EP1060334B1 - Radial piston pump for fuel high pressure generation - Google Patents
Radial piston pump for fuel high pressure generation Download PDFInfo
- Publication number
- EP1060334B1 EP1060334B1 EP99907315A EP99907315A EP1060334B1 EP 1060334 B1 EP1060334 B1 EP 1060334B1 EP 99907315 A EP99907315 A EP 99907315A EP 99907315 A EP99907315 A EP 99907315A EP 1060334 B1 EP1060334 B1 EP 1060334B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- plate
- piston pump
- radial piston
- pump according
- groove
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
- F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
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- 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
- F04B1/0408—Pistons
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- 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
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- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/02—Fuel-injection apparatus having means for reducing wear
Definitions
- the invention relates to a radial piston pump for High-pressure fuel generation 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, which has a blind hole in the middle, in which is the end of the associated piston, wherein the piston has a groove on its circumference in which a snap ring is attached to a plate holder on the To attach the piston that holds the plate to the piston.
- the invention is therefore based on the problem of a Provide radial piston pump, which at a Partial filling of the cylinder pressures from to withstands up to 2000 bar and is still simple and inexpensive can be manufactured.
- the problem is with a radial piston pump High-pressure fuel generation 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, which has a blind hole in the middle, in which is the end of the associated piston, wherein the piston has a groove on its circumference in which a snap ring is attached to a plate holder on the To attach the piston that holds the plate to the piston, solved in that at the edge of the blind hole in the plate a cylinder countersink is attached, the game between the snap ring and the circumference of the cylinder countersink is smaller than the depth of the groove.
- the cylinder countersink is used for mounting of the snap ring, more precisely, to accommodate the part of the Snap ring that protrudes from the groove.
- This dimensioning of the groove and the Snap rings provide the advantage that the snap ring is always in the Groove base lies and not on the edges of the groove. Thereby damage to the seat is avoided and the Snap ring preload can be optimally used.
- the Snap ring preload can be increased by the thickness and the diameter of the snap ring and the diameter of the groove increase.
- Another special embodiment of the invention is characterized in that the area of Plate holder, which rests on the snap ring, radially to the Piston expands and is flat. This is the Snap ring more visible before the plate in the Plate holder is used.
- the Assembly is simplified and assembly errors Radial piston pump according to the invention can be avoided. Consequently can save valuable time and target zero errors can be better realized.
- Another special embodiment of the invention is characterized in that a step on the plate holder is trained.
- the stage is used in an advantageous manner Centering a spring that is used to hold the plate to bias towards the drive shaft.
- Another special embodiment of the invention is characterized in that the plate has a circumference Has groove in which a retaining ring is received, the abuts the plate holder. Due to the elastic Circlip becomes a non-positive and therefore free of play Connection between the plate holder and the plate reached. This ensures that the piston foot in the Operation remains in contact with the plate. When inserting the Plate in the plate holder gives way to the locking ring, see above that the plate holder can be rigid.
- Another special embodiment of the invention is characterized in that on the plate holder Snap segments are formed on the circumference of the plate issue.
- the snap segments have compared to those from the Prior art known claws have the advantage that they are more stable due to their size.
- Another special embodiment of the invention is characterized in that the ends of the snap segments are each slightly bent outwards. This will make the Assembly of the plate simplified in an advantageous manner, because spread when inserting the plate into the plate holder the snap segments bent slightly outwards automatically.
- Another special embodiment of the invention is characterized in that the ends of the snap segments each have a bevel. This will do the same Effect achieved as with the slightly curved outwards Snap segments.
- the assembly of the plate is simplified.
- Another special embodiment of the invention is characterized in that between the drive shaft and the plate is a polygonal or cylindrical ring is arranged.
- the ring is used to transmit the forces from the eccentrically designed drive shaft on the plate.
- the ring is advantageously sliding on the drive shaft stored.
- the ring can either be cylindrical be formed or be flattened.
- the present invention generally has the advantage that Basic idea of the present invention in a simple manner and Be applied to existing radial piston pumps can.
- the component strength, especially at a zero funding in the suction stroke, increased without the installation space the radial piston pump increases.
- Figure 1 shows a section of a conventional Radial piston pump for high-pressure fuel generation Fuel injection systems for internal combustion engines.
- FIG 1 is only the part of the radial piston pump in section to which it is shown in the present invention arrives.
- the basic structure of a radial piston pump is for example from German patent DE 42 16 877 C2 is assumed to be known and is therefore only in the following briefly described.
- the radial piston pump according to the invention is particularly in Common rail fuel injection systems for Diesel engines used.
- “Common rail” means so much like “common management”, “common rail” or “common distribution bar”.
- High pressure injection systems in which the fuel is over separate lines to the individual combustion chambers are promoted the injectors in common rail injection systems fed from a common line.
- Radial piston pump includes one in a pump housing mounted drive shaft with an eccentrically trained Shaft section.
- On the eccentric shaft section is a polygonal ring is provided against which the Shaft section is rotatable.
- the ring comprises several mutually offset flats against each other Piston 1 is supported.
- the pistons 1 are each in one Cylinder chamber 2 towards the drive shaft in the radial direction movably added.
- a plate holder 4 also called a cage or spring plate is referred to, on the associated piston 1st held.
- the plate 3 is countered by a spring 5 pressed the ring (not shown).
- a snap ring 6 is mounted in a groove 7 of the piston 1.
- Figure 2 is divided into Figures 2a, 2b and 2c.
- Figure 2a is a section of an inventive Radial piston pump shown, which is the representation of figure 1 is similar in structure. Therefore simplicity the same for parts that appear in both figures Reference numerals used.
- Figure 2b is the plate holder shown from Figure 2a alone.
- Figure 2c is one View of the plate holder in the direction of arrow A in Figure 2a shown.
- FIG. 1 There is a plate 3 on the piston 1 shown in FIG. 1 appropriate.
- the plate 3 is supported by a plate holder 4 the piston 1 held.
- a snap ring 6 mounted in a groove 7 on the circumference of the piston 1 is provided.
- the plate holder 4 by a Spring (see Figure 1) pressed against the snap ring 6.
- the dimensioning of the snap ring 6 and the cylinder countersink 26 is shown enlarged in FIG.
- the tolerances are according to the invention chosen so that the snap ring 6 is always in the Lowering 26 lies.
- Dimension 1 is designed so that it is always smaller than dimension even with the most unfavorable tolerance position. 2. This locks the snap ring 6 in the depression 26 and cannot slide off the piston 1.
- the dimensioning of the snap ring 6 and the groove 7 is in Figure 6 is shown enlarged.
- the tolerances of the groove 7 and of the snap ring 6 are chosen so that the snap ring 6 always in the groove base 60 and not at the edges 61, 62 of the groove 7. This prevents damage to the seat.
- the Wire diameter of the snap ring 6, the diameter of the Snap rings 6 and the diameter of the groove enlarged. Thereby a higher snap ring preload can be realized than in the solution shown in Figure 1.
- the Region of the plate holder 4 which bears against the piston 1 which bears against the piston 1, the shape of a round disc 20, which is radial to the Piston 1 extends. This ensures that the groove 7th can be viewed before the plate 3 in the Plate holder 4 is used.
- the plate 3 is with a Bevel 25 equipped, which is spaced from the stage 21 is.
- Three snap segments 22 extend from step 20 parallel to the piston 1.
- the ends 23 of the snap segments 22 are first bent inwards and then slightly outwards.
- the inwardly curved piece of the snap segments 22 forms in the plate holder 4 an annular space, which is used to hold a Federal 24 is used, which is formed on the plate 3.
- the outwardly bent end pieces 23 of the snap segments 22 facilitate the insertion of the plate 3 in the plate holder 4th
- FIG. 3 In the embodiment shown in FIG. 3, as in FIG Figure 2a, only a portion of a piston 1 shown.
- the End of the piston 1 is received in a blind hole 9, the is mounted centrally in a plate 3.
- the plate 3 is held by a plate holder 4 on the piston 1.
- the Plate holder 4 is on the piston 1 by a snap ring 6 attached.
- the snap ring 6 is partially in a groove 7 of the Piston 1 and partially in a cylinder countersink 26 Plate 3 added.
- the plate holder 4 is around a rotating part on which a step 21 is formed. Of the stage 21 extends parallel to the piston 1 continuous collar 32.
- the edge of the collar 32 of the Plate holder 4 is provided with a bevel 40, which facilitates the assembly of the plate 3.
- a groove 30 is attached to the circumference of the round plate 3, in a locking ring 31 is received.
- the locking ring 31 is resilient and can be used in the assembly of Plate 3 are pressed into the groove 30. That has the advantage, that the plate holder 4 with the continuous collar 32 and can be rigid.
- the plate holder 4 in contrast to that in FIG. 3 shown embodiment as a deep-drawn part with rounded Edges formed.
- the edge of the collar 32 of the Plate holder 4 as in that shown in Figure 3 Design, with a 40-bevel, which the Assembly of the plate 3 facilitated.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Description
Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung 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, die in der Mitte ein Sackloch aufweist, in welches das Ende des zugehörigen Kolbens aufgenommen ist, wobei der Kolben auf seinem Umfang eine Nut aufweist, in der ein Sprengring angebracht ist, um einen Plattenhalter an dem Kolben zu befestigen, der die Platte an dem Kolben hält.The invention relates to a radial piston pump for High-pressure fuel generation 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, which has a blind hole in the middle, in which is the end of the associated piston, wherein the piston has a groove on its circumference in which a snap ring is attached to a plate holder on the To attach the piston that holds the plate to the piston.
Bei einer Teilbefüllung der Zylinderräume werden die mit Hochdruck beaufschlagten Bauteile der Radialkolbenpumpe extrem hoch belastet.If the cylinder spaces are partially filled, Components of the radial piston pump under high pressure extremely heavily loaded.
Der Erfindung liegt daher das Problem zugrunde, eine Radialkolbenpumpe bereitzustellen, welche die bei einer Teilbefüllung der Zylinderräume auftretenden Drücke von bis zu 2000 bar aushält und trotzdem einfach und kostengünstig hergestellt werden kann.The invention is therefore based on the problem of a Provide radial piston pump, which at a Partial filling of the cylinder pressures from to withstands up to 2000 bar and is still simple and inexpensive can be manufactured.
Das Problem ist bei einer Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung 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, die in der Mitte ein Sackloch aufweist, in welches das Ende des zugehörigen Kolbens aufgenommen ist, wobei der Kolben auf seinem Umfang eine Nut aufweist, in der ein Sprengring angebracht ist, um einen Plattenhalter an dem Kolben zu befestigen, der die Platte an dem Kolben hält, dadurch gelöst, daß an dem Rand des Sacklochs in der Platte eine Zylindersenkung angebracht ist, wobei das Spiel zwischen dem Sprengring und dem Umfang der Zylindersenkung kleiner ist als die Tiefe der Nut. Die Zylindersenkung dient zur Aufnahme des Sprengrings, genauer gesagt, zur Aufnahme des Teils des Sprengrings der aus der Nut übersteht. Durch die erfindungsgemäße Dimensionierung der Zylindersenkung wird erreicht, daß der Sprengring in seinem Bauraum gefesselt wird. Dadurch können größere Kräfte übertragen werden als bei herkömmlichen Radialkolbenpumpen.The problem is with a radial piston pump High-pressure fuel generation 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, which has a blind hole in the middle, in which is the end of the associated piston, wherein the piston has a groove on its circumference in which a snap ring is attached to a plate holder on the To attach the piston that holds the plate to the piston, solved in that at the edge of the blind hole in the plate a cylinder countersink is attached, the game between the snap ring and the circumference of the cylinder countersink is smaller than the depth of the groove. The cylinder countersink is used for mounting of the snap ring, more precisely, to accommodate the part of the Snap ring that protrudes from the groove. Through the Dimensioning of the cylinder counterbore according to the invention achieved that the snap ring tied up in its space becomes. As a result, greater forces can be transmitted than with conventional radial piston pumps.
Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß der Radius der Nut größer ist als der Radius des Sprengrings. Diese Dimensionierung der Nut und des Sprengrings liefert den Vorteil, daß der Sprengring immer im Nutgrund anliegt und nicht an den Kanten der Nut. Dadurch werden Beschädigungen des Sitzes vermieden und die Sprengringvorspannung kann optimal ausgenutzt werden. Die Sprengringvorspannung kann erhöht werden, indem die Dicke und der Durchmesser des Sprengrings sowie der Durchmesser der Nut erhöht werden.This is a special embodiment of the invention characterized in that the radius of the groove is larger than that Radius of the snap ring. This dimensioning of the groove and the Snap rings provide the advantage that the snap ring is always in the Groove base lies and not on the edges of the groove. Thereby damage to the seat is avoided and the Snap ring preload can be optimally used. The Snap ring preload can be increased by the thickness and the diameter of the snap ring and the diameter of the groove increase.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß sich der Bereich des Plattenhalters, der an dem Sprengring anliegt, radial zu dem Kolben ausdehnt und eben ausgebildet ist. Dadurch ist der Sprengring besser sichtbar, bevor die Platte in den Plattenhalter eingesetzt wird. Das hat zur Folge, daß die Montage vereinfacht wird und Fehler beim Zusammenbau der erfindungsgemäßen Radialkolbenpumpe vermieden werden. Somit kann wertvolle Zeit eingespart und das Ziel Null Fehler besser realisiert werden.Another special embodiment of the invention is characterized in that the area of Plate holder, which rests on the snap ring, radially to the Piston expands and is flat. This is the Snap ring more visible before the plate in the Plate holder is used. As a result, the Assembly is simplified and assembly errors Radial piston pump according to the invention can be avoided. Consequently can save valuable time and target zero errors can be better realized.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß an dem Plattenhalter eine Stufe ausgebildet ist. Die Stufe dient in vorteilhafter Weise zur Zentrierung einer Feder, die verwendet wird, um die Platte zur Antriebswelle hin vorzuspannen.Another special embodiment of the invention is characterized in that a step on the plate holder is trained. The stage is used in an advantageous manner Centering a spring that is used to hold the plate to bias towards the drive shaft.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Platte an ihrem Umfang eine Nut aufweist, in die ein Sicherungsring aufgenommen ist, der an dem Plattenhalter anliegt. Durch den elastischen Sicherungsring wird eine kraftschlüssige und somit spielfreie Verbindung zwischen dem Plattenhalter und der Platte erreicht. Dadurch wird sichergestellt, daß der Kolbenfuß im Betrieb in Kontakt mit der Platte bleibt. Beim Einsetzen der Platte in den Plattenhalter gibt der Sicherungsring nach, so daß der Plattenhalter starr ausgebildet sein kann.Another special embodiment of the invention is characterized in that the plate has a circumference Has groove in which a retaining ring is received, the abuts the plate holder. Due to the elastic Circlip becomes a non-positive and therefore free of play Connection between the plate holder and the plate reached. This ensures that the piston foot in the Operation remains in contact with the plate. When inserting the Plate in the plate holder gives way to the locking ring, see above that the plate holder can be rigid.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß an dem Plattenhalter Schnappsegmente ausgebildet sind, die am Umfang der Platte anliegen. Die Schnappsegmente haben gegenüber den aus dem Stand der Technik bekannten Krallen den Vorteil, daß sie infolge ihrer Größe stabiler sind. Darüber hinaus verhaken die Schnappsegmente eines Plattenhalters bei der Aufbewahrung nicht so leicht mit den Schnappsegmenten anderer Plattenhalter. Dadurch wird die Montage der Plattenhalter vereinfacht.Another special embodiment of the invention is characterized in that on the plate holder Snap segments are formed on the circumference of the plate issue. The snap segments have compared to those from the Prior art known claws have the advantage that they are more stable due to their size. In addition, get caught the snap segments of a plate holder when storing not so easy with the snap segments of others Plate holder. This will assemble the plate holder simplified.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Enden der Schnappsegmente jeweils leicht nach außen gebogen sind. Dadurch wird die Montage der Platte in vorteilhafter Weise vereinfacht, denn beim Einsetzen der Platte in den Plattenhalter spreizen sich die leicht nach außen gebogenen Schnappsegmente automatisch.Another special embodiment of the invention is characterized in that the ends of the snap segments are each slightly bent outwards. This will make the Assembly of the plate simplified in an advantageous manner, because spread when inserting the plate into the plate holder the snap segments bent slightly outwards automatically.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Enden der Schnappsegmente jeweils eine Abschrägung aufweisen. Dadurch wird der gleiche Effekt erzielt wie mit den leicht nach außen gebogenen Schnappsegmenten. Die Montage der Platte wird vereinfacht.Another special embodiment of the invention is characterized in that the ends of the snap segments each have a bevel. This will do the same Effect achieved as with the slightly curved outwards Snap segments. The assembly of the plate is simplified.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß zwischen der Antriebswelle und der Platte ein polygonförmiger oder zylindrischer 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 ausgebildet sein oder mit Abflachungen versehen sein.Another special embodiment of the invention is characterized in that between the drive shaft and the plate is a polygonal or cylindrical ring is arranged. The ring is used to transmit the forces from the eccentrically designed drive shaft on the plate. The ring is advantageously sliding on the drive shaft stored. The ring can either be cylindrical be formed or be flattened.
Die vorliegende Erfindung hat allgemein den Vorteil, daß der Grundgedanke der vorliegenden Erfindung in einfacher Art und Weise auf bestehende Radialkolbenpumpen angewendet werden kann. Generell wird die Bauteilfestigkeit, insbesondere bei einer Nullförderung im Saughub, erhöht, ohne daß der Bauraum der Radialkolbenpumpe zunimmt.The present invention generally has the advantage that Basic idea of the present invention in a simple manner and Be applied to existing radial piston pumps can. In general, the component strength, especially at a zero funding in the suction stroke, increased without the installation space the radial piston pump increases.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus den Unteransprüchen sowie der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnungen drei Ausführungsbeispiele im Einzelnen beschrieben sind.
Figur 1- zeigt einen Kolben und eine Platte von einer herkömmlichen Radialkolbenpumpe;
Figur 2- zeigt einen Kolben und eine Platte von einer Radialkolbenpumpe gemäß einer ersten Ausführungsform der vorliegenden Erfindung;
Figur 3- zeigt einen Kolben und eine Platte von einer Radialkolbenpumpe gemäß einer zweiten Ausführungsform der vorliegenden Erfindung;
Figur 4- zeigt einen Kolben und eine Platte von einer Radialkolbenpumpe gemäß einer dritten Ausführungsform der vorliegenden Erfindung;
Figur 5- zeigt eine vergrößerte Darstellung des Sprengrings in der Zylindersenkung; und
Figur 6- zeigt eine vergrößerte Darstellung des Sprengrings in der Nut.
- Figure 1
- shows a piston and a plate from a conventional radial piston pump;
- Figure 2
- shows a piston and a plate of a radial piston pump according to a first embodiment of the present invention;
- Figure 3
- shows a piston and a plate of a radial piston pump according to a second embodiment of the present invention;
- Figure 4
- shows a piston and a plate of a radial piston pump according to a third embodiment of the present invention;
- Figure 5
- shows an enlarged view of the snap ring in the cylinder countersink; and
- Figure 6
- shows an enlarged view of the snap ring in the groove.
Die Figur 1 zeigt einen Ausschnitt einer herkömmlichen Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen. In Figur 1 ist nur der Teil der Radialkolbenpumpe im Schnitt dargestellt, auf den es bei der vorliegenden Erfindung ankommt. Der prinzipielle Aufbau einer Radialkolbenpumpe wird beispielsweise aus der deutschen Patentschrift DE 42 16 877 C2 als bekannt vorausgesetzt und ist deshalb im folgenden nur kurz beschrieben.Figure 1 shows a section of a conventional Radial piston pump for high-pressure fuel generation Fuel injection systems for internal combustion engines. In figure 1 is only the part of the radial piston pump in section to which it is shown in the present invention arrives. The basic structure of a radial piston pump is for example from German patent DE 42 16 877 C2 is assumed to be known and is therefore only in the following briefly described.
Die erfindungsgemäße Radialkolbenpumpe wird insbesondere in Common-Rail-Einspritzsystemen zur Kraftstoffversorgung von Dieselmotoren eingesetzt. Dabei bedeutet "common rail" soviel wie "gemeinsame Leitung", "gemeinsame Schiene" oder "gemeinsame Verteilerleiste". 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 so much like "common management", "common rail" or "common distribution bar". In contrast to conventional ones High pressure injection systems in which the fuel is over separate lines to the individual combustion chambers are promoted the injectors in common rail injection systems fed from a common line.
Die in der Figur 1 ausschnittsweise dargestellte
Radialkolbenpumpe umfaßt eine in einem Pumpengehäuse
gelagerte Antriebswelle mit einem exzentrisch ausgebildeten
Wellenabschnitt. Auf dem exzentrischen Wellenabschnitt ist
ein polygonförmiger Ring vorgesehen, gegenüber dem der
Wellenabschnitt drehbar ist. Der Ring umfaßt mehrere
zueinander versetzte Abflachungen gegen die sich jeweils ein
Kolben 1 abstützt. Die Kolben 1 sind jeweils in einem
Zylinderraum 2 zur Antriebswelle in radialer Richtung hinund
herbewegbar aufgenommen.The section shown in Figure 1
Radial piston pump includes one in a pump housing
mounted drive shaft with an eccentrically trained
Shaft section. On the eccentric shaft section is
a polygonal ring is provided against which the
Shaft section is rotatable. The ring comprises several
mutually offset flats against each
Wie in Figur 1 gezeigt, ist an dem zur Antriebswelle hin
gerichteten Ende des Kolbens 1 eine Platte 3 befestigt. Die
Platte 3 ist durch einen Plattenhalter 4, der auch als Käfig
oder Federteller bezeichnet wird, an dem zugehörigen Kolben 1
gehalten. Zudem wird die Platte 3 durch eine Feder 5 gegen
den (nicht dargestellten) Ring gedrückt. Um zu verhindern,
daß der Plattenhalter 4 von dem Kolben 1 herunterrutscht, ist
ein Sprengring 6 in einer Nut 7 des Kolbens 1 angebracht.As shown in Figure 1, is on the drive shaft
directed end of the
Die Figur 2 ist unterteilt in die Figuren 2a, 2b und 2c. In Figur 2a ist ein Ausschnitt einer erfindungsgemäßen Radialkolbenpumpe gezeigt, welcher der Darstellung von Figur 1 vom Aufbau her ähnlich ist. Deshalb werden der Einfachheit halber für Teile die in beiden Figuren vorkommen die gleichen Bezugszeichen verwendet. In Figur 2b ist der Plattenhalter aus der Figur 2a alleine dargestellt. In Figur 2c ist eine Ansicht des Plattenhalters in Richtung des Pfeils A in Figur 2a dargestellt.Figure 2 is divided into Figures 2a, 2b and 2c. In Figure 2a is a section of an inventive Radial piston pump shown, which is the representation of figure 1 is similar in structure. Therefore simplicity the same for parts that appear in both figures Reference numerals used. In Figure 2b is the plate holder shown from Figure 2a alone. In Figure 2c is one View of the plate holder in the direction of arrow A in Figure 2a shown.
An dem in Figur 1 gezeigten Kolben 1 ist eine Platte 3
angebracht. Die Platte 3 wird durch einen Plattenhalter 4 an
dem Kolben 1 gehalten. Zu diesem Zweck ist ein Sprengring 6
in einer Nut 7 montiert, die am Umfang des Kolbens 1
vorgesehen ist. Zudem wird der Plattenhalter 4 durch eine
Feder (siehe Figur 1) gegen den Sprengring 6 gedrückt.There is a
Die Platte 3 hat in der Mitte ein Sackloch 9, in das ein Ende
des Kolbens 1 formschlüssig aufgenommen ist. Der Rand des
Sacklochs 9 ist mit einer Zylindersenkung 26 versehen. Die
Zylindersenkung 26 dient zur Aufnahme desjenigen Teils des
Sprengrings 6, der aus der Nut 7 herausragt.The
Die Dimensionierung des Sprengrings 6 und der Zylindersenkung
26 ist in Figur 5 vergrößert dargestellt. Die Toleranzen sind
erfindungsgemäß so gewählt, daß der Sprengring 6 immer in der
Senkung 26 liegt. Das Maß 1 ist dabei so ausgelegt, daß es
auch bei ungünstigster Toleranzlage immer kleiner ist als Maß.
2. Dadurch wird der Sprengring 6 in der Senkung 26 gefesselt
und kann nicht von dem Kolben 1 rutschen.The dimensioning of the
Die Dimensionierung des Sprengrings 6 und der Nut 7 ist in
Figur 6 vergrößert dargestellt. Die Toleranzen der Nut 7 und
des Sprengrings 6 sind so gewählt, daß der Sprengring 6 immer
im Nutgrund 60 anliegt und.nicht an den Kanten 61, 62 der Nut
7. Dadurch werden Beschädigungen des Sitzes vermieden.
Gegenüber der in Figur 1 dargestellten Lösung wurde der
Drahtdurchmesser des Sprengrings 6, der Durchmesser des
Sprengrings 6 und der Durchmesser der Nut vergrößert. Dadurch
kann eine höhere Sprengringvorspannung realisiert werden als
bei der in Figur 1 dargestellten Lösung.The dimensioning of the
Bei der in Figur 2a gezeigten Radialkolbenpumpe hat der
Bereich des Plattenhalters 4, der an dem Kolben 1 anliegt,
die Form einer runden Scheibe 20, die sich radial zu dem
Kolben 1 erstreckt. Dadurch wird erreicht, daß die Nut 7
eingesehen werden kann, bevor die Platte 3 in den
Plattenhalter 4 eingesetzt wird. An den scheibenförmigen
Bereich 20 grenzt eine Stufe 21, die an dem Umfang der runden
Scheibe 20 ausgebildet ist. Die Platte 3 ist mit einer
Abschrägung 25 ausgestattet, die von der Stufe 21 beabstandet
ist.In the radial piston pump shown in FIG. 2a, the
Region of the
Von der Stufe 20 aus erstrecken sich drei Schnappsegmente 22
parallel zu dem Kolben 1. Die Enden 23 der Schnappsegmente 22
sind zunächst nach innen und dann leicht nach außen gebogen.
Das nach innen gebogene Stück der Schnappsegmente 22 bildet
in dem Plattenhalter 4 einen Ringraum, der zur Aufnahme eines
Bundes 24 dient, der an der Platte 3 ausgebildet ist. Die
nach außen gebogenen Endstücke 23 der Schnappsegmente 22
erleichtern das Einsetzen der Platte 3 in den Plattenhalter
4.Three
Bei der in Figur 3 gezeigten Ausführungsform ist, wie in
Figur 2a, nur ein Abschnitt eines Kolbens 1 dargestellt. Das
Ende des Kolbens 1 ist in ein Sackloch 9 aufgenommen, das
mittig in einer Platte 3 angebracht ist. Die Platte 3 ist
durch einen Plattenhalter 4 an dem Kolben 1 gehalten. Der
Plattenhalter 4 ist durch einen Sprengring 6 an dem Kolben 1
befestigt. Der Sprengring 6 ist teilweise in einer Nut 7 des
Kolbens 1 und teilweise in einer Zylindersenkung 26 der
Platte 3 aufgenommen. Bei dem Plattenhalter 4 handelt es sich
um ein Drehteil, an dem eine Stufe 21 ausgebildet ist. Von
der Stufe 21 aus erstreckt sich parallel zu dem Kolben 1 ein
durchgehender Kragen 32. Der Rand des Kragens 32 des
Plattenhalters 4 ist mit einer Abschrägung 40 versehen,
welche die Montage der Platte 3 erleichtert.In the embodiment shown in FIG. 3, as in FIG
Figure 2a, only a portion of a
Am Umfang der runden Platte 3 ist eine Nut 30 angebracht, in
der ein Sicherungsring 31 aufgenommen ist. Der Sicherungsring
31 ist federnd ausgebildet und kann bei der Montage der
Platte 3 in die Nut 30 gedrückt werden. Das hat den Vorteil,
daß der Plattenhalter 4 mit dem durchgehenden Kragen 32 und
starr ausgebildet sein kann.A
Bei dem in Figur 4 dargestellten Ausschnitt einer weiteren
Ausführungsform der erfindungsgemäßen Radialkolbenpumpe ist
der Plattenhalter 4 im Unterschied zu der in Figur 3
gezeigten Ausführungsform als Tiefziehteil mit abgerundeten
Kanten ausgebildet. Zudem ist der Rand des Kragens 32 des
Plattenhalters 4, wie bei der in Figur 3 gezeigten
Ausführungsart, mit einer Abschrägung 40-versehen, welche die
Montage der Platte 3 erleichtert.In the section of another shown in FIG. 4
Embodiment of the radial piston pump according to the invention
the
Die in den Figuren 1 bis 6 nur ausschnittsweise dargestellte Radialkolbenpumpe dient dazu, Kraftstoff, der von einer Vorförderpumpe aus einem Tank geliefert wird, mit Hochdruck zu beaufschlagen. Der mit Hochdruck beaufschlagte Kraftstoff wird dann in die oben angesprochene gemeinsame Verteilerleiste gefördert.The only partially shown in Figures 1 to 6 Radial piston pump is used to remove fuel from a Pre-feed pump is delivered from a tank at high pressure to act upon. The high pressure fuel then becomes common in the above Supported distribution strip.
Claims (9)
- Radial piston pump for the generation of high fuel pressure in fuel injection systems of internal combustion engines, in particular in a common-rail injection system, with a driveshaft which is mounted in a pump casing and which is designed eccentrically or has cam-like elevations in the circumferential direction, and with preferably a plurality of pistons (1) which are arranged in a respective cylinder space (2) radially with respect to the driveshaft and at whose ends facing the driveshaft is attached in each case a plate (3) which in the middle has a blind hole (9) in which the end of the associated piston (1) is received, the piston (1) having on its circumference a groove (7) in which is attached a spring ring (6), in order to fasten to the piston (1) a plate holder (4) which holds the plate (3) on the piston (1), characterized in that a cylindrical countersink (26) is formed at the edge of the blind hole (9) in the plate (3), the diameter of the cylindrical countersink (26) being dimensioned such that the play between the spring ring (6) and the circumference of the cylindrical countersink (26) is lower than the depth of the groove (7).
- Radial piston pump according to Claim 1, characterized in that the radius of the groove (7) is greater than the wire radius of the spring ring (6).
- Radial piston pump according to one of the preceding claims, characterized in that that region (20) of the plate holder (4) which bears against the spring ring (6) extends radially with respect to the piston (1) and is of plane design.
- Radial piston pump according to one of the preceding claims, characterized in that a step (21) is formed radially on the outside on the plate holder (4) contiguously to a disc-shaped region (20).
- Radial piston pump according to one of the preceding claims, characterized in that the plate (3) has on its circumference a groove (30) in which is received a securing ring (31) which bears against the plate holder (3).
- Radial piston pump according to one of Claims 1 to 4, characterized in that snap segments (22) which bear against the circumference of the plate (3) are formed on the plate holder (3).
- Radial piston pump according to Claim 6, characterized in that the ends (23) of the snap segments (22) are in each case bent slightly outwards.
- Radial piston pump according to Claim 6, characterized in that the ends (40) of the snap segments (22) have in each case a bevel.
- Radial piston pump according to one of the preceding claims, characterized in that a polygonal or cylindrical ring is arranged between the driveshaft and the plate (3).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19809315A DE19809315A1 (en) | 1998-03-05 | 1998-03-05 | Radial piston pump for high-pressure fuel generation |
DE19809315 | 1998-03-05 | ||
PCT/DE1999/000345 WO1999045271A1 (en) | 1998-03-05 | 1999-02-09 | Radial piston pump for fuel high pressure generation |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1060334A1 EP1060334A1 (en) | 2000-12-20 |
EP1060334B1 true EP1060334B1 (en) | 2004-09-29 |
Family
ID=7859738
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99907315A Expired - Lifetime EP1060334B1 (en) | 1998-03-05 | 1999-02-09 | Radial piston pump for fuel high pressure generation |
Country Status (5)
Country | Link |
---|---|
US (1) | US6412474B1 (en) |
EP (1) | EP1060334B1 (en) |
JP (1) | JP2002506163A (en) |
DE (2) | DE19809315A1 (en) |
WO (1) | WO1999045271A1 (en) |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10039210A1 (en) * | 2000-08-10 | 2002-02-28 | Siemens Ag | Radial piston pump has two-part spring carrier in form of pivoted connecting element between piston and return spring |
DE10150351A1 (en) * | 2001-10-15 | 2003-05-08 | Bosch Gmbh Robert | Pump element and piston pump for high-pressure fuel generation |
DE10157375A1 (en) * | 2001-11-22 | 2003-06-05 | Daimler Chrysler Ag | high pressure pump |
DE10200792A1 (en) | 2002-01-11 | 2003-07-31 | Bosch Gmbh Robert | Fuel pump for an internal combustion engine |
DE10203600B4 (en) * | 2002-01-30 | 2004-12-23 | Siemens Ag | Leakage connection for attaching a leakage line to a fuel injector |
DE10326879A1 (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 |
US7726000B2 (en) * | 2005-05-17 | 2010-06-01 | Dana Automotive Systems Group, Llc | Method of securing first and second splined members together |
GB2463822B (en) * | 2005-05-17 | 2010-06-09 | Thomas Industries Inc | Pump improvements |
FR2899285B1 (en) | 2006-03-31 | 2008-06-27 | Poclain Hydraulics Ind Soc Par | PISTON FOR A RADIAL PISTON HYDRAULIC ENGINE AND METHOD OF MANUFACTURING THE SAME |
DE102006032244A1 (en) * | 2006-07-12 | 2008-01-17 | Siemens Ag | Radial piston pump for high pressure fuel injection system, has high pressure piston formed as two-piece with cylindrical piston part and ring that are connected with each other in force-fitting and/or form-fitting manner |
JP5254979B2 (en) * | 2006-09-05 | 2013-08-07 | ガードナー デンバー トーマス インコーポレーテッド | Fluid intake / discharge connector for compressor or pump |
ES2542856T3 (en) * | 2007-10-12 | 2015-08-12 | Delphi International Operations Luxembourg S.À R.L. | Improvements related to fuel pumps |
DE102008000824A1 (en) * | 2008-03-26 | 2009-10-01 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump |
IT1401914B1 (en) * | 2010-09-01 | 2013-08-28 | Bosch Gmbh Robert | PUMPING UNIT FOR FUEL SUPPLEMENT, PREFERABLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE AND RELATIVE ASSEMBLY METHOD |
JP5352646B2 (en) * | 2011-01-27 | 2013-11-27 | 株式会社日本自動車部品総合研究所 | High pressure pump |
US20130084198A1 (en) * | 2011-10-04 | 2013-04-04 | Woodward, Inc. | Pump with centralized spring forces |
JP6339492B2 (en) * | 2014-12-25 | 2018-06-06 | 株式会社Soken | High pressure fuel pump |
DE102019106531A1 (en) * | 2019-03-14 | 2020-09-17 | Baier & Köppel GmbH & Co. KG | Lubricant pump with automatically coupling pump unit and method for coupling a pump unit to a lubricant pump |
DE102020104313B3 (en) * | 2020-02-19 | 2021-01-28 | Schaeffler Technologies AG & Co. KG | Plunger for acting on a pump piston of a high-pressure fuel pump |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3857642A (en) * | 1973-02-26 | 1974-12-31 | Ingersoll Rand Co | Flexible or universal coupling means |
DE4216877C2 (en) * | 1991-08-12 | 1996-08-29 | Elasis Sistema Ricerca Fiat | Radial piston pump |
DE4213798C2 (en) * | 1992-04-27 | 2002-10-24 | Bosch Gmbh Robert | Radial piston pump, in particular fuel pump for internal combustion engines |
US5364234A (en) * | 1992-05-20 | 1994-11-15 | Karl Eickmann | High pressure devices |
US5382140A (en) * | 1993-02-11 | 1995-01-17 | Elasis Sistema Ricerca Fiat Nel Mezzogiorno | Radial-piston pump |
GB2283533B (en) * | 1993-05-06 | 1996-07-10 | Cummins Engine Co Inc | Distributor for a high pressure fuel system |
DE19705205A1 (en) * | 1997-02-12 | 1998-08-13 | Bosch Gmbh Robert | Piston pump, esp. high pressure fuel injection pump for IC engine |
DE19804275A1 (en) * | 1998-02-04 | 1999-08-12 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel supply |
BR9904868A (en) * | 1998-02-27 | 2000-09-26 | Stanadyne Automotive Corp | Fuel supply pump and process of operating a fuel injection system |
EP0964150B1 (en) * | 1998-04-15 | 2005-06-15 | Denso Corporation | Fuel injection system for internal combustion engine |
-
1998
- 1998-03-05 DE DE19809315A patent/DE19809315A1/en not_active Withdrawn
-
1999
- 1999-02-09 EP EP99907315A patent/EP1060334B1/en not_active Expired - Lifetime
- 1999-02-09 DE DE59910657T patent/DE59910657D1/en not_active Expired - Lifetime
- 1999-02-09 US US09/623,429 patent/US6412474B1/en not_active Expired - Fee Related
- 1999-02-09 JP JP2000534775A patent/JP2002506163A/en not_active Withdrawn
- 1999-02-09 WO PCT/DE1999/000345 patent/WO1999045271A1/en active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
US6412474B1 (en) | 2002-07-02 |
DE59910657D1 (en) | 2004-11-04 |
JP2002506163A (en) | 2002-02-26 |
WO1999045271A1 (en) | 1999-09-10 |
DE19809315A1 (en) | 1999-09-09 |
EP1060334A1 (en) | 2000-12-20 |
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