EP1149244B1 - Device for reducing the axial load of a pump which delivers fluid - Google Patents
Device for reducing the axial load of a pump which delivers fluid Download PDFInfo
- Publication number
- EP1149244B1 EP1149244B1 EP00988601A EP00988601A EP1149244B1 EP 1149244 B1 EP1149244 B1 EP 1149244B1 EP 00988601 A EP00988601 A EP 00988601A EP 00988601 A EP00988601 A EP 00988601A EP 1149244 B1 EP1149244 B1 EP 1149244B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- housing
- conveyance
- fuel according
- conveyor
- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/041—Arrangements for driving gear-type pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
Definitions
- the invention relates to a device for reducing the Axialkraftbelastung a fluid pump, such as a gear pump, which acts as Kraftstof functionpumpe for supplying fuel to the engine from the storage tank of a motor vehicle.
- a fluid pump is generally known from WO 99/39103 and corresponds to the preamble of claim 1.
- a device for conveying fuel from a storage tank of an internal combustion engine which serves to drive a motor vehicle.
- a feed pump is used in a delivery line from the storage tank to the internal combustion engine, which has at least one pumping chamber in its housing.
- a pair of rotationally driven and intermeshing gears is arranged, the fuel from a connectable to the storage tank suction chamber along a feed channel formed between the end face of the gears and the wall convey in a connectable at least indirectly with the internal combustion engine pressure chamber.
- a further air-conveying pump is arranged in the housing of the feed pump, the suction side is connected to a brake booster of the motor vehicle.
- Gear pumps which serve to deliver fuel from the storage tank of motor vehicles, may experience pressures of up to 800 kPa (8 bar).
- Pressurization of up to 8 bar which is directed substantially from the pressure side to the suction side of the pump, occurs on the pressure-side conveying elements of the pump acting on axial force, which presses a front side of the shaft against a seat.
- signs of wear on the seating surface occur due to premature wear of the shaft on the front and seat surfaces.
- An attempt to prevent the premature wear of an end face of the shaft was to provide the boundary surface at the suction end of the shaft with a relief groove, which joined the face of the shaft opposite the bonding surface with the suction side of the conveyor.
- a fuel pump according to the invention With the configuration of a fuel pump according to the invention, on the one hand, its manufacture can be simplified and, consequently, made more cost-effective.
- the suction-side limiting the conveyor wall can now be made without the additional operation of milling a relief groove in the end face of the wave received in the housing opposite area.
- a surface treatment of the groove in the suction side provided boundary wall to increase the surface hardness can be omitted, so that this component is generally cheaper to manufacture.
- a reduction of acting on the shaft received in the housing unilaterally directed axial force. The occurring axial force has previously led to premature wear of an end face by frictional contact with the seat surface of the shaft.
- the unloading force acts on the axial force in the shaft and is generated by the concern of a negative pressure on a surface enlargement in the form of a concave curvature on the front side of the shaft.
- the channel system terminates in the shaft below a sealing ring accommodated on the shaft, which seals a front side of a cavity formed as a circumferential groove. This cavity communicates through a housing-side channel with the suction side of the conveyor in connection.
- the negative pressure is applied via the channel system to the end face of the shaft, where the Oberfumbleenveriererung is formed.
- the surface enlargement formed in the form of, for example, a concave curvature formed on the end face of the shaft makes it possible to provide an increased effective area for the application of the negative pressure.
- the resulting axial force in the shaft by the pressurization of the conveyor can effectively counteract in the shaft, so that premature Reibverschl corrosion between the boundary wall and the opposite end face of the shaft can be counteracted.
- Fig. 1 shows the cross section through the conveyor according to the invention for Axialkraftentlastung.
- the housing 2 of the conveyor 1 is closed on the suction side by a boundary surface 3.
- a flange is cast, which encloses a coupling element 19.
- the boundary surface 3 and the housing 2 have through holes 4.
- housing 2 and boundary surface 3 sealing elements 5 are added, which enclose the accommodated in the housing 2 displacement elements 6 in the region of the contact surface to the boundary surface 3.
- a shaft 8 is received, on which at one end a displacement element 6 is mounted, which is sealed by the boundary surface 3 to the outside.
- This displacement element 6 accommodated on the shaft designed as a stub shaft 8 works together with a further displacement element 6 mounted on the suction side 17.
- On the drive side 22 of the conveyor 1 is on the shaft 8 a dog clutch 19 taken over which the drive of the shaft 8 takes place.
- the jaw clutch 19 has a groove 21, so that a positive drive of the shaft 8 can take place.
- non-positive drives via suitable drive connections are also conceivable.
- the shaft 8 in turn is penetrated by a through hole 11 which opens on the one hand in the end face 9 of the shaft 8 in a Oberfumbleenveriererung 10 and on the other hand opens into a transverse bore 12 which is transverse to the axis of rotation of the shaft 8 and whose openings in the peripheral surface of the shaft. 8 lead.
- the transverse bore 12 opens into the lateral surface of the shaft 8 in the region of a received on the shaft 8 sealing ring 13.
- the sealing ring 13 is located with a lower sealing lip 15 above the mouths of the transverse bore 12 in the peripheral surface of the shaft 8 and seals a housing side provided cavity 14 from ,
- the housing-side cavity 14 is executed in the embodiment variant shown in Fig. 1 as a circumferential groove. From the cavity 14 extends to the suction side 17 of the conveyor 1, a housing bore 16, which is indicated here only by a center line.
- the shaft-side channel system 11, 12 with the surface enlargement 10 on the front side 9 of the shaft 8 are in communication, lies on the surface the concave curvature to a negative pressure, which generates on the shaft 8 opposite to the axial force unloading force.
- the force acting on the end face 9 of the shaft 8 axial forces can be reduced so that in the housing 2 final boundary surface 3 relief grooves 27 (see FIG. 4) can be omitted and the limiting surface 3 performing component can be produced more cost-effectively.
- the jaw clutch 19 for driving the shaft final flange may be provided with an O-ring, which in conjunction with the cap encapsulates the drive of the conveyor 1.
- the housing 2 of the conveyor 1 - made as a casting - has, for example, reinforcing ribs 18, but may well be equipped on its outside with a smooth surface similar to the boundary surface 3.
- FIG. 2 shows the plan view of a conveyor device according to FIG. 1.
- the housing 2 of the conveyor 1 is provided with two provided in the middle of the housing through holes 4. On the housing 2 are each a pressure-side and one suction-side nozzle 23 is formed, on the one hand sucked fuel from the storage tank and on the other hand under pressure fuel to the injection system of an internal combustion engine can be passed. About four each at the vertices of the conveyor 1 recorded fasteners 25, the housing 2 and the sealing boundary surface 3 are screwed together. From the plan view of FIG. 2 shows that the end of the shaft 8 is positively received between the jaws of the dog clutch 19. About the jaw clutch 19 provides a not shown here drive for the rotation of the shaft 8, to which one of the displacement elements 6 is received, through which the pressure build-up on the housing 2 of the conveyor 1 takes place.
- Fig. 3 shows the running still with a relief groove boundary wall of the conveyor.
- the boundary surface 3 is provided with threads for the fasteners 25 so that the housing 2, and the boundary surface 3 can be associated with each other.
- the relief groove 27, is now be omitted because of the inventive channel system 11, 12 in the shaft 8 and the bore 16 in the housing 2 and the cavity 14 in the housing 2, a discharge force on the displacement element 6 receiving shaft 8 can be generated.
- FIG. 4 shows the sectional profile corresponding to the sectional profile IV-IV drawn in FIG. 3.
- the relief groove 27, shown here in section, has hitherto made an additional milling operation to be performed on the surface 2 delimiting the housing 2, which can now be dispensed with.
- the boundary surface 3 can now be produced without such an operation, so that a planar installation of the boundary surface 3 can be achieved on the sealing elements 5 contained in the housing 2 of the conveyor 1 and the displacement elements 6 can be sealed to the outside.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Description
Die Erfindung bezieht sich auf eine Vorrichtung zur Reduzierung der Axialkraftbelastung einer ein Fluid fördernden Pumpe, wie beispielsweise einer Zahnradpumpe, die als Kraftstofförderpumpe zur Zufuhr von Kraftstoff zur Brennkraftmaschine aus dem Vorratstank eines Kraftfahrzeuges fungiert. Eine solche Fluidpumpe ist im allgemeinen aus der WO 99/39103 bekannt und entspricht dem Oberbegriff von Anspruch 1.The invention relates to a device for reducing the Axialkraftbelastung a fluid pump, such as a gear pump, which acts as Kraftstofförderpumpe for supplying fuel to the engine from the storage tank of a motor vehicle. Such a fluid pump is generally known from WO 99/39103 and corresponds to the preamble of
Aus DE 195 138 22 A1 ist eine Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank einer Brennkraftmaschine bekannt geworden, die zum Antrieb eines Kraftfahrzeuges dient. Bei dieser Lösung ist in eine Förderleitung vom Vorratstank zur Brennkraftmaschine eine Förderpumpe eingesetzt, die in ihrem Gehäuse wenigstens eine Pumpkammer aufweist. In der Pumpkammer ist ein Paar rotierend angetriebener und miteinander kämmender Zahnräder angeordnet, die Kraftstoff aus einem mit dem Vorratstank verbindbaren Ansaugraum entlang einem zwischen der Stirnfläche der Zahnräder und der Wand gebildeten Förderkanal in einen wenigstens mittelbar mit der Brennkraftmaschine verbindbaren Druckraum fördern. Für eine Verringerung des Bauraumes und des Fertigungsaufwandes ist im Gehäuse der Förderpumpe eine weitere luftfördernde Pumpe angeordnet, deren Saugseite mit einer Bremskraftverstärkung des Kraftfahrzeuges verbunden ist.From DE 195 138 22 A1 a device for conveying fuel from a storage tank of an internal combustion engine has become known which serves to drive a motor vehicle. In this solution, a feed pump is used in a delivery line from the storage tank to the internal combustion engine, which has at least one pumping chamber in its housing. In the pumping chamber, a pair of rotationally driven and intermeshing gears is arranged, the fuel from a connectable to the storage tank suction chamber along a feed channel formed between the end face of the gears and the wall convey in a connectable at least indirectly with the internal combustion engine pressure chamber. For a reduction of the installation space and the production costs, a further air-conveying pump is arranged in the housing of the feed pump, the suction side is connected to a brake booster of the motor vehicle.
Bei Zahnradpumpen, die der Förderung von Kraftstoff aus dem Vorratstank von Kraftfahrzeugen dient, können Drücke von bis zu 800 kPa (8 bar) auftreten. Durch die Druckbeaufschlagung von bis zu 8 bar, die im wesentlichen von der Druckseite auf die Saugseite der Pumpe gerichtet ist, tritt ein die die druckseitigen Förderelemente der Pumpe beaufschlagende Axialkraft auf, die eine Stirnseite der Welle gegen eine Sitzfläche drückt. Nach längerem Betrieb treten Abnutzungserscheinungen an der Sitzfläche auf vorzeitiger Verschleiß der Welle an Stirnseite und an der Sitzfläche sind die Folge. Ein Versuch, dem vorzeitigen Verschleiß einer Stirnseite der Welle vorzubeugen lag darin, die Begrenzungsfläche am saugseitigen Ende der Welle mit einer Entlastungsnut zu versehen, die die der Brenzungsfläche gegenüberliegende Stirnseite der Welle mit der Saugseite der Fördereinrichtung verband. Dies bedeutet jedoch bei der Herstellung der Begrenzungsfläche einen zusätzlichen Arbeitsgang in Gestalt des Ausfräsens der Entlastungsnut.Gear pumps, which serve to deliver fuel from the storage tank of motor vehicles, may experience pressures of up to 800 kPa (8 bar). By the Pressurization of up to 8 bar, which is directed substantially from the pressure side to the suction side of the pump, occurs on the pressure-side conveying elements of the pump acting on axial force, which presses a front side of the shaft against a seat. After prolonged use, signs of wear on the seating surface occur due to premature wear of the shaft on the front and seat surfaces. An attempt to prevent the premature wear of an end face of the shaft was to provide the boundary surface at the suction end of the shaft with a relief groove, which joined the face of the shaft opposite the bonding surface with the suction side of the conveyor. However, this means in the production of the boundary surface an additional operation in the form of the milling of the relief groove.
Mit der erfindungsgemäßen Konfiguration einer Kraftstoff fördernden Pumpe kann zum einen deren Fertigung vereinfacht und demzufolge kostengünstiger gestaltet werden. Die die Fördereinrichtung saugseitig begrenzende Wand kann nun ohne den zusätzlichen Arbeitsgang des Ausfräsens einer Entlastungsnut in der Stirnseite der im Gehäuse aufgenommenen Welle gegenüberliegenden Bereich gefertigt werden. Auch eine Oberflächenbehandlung der Nut in der saugseitig vorgesehenen Begrenzungswand zur Erhöhung der Oberflächenhärte kann entfallen, so daß dieses Bauteil insgesamt günstiger zu fertigen ist. Andererseits läßt sich mit der erfindungsgemäßen Lösung eine Reduzierung der auf die im Gehäuse aufgenommenen Welle einwirkenden einseitig gerichteten Axialkraft erzielen. Die auftretende Axialkraft hat bisher zum vorzeitigen Verschleiß einer Stirnseite durch Reibkontakt mit der Sitzfläche der Welle geführt. Durch das Kanalsystem im Gehäuse der Fördereinrichtung und in der Welle selbst läßt sich an der der Begrenzungsfläche gegenüberliegenden Stirnseite der Welle an einer Oberflächenvergrößerung dort eine auf die Welle einwirkende der Axialkraft entgegenwirkende Entlastungskraft erzielen. Die Entlastungskraft wirkt der Axialkraft in der Welle entgegen und wird durch das Anliegen eines Unterdrucks an einer Oberflächenvergrößerung in Gestalt einer konkaven Wölbung an der Stirnseite der Welle erzeugt.With the configuration of a fuel pump according to the invention, on the one hand, its manufacture can be simplified and, consequently, made more cost-effective. The suction-side limiting the conveyor wall can now be made without the additional operation of milling a relief groove in the end face of the wave received in the housing opposite area. Also, a surface treatment of the groove in the suction side provided boundary wall to increase the surface hardness can be omitted, so that this component is generally cheaper to manufacture. On the other hand, can be achieved with the solution according to the invention, a reduction of acting on the shaft received in the housing unilaterally directed axial force. The occurring axial force has previously led to premature wear of an end face by frictional contact with the seat surface of the shaft. Through the channel system in the housing of the conveyor and in the shaft itself can be achieved on the surface opposite the boundary surface of the shaft at a surface enlargement there acting on the shaft counteracting the axial force relief force. The unloading force acts on the axial force in the shaft and is generated by the concern of a negative pressure on a surface enlargement in the form of a concave curvature on the front side of the shaft.
In weiterer Ausgestaltung der der Erfindung zugrundeliegenden Lösung mündet das Kanalsystem in der Welle unterhalb eines auf der Welle aufgenommenen Dichtringes, der stirnseitig einen als Umfangsnut ausgebildeten Hohlraum abdichtet. Dieser Hohlraum steht durch einen gehäuseseitigen Kanal mit der Saugseite der Fördereinrichtung in Verbindung.In a further embodiment of the solution on which the invention is based, the channel system terminates in the shaft below a sealing ring accommodated on the shaft, which seals a front side of a cavity formed as a circumferential groove. This cavity communicates through a housing-side channel with the suction side of the conveyor in connection.
Ausgehend von der Saugseite der Fördereinrichtung liegt der Unterdruck über das Kanalsystem an der Stirnseite der Welle an, wo die Oberfächenvergrößerung ausgebildet ist.Starting from the suction side of the conveyor, the negative pressure is applied via the channel system to the end face of the shaft, where the Oberfächenvergrößerung is formed.
Die an der Stirnseite der Welle ausgebildete Oberflächenvergrößerung in Gestalt beispielsweise einer konkav geformten Wölbung erlaubt, eine vergrößerte Wirkfläche für das Anliegen des Unterdruckes zur Verfügung zu stellen. Je größer die Oberflächenvergrößerung ausgestaltet werden kann, desto größer kann die auf die Welle einwirkende Entlastungskraft eingestellt werden. Damit läßt sich der durch die Druckbeaufschlagung der Fördereinrichtung entstehenden Axialkraft in der Welle wirksam entgegenwirken, so daß vorzeitigem Reibverschleiß zwischen der Begrenzungswand und der dieser gegenüberliegenden Stirnseite der Welle entgegengewirkt werden kann.The surface enlargement formed in the form of, for example, a concave curvature formed on the end face of the shaft makes it possible to provide an increased effective area for the application of the negative pressure. The larger the surface enlargement can be configured, the larger the release force acting on the shaft can be set. Thus, the resulting axial force in the shaft by the pressurization of the conveyor can effectively counteract in the shaft, so that premature Reibverschleiß between the boundary wall and the opposite end face of the shaft can be counteracted.
Somit läßt sich durch ein an der Welle einstellbares Kräftegleichgewicht die Stirnseite der Welle vom Kontakt mit der gegenüberliegenden Begrenzungswand bewahren und vorzeitigem Verschleiß vorbeugen.Thus, can be maintained by contact with the opposite boundary wall and prevent premature wear by an adjustable force balance on the shaft, the end face of the shaft.
Anhand der Zeichnung wird die Erfindung nachstehend näher erläutert.Reference to the drawings, the invention will be explained in more detail below.
Es zeigt:
- Fig. 1
- den Querschnitt durch eine erfindungsgemäße Fördereinrichtung mit Axialkraftentlastung
- Fig. 2
- die Draufsicht auf eine Fördereinrichtung gemäß Fig. 1,
- Fig. 3
- eine Ansicht der saugseitigen Begrenzungsfläche und
- Fig. 4
- den Schnittverlauf gemäß IV-IV.
- Fig. 1
- the cross section through a conveyor according to the invention with axial force relief
- Fig. 2
- the top view of a conveyor according to FIG. 1,
- Fig. 3
- a view of the suction-side boundary surface and
- Fig. 4
- the intersection according to IV-IV.
Fig. 1 zeigt den Querschnitt durch die erfindungsgemäße Fördereinrichtung zur Axialkraftentlastung.Fig. 1 shows the cross section through the conveyor according to the invention for Axialkraftentlastung.
Das Gehäuse 2 der Fördereinrichtung 1 ist saugseitig durch eine Begrenzungsfläche 3 abgeschlossen. Antriebseitig ist ein Flansch angegossen, der ein Kupplungselement 19 umschließt. Die Begrenzungsfläche 3 und das Gehäuse 2 weisen Durchgangsbohrungen 4 auf. Auf der Saugseite 17 der Fördereinrichtung 1 sind Gehäuse 2 und Begrenzungsfläche 3 Dichtelemente 5 aufgenommen, die die im Gehäuse 2 aufgenommenen Verdrängungselemente 6 im Bereich der Kontaktfläche zur Begrenzungsfläche 3 umschließen.The housing 2 of the
Im Gehäuse 2 der Fördereinrichtung 1 ist eine Welle 8 aufgenommen, an der an einem Ende ein Verdrängungselement 6 gelagert ist, welches durch die Begrenzungsfläche 3 nach außen hin abgedichtet ist. Dieses auf der als Stummelwelle 8 ausgeführten Welle aufgenommene Verdrängungselement 6 arbeitet mit einem an der Saugseite 17 gelagerten weiteren Verdrängungselement 6 zusammen. Auf der Antriebsseite 22 der Fördereinrichtung 1 ist auf der Welle 8 eine Klauenkupplung 19 aufgenommen, über welche der Antrieb der Welle 8 erfolgt. Die Klauenkupplung 19 weist eine Nut 21 auf, so daß ein formschlüssiger Antrieb der Welle 8 erfolgen kann. Neben einem formschlüssigen Antrieb sind selbstverständlich auch kraftschlüssige Antriebe über geeignete Antriebsverbindungen denkbar. Die Welle 8 ihrerseits ist von einer Durchgangsbohrung 11 durchsetzt, die einerseits im stimseitigen Bereich 9 der Welle 8 in eine Oberfächenvergrößerung 10 mündet und andererseits in eine Querbohrung 12 mündet, die quer zur Rotationsachse der Welle 8 verläuft und deren Öffnungen in der Umfangsfläche der Welle 8 münden.In the housing 2 of the
Die Querbohrung 12 mündet in die Mantelfläche der Welle 8 im Bereich eines auf der Welle 8 aufgenommenen Dichtringes 13. Der Dichtring 13 liegt mit einer unteren Dichtlippe 15 oberhalb der Mündungen der Querbohrung 12 in die Umfangsfläche der Welle 8 und dichtet einen gehäuseseitig vorgesehenen Hohlraum 14 ab. Der gehäuseseitige Hohlraum 14 ist in der in Fig. 1 dargestellten Ausführungsvariante als Umfangsnut ausgeführt. Aus dem Hohlraum 14 erstreckt sich zur Saugseite 17 der Fördereinrichtung 1 eine Gehäusebohrung 16, die hier lediglich durch eine Mittellinie angedeutet ist.The transverse bore 12 opens into the lateral surface of the shaft 8 in the region of a received on the shaft 8
Durch die Gehäusebohrung 16, die in den Hohlraum 14 am Gehäuse 2 mündet und die den Dichtring 13 umschließt, unter dessen Dichtlippe 15 das wellenseitige Kanalsystem 11, 12 mit der Oberflächenvergrößerung 10 an der Stirnseite 9 der Welle 8 in Verbindung stehen, liegt an der Fläche der konkaven Wölbung ein Unterdruck an, der an der Welle 8 eine der Axialkraft entgegengesetzte Entlastungskraft erzeugt. Dadurch lassen sich die auf die Stirnseite 9 der Welle 8 einwirkenden Axialkräfte so reduzieren, daß in der das Gehäuse 2 abschließenden Begrenzungsfläche 3 Entlastungsnuten 27 (vergleiche Fig. 4) entfallen können und sich das die Begrenzungsfläche 3 darstellende Bauteil kostengünstiger fertigen läßt.Through the housing bore 16, which opens into the
Der die Klauenkupplung 19 zum Antrieb der Welle abschließende Flansch kann mit einem O-Ring versehen sein, welcher im Zusammenspiel mit der Abdeckkappe den Antrieb der Fördereinrichtung 1 kapselt. Das Gehäuse 2 der Fördereinrichtung 1 - gefertigt als Gußteil - weist beispielsweise Verstärkungsrippen 18 auf, kann aber auf seiner Außenseite durchaus mit einer glatten Oberfläche ähnlich der Begrenzungsfläche 3 ausgestattet sein.The
Fig. 2 zeigt die Draufsicht auf eine Fördereinrichtung gemäß Fig. 1.FIG. 2 shows the plan view of a conveyor device according to FIG. 1. FIG.
Das Gehäuse 2 der Fördereinrichtung 1 ist mit zwei in der Gehäusemitte vorgesehenen Durchgangsbohrungen 4 versehen. Am Gehäuse 2 sind je ein druckseitiger und je ein saugseitiger Stutzen 23 ausgebildet, über die einerseits Kraftstoff aus dem Vorratstank angesaugt und andererseits unter Druck stehender Kraftstoff an das Einspritzsystem einer Brennkraftmaschine geleitet werden können. Über vier jeweils an den Eckpunkten der Fördereinrichtung 1 aufgenommene Befestigungselemente 25 sind das Gehäuse 2 und die es abdichtende Begrenzungsfläche 3 miteinander verschraubt. Aus der Draufsicht gemäß Fig. 2 geht hervor, daß das Ende der Welle 8 formschlüssig zwischen den Klauen der Klauenkupplung 19 aufgenommen ist. Über die Klauenkupplung 19 sorgt ein hier nicht dargestellter Antrieb für die Rotation der Welle 8, an der eines der Verdrängungselemente 6 aufgenommen ist, durch welche der Druckaufbau am Gehäuse 2 der Fördereinrichtung 1 erfolgt.The housing 2 of the
Fig. 3 zeigt die noch mit einer Entlastungsnut ausgeführte Begrenzungswand der Fördereinrichtung.Fig. 3 shows the running still with a relief groove boundary wall of the conveyor.
Im Bereich der das Gehäuse 2 der Fördereinrichtung 1 durchsetzenden Befestigungselemente ist die Begrenzungsfläche 3 mit Gewinden für die Befestigungselemente 25 versehen, so daß sich das Gehäuse 2, und die Begrenzungsfläche 3 miteinander in Verbindung bringen lassen. Die Entlastungsnut 27, sich ersteckend von der Saugseite 17 zur Standfläche 9 der Welle 8 kann nunmehr entfallen, da über das erfindungsgemäße Kanalsystem 11, 12 in der Welle 8 und die Bohrung 16 im Gehäuse 2 sowie den Hohlraum 14 im Gehäuse 2 eine Entlastungskraft an der das Verdrängungselement 6 aufnehmende Welle 8 erzeugt werden kann.In the area of the housing 2 of the
Fig. 4 zeigt den Schnittverlauf entsprechend des in Fig. 3 eingezeichneten Schnittverlaufes IV-IV.FIG. 4 shows the sectional profile corresponding to the sectional profile IV-IV drawn in FIG. 3.
Die Entlastungsnut 27, hier im Schnitt dargestellt, hat bisher an der das Gehäuse 2 begrenzenden Fläche 3 einen zusätzlich auszuführenden Fräsvorgang erforderlich gemacht, der nunmehr entfallen kann. Die Begrenzungsfläche 3 läßt sich nunmehr ohne einen solchen Arbeitsgang herstellen, so daß eine Plananlage der Begrenzungsfläche 3 an dem im Gehäuse 2 der Fördereinrichtung 1 enthaltenen Dichtelemente 5 erzielbar ist und die Verdrängungselemente 6 jeweils nach außen hin abgedichtet werden können.The
Claims (7)
- Device for the conveyance of fuel out of a storage tank to an internal combustion engine, a pumping chamber being formed in the housing (2) of the conveying device, and rotary-driven displacement elements (6) being received on a shaft (8) in the housing (2), the shaft (8) having a drive side and an end face (9) lying opposite the drive side, characterized in that, in the shaft (8) receiving a displacement element (6), bores (11, 12) are formed, via which the end face (9) of the shaft (8) is connected to the suction side (17) of the conveying device (1), a surface enlargement (10) being formed on the end face (9), and the surface enlargement (10) being connected to the bores (11, 12) in the shaft (8).
- Device for the conveyance of fuel according to Claim 1, characterized in that a bore (11) passing through the shaft (8) issues into a transverse bore (12) of the shaft (8).
- Device for the conveyance of fuel according to Claim 1, characterized in that the bores (11, 12) issue in the region upstream of a sealing ring (13) arranged on the shaft (8).
- Device for the conveyance of fuel according to Claim 3, characterized in that the transverse bore (12) issues below a sealing lip (15) of the sealing ring (13).
- Device for the conveyance of fuel according to Claim 3, characterized in that the sealing ring (13) seals off a circumferential groove (14) in the housing (2).
- Device for the conveyance of fuel according to Claim 1, characterized in that the housing (2) contains a housing bore (16) which connects a drive-side cavity (14) to the suction side (17) of the conveying device (1).
- Device for the conveyance of fuel according to Claim 1, characterized in that the surface enlargement (10) is designed as a concavely running curvature.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19956520 | 1999-11-24 | ||
| DE19956520A DE19956520A1 (en) | 1999-11-24 | 1999-11-24 | Device for reducing the axial force load of a pump delivering a fluid |
| PCT/DE2000/004006 WO2001038739A1 (en) | 1999-11-24 | 2000-11-10 | Device for reducing the axial load of a pump which delivers fluid |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1149244A1 EP1149244A1 (en) | 2001-10-31 |
| EP1149244B1 true EP1149244B1 (en) | 2006-05-24 |
Family
ID=7930165
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP00988601A Expired - Lifetime EP1149244B1 (en) | 1999-11-24 | 2000-11-10 | Device for reducing the axial load of a pump which delivers fluid |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US6537046B1 (en) |
| EP (1) | EP1149244B1 (en) |
| JP (1) | JP2003515058A (en) |
| DE (2) | DE19956520A1 (en) |
| WO (1) | WO2001038739A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112007000940A5 (en) * | 2006-05-06 | 2009-01-22 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Conveying device for a fluid |
| US20120258006A1 (en) * | 2011-04-11 | 2012-10-11 | Viking Pump, Inc. | External Gear Pump for Hot Cooking Oil |
| US20120269668A1 (en) * | 2011-04-19 | 2012-10-25 | Viking Pump, Inc. | Polymeric External Gear Pump for Hot Cooking Oil |
Family Cites Families (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE152393C (en) * | 1902-10-24 | |||
| DE1027988B (en) * | 1953-04-17 | 1958-04-10 | Dowty Hydraulic Units Ltd | Gear pump |
| DE1134590B (en) * | 1957-11-09 | 1962-08-09 | Bosch Gmbh Robert | Gear pump |
| DE1170786B (en) * | 1959-07-21 | 1964-05-21 | Friedrich Reichert Maschf | Gear pump suitable for both directions of rotation |
| US3063378A (en) * | 1961-01-17 | 1962-11-13 | Gen Metals Corp | Pump construction |
| US3415459A (en) * | 1965-06-14 | 1968-12-10 | United Eng Foundry Co | Coil uncoiling arrangement |
| US3416459A (en) * | 1966-05-24 | 1968-12-17 | Parker Hannifin Corp | Rotary pump or motor |
| US4470776A (en) * | 1979-11-28 | 1984-09-11 | Commercial Shearing, Inc. | Methods and apparatus for gear pump lubrication |
| JPS5830493A (en) * | 1981-08-18 | 1983-02-22 | Matsushita Electric Ind Co Ltd | Pump case of gear pump |
| DE3307099A1 (en) * | 1983-03-01 | 1984-09-06 | Alfred Teves Gmbh, 6000 Frankfurt | Adjustable vane cell pump |
| JPH01174585U (en) * | 1988-05-27 | 1989-12-12 | ||
| JP3032411B2 (en) * | 1993-07-30 | 2000-04-17 | トリニティ工業株式会社 | Gear pump for paint |
| DE19513822C2 (en) | 1995-04-12 | 1999-10-28 | Volkswagen Ag | Device for delivering fuel from a storage tank to an internal combustion engine of a motor vehicle |
| DE19647053C1 (en) * | 1996-11-14 | 1998-04-30 | Bosch Gmbh Robert | Device for delivering fuel from a storage tank to an internal combustion engine of a motor vehicle |
| DE19714648B4 (en) * | 1997-04-09 | 2005-06-30 | Robert Bosch Gmbh | Fuel feed pump |
| DE29706316U1 (en) * | 1997-04-09 | 1998-08-06 | Robert Bosch Gmbh, 70469 Stuttgart | Feed pump |
| US6152715A (en) * | 1998-01-30 | 2000-11-28 | Kaempe; Staffan I. | Pressure clamped hydraulic pump |
-
1999
- 1999-11-24 DE DE19956520A patent/DE19956520A1/en not_active Withdrawn
-
2000
- 2000-11-10 DE DE50012820T patent/DE50012820D1/en not_active Expired - Lifetime
- 2000-11-10 WO PCT/DE2000/004006 patent/WO2001038739A1/en active IP Right Grant
- 2000-11-10 JP JP2001540055A patent/JP2003515058A/en active Pending
- 2000-11-10 EP EP00988601A patent/EP1149244B1/en not_active Expired - Lifetime
- 2000-11-10 US US09/889,892 patent/US6537046B1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| EP1149244A1 (en) | 2001-10-31 |
| JP2003515058A (en) | 2003-04-22 |
| WO2001038739A1 (en) | 2001-05-31 |
| US6537046B1 (en) | 2003-03-25 |
| DE19956520A1 (en) | 2001-06-13 |
| DE50012820D1 (en) | 2006-06-29 |
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