EP1068448B1 - Radial piston pump for high-pressure fuel supply - Google Patents
Radial piston pump for high-pressure fuel supply Download PDFInfo
- Publication number
- EP1068448B1 EP1068448B1 EP99907314A EP99907314A EP1068448B1 EP 1068448 B1 EP1068448 B1 EP 1068448B1 EP 99907314 A EP99907314 A EP 99907314A EP 99907314 A EP99907314 A EP 99907314A EP 1068448 B1 EP1068448 B1 EP 1068448B1
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- 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.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
Definitions
- the invention relates to a radial piston pump for High-pressure fuel supply in fuel injection systems of internal combustion engines, especially in a common rail injection system, with one stored in a pump housing Drive shaft which is eccentric or in Has circumferential cam-like elevations, and with preferably several radially in relation to the drive shaft a piston arranged in each cylinder space, at the ends facing the drive shaft each have a plate is attached, the piston by rotating the Radial drive shaft in the respective cylinder space Direction can be moved back and forth.
- the invention is therefore based on the problem of a Radial piston pump to provide the above overcomes the disadvantages mentioned.
- the plate is supposed to work wear-free in operation, even at high ones To press. In doing so, the proper operation of the Radial piston pump even with partial filling of the cylinder chambers to be guaranteed.
- the radial piston pump according to the invention should withstand a pump pressure of up to 2000 bar.
- the problem is with a radial piston pump High-pressure fuel supply in fuel injection systems of internal combustion engines, especially in a common rail injection system, with one stored in a pump housing Drive shaft which is eccentric or in Has circumferential cam-like elevations, and with preferably several radially in one with respect to the drive shaft Pistons arranged in each cylinder chamber, at the for Drive shaft facing ends each have a plate is attached, the piston by rotating the Radial drive shaft in the respective cylinder space Direction can be moved back and forth, solved in that the Plate in the middle is designed so that in operation occurring voltages can be reduced at this point.
- the Plate in the middle is designed so that in operation occurring voltages can be reduced at this point.
- the plate in the middle is less Thickness than in the outer areas. This will the stresses in the middle of the plate are reduced. The Power flow is redirected to the outer areas. Thereby there is a force redirection to those places be less burdened. So the critical area in relieved the middle of the plate.
- a special meaning comes to the concrete shape of the plate.
- the plate can be one central recess for receiving one end of one of the Have pistons. In such a case it is Training the plate center according to the invention within Well arranged.
- Another special embodiment of the invention is 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 produced, for example, by turning. This has the advantage that conventional plates can be easily formed in accordance with the present invention.
- the cone shape is particularly well suited to optimize the stress distribution in the plate.
- Another special embodiment of the invention is characterized in that the plate in the middle on the a recess in the form facing the drive shaft has a cone, the tip of which is towards the inside of the plate is directed.
- the plate can either be on its top or be conical on its underside. The Deciding on the top or bottom depends on the forces acting on the plate. It has in the Within the scope of the present invention it has been proven that is advantageous, the cone in particular on the side to train on which the greatest forces occur. This will usually be the side on which the drive shaft is arranged.
- Another special embodiment of the invention is characterized in that the plate in the middle on the away from the drive shaft and on the Drive shaft facing side each have a recess in Has the shape of a cone, with the tips of the two cones are directed towards each other. According to the best results if both the top and also the bottom of the plate is conical in the middle be formed. This results in an optimal one 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 at that of the side facing away from the drive shaft is about 1/10 of the height of the Cone on the side facing the drive shaft. This is an advantage because on the drive shaft facing the greatest forces occur. This is especially the case when the cylinder rooms are not be 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.
- Another special embodiment of the invention is characterized in that the plate is round.
- the In principle, rectangular plates are also used possible, but the round shape is because of the cheaper introduction of force in cooperation with the Prefer drive shaft.
- Another special embodiment of the invention is characterized in that the plate in the middle has a round recess.
- the round depression in the The middle of the plate is used to hold the drive shaft directed end of one of the pistons. If the end of the Piston is received in the recess, the Plate essentially no longer relative to the drive shaft move.
- Another special embodiment of the invention is characterized in that the plate has a collar.
- the federal government forms a stop for a cage, which on the Is attached to the piston and serves to attach the plate to the To keep pistons.
- Another special embodiment of the invention is characterized in that between the drive shaft and a ring is arranged on the plate.
- the ring is used for Transfer of forces from the eccentrically trained Drive shaft to the plate.
- the ring is advantageous slidably mounted on the drive shaft.
- the Ring either cylindrical or polygonal his.
- the present invention generally has the advantage that the basic idea of the present invention in simpler Way applied to existing radial piston pumps can be.
- component strength especially in the event of zero delivery in the suction stroke.
- Figure 1 shows a radial piston pump High pressure fuel supply at Fuel injection systems for internal combustion engines.
- the Radial piston pump is with an integrated Required quantity control.
- the fuel supply and dimensioning takes place via a not shown Metering unit.
- the radial piston pump according to the invention is particularly in Common rail fuel injection systems for Diesel engines used.
- “Common rail” means as much as “common management” or “common rail”.
- Injectors in common rail injection systems from one fed common line Injectors in common rail injection systems from one fed 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 chamber 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 by a spring 16 against the ring 8. As can be seen in FIG. 1, the plates 14 are in contact with the flats 10 of the ring 8.
- the plate 14 according to the invention is alone shown.
- the plate shown in cross section in FIG. 2 has the shape of a circular cylinder with a diameter of about 15 millimeters and a height of about 5 millimeters.
- On the top of the plate 14 is also in the middle circular cylindrical recess 20 with a rounded Edge 21 recessed.
- the recess 20 is used for receiving One end of one of the pistons 12 is on the plate 14 a collar 22 is also provided, the upper edge 23 is chamfered and into the top of the plate 14 transforms. There is a chamfer on the underside of the plate 14 24 provided.
- Figure 3 shows the detail X from Figure 1 on a scale of 20: 1.
- the plate 14 on the underside opposite the depression 20 has a conical recess 25 in the center.
- the height H of the conical recess 25 is approximately 0.2 Millimeter.
- the diameter of the conical recess 25 is about 2.8 millimeters.
- Figure 4 shows the detail Y from Figure 1 on a scale of 20: 1.
- the plate 14 in a conical recess in the middle of the recess 20 26 has.
- the height h of the conical recess 26 is approximately 0.02 millimeters.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Fuel-Injection Apparatus (AREA)
- Details Of Reciprocating Pumps (AREA)
Description
Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei 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 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.The invention relates to a radial piston pump for High-pressure fuel supply in fuel injection systems of internal combustion engines, especially in a common rail injection system, with one stored in a pump housing Drive shaft which is eccentric or in Has circumferential cam-like elevations, and with preferably several radially in relation to the drive shaft a piston arranged in each cylinder space, at the ends facing the drive shaft each have a plate is attached, the piston by rotating the Radial drive shaft in the respective cylinder space Direction can be moved back and forth.
Bei einer derartigen innen abgestützten Radialkolbenpumpe, die beispielsweise aus der DE 44 01 074 A1 oder der DE 196 35 164 bekannt ist, 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 Kraftstoffmengen 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.With such an internally supported radial piston pump, the for example from DE 44 01 074 A1 or DE 196 35 164 is known, has at the ends of the pistons attached plate contact with the drive shaft. The pistons are caused by the eccentricity of the drive shaft or by cam-like elevations in succession on the drive shaft a back and forth movement. Doing so will rotating drive shaft on the pistons depending on the Relative amounts of fuel drawn into the cylinder chambers great forces are applied to the fuel with pressure apply. When the fuel is drawn in, the pistons with the plate usually by a spring against the Drive shaft pressed.
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 conventionally used plates in operation, especially in the middle, often damaged. This Signs of wear can lead to the plate breaking and are therefore undesirable. The function of the radial piston pump is no longer guaranteed with a damaged plate. Replacing a damaged plate is time-consuming because the radial piston pump disassembled and the drive shaft must be removed to get to the damaged plate get hold.
Der Erfindung liegt daher das Problem zugrunde, eine 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 der Radialkolbenpumpe auch bei Teilbefüllung der Zylinderräume gewährleistet sein. Die erfindungsgemäße Radialkolbenpumpe soll einen Pumpendruck von bis zu 2000 bar aushalten.The invention is therefore based on the problem of a Radial piston pump to provide the above overcomes the disadvantages mentioned. In particular, should Damage to the plate can be prevented. The plate is supposed to work wear-free in operation, even at high ones To press. In doing so, the proper operation of the Radial piston pump even with partial filling of the cylinder chambers to be guaranteed. The radial piston pump according to the invention should withstand a pump pressure of up to 2000 bar.
Das Problem wird durch die in dem unabhängigen Patentanspruch offenbarte Radialkolbenpumpe gelöst. Besondere Ausführungsarten der Erfindung sind in den Unteransprüchen offenbart.The problem is explained in the independent claim disclosed radial piston pump solved. Special Embodiments of the invention are in the subclaims disclosed.
Das Problem ist bei einer Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei 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 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, 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 der 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 bei Spitzendrücken bis zu 2000 bar eine einwandfreie Funktion der Platte gewährleistet.The problem is with a radial piston pump High-pressure fuel supply in fuel injection systems of internal combustion engines, especially in a common rail injection system, with one stored in a pump housing Drive shaft which is eccentric or in Has circumferential cam-like elevations, and with preferably several radially in one with respect to the drive shaft Pistons arranged in each cylinder chamber, at the for Drive shaft facing ends each have a plate is attached, the piston by rotating the Radial drive shaft in the respective cylinder space Direction can be moved back and forth, solved in that the Plate in the middle is designed so that in operation occurring voltages can be reduced at this point. When examining with the help of the finite element method it has been found that in the middle of the Plate in operation the greatest voltages occur. The Damage to the plate during operation is due to this Tensions reduced. By reducing the Tension in the middle of the plate will increase the lifespan of Advantageously extended plate. So is also at Peak pressures up to 2000 bar function perfectly the plate ensures.
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.This is a special embodiment of the invention characterized in that the plate in the middle is less Thickness than in the outer areas. This will the stresses in the middle of the plate are reduced. The Power flow is redirected to the outer areas. Thereby there is a force redirection to those places be less burdened. So the critical area in relieved the middle of the plate. A special meaning comes to the concrete shape of the plate. Are different versions possible, but all the common principles of the present invention realize. Depending on the type of plate, the plate can be one central recess for receiving one end of one of the Have pistons. In such a case it is Training the plate center according to the invention within Well arranged.
Eine weitere besondere Ausführungsart der Erfindung ist
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 eine
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.Another special embodiment of the invention is
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 produced, for example, by turning. 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 in the middle on the a recess in the form facing the drive shaft has a cone, the tip of which is towards the inside of the plate is directed. The plate can either be on its top or be conical on its underside. The Deciding on the top or bottom depends on the forces acting on the plate. It has in the Within the scope of the present invention it has been proven that is advantageous, the cone in particular on the side to train on which the greatest forces occur. This will usually 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. Another special embodiment of the invention is characterized in that the plate in the middle on the away from the drive shaft and on the Drive shaft facing side each have a recess in Has the shape of a cone, with the tips of the two cones are directed towards each other. According to the best results if both the top and also the bottom of the plate is conical in the middle be formed. This results in an optimal one Voltage curve during operation. The wear resistance of a plate designed in this way is advantageously increased.
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.Another special embodiment of the invention is characterized in that the height of the cone at that of the side facing away from the drive shaft is about 1/10 of the height of the Cone on the side facing the drive shaft. This is an advantage because on the drive shaft facing the greatest forces occur. This is especially the case when the cylinder rooms are not be 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. The In principle, rectangular plates are also used possible, but the round shape is because of the cheaper introduction of force in cooperation with the Prefer 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 in the middle has a round recess. The round depression in the The middle of the plate is used to hold the drive shaft directed end of one of the pistons. If the end of the Piston is received in the recess, the Plate essentially no longer relative to the drive shaft move.
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 federal government forms a stop for a cage, which on the Is attached to the piston and serves to attach the plate to the To keep pistons.
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 between the drive shaft and a ring is arranged on the plate. The ring is used for Transfer of forces from the eccentrically trained Drive shaft to the plate. The ring is advantageous slidably mounted on the drive shaft. The Ring either cylindrical or polygonal his.
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 generally has the advantage that the basic idea of the present invention in simpler Way applied to existing radial piston pumps can be. In addition, component strength, especially in the event of 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.
- Figur 1
- zeigt eine Schnittdarstellung einer Radialkolbenpumpe;
Figur 2- zeigt eine Platte gemäß der vorliegenden Erfindung;
- Figur 3
- zeigt eine vergrößerte Ansicht der Einzelheit X aus Figur 1 im Maßstab 20:1;
- Figur 4
- zeigt eine vergrößerte Ansicht der Einzelheit Y aus Figur 1 im Maßstab 20:1.
- Figure 1
- shows a sectional view of a radial piston pump;
- Figure 2
- shows a plate according to the present invention;
- Figure 3
- shows an enlarged view of the detail X of Figure 1 on a scale of 20: 1;
- Figure 4
- shows an enlarged view of detail Y from Figure 1 on a scale of 20: 1.
Die Figur 1 zeigt eine Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen. Die Radialkolbenpumpe ist mit einer integrierten Bedarfsmengenregelung ausgestattet. Die Kraftstoffzufuhr und Dimensionierung erfolgt über eine nicht dargestellte Zumesseinheit.Figure 1 shows a radial piston pump High pressure fuel supply at Fuel injection systems for internal combustion engines. The Radial piston pump is with an integrated Required quantity control. The fuel supply and dimensioning takes place via a not shown Metering unit.
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 particularly in Common rail fuel injection systems for Diesel engines used. "Common rail" means as much as "common management" or "common rail". In contrast to conventional high pressure injection systems, in which the fuel via separate lines to the individual combustion chambers is promoted Injectors in common rail injection systems from one fed 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. The radial piston pump shown in FIG. 1 comprises a drive shaft 4 mounted in a
A
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
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
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 you can see that the
Claims (8)
- Radial piston pump for fuel high-pressure 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 which is designed eccentrically or has cam-like elevations in the circumferential direction, and with preferably a plurality of pistons which are arranged in a respective cylinder space (18) radially with respect to the drive shaft (4) and at the ends of which, facing the drive shaft (4), a plate (14) is mounted in each case, the pistons (12) being moveable back and forth in the radial direction in the respective cylinder space (18) as a result of the rotation of the drive shaft (4), characterized in that the plate (14) has in the middle, on the side facing away from the drive shaft (4), a clearance in the form of a cone (26), the apex of which is directed towards the inside of the plate (14), in order to reduce the stresses which occur in the middle of the plate during operation.
- Radial piston pump according to the pre-characterizing clause of Claim 1, characterized in that the plate (14) has in the middle, on the side facing the drive shaft (4), a clearance in the form of a cone (25), the apex of which is directed towards the inside of the plate (14).
- Radial piston pump according to the pre-characterizing clause of Claim 1, characterized in that the plate (14) has in the middle, on the side facing away from the drive shaft (4) and on the side facing the drive shaft (4), in each case a clearance in the form of a cone (25, 26), the apices of the two cones (25, 26) being directed towards one another.
- Radial piston pump according to Claim 3, characterized in that the height of the cone (26) on the side facing away from the drive shaft (4) is about 1/10 of the height of the cone (25) on the side facing the drive shaft (4).
- Radial piston pump according to one of the preceding claims, characterized in that the plate (14) is round.
- Radial piston pump according to one of the preceding claims, characterized in that the plate (14) has a round depression (20) in the middle.
- Radial piston pump according to one of the preceding claims, characterized in that the plate (14) has a collar (22).
- 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).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19814506A DE19814506A1 (en) | 1998-04-01 | 1998-04-01 | Radial piston pump for high-pressure fuel supply |
| DE19814506 | 1998-04-01 | ||
| 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 EP1068448A1 (en) | 2001-01-17 |
| EP1068448B1 true EP1068448B1 (en) | 2003-07-30 |
Family
ID=7863182
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99907314A Expired - Lifetime EP1068448B1 (en) | 1998-04-01 | 1999-02-09 | Radial piston pump for high-pressure fuel supply |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US6350107B1 (en) |
| EP (1) | EP1068448B1 (en) |
| JP (1) | JP4288000B2 (en) |
| DE (2) | DE19814506A1 (en) |
| WO (1) | WO1999050555A1 (en) |
Families Citing this family (35)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10044997A1 (en) * | 2000-09-11 | 2002-03-21 | Schaeffler Waelzlager Ohg | Compression plate of radial piston pump has piston rest with conical or curved profile |
| DE10108703C1 (en) * | 2001-02-23 | 2002-11-21 | Ats Spartec Inc | Radial piston pump, with tandem pump stages, has radial pistons supported by bearing sleeves in two identical pump housings |
| US6461117B2 (en) * | 2001-02-27 | 2002-10-08 | International Truck Intellectual Property Company, L.L.C. | Reversible volume oil pump |
| DE10110658C1 (en) * | 2001-03-06 | 2002-07-11 | Lucas Automotive Gmbh | Pump assembly, for a vehicle brake system, has one liner moved by the pistons which acts on the other liners and give pressure compensation in the brake circuits |
| JP2003074439A (en) * | 2001-06-19 | 2003-03-12 | Denso Corp | Fuel injection pump |
| WO2003014569A1 (en) * | 2001-08-08 | 2003-02-20 | Crt Common Rail Technologies Ag | High pressure feed pump |
| DE10147981A1 (en) * | 2001-09-28 | 2003-04-24 | Siemens Ag | Connecting element for piston movable inside cylinder by means of re-adjusting element, consists of two parts with first part in piston cavity |
| DE10150351A1 (en) * | 2001-10-15 | 2003-05-08 | Bosch Gmbh Robert | Pump element and piston pump for high-pressure fuel generation |
| JP3733928B2 (en) * | 2002-05-28 | 2006-01-11 | 三菱電機株式会社 | High pressure fuel supply device |
| DE10247645A1 (en) * | 2002-10-11 | 2004-04-22 | Robert Bosch Gmbh | Radial piston pump for high pressure fuel supply has at least one lubricant pocket in plates |
| DE10249818B4 (en) * | 2002-10-24 | 2005-10-20 | Daimler Chrysler Ag | Surface of a body on which another body in a preferred sliding direction against each other can be slidably arranged |
| GB0311814D0 (en) * | 2003-05-22 | 2003-06-25 | Delphi Tech Inc | Pump assembly |
| DE10326863A1 (en) * | 2003-06-14 | 2004-12-30 | Daimlerchrysler Ag | Radial piston pump for fuel high pressure generation in fuel injection systems of internal combustion engines |
| DE60309145T2 (en) * | 2003-06-18 | 2007-08-16 | Delphi Technologies, Inc., Troy | Drive arrangement for a pump |
| DE10347715A1 (en) * | 2003-10-14 | 2005-05-12 | Zahnradfabrik Friedrichshafen | Radial piston pump |
| DE102004018163A1 (en) * | 2004-04-14 | 2005-11-10 | Siemens Ag | Radial piston pump |
| JP4467469B2 (en) | 2005-06-08 | 2010-05-26 | ボッシュ株式会社 | Fuel supply pump and tappet structure |
| DE102006045897B4 (en) * | 2006-09-28 | 2008-09-11 | Continental Automotive Gmbh | Radial piston pump for high-pressure fuel supply |
| DE102006048605B3 (en) * | 2006-10-13 | 2008-04-17 | Siemens Ag | Radial piston pump for fuel supply in fuel injection system of internal combustion engine, has driving shaft which is mounted in pump housing with eccentric cam and piston arranged with respect to driving shaft in cylinder chamber |
| EP2048359B1 (en) * | 2007-10-12 | 2015-06-24 | Delphi International Operations Luxembourg S.à r.l. | Improvements relating to fuel pumps |
| DE102007060772A1 (en) | 2007-12-17 | 2009-06-18 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump |
| CN102027226B (en) | 2008-05-14 | 2014-04-02 | 株式会社小金井精机制作所 | Diesel pump |
| DE102008001858A1 (en) | 2008-05-19 | 2009-11-26 | Robert Bosch Gmbh | Plug-in pump has hollow cylinder with cylinder head and piston which is included in hollow cylinder, where piston is limited by end of pump chamber and is overlapped by another end of hollow cylinder |
| DE102008002101A1 (en) | 2008-05-30 | 2009-12-03 | Robert Bosch Gmbh | Radial piston pump for feeding fuel into combustion chamber of internal combustion engine, has through-hole for displacing and play-freely contacting driver in direction, where hole is radially outwardly displaced in another direction |
| DE102008040239A1 (en) | 2008-07-08 | 2010-01-14 | Robert Bosch Gmbh | Radial piston pump for feeding fuel into combustion chamber of internal combustion engine, has piston accommodated in hollow cylinder, and drive shaft comprising cross hole that encloses guide column sliding in longitudinal direction |
| DE102008041449A1 (en) | 2008-08-22 | 2010-02-25 | Robert Bosch Gmbh | High pressure pump for supplying fuel in internal combustion engine, has cylinder heads and drive shaft, which are connected with pump housing rotated by one hundred eighty degree according to position of central axis |
| DE102008042068A1 (en) | 2008-09-12 | 2010-03-18 | Robert Bosch Gmbh | Piston pump for fuel system of internal combustion engine, has crankpin comprising cylindrical lateral surface that is formed on side of crankpin by groove base of notch, which has depth extending on both sides in circumferential direction |
| GB0818811D0 (en) * | 2008-10-14 | 2008-11-19 | Delphi Tech Inc | Fuel pump assembly |
| DE102008057089A1 (en) | 2008-11-13 | 2010-05-20 | Continental Mechanical Components Germany Gmbh | Pump unit for a high-pressure pump |
| DE102008043993B3 (en) * | 2008-11-21 | 2010-04-29 | Thielert Aircraft Engines Gmbh | Common-rail high-pressure pump |
| DE102009002529A1 (en) | 2009-04-21 | 2010-10-28 | Robert Bosch Gmbh | Injection pump for internal combustion engine, has sliding bearing whose surface is formed with groove, and glide layer made from PTFE or polyetheretherketone and anchored in groove |
| DE102018211654A1 (en) * | 2018-07-12 | 2020-01-16 | Robert Bosch Gmbh | Piston pump, in particular high-pressure fuel pump for an injection system of an internal combustion engine |
| RU191730U1 (en) * | 2019-06-06 | 2019-08-19 | Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" | HIGH PRESSURE FUEL PUMP |
| RU202059U1 (en) * | 2020-09-18 | 2021-01-28 | Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" | FUEL INJECTION PUMP |
| JP2023013759A (en) * | 2021-07-16 | 2023-01-26 | 株式会社Soken | supply pump |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3628425A (en) * | 1968-12-13 | 1971-12-21 | Messrs Mitsubishi Jukogyo Kk | Fluid motor-pump construction |
| DE2061960B2 (en) * | 1970-12-16 | 1974-01-17 | Fichtel & Sachs Ag, 8720 Schweinfurt | Radial piston pump with throttle device to limit the delivery volume |
| US4075932A (en) * | 1972-01-07 | 1978-02-28 | Karl Eickmann | Rotor, pistons, piston shoes and associated means in fluid handling devices |
| GB1436752A (en) * | 1973-05-09 | 1976-05-26 | Eickmann K | Fluid handling devices having pistons and piston shoes |
| CH570541A5 (en) * | 1973-10-10 | 1975-12-15 | Sulzer Ag | |
| DE2529473C3 (en) * | 1975-07-02 | 1980-11-20 | Danfoss A/S, Nordborg (Daenemark) | Slide shoe arrangement, especially for axial and radial piston machines |
| DE3505176C1 (en) * | 1985-02-15 | 1986-04-24 | Hauhinco Maschinenfabrik G. Hausherr, Jochums Gmbh & Co Kg, 4300 Essen | Radial-piston pump for hydraulic media |
| DE4136624A1 (en) * | 1991-11-07 | 1993-05-27 | Daimler Benz Ag | VALVE CONTROLLED DISPLAY UNIT WITH VALVE RELEASE |
| US5382140A (en) * | 1993-02-11 | 1995-01-17 | Elasis Sistema Ricerca Fiat Nel Mezzogiorno | Radial-piston pump |
| DE4401074B4 (en) * | 1994-01-15 | 2007-01-18 | Robert Bosch Gmbh | Pump arrangement, in particular for conveying fuel from a reservoir to an internal combustion engine |
| DE19635164A1 (en) * | 1996-08-30 | 1998-03-05 | Bosch Gmbh Robert | Piston pump |
| DE19705205A1 (en) * | 1997-02-12 | 1998-08-13 | Bosch Gmbh Robert | Piston pump, esp. high pressure fuel injection pump for IC engine |
| DE19725564C2 (en) * | 1997-05-27 | 2001-05-23 | Hydraulik Ring Gmbh | Radial piston pump |
-
1998
- 1998-04-01 DE DE19814506A patent/DE19814506A1/en not_active Ceased
-
1999
- 1999-02-09 DE DE59906437T patent/DE59906437D1/en not_active Expired - Lifetime
- 1999-02-09 EP EP99907314A patent/EP1068448B1/en not_active Expired - Lifetime
- 1999-02-09 WO PCT/DE1999/000344 patent/WO1999050555A1/en active IP Right Grant
- 1999-02-09 US US09/647,358 patent/US6350107B1/en not_active Expired - Fee Related
- 1999-02-09 JP JP2000541427A patent/JP4288000B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| WO1999050555A1 (en) | 1999-10-07 |
| EP1068448A1 (en) | 2001-01-17 |
| DE19814506A1 (en) | 1999-10-14 |
| US6350107B1 (en) | 2002-02-26 |
| JP4288000B2 (en) | 2009-07-01 |
| JP2002510015A (en) | 2002-04-02 |
| DE59906437D1 (en) | 2003-09-04 |
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