overlapping or communicating lubricant guide to the surfaces of the bolt / roller pair sliding against each other having. These are located when the bolt is stationary Inner sliding surfaces between roller and bolt. The Lubricant guide device therefore serves the purpose of Lubricant feed opening in the hubs or in the roller chamber pumped lubricant to the surfaces sliding against each other to be transported by roller and bolt.

Es erweist sich auch als vorteilhaft, wenn in der Mantelfläche des Stößels und/oder in der Zylinderinnenfläche eine in Hubrichtung verlaufende Nut vorgesehen ist. Die Nut stellt beim Hin- und Hergehen des Stößels sicher, dass die Schmiermittelzuführöffnung des Stößels in jeder Hubhöhe mit der Schmiermittelzuführleitung des Gehäuses, welche in der Zylinderinnenfläche mündet, kommuniziert.It also proves to be advantageous if in the outer surface of the plunger and / or one in Stroke extending groove is provided. The groove provides Back and forth of the ram sure that the Lubricant feed opening of the tappet at every stroke height with the Lubricant supply line of the housing, which in the Internal cylinder surface opens, communicates.

Um den Schmiermitteldurchsatz im System steuern zu können, wird vorgeschlagen in der Schmiermittelzuführleitung des Gehäuses, also in Zuführrichtung vor dem Stößel, eine Drosseleinrichtung vorzusehen. Dies schafft Freiheit im Hinblick auf die Dimensionierung und den Wirkungsgrad der Schmiermittelversorgung. In order to be able to control the lubricant throughput in the system, proposed in the lubricant supply line of the housing, So in the feed direction in front of the plunger, a throttle device provided. This creates freedom in terms of Dimensioning and efficiency of Lubricant supply.

In weiterer Ausbildung der Erfindung besteht der Bolzen und/oder die Rolle aus keramischem Material und zeichnet sich daher im Hinblick auf die Temperaturbelastbarkeit und Verschleißbarkeit gegenüber metallischen Gleitpaarungen aus.In a further embodiment of the invention, the bolt and / or the role of ceramic material and is therefore characterized in With regard to temperature resistance and wear resistance against metallic sliding pairings.

In ganz besonders vorteilhafter Weiterbildung der Erfindung weist der Bolzen eine strukturierte Mantelfläche auf, die vorzugsweise nutförmige Ausnehmungen aufweist, die sich in ansich beliebiger Form entlang des Bolzens erstrecken, oder es können Schmiertaschen vorgesehen werden. Durch diese Oberflächenstrukturierung wird einerseits durch die insbesondere kapillare Wirkung der Struktur ein Schmiermitteltransport in den Spalt zwischen Lagerzapfen und Nabe oder zwischen Rolle und insbesondere feststehendem Bolzen und andererseits eine Speicherung des Schmieröls in der belasteten Zone (Schmiertaschenwirkung) bewirkt. Bevorzugte Abmessungen der Oberflächenstrukturen ergeben sich aus den abhängigen Patentansprüchen.In a particularly advantageous development of the invention the bolt has a structured lateral surface that preferably has groove-shaped recesses which are in to extend in any shape along the bolt, or it lubrication pockets can be provided. Through this Surface structuring is on the one hand due to the particular capillary effect of the structure a lubricant transport in the Gap between the journal and the hub or between the roller and in particular fixed bolt and on the other hand a Storage of the lubricating oil in the contaminated zone (Lubrication pocket effect). Preferred dimensions of the Surface structures result from the dependent ones Claims.

Es hat sich auch als vorteilhaft erwiesen, wenn zwischen dem Bolzen und der Rolle eine Zwischenbuchse vorgesehen ist, da hierdurch die Relativgeschwindigkeit der Gleitpartner und somit der Energieumsatz bei der auftretenden Misch- bzw. Festkörperreibung reduziert wird.It has also proven to be advantageous if between the Bolt and the roller an intermediate bush is provided because thereby the relative speed of the sliding partners and thus the energy turnover during the mixing or Solid friction is reduced.

Weitere Merkmale, Einzelheiten und Vorteile der Erfindung ergeben sich aus den beigefügten Patentansprüchen und aus der zeichnerischen Darstellung und nachfolgenden Beschreibung bevorzugter Ausführungsformen der Erfindung. In der Zeichnung zeigt:

Figur 1
eine teilweise Schnittansicht durch eine erfindungsgemäße Kolbenpumpe;
Figur 2
eine Schnittansicht mit Detaildarstellung entlang der Linie II-II in Figur 1;
Figur 3
zwei Schnittansichten eines Stößels nach Figur 1;
Figur 4
zwei weitere Schnittansichten einer weiteren Ausführungsform eines erfindungsgemäßen Stößels sowie Ansichten zweier Ausführungsformen eines Bolzens für die Stößelrolle;
Figur 5
eine Schnittansicht des Stößels nach Figur 4 mit einer Verdrehsicherung des Bolzens;
Figur 6
zwei Schnittansichten eines Stößels mit einer Schmierölzuführung direkt in den Rollenraum;
Figur 7
zwei Schnittansichten eines Stößels mit zusätzlicher Zwischenbuchse zwischen Bolzen und Rolle.
Further features, details and advantages of the invention result from the attached patent claims and from the drawing and the following description of preferred embodiments of the invention. The drawing shows:
Figure 1
a partial sectional view through a piston pump according to the invention;
Figure 2
a sectional view with a detailed representation along the line II-II in Figure 1;
Figure 3
two sectional views of a plunger according to Figure 1;
Figure 4
two further sectional views of a further embodiment of a tappet according to the invention and views of two embodiments of a bolt for the tappet roller;
Figure 5
a sectional view of the plunger of Figure 4 with an anti-rotation of the bolt;
Figure 6
two sectional views of a plunger with a lubricating oil supply directly into the roller chamber;
Figure 7
two sectional views of a plunger with an additional intermediate bush between pin and roller.

Die Figuren 1 und 2 zeigen eine Kolbenpumpe mit einem Pumpengehäuse 2, in dem eine Antriebswelle 4 sowie mehrere Rollenstößel-Verdichtungseinheiten 6 in radialer Richtung oder sternförmig zueinander angeordnet sind. Die Antriebswelle 4 umfasst in Umfangsrichtung drei nockenartige Erhebungen 8, deren radial äußerste Punkte jeweils um 120° in Umfangsrichtung zueinander versetzt angeordnet ist und den Scheitel einer gleichmäßigen Verrundung bilden. Desweiteren ist in einer parallel zur Figurenebene verlaufenden Ebene eine entsprechende nockenartige Ausbildung 10 der Antriebswelle 4 vorgesehen, welche jedoch zu ersterer um 60° verdreht ist und mit einer weiteren Rollenstößelverdichtereinheit 6' (Figur 2) zusammenwirkt.Figures 1 and 2 show a piston pump with a Pump housing 2, in which a drive shaft 4 and several Roller tappet compression units 6 in the radial direction or are arranged in a star shape to each other. The drive shaft 4 comprises three cam-like elevations 8 in the circumferential direction, the radially outermost points in each case by 120 ° in the circumferential direction is staggered and the apex of one form an even fillet. Furthermore is in one a corresponding plane parallel to the plane of the figure cam-like design 10 of the drive shaft 4 is provided, which, however, is rotated by 60 ° to the former and with a further roller tappet compressor unit 6 '(FIG. 2) interacts.

Die Rollenstößelverdichtereinheit 6 umfasst einen Stößel 12, der in radialer Richtung 14 hin- und herbewegbar in einem Zylinderraum 16 des Pumpengehäuses 2 vorgesehen ist. An seinem der Antriebswelle 4 zugewandten Endabschnitt 18 ist eine Rolle 20 umdrehbar gelagert. Hierfür bildet der Endabschnitt 18 einen Bolzenstuhl 22 (Figur 3), in dem Naben 24 vorgesehen sind, um einen Bolzen 26 zur umdrehbaren Lagerung der Rolle 20 aufzunehmen. Die Rolle 20 rollt gegen die nockenartigen Erhebungen 8 der Antriebswelle 4 in Umfangsrichtung ab und bewirkt dadurch ein Hin- und Hergehen des Stößels 12. The roller tappet compressor unit 6 comprises a tappet 12 which in the radial direction 14 back and forth in one Cylinder chamber 16 of the pump housing 2 is provided. On his The end section 18 facing the drive shaft 4 is a roller 20 rotatably mounted. For this purpose, the end section 18 forms one Bolt chair 22 (Figure 3) in which hubs 24 are provided to a pin 26 for the rotatable mounting of the roller 20th take. The roller 20 rolls against the cam-like Elevations 8 of the drive shaft 4 in the circumferential direction and this causes the plunger 12 to move back and forth.

Auf seiner von der Antriebswelle 4 abgewandten Seite ist der Stößel 12 durch eine Feder 28 in radialer Richtung 14 nach innen auf die Antriebswelle 4 hin vorgespannt. Die Feder 28 stützt sich stößelseitig gegen einen Federteller 30 ab, welches mit seinem Außenbereich 32 gegen den Stößel 12 gedrückt ist. Im Innenbereich 34 ist eine zentrale Öffnung 36 vorgesehen, durch welche ein Kolben 38 hindurchgeführt ist. Der Kolben 38 stützt sich stößelseitig gegen einen zentralen Ansatz 40 des Stößels 12 ab und ragt mit seinem gegenüberliegenden freien Ende 42 in einen hochdruckseitigen Zylinderraum 44 hinein, der von einem flanschförmigen Abschnitt 46 des Pumpengehäuses 2 gebildet ist. Bei Hin- und Hergehen des Stößels 12 wird der Kolben 38 in dem hochdruckseitigen Zylinderraum 44 in Verdichtungsrichtung bzw. Ansaugrichtung hin- und herbewegt.On its side facing away from the drive shaft 4 is the Ram 12 by a spring 28 in the radial direction 14 inwards biased towards the drive shaft 4. The spring 28 supports plunger side against a spring plate 30, which with its outer area 32 is pressed against the plunger 12. in the A central opening 36 is provided in the inner region 34 which a piston 38 is passed. The piston 38 supports on the ram side against a central extension 40 of the ram 12 and projects with its opposite free end 42 in a cylinder chamber 44 on the high-pressure side, which is surrounded by a flange-shaped section 46 of the pump housing 2 is formed. When the plunger 12 goes back and forth, the piston 38 is in the cylinder chamber 44 on the high-pressure side in the compression direction or Intake direction moved back and forth.

Der hochdruckseitige Zylinderraum 44 ist in nicht dargestellter Weise mit einer Ansaugleitung sowie einer zu einem Common-Rail-Speicher führenden Hochdruckleitung verbunden. Der antriebsachsenseitige Endabschnitt 18 sowie der Bolzenstuhl 22 des Stößels 12 bilden oberhalb der Bolzenlängsachse 48 einen Rollenraum 50. Dieser Rollenraum 50 ist über eine Entlüftungsöffnung 52 mit der antriebswellenabgewandten Seite des Stößels 12, an der sich die Feder 28 abstützt verbunden, um das Hin- und Hergehen des Stößels 12 nicht durch Druck/Unterdruckbildung zu behindern.The high-pressure side cylinder space 44 is not shown in FIG Way with an intake line and one to a common rail storage leading high pressure line connected. The end section 18 on the drive axle side and the bolt chair 22 of the plunger 12 form a above the longitudinal axis 48 of the bolt Roll room 50. This roll room 50 is over a Vent opening 52 with the side facing away from the drive shaft of the plunger 12 on which the spring 28 is connected to the back and forth of the plunger 12 does not go through To prevent pressure / negative pressure formation.

In dem Pumpengehäuse 2 ist desweiteren ein Schmiermittelzuführkanal 54 vorgesehen, welcher mit einer Schmiermittelversorgung eines Kraftfahrzeugmotors zusammenwirkt. Von dem Schmiermittelzuführkanal 54 führt eine in der Figur 1 nicht dargestellte Stichleitung 56 mit einer Drosseleinrichtung 55 (Figur 2) weg und mündet in der inneren Zylinderfläche des Zylinderraums 16. An der entsprechenden Stelle ist in der äußeren Mantelfläche 56 des Stößels 12 eine in Hubrichtung erstreckte Nut 58 (Figur 3) vorgesehen. Von dieser Nut 58 erstreckt sich eine Schmiermittelzuführöffnung 60 in den Stößel und mündet im Bereich der Nabe 24, also im Bereich der Lagerstelle des Bolzens 26.In the pump housing 2 is also a Lubricant supply channel 54 is provided, which with a Lubricant supply of a motor vehicle engine interacts. One leads from the lubricant feed channel 54 in FIG. 1 Stub 56, not shown, with a throttle device 55 (Figure 2) away and opens into the inner cylinder surface of the Cylinder space 16. At the corresponding point in the outer lateral surface 56 of the plunger 12 one in the stroke direction extending groove 58 (Figure 3) is provided. From this groove 58 a lubricant supply opening 60 extends into the plunger and opens in the area of the hub 24, that is in the area of the Bearing point of the pin 26.

Figur 4 zeigt einen Stößel 90 mit Rolle 92 und feststehendem Bolzen 94. Der Stößel 90 weist wiederum eine in Hubrichtung verlaufende Längsnut 96 an seiner äußeren Mantelfläche 98 auf, von der eine Schmiermittelzuführöffnung 100 wegführt und im Bereich der Nabe 102 mündet. Der Bolzen 94'weist eine Schmiermittelleiteinrichtung 104 in Form einer in Bolzenlängsrichtung verlaufenden Abflachung 108 an der Bolzenmantelfläche auf. Über die Schmiermittelleiteinrichtung 104 wird das über die Schmiermittelzuführöffnung 100 in den Nabenbereich geförderte Schmiermittel in axialer Richtung (Pfeil 110) in den Bereich der gegeneinander gleitenden Flächen von Rolle 92 und Bolzen 94 gebracht. Die Abflachung 108 ist in axialer Richtung des Bolzens abgeschlossen In Figur 4 ist ein Bolzen 94' dargestellt, der eine Abflachung 108 aufweist, die auch in der Einzelheit Y dargestellt ist. Figure 4 shows a plunger 90 with roller 92 and fixed Bolt 94. The plunger 90 in turn has a stroke direction extending longitudinal groove 96 on its outer lateral surface 98, from which a lubricant feed opening 100 leads away and in Area of the hub 102 opens. The bolt 94 'has one Lubricant guide device 104 in the form of an in Flattening 108 extending in the longitudinal direction of the bolt on the Bolt surface on. About the Lubricant guide device 104 will Lubricant feed opening 100 conveyed into the hub area Lubricant in the axial direction (arrow 110) in the area of surfaces of roller 92 and pin 94 sliding against each other brought. The flat 108 is in the axial direction of the bolt completed In Figure 4 is a bolt 94 'is shown, which has a flattening 108 which is also shown in detail Y.

Figur 5 zeigt einen Figur 4 entsprechenden Stößel 110, bei dem eine Verdrehsicherung 112 des Bolzens 114 gegenüber der Nabe 116 vorgesehen ist. Die Verdrehsicherung 112 ist von einem radial zur Bolzenlängsrichtung durch den Stößel 110 hindurch eingeführten Stift 118 gebildet.FIG. 5 shows a plunger 110 corresponding to FIG. 4, in which an anti-rotation device 112 of the pin 114 with respect to the hub 116 is provided. The anti-rotation device 112 is radial to the longitudinal direction of the bolt through the plunger 110 inserted pin 118 formed.

Figur 6 zeigt eine weitere Ausführungform, wonach ein Stößel 120 mit im Rollenraum 122 mündenden Schmiermittelzuführöffnungen 124 ausgebildet ist. Die Schmierung erfolgt hier also über den Rollenraum 122. Diese Ausführungsform erweist sich im Zusammenhang mit einem losen Bolzen als vorteilhaft. Hierdurch wird zumindest ein erhöhtes Schmierölangebot bei fertigungstechnisch verhältnismäßig geringem Bearbeitungs- und Montageaufwand erreicht.FIG. 6 shows a further embodiment, according to which a plunger 120 with lubricant supply openings 124 opening into the roller chamber 122 is trained. The lubrication takes place here via the Roller room 122. This embodiment proves itself in Connection with a loose bolt is advantageous. hereby will at least increase the supply of lubricating oil Relatively low manufacturing and processing Assembly effort reached.

Schließlich zeigt Figur 7 einen Stößel, bei dem zwischen der Rolle 154 und dem Bolzen 156 eine gegenüber dem Bolzen 156 und gegenüber der Rolle 154 laufende Zwischenbuchse 158 zur Reduzierung der Relativgeschwindigkeit der Reibpartner vorgesehen ist.Finally, Figure 7 shows a plunger, in which between the Roller 154 and bolt 156 one opposite bolt 156 and intermediate bush 158 running relative to the roller 154 Reduction of the relative speed of the friction partners is provided.

Claims (16)

  1. High-pressure fuel pump of the roller-tappet type for high-pressure fuel supply in fuel injection systems of internal combustion engines, in particular in a common-rail injection system, with a drive shaft (4) which is mounted in a pump casing (2) and has a plurality of cam-like elevations (8) in the circumferential direction, and with at least one tappet (12) which is arranged in a cylinder space (16) radially with respect to the drive shaft (4) and on its radially inner end region (18) has a rotatable roller (20) which is supported against the drive shaft (4) in the region of the elevations (8) of the latter so as to be capable of rolling in the circumferential direction, a lubricant supply orifice (60, 100), which emanates from the casing of the tappet (12, 90) and issues in the radially inner tappet end region (18) supporting the roller (20, 92), communicating, at least during part of the stroke, with a lubricant supply line (54, 56), issuing in the cylinder space (16), of the casing (2), and the roller (20, 92, 114) being mounted rotatably with respect to a bolt (26, 74, 94, 114), extended parallel to the axis of rotation of the drive shaft (4), and, via this bolt (26, 74, 94, 114), on the radially inner end region (18) of the tappet (12, 90, 110), characterized in that the supply of oil to the sliding faces of the bolt/roller pairing takes place via a lubricant guide device (104) arranged on the bolt outer surface (108) and communicating with the lubricant supply orifice (60, 100), and in that the lubricant guide device (104) is formed by a flattening (108) running in the bolt longitudinal direction and located on the bolt casing.
  2. High-pressure fuel pump according to Claim 1, characterized in that the flattening (108) is closed off in the bolt longitudinal direction.
  3. High-pressure fuel pump according to one of the preceding claims, characterized in that the lubricant supply orifice (60, 100) is connected to a lubricant circuit of the engine.
  4. High-pressure fuel pump according to one of the preceding claims, characterized in that the lubricant supply orifice (60, 100) issues in the end region of the tappet (12, 90, 110) in at least one hub (116) of the tappet.
  5. High-pressure fuel pump according to one of the preceding claims, characterized in that the bolt (26, 74, 94, 114) is stationary with respect to the tappet (12, 90, 110).
  6. High-pressure fuel pump according to one of the preceding claims, characterized in that the bolt (114) is held non-rotatably with respect to the tappet (110) by means of an anti-rotation device (112).
  7. High-pressure fuel pump according to one of the preceding claims, characterized in that, emanating from the lubricant supply orifice (60, 100) in the outer surface of the tappet (12, 90), a groove (58, 96) running in the stroke direction is provided in the outer surface and/or in the cylinder inner surface.
  8. High-pressure fuel pump according to one of the preceding claims, characterized in that a throttle device (55) is provided, upstream of the tappet (12), in the lubricant supply (54, 56).
  9. High-pressure fuel pump according to one of the preceding claims, characterized in that the bolt and/or the roller consist of ceramic material.
  10. High-pressure fuel pump according to Claim 9, characterized in that the bolt and/or the roller consists of silicon nitride or zirconium oxide.
  11. High-pressure fuel pump according to one of the preceding claims, characterized in that the bolt (130) has a structured outer surface (132).
  12. High-pressure fuel pump according to one of the preceding claims, characterized in that the structured outer surface (132) has groove-shaped recesses (134), preferably in helical form or cross-helical form.
  13. High-pressure fuel pump according to Claim 11 or 12, characterized in that the structured outer surface has lubricating pockets (138).
  14. High-pressure fuel pump according to Claim 11, 12 or 13, characterized in that the depth of the surface structures is 0.005 - 0.2 mm, preferably 0.020 - 0.80 mm.
  15. High-pressure fuel pump according to Claims 11 to 14, characterized in that the width of the surface structures is 0.010 - 0.2 mm, preferably 0.020 - 0.080 mm.
  16. High-pressure fuel pump according to one of the preceding claims, characterized in that an intermediate bush (158) is provided between the bolt (156) and the roller (154).
EP98936263A 1997-07-11 1998-06-30 Piston pump for high pressure fuel supply Expired - Lifetime EP0925443B1 (en)

Applications Claiming Priority (3)

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DE19729793A DE19729793A1 (en) 1997-07-11 1997-07-11 Piston pump for high-pressure fuel supply
DE19729793 1997-07-11
PCT/DE1998/001791 WO1999002852A1 (en) 1997-07-11 1998-06-30 Piston pump for high pressure fuel supply

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EP0925443A1 EP0925443A1 (en) 1999-06-30
EP0925443B1 true EP0925443B1 (en) 2003-10-15

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EP (1) EP0925443B1 (en)
JP (1) JP2001500221A (en)
DE (2) DE19729793A1 (en)
WO (1) WO1999002852A1 (en)

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Also Published As

Publication number Publication date
US6216583B1 (en) 2001-04-17
DE19729793A1 (en) 1999-01-14
JP2001500221A (en) 2001-01-09
EP0925443A1 (en) 1999-06-30
DE59809920D1 (en) 2003-11-20
WO1999002852A1 (en) 1999-01-21

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