EP1068448A1 - Radial piston pump for high-pressure fuel supply - Google Patents

Radial piston pump for high-pressure fuel supply

Info

Publication number
EP1068448A1
EP1068448A1 EP99907314A EP99907314A EP1068448A1 EP 1068448 A1 EP1068448 A1 EP 1068448A1 EP 99907314 A EP99907314 A EP 99907314A EP 99907314 A EP99907314 A EP 99907314A EP 1068448 A1 EP1068448 A1 EP 1068448A1
Authority
EP
European Patent Office
Prior art keywords
plate
drive shaft
piston pump
radial piston
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP99907314A
Other languages
German (de)
French (fr)
Other versions
EP1068448B1 (en
Inventor
Kasim-Melih Hamutcu
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1068448A1 publication Critical patent/EP1068448A1/en
Application granted granted Critical
Publication of EP1068448B1 publication Critical patent/EP1068448B1/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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam

Definitions

  • Radial piston pump for supplying high-pressure fuel
  • the invention relates to a radial piston pump for high-pressure fuel supply
  • Fuel injection systems of internal combustion engines in particular in the case of a common rail injection system, with a drive shaft mounted in a pump housing, which is eccentrically formed or has cam-like elevations in the circumferential direction, and preferably with a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space, on the other of which A shaft is attached to the ends facing the drive shaft, the pistons being movable back and forth in the respective cylinder space by rotating the drive shaft in the radial direction.
  • the plate attached to the ends of the pistons is in contact with the drive shaft.
  • the pistons are successively caused to reciprocate by the eccentricity of the drive shaft or by cam-like elevations on the drive shaft. Relatively large forces are applied to the pistons by the rotating drive shaft depending on the force sucked into the cylinder chambers in order to pressurize the fuel.
  • sucking fuel the pistons with the plate are usually pressed against the drive shaft by a spring.
  • the invention is therefore based on the problem of a
  • Radial piston pump can be guaranteed even with partial filling of the cylinder chambers.
  • the radial piston pump according to the invention is designed to withstand a pump pressure of up to 2000 bar.
  • Fuel injection systems of internal combustion engines in particular in a common rail injection system, with a drive shaft mounted in a pump housing, which is eccentrically formed or has cam-like elevations in the circumferential direction, and preferably - 3 - a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space, on each of whose ends facing the drive shaft a plate is attached, the pistons being turned radially in the respective cylinder space by rotating the drive shaft
  • Peak pressures of up to 2000 bar ensure that the plate functions properly.
  • a special embodiment of the invention is characterized in that the plate has a smaller thickness in the middle than in the outer areas. This reduces the tension in the middle of the plate. The power flow is redirected to the outer areas. As a result, the force is redirected to those points that are less stressed. This relieves the critical area in the middle of the plate.
  • the concrete shape of the plate is particularly important. Various designs are possible, but all of them implement the common basic idea of the present invention. Depending on the type of plate, the plate may have a central recess for receiving one end of one of the pistons. In such a case, the design of the plate center according to the invention is arranged within the depression.
  • Another special embodiment of the invention is - 4 - characterized in that the plate in the middle on the side facing away from the drive shaft has a recess in the form of a cone, the tip of which is directed towards the inside of the plate.
  • This conical shape of the plate in the middle can be achieved, for example, by a
  • the plate has a recess in the center on the side facing the drive shaft in the form of a cone, the tip of which is directed towards the inside of the plate.
  • the plate can either be conical on its upper side or on its lower side. The decision for the top or bottom depends on the forces acting on the plate. It has proven in the context of the present invention that it is advantageous to form the cone in particular on the side on which the greatest forces occur. As a rule, this will be the side on which the drive shaft is arranged.
  • a further special embodiment of the invention is characterized in that the plate has a recess in the form of a cone in the middle on the side facing away from the drive shaft and on the side facing the drive shaft, the tips of the two cones being directed towards one another. According to the invention, the best results are achieved if both the top and the bottom of the plate are conical in the middle. This results in an optimal voltage curve during operation.
  • the wear resistance of a plate designed in this way is advantageously increased.
  • Another special embodiment of the invention is characterized in that the height of the cone on the side facing away from the drive shaft is approximately 1/10 of the height of the cone on the side facing the drive shaft. This is advantageous because the greatest forces occur on the side facing the drive shaft. This is particularly the case if the cylinder spaces are not completely filled.
  • the exact dimensions of the plate depend, among other things, on the pump pressure and the number of load changes per unit of time.
  • the plate is round.
  • rectangular plates can also be used, but the round shape is preferable because of the more favorable force transmission in cooperation with the drive shaft.
  • the plate has a round recess in the middle.
  • the round recess in the middle of the plate serves to receive the end of one of the pistons facing the drive shaft. When the end of the piston is received in the recess, the plate is essentially unable to move relative to the drive shaft.
  • the plate has a collar.
  • the collar forms a stop for a cage, which is attached to the piston and serves to hold the plate on the piston.
  • Another special embodiment of the invention is characterized in that a ring is arranged between the drive shaft and the plate.
  • the ring is used for Transfer of forces from the eccentrically designed drive shaft to the plate.
  • the ring is advantageously slidably mounted on the drive shaft.
  • the ring can be either cylindrical or polygonal.
  • the present invention has the general advantage that the basic idea of the present invention can be applied to existing radial piston pumps in a simple manner.
  • the component strength is increased, especially with zero delivery in the suction stroke.
  • Figure 1 shows a sectional view of a radial piston pump
  • Figure 2 shows a plate according to the present invention
  • FIG. 3 shows an enlarged view of the detail X from FIG. 1 on a scale of 20: 1;
  • FIG. 4 shows an enlarged view of detail Y from FIG. 1 on a 20: 1 scale.
  • FIG. 1 shows a radial piston pump for supplying high-pressure fuel Fuel injection systems of internal combustion engines.
  • the radial piston pump is equipped with an integrated demand control.
  • the fuel supply and dimensioning takes place via a metering unit, not shown.
  • the radial piston pump according to the invention is used in particular in common rail injection systems for supplying fuel to diesel engines.
  • Common rail means “common line” or “common rail”.
  • the injection nozzles in common-rail injection systems are fed from a common line.
  • the radial piston pump shown in FIG. 1 comprises a drive shaft 4 mounted in a pump housing 2 with an eccentrically designed shaft section 6.
  • a polygonal ring 8 is provided on the eccentric shaft section 6, with respect to which the shaft section 6 can be rotated.
  • the ring 8 comprises three flats 10, each offset by 120 ° to each other, against which a piston 12 is supported.
  • a cylindrical ring can also be used.
  • the pistons 12 are each received in a cylinder space 18 so that they can move back and forth in the radial direction relative to the drive shaft 4.
  • a plate 14 is fastened to the end of the pistons 12 facing the drive shaft 4.
  • the plates 14 are each held by a cage 15 on the associated piston 12.
  • the plates 14 are each biased against the ring 8 by a spring 16. As can be seen in FIG. 1, the plates 14 are in contact with the flats 10 of the ring 8. - 8th -
  • the plate 14 according to the invention is shown alone.
  • the plate shown in cross section in FIG. 2 has the shape of a circular cylinder with a diameter of approximately 15 millimeters and a height of approximately 5 millimeters.
  • a likewise circular-cylindrical depression 20 with a rounded edge 21 is cut out in the center on the top of the plate 14.
  • the recess 20 serves to receive one end of one of the pistons 12.
  • a collar 22 is also provided on the plate 14, the upper edge 23 of which is chamfered and merges into the top of the plate 14.
  • a chamfer 24 is provided on the underside of the plate 14.
  • Figure 3 shows the detail X from Figure 1 on a scale of 20: 1.
  • the plate 14 has a conical recess 25 in the center on the underside opposite the depression 20.
  • the height H of the conical recess 25 is approximately 0.2 millimeters.
  • the diameter of the conical recess 25 is approximately 2.8 millimeters.
  • Figure 4 shows the detail Y from Figure 1 on a scale of 20: 1.
  • the plate 14 has a conical recess 26 in the center of the recess 20.
  • the height h of the conical recess 26 is approximately 0.02 millimeters.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

The invention relates to a radial piston pump for high-pressure fuel supply in internal combustion engine fuel injection systems, especially common-rail injection systems. A disk (14) is placed on each radially arranged piston in a respective cylinder chamber. In relation to the above-mentioned invention it was noted that traditionally used disks (14) often became damaged, especially in the centre, during operation. The aim of the invention is thus to avoid damage to said disks. This is achieved by designing the centre of the disk (14) in such a way that the strain arising therein during operation is reduced. By reducing the strain on the centre of the disk (25,26) it is possible to extend the operational life of said disk (14) in an advantageous manner. The disk (14) functions in an impeccable manner even at high pressures of up to 2,000 bars.

Description

Radialkolbenpumpe zur KraftStoffhochdruckversorgungRadial piston pump for supplying high-pressure fuel
Stand der TechnikState of the art
Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckversorgung beiThe invention relates to a radial piston pump for high-pressure fuel supply
Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail-Einspritzsystem, mit einer in einem Pumpengehäuse gelagerten Antriebswelle, die exzentrisch ausgebildet ist oder in Umfangsriehtung nockenartige Erhebungen aufweist, und mit vorzugsweise mehreren bezüglich der Antriebswelle radial in einem jeweiligen Zylinderraum angeordneten Kolben, an deren zur Antriebswelle gewandten Enden jeweils eine Platte angebracht ist, wobei die Kolben durch Drehen der Antriebswelle in dem jeweiligen Zylinderraum in radialer Richtung hin und her bewegbar sind.Fuel injection systems of internal combustion engines, in particular in the case of a common rail injection system, with a drive shaft mounted in a pump housing, which is eccentrically formed or has cam-like elevations in the circumferential direction, and preferably with a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space, on the other of which A shaft is attached to the ends facing the drive shaft, the pistons being movable back and forth in the respective cylinder space by rotating the drive shaft in the radial direction.
Bei einer derartigen innen abgestützten Radialkolbenpumpe hat die jeweils an den Enden der Kolben angebrachte Platte Kontakt mit der Antriebswelle. Die Kolben werden durch die Exzentrizität der Antriebswelle oder durch nockenartige Erhebungen auf der Antriebswelle nacheinander in eine Hin- und Herbewegung versetzt. Dabei werden von der sich drehenden Antriebswelle auf die Kolben in Abhängigkeit von den in die Zylinderräume angesaugten Kraf Stoffmengen relativ große Kräfte aufgebracht, um den Kraftstoff mit Druck zu beaufschlagen. Beim Ansaugen von Kraftstoff werden die Kolben mit der Platte in der Regel jeweils durch eine Feder gegen die Antriebswelle gedrückt .In such an internally supported radial piston pump, the plate attached to the ends of the pistons is in contact with the drive shaft. The pistons are successively caused to reciprocate by the eccentricity of the drive shaft or by cam-like elevations on the drive shaft. Relatively large forces are applied to the pistons by the rotating drive shaft depending on the force sucked into the cylinder chambers in order to pressurize the fuel. When sucking fuel the pistons with the plate are usually pressed against the drive shaft by a spring.
Im Rahmen der vorliegenden Erfindung hat sich gezeigt, daß die herkömmlich verwendeten Platten im Betrieb, insbesondere in der Mitte, häufig beschädigt werden. Diese Verschleißerscheinungen können zum Bruch der Platte führen und sind deshalb unerwünscht. Die Funktion der Radialkolbenpumpe ist mit einer beschädigten Platte nicht mehr gewährleistet. Ein Austauschen einer beschädigten Platte ist zeitaufwendig, weil die Radialkolbenpumpe zerlegt und die Antriebswelle ausgebaut werden muß, um an die beschädigte Platte heranzukommen.In the context of the present invention, it has been shown that the plates conventionally used are frequently damaged during operation, particularly in the middle. These signs of wear can break the plate and are therefore undesirable. The function of the radial piston pump can no longer be guaranteed with a damaged plate. Replacing a damaged plate is time consuming because the radial piston pump must be disassembled and the drive shaft must be removed to access the damaged plate.
Der Erfindung liegt daher das Problem zugrunde, eineThe invention is therefore based on the problem of a
Radialkolbenpumpe bereitzustellen, welche die vorstehend genannten Nachteile überwindet . Insbesondere sollen Beschädigungen der Platte verhindert werden. Die Platte soll im Betrieb verschleißfrei arbeiten und zwar auch bei hohen Drücken. Dabei soll ein einwandfreier Betrieb derTo provide radial piston pump, which overcomes the disadvantages mentioned above. In particular, damage to the plate should be prevented. The plate should work wear-free during operation, even at high pressures. In doing so, the proper operation of the
Radialkolbenpumpe auch bei Teilbefüllung der Zylinderräume gewährleistet sein. Die erfindungsgemäße Radialkolbenpumpe soll einen Pumpendruck von bis zu 2000 bar aushalten.Radial piston pump can be guaranteed even with partial filling of the cylinder chambers. The radial piston pump according to the invention is designed to withstand a pump pressure of up to 2000 bar.
Das Problem wird durch die in dem unabhängigenThe problem is solved by those in the independent
Patentanspruch offenbarte Radialkolbenpumpe gelöst . Besondere Ausführungsarten der Erfindung sind in den Unteransprüchen offenbart.Radial piston pump disclosed solved. Particular embodiments of the invention are disclosed in the subclaims.
Das Problem ist bei einer Radialkolbenpumpe zurThe problem is with a radial piston pump
Kraftstoffhochdruckversorgung beiHigh pressure fuel supply at
Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail-Einspritzsystem, mit einer in einem Pumpengehäuse gelagerten Antriebswelle, die exzentrisch ausgebildet ist oder in Umfangsrichtung nockenartige Erhebungen aufweist, und mit vorzugsweise - 3 - mehreren bezüglich der Antriebswelle radial in einem jeweiligen Zylinderraum angeordneten Kolben, an deren zur Antriebswelle gewandten Enden jeweils eine Platte angebracht ist, wobei die Kolben durch Drehen der Antriebswelle in dem jeweiligen Zylinderraum in radialerFuel injection systems of internal combustion engines, in particular in a common rail injection system, with a drive shaft mounted in a pump housing, which is eccentrically formed or has cam-like elevations in the circumferential direction, and preferably - 3 - a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space, on each of whose ends facing the drive shaft a plate is attached, the pistons being turned radially in the respective cylinder space by rotating the drive shaft
Richtung hin und her bewegbar sind, dadurch gelöst, daß die Platte in der Mitte so ausgebildet ist, daß die im Betrieb auftretenden Spannungen an dieser Stelle verringert werden. Bei Untersuchen unter Zuhilfenahme der Finite-Elemente- Methode hat sich herausgestellt, daß in der Mitte derDirection can be moved back and forth, solved in that the plate is formed in the middle so that the stresses occurring during operation are reduced at this point. When examining with the help of the finite element method, it was found that in the middle of the
Platte im Betrieb die größten Spannungen auftreten. Die Beschädigungen der Platte im Betrieb werden auf diese Spannungen zurückgeführt. Durch das Verringern der Spannungen in der Plattenmitte wird die Lebensdauer der Platte vorteilhaft verlängert. Somit ist auch beiPlate in operation the greatest voltages occur. The damage to the plate during operation is attributed to these voltages. By reducing the stresses in the middle of the plate, the life of the plate is advantageously extended. So is also at
Spitzendrücken bis zu 2000 bar eine einwandfreie Funktion der Platte gewährleistet.Peak pressures of up to 2000 bar ensure that the plate functions properly.
Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Platte in der Mitte eine geringere Dicke aufweist als in den äußeren Bereichen. Dadurch werden die Spannungen in der Mitte der Platte vermindert. Der Kraftfluß wird auf die äußeren Bereiche umgeleitet. Dadurch erfolgt eine Kraftumleitung an diejenigen Stellen, die weniger belastet werden. So wird der kritische Bereich in der Mitte der Platte entlastet. Eine besondere Bedeutung kommt der konkreten Gestalt der Platte zu. Dabei sind verschiedene Ausführungen möglich, die jedoch alle den gemeinsamen Grundgedanken der vorliegenden Erfindung verwirklichen. Je nach Plattentyp kann die Platte eine mittige Vertiefung zur Aufnahme eines Endes von einem der Kolben aufweisen. In einem solchen Fall ist die erfindungsgemäße Ausbildung der Plattenmitte innerhalb der Vertiefung angeordnet.A special embodiment of the invention is characterized in that the plate has a smaller thickness in the middle than in the outer areas. This reduces the tension in the middle of the plate. The power flow is redirected to the outer areas. As a result, the force is redirected to those points that are less stressed. This relieves the critical area in the middle of the plate. The concrete shape of the plate is particularly important. Various designs are possible, but all of them implement the common basic idea of the present invention. Depending on the type of plate, the plate may have a central recess for receiving one end of one of the pistons. In such a case, the design of the plate center according to the invention is arranged within the depression.
Eine weitere besondere Ausführungsart der Erfindung ist - 4 - dadurch gekennzeichnet, daß die Platte in der Mitte auf der von der Antriebswelle abgewandten Seite eine Aussparung in Form die Form eines Kegels hat, dessen Spitze zum Inneren der Platte gerichtet ist. Diese kegelige Ausbildung der Platte in der Mitte kann beispielsweise durch eineAnother special embodiment of the invention is - 4 - characterized in that the plate in the middle on the side facing away from the drive shaft has a recess in the form of a cone, the tip of which is directed towards the inside of the plate. This conical shape of the plate in the middle can be achieved, for example, by a
Drehbearbeitung hergestellt werden. Dies hat zum Vorteil, daß herkömmliche Platten einfach gemäß der vorliegenden Erfindung ausgebildet werden können. Darüber hinaus hat sich gezeigt, daß die Kegelform besonders gut geeignet ist, um die Spannungsverteilung in der Platte zu optimieren.Turning can be manufactured. This has the advantage that conventional plates can be easily formed in accordance with the present invention. In addition, it has been shown that the cone shape is particularly well suited to optimize the stress distribution in the plate.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Platte in der Mitte auf der zur Antriebswelle gewandten Seite eine Aussparung in Form eines Kegels hat, dessen Spitze zum Inneren der Platte gerichtet ist. Die Platte kann entweder auf ihrer Oberseite oder auf ihrer Unterseite kegelförmig ausgebildet sein. Die Entscheidung für die Ober- oder die Unterseite hängt von den auf die Platte wirkenden Kräften ab. Es hat sich im Rahmen der vorliegenden Erfindung erwiesen, daß es vorteilhaft ist, den Kegel insbesondere auf der Seite auszubilden, auf der die größten Kräfte auftreten. Dies wird in der Regel die Seite sein, auf der die Antriebswelle angeordnet ist.Another special embodiment of the invention is characterized in that the plate has a recess in the center on the side facing the drive shaft in the form of a cone, the tip of which is directed towards the inside of the plate. The plate can either be conical on its upper side or on its lower side. The decision for the top or bottom depends on the forces acting on the plate. It has proven in the context of the present invention that it is advantageous to form the cone in particular on the side on which the greatest forces occur. As a rule, this will be the side on which the drive shaft is arranged.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Platte in der Mitte auf der von der Antriebswelle abgewandten Seite und auf der zur Antriebswelle gewandten Seite jeweils eine Aussparung in Form eines Kegels hat, wobei die Spitzen der beiden Kegel zueinander gerichtet sind. Erfindungsgemäß werden die besten Ergebnisse erzielt, wenn sowohl die Oberseite als auch die Unterseite der Platte in der Mitte kegelförmig ausgebildet werden. Dadurch ergibt sich ein optimaler Spannungsverlauf im Betrieb. Die Verschleißfestigkeit einer derart gestalteten Platte ist vorteilhaft erhöht. Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Höhe des Kegels auf der von der Antriebswelle abgewandten Seite etwa 1/10 der Höhe des Kegels auf der zur Antriebswelle gewandten Seite beträgt. Das ist deshalb von Vorteil, weil auf der zur Antriebswelle gewandten Seite die größten Kräfte auftreten. Dies ist insbesondere der Fall, wenn die Zylinderräume nicht vollständig befüllt werden. Die genauen Abmessungen der Platte hängen unter anderem vom Pumpendruck und von der Anzahl der Lastwechsel pro Zeiteinheit ab.A further special embodiment of the invention is characterized in that the plate has a recess in the form of a cone in the middle on the side facing away from the drive shaft and on the side facing the drive shaft, the tips of the two cones being directed towards one another. According to the invention, the best results are achieved if both the top and the bottom of the plate are conical in the middle. This results in an optimal voltage curve during operation. The wear resistance of a plate designed in this way is advantageously increased. Another special embodiment of the invention is characterized in that the height of the cone on the side facing away from the drive shaft is approximately 1/10 of the height of the cone on the side facing the drive shaft. This is advantageous because the greatest forces occur on the side facing the drive shaft. This is particularly the case if the cylinder spaces are not completely filled. The exact dimensions of the plate depend, among other things, on the pump pressure and the number of load changes per unit of time.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Platte rund ist. Der Einsatz von rechteckigen Platten ist prinzipiell auch möglich, allerdings ist die runde Form wegen der günstigeren Krafteinleitung im Zusammenwirken mit der Antriebswelle vorzuziehen.Another special embodiment of the invention is characterized in that the plate is round. In principle, rectangular plates can also be used, but the round shape is preferable because of the more favorable force transmission in cooperation with the drive shaft.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Platte in der Mitte ein runde Vertiefung aufweist . Die runde Vertiefung in der Mitte der Platte dient zur Aufnahme des zur Antriebswelle gerichteten Endes eines der Kolben. Wenn das Ende des Kolbens in der Vertiefung aufgenommen ist, kann sich die Platte im wesentlichen nicht mehr relativ zur Antriebswelle verschieben.Another special embodiment of the invention is characterized in that the plate has a round recess in the middle. The round recess in the middle of the plate serves to receive the end of one of the pistons facing the drive shaft. When the end of the piston is received in the recess, the plate is essentially unable to move relative to the drive shaft.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Platte einen Bund aufweist. Der Bund bildet einen Anschlag für einen Käfig, der an dem Kolben befestigt ist und dazu dient, die Platte an dem Kolben zu halten.Another special embodiment of the invention is characterized in that the plate has a collar. The collar forms a stop for a cage, which is attached to the piston and serves to hold the plate on the piston.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß zwischen der Antriebswelle und der Platte ein Ring angeordnet ist. Der Ring dient zur Übertragung der Kräfte von der exzentrisch ausgebildeten Antriebswelle auf die Platte. Vorteilhaft ist der Ring gleitend auf der Antriebswelle gelagert. Dabei kann der Ring entweder zylindrisch oder polygonförmig ausgebildet sein.Another special embodiment of the invention is characterized in that a ring is arranged between the drive shaft and the plate. The ring is used for Transfer of forces from the eccentrically designed drive shaft to the plate. The ring is advantageously slidably mounted on the drive shaft. The ring can be either cylindrical or polygonal.
Die vorliegende Erfindung hat allgemein den Vorteil, daß der Grundgedanke der vorliegenden Erfindung in einfacher Art und Weise auf bestehende Radialkolbenpumpen angewendet werden kann. Darüber hinaus wird die Bauteilfestigkeit, insbesondere bei einer Nullförderung im Saughub, erhöht.The present invention has the general advantage that the basic idea of the present invention can be applied to existing radial piston pumps in a simple manner. In addition, the component strength is increased, especially with zero delivery in the suction stroke.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus den Unteransprüchen sowie der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnungen ein Ausführungsbeispiel im Einzelnen beschrieben ist. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein. Ein Weg zum Ausführen der beanspruchten Erfindung ist nachfolgend anhand der Zeichnungen im Einzelnen erläutert.Further advantages, features and details of the invention emerge from the subclaims and the following description, in which an exemplary embodiment is described in detail with reference to the drawings. The features mentioned in the claims and in the description can each be essential to the invention individually or in any combination. One way of carrying out the claimed invention is explained in detail below with reference to the drawings.
Figur 1 zeigt eine Schnittdarstellung einer Radialkolbenpumpe ;Figure 1 shows a sectional view of a radial piston pump;
Figur 2 zeigt eine Platte gemäß der vorliegenden Erfindung;Figure 2 shows a plate according to the present invention;
Figur 3 zeigt eine vergrößerte Ansicht der Einzelheit X aus Figur 1 im Maßstab 20:1;FIG. 3 shows an enlarged view of the detail X from FIG. 1 on a scale of 20: 1;
Figur 4 zeigt eine vergrößerte Ansicht der Einzelheit Y aus Figur 1 im Maßstab 20:1.FIG. 4 shows an enlarged view of detail Y from FIG. 1 on a 20: 1 scale.
Die Figur 1 zeigt eine Radialkolbenpumpe zur KraftStoffhochdruckversorgung bei Kraftstoffeinspritzsyste en von Brennkraftmaschinen. Die Radialkolbenpumpe ist mit einer integrierten Bedarfsmengenregelung ausgestattet. Die Kraftstoffzufuhr und Dimensionierung erfolgt über eine nicht dargestellte Zumesseinheit .FIG. 1 shows a radial piston pump for supplying high-pressure fuel Fuel injection systems of internal combustion engines. The radial piston pump is equipped with an integrated demand control. The fuel supply and dimensioning takes place via a metering unit, not shown.
Die erfindungsgemäße Radialkolbenpumpe wird insbesondere in Common-Rail-Einspritzsystemen zur KraftstoffVersorgung von Dieselmotoren eingesetzt. Dabei bedeutet "common rail" soviel wie "gemeinsame Leitung" oder "gemeinsame Schiene". Im Gegensatz zu herkömmlichen Hochdruckeinspritzsystemen, in denen der Kraftstoff über getrennte Leitungen zu den einzelnen Brennräumen gefördert wird, werden die Einspritzdüsen in Common-Rail-Einspritzsystemen aus einer gemeinsamen Leitung gespeist.The radial piston pump according to the invention is used in particular in common rail injection systems for supplying fuel to diesel engines. "Common rail" means "common line" or "common rail". In contrast to conventional high-pressure injection systems, in which the fuel is delivered to the individual combustion chambers via separate lines, the injection nozzles in common-rail injection systems are fed from a common line.
Die in der Figur 1 gezeigte Radialkolbenpumpe umfaßt eine in einem Pumpengehäuse 2 gelagerte Antriebswelle 4 mit einem exzentrisch ausgebildeten Wellenabschnitt 6. Auf dem exzentrischen Wellenabschnitt 6 ist ein polygonförmiger Ring 8 vorgesehen, gegenüber dem der Wellenabschnitt 6 drehbar ist. Der Ring 8 umfaßt drei jeweils um 120° zueinander versetzte Abflachungen 10 gegen die sich jeweils ein Kolben 12 abstützt . Statt des polygonförmigen Rings 8 kann auch ein zylinderförmiger Ring verwendet werden. Die Kolben 12 sind jeweils in einem Zylinderraum 18 zur Antriebswelle 4 in radialer Richtung hin- und herbewegbar aufgenommen . An dem zur Antriebswelle 4 hin gerichteten Ende der Kolben 12 ist jeweils eine Platte 14 befestigt. Die Platten 14 sind jeweils durch einen Käfig 15 an den zugehörigen Kolben 12 gehalten. Zudem sind die Platten 14 jeweils durch eine Feder 16 gegen den Ring 8 vorgespannt. Wie in Figur 1 zu sehen ist, befinden sich die Platten 14 in Anlage mit den Abflachungen 10 des Rings 8. - 8 -The radial piston pump shown in FIG. 1 comprises a drive shaft 4 mounted in a pump housing 2 with an eccentrically designed shaft section 6. A polygonal ring 8 is provided on the eccentric shaft section 6, with respect to which the shaft section 6 can be rotated. The ring 8 comprises three flats 10, each offset by 120 ° to each other, against which a piston 12 is supported. Instead of the polygonal ring 8, a cylindrical ring can also be used. The pistons 12 are each received in a cylinder space 18 so that they can move back and forth in the radial direction relative to the drive shaft 4. A plate 14 is fastened to the end of the pistons 12 facing the drive shaft 4. The plates 14 are each held by a cage 15 on the associated piston 12. In addition, the plates 14 are each biased against the ring 8 by a spring 16. As can be seen in FIG. 1, the plates 14 are in contact with the flats 10 of the ring 8. - 8th -
In Figur 2 ist die erfindungsgemäße Platte 14 alleine gezeigt. Die in Figur 2 im Querschnitt dargestellte Platte hat die Form eines Kreiszylinders mit einem Durchmesser von etwa 15 Millimetern und einer Höhe von etwa 5 Millimetern. Auf der Oberseite der Platte 14 ist mittig eine ebenfalls kreiszylinderförmige Vertiefung 20 mit einer abgerundeten Kante 21 ausgespart. Die Vertiefung 20 dient zur Aufnahme von einem Ende eines der Kolben 12. An der Platte 14 ist zudem ein Bund 22 vorgesehen, dessen oberer Rand 23 angeschrägt ist und in die Oberseite der Platte 14 übergeht. An der Unterseite der Platte 14 ist eine Abfasung 24 vorgesehen.In Figure 2, the plate 14 according to the invention is shown alone. The plate shown in cross section in FIG. 2 has the shape of a circular cylinder with a diameter of approximately 15 millimeters and a height of approximately 5 millimeters. A likewise circular-cylindrical depression 20 with a rounded edge 21 is cut out in the center on the top of the plate 14. The recess 20 serves to receive one end of one of the pistons 12. A collar 22 is also provided on the plate 14, the upper edge 23 of which is chamfered and merges into the top of the plate 14. A chamfer 24 is provided on the underside of the plate 14.
Figur 3 zeigt die Einzelheit X aus Figur 1 im Maßstab 20:1. In der vergrößerten Ansicht sieht man, daß die Platte 14 auf der der Vertiefung 20 gegenüberliegenden Unterseite mittig eine kegelförmigen Aussparung 25 aufweist. Die Höhe H der kegelförmigen Aussparung 25 beträgt etwa 0,2 Millimeter. Der Durchmesser der kegelförmigen Aussparung 25 beträgt etwa 2,8 Millimeter.Figure 3 shows the detail X from Figure 1 on a scale of 20: 1. In the enlarged view it can be seen that the plate 14 has a conical recess 25 in the center on the underside opposite the depression 20. The height H of the conical recess 25 is approximately 0.2 millimeters. The diameter of the conical recess 25 is approximately 2.8 millimeters.
Figur 4 zeigt die Einzelheit Y aus Figur 1 im Maßstab 20:1. In der vergrößerten Ansicht sieht man, daß die Platte 14 in der Mitte der Vertiefung 20 eine kegelförmigen Aussparung 26 aufweist. Die Höhe h der kegelförmigen Aussparung 26 beträgt etwa 0,02 Millimeter. Figure 4 shows the detail Y from Figure 1 on a scale of 20: 1. In the enlarged view it can be seen that the plate 14 has a conical recess 26 in the center of the recess 20. The height h of the conical recess 26 is approximately 0.02 millimeters.

Claims

9 -Patentansprüche 9 -patent claims
1. Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-1. Radial piston pump for high-pressure fuel supply in fuel injection systems of internal combustion engines, in particular in a common
Rail-Einspritzsystem, mit einer in einem Pumpengehäuse (2) gelagerten Antriebswelle (4) , die exzentrisch ausgebildet ist oder in Umfangsrichtung nockenartige Erhebungen aufweist , und mit vorzugsweise mehreren bezüglich der Antriebswelle (4) radial in einem jeweiligen Zylinderraum (18) angeordneten Kolben, an deren zur Antriebswelle (4) gewandten Enden jeweils eine Platte (14) angebracht ist, wobei die Kolben (12) durch Drehen der Antriebswelle (4) in dem jeweiligen Zylinderraum (18) in radialer Richtung hin und her bewegbar sind, dadurch gekennzeichnet, daß die Platte (14) in der Mitte so ausgebildet ist, daß die im Betrieb auftretenden Spannungen an dieser Stelle verringert werden.Rail injection system, with a drive shaft (4) mounted in a pump housing (2), which is eccentric or has cam-like elevations in the circumferential direction, and preferably with a plurality of pistons arranged radially with respect to the drive shaft (4) in a respective cylinder space (18), A plate (14) is attached to each of the ends facing the drive shaft (4), the pistons (12) being movable back and forth in the respective cylinder space (18) by rotating the drive shaft (4), characterized in that that the plate (14) is formed in the middle so that the stresses occurring during operation are reduced at this point.
2. Radialkolbenpumpe nach Anspruch 1 , dadurch gekennzeichnet, daß die Platte (14) in der Mitte eine geringere Dicke aufweist als in den äußeren Bereichen.2. Radial piston pump according to claim 1, characterized in that the plate (14) has a smaller thickness in the middle than in the outer regions.
3. Radialkolbenpumpe nach Anspruch 2 , dadurch gekennzeichnet, daß die Platte (14) in der Mitte auf der von der Antriebswelle (4) abgewandten Seite eine Aussparung in Form eines Kegels (26) hat, dessen Spitze zum Inneren der Platte (14) gerichtet ist. - 10 -3. Radial piston pump according to claim 2, characterized in that the plate (14) in the middle on the side facing away from the drive shaft (4) has a recess in the form of a cone (26), the tip of which is directed towards the inside of the plate (14) is. - 10 -
4. Radialkolbenpumpe nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß die Platte (14) in der Mitte auf der zur Antriebswelle (4) gewandten Seite eine Aussparung in Form eines Kegels (25) hat, dessen Spitze zum Inneren der Platte (14) gerichtet ist.4. Radial piston pump according to one of claims 1 or 2, characterized in that the plate (14) in the middle on the side facing the drive shaft (4) has a recess in the form of a cone (25), the tip of which towards the inside of the plate ( 14) is directed.
5. Radialkolbenpumpe nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß die Platte (14) in der Mitte auf der von der Antriebswelle (4) abgewandten Seite und auf der zur Antriebswelle (4) gewandten5. Radial piston pump according to one of claims 1 or 2, characterized in that the plate (14) in the middle on the side facing away from the drive shaft (4) and on the side facing the drive shaft (4)
Seite jeweils eine Aussparung in Form eines Kegels (25, 26) hat, wobei die Spitzen der beiden Kegel (25, 26) zueinander gerichtet sind.Each side has a recess in the form of a cone (25, 26), the tips of the two cones (25, 26) facing each other.
6. Radialkolbenpumpe nach Anspruch 5, dadurch gekennzeichnet, daß die Höhe des Kegels (26) auf der von der Antriebswelle (4) abgewandten Seite etwa 1/10 der Höhe des Kegels (25) auf der zur Antriebswelle (4) gewandten Seite beträgt.6. Radial piston pump according to claim 5, characterized in that the height of the cone (26) on the side facing away from the drive shaft (4) is approximately 1/10 of the height of the cone (25) on the side facing the drive shaft (4).
7. Radialkolbenpumpe nach einem der vorhergehenden7. Radial piston pump according to one of the preceding
Ansprüche, dadurch gekennzeichnet, daß die Platte (14) rund ist.Claims, characterized in that the plate (14) is round.
8. Radialkolbenpumpe nach einem der vorhergehenden8. Radial piston pump according to one of the preceding
Ansprüche, dadurch gekennzeichnet, daß die Platte (14) in der Mitte ein runde Vertiefung (20) aufweist.Claims, characterized in that the plate (14) has a round recess (20) in the middle.
9. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Platte (14) einen Bund (22) aufweist.9. Radial piston pump according to one of the preceding claims, characterized in that the plate (14) has a collar (22).
10. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zwischen der Antriebswelle (4) und der Platte (14) ein Ring (8) angeordnet ist . 10. Radial piston pump according to one of the preceding claims, characterized in that a ring (8) is arranged between the drive shaft (4) and the plate (14).
EP99907314A 1998-04-01 1999-02-09 Radial piston pump for high-pressure fuel supply Expired - Lifetime EP1068448B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19814506 1998-04-01
DE19814506A DE19814506A1 (en) 1998-04-01 1998-04-01 Radial piston pump for high-pressure fuel supply
PCT/DE1999/000344 WO1999050555A1 (en) 1998-04-01 1999-02-09 Radial piston pump for high-pressure fuel supply

Publications (2)

Publication Number Publication Date
EP1068448A1 true EP1068448A1 (en) 2001-01-17
EP1068448B1 EP1068448B1 (en) 2003-07-30

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EP99907314A Expired - Lifetime EP1068448B1 (en) 1998-04-01 1999-02-09 Radial piston pump for high-pressure fuel supply

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US (1) US6350107B1 (en)
EP (1) EP1068448B1 (en)
JP (1) JP4288000B2 (en)
DE (2) DE19814506A1 (en)
WO (1) WO1999050555A1 (en)

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Publication number Publication date
US6350107B1 (en) 2002-02-26
DE59906437D1 (en) 2003-09-04
JP2002510015A (en) 2002-04-02
JP4288000B2 (en) 2009-07-01
EP1068448B1 (en) 2003-07-30
WO1999050555A1 (en) 1999-10-07
DE19814506A1 (en) 1999-10-14

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