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EP1828609B1 - Vane cell pump - Google Patents

Vane cell pump Download PDF

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Publication number
EP1828609B1
EP1828609B1 EP05813372A EP05813372A EP1828609B1 EP 1828609 B1 EP1828609 B1 EP 1828609B1 EP 05813372 A EP05813372 A EP 05813372A EP 05813372 A EP05813372 A EP 05813372A EP 1828609 B1 EP1828609 B1 EP 1828609B1
Authority
EP
European Patent Office
Prior art keywords
rotor
rotation
region
groove
annular 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
Application number
EP05813372A
Other languages
German (de)
French (fr)
Other versions
EP1828609A1 (en
Inventor
Achim Koehler
Christian Langenbach
Joerg Wuerz
Joerg Morlok
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1828609A1 publication Critical patent/EP1828609A1/en
Application granted granted Critical
Publication of EP1828609B1 publication Critical patent/EP1828609B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/70—Safety, emergency conditions or requirements
    • F04C2270/701—Cold start

Definitions

  • the invention relates to a vane pump according to the preamble of claim 1.
  • Such a vane pump is through the DE 199 52 167 A1 known.
  • This vane pump has a pump housing, in which a rotor is arranged, which is driven in rotation by a drive shaft.
  • the rotor has distributed over its circumference a plurality of grooves which extend at least substantially radially to the axis of rotation of the rotor and in each of which a wing-shaped conveying element is guided displaceably.
  • the pump housing has a surrounding the rotor, to its axis of rotation eccentric peripheral wall, against which the wings with their radially outer ends.
  • the pump housing has in the direction of the axis of rotation of the rotor to these adjacent housing end walls.
  • enlarging and reducing chambers are formed due to the eccentric arrangement of the peripheral wall between the wings, between which the medium to be conveyed is promoted by increasing the pressure from a suction to a circumferentially offset to this pressure range.
  • the wings are held due to the centrifugal forces with a rotating rotor in abutment against the peripheral wall, but especially at start-up of the vane pump at low speed only small Centrifugal forces act, so that the vane pump promotes little.
  • an annular groove extending over part of the circumference of the rotor is provided in a housing end wall, which is supplied with compressed medium from another feed pump, which forms a common pump arrangement with the vane pump.
  • the annular groove is connected to the radially inner areas bounded by the vanes in the grooves of the rotor through the wings. Due to the increased pressure in the inner regions of the grooves, the wings are pressed in addition to the centrifugal force radially outward to the peripheral wall. However, this measure is only possible if the additional pump is present. Moreover, can be pressurized by the only over a part of the circumference of the rotor extending annular groove, the inner regions of the grooves of the rotor only over a corresponding part of a revolution of the rotor, which may result in only a small contact pressure of the wings on the peripheral wall.
  • JP 63 280883 A which is considered as a matter of prior art, discloses a vane pump with a rotor, the conveying elements promote during a rotational movement of the rotor medium from a suction to a pressure range, wherein provided in a housing end wall over a part of the circumference of the rotor extending annular groove is, which is connected to the pressure area via a connecting groove in the housing end wall.
  • the vane pump according to the invention with the features according to claim 1 has the advantage that a pressurization of the radially inner inner regions of the grooves of the rotor is effected by the pressure generated by the vane pump itself.
  • the pressurization of the inner regions of the grooves of the rotor is improved.
  • a drag flow is produced, through which an increase in pressure in the annular groove is effected, which in turn leads to an increase in pressure in the inner regions of the grooves of the rotor communicating with the annular groove.
  • FIG. 1 a vane pump in a simplified representation in a cross section along line II in FIG. 2, FIG. 2 the vane pump according to a first embodiment in a cross section along line II-II in FIG. 3, FIG. 3 the vane pump in a longitudinal section along line III-III in FIG. 1 and FIG. 4 the vane pump in a cross section according to a second embodiment.
  • a vane pump is shown, which is preferably provided for conveying fuel, in particular diesel fuel. Through the vane pump while fuel from a Reservoir fed to a high pressure pump.
  • the vane pump may be arranged separately from the high pressure pump, attached to the high pressure pump or integrated into the high pressure pump.
  • the vane pump has a pump housing 10, which is designed in several parts, and a drive shaft 12, which projects into the pump housing 10.
  • the pump housing 10 has two housing end walls 14,16, is limited by the axial direction, that is, in the direction of the axis of rotation 13 of the drive shaft 12, a pump chamber. In the circumferential direction, the pump chamber is bounded by a peripheral wall 18, which may be formed integrally with one of the housing end walls 14,16 or separated from them.
  • a rotor 20 is arranged, which is rotatably connected to the drive shaft 12, for example via a tongue and groove connection 22.
  • the rotor 20 has a plurality of distributed over its circumference, at least substantially radially to the axis of rotation 13 of the rotor 20 extending grooves 24th on.
  • the grooves 24 extend, starting from the outer jacket of the rotor 20, towards the axis of rotation 13 and into the rotor 20.
  • four grooves 24 are provided, wherein fewer or more than four grooves 24 may be provided.
  • a disk-shaped conveying element 26 is slidably disposed, which is referred to below as a wing and protrudes with its radially outer end portion of the groove 24.
  • the inside of the peripheral wall 18 of the pump housing 10 is formed eccentrically to the axis of rotation 13 of the rotor 20, for example circular or other shape.
  • a suction area is provided, in which at least one suction opening 28 opens.
  • In the suction region is preferably in at least one housing end wall 14,16 an elongated in the circumferential direction of the rotor 20, approximately kidney-shaped curved suction groove 30th formed, in which the suction opening 28 opens.
  • the suction opening 28 opens into the suction groove 30, preferably in its counter to the direction of rotation 21 of the rotor 20 facing end region.
  • the suction opening 28 is connected to an inlet leading from the reservoir.
  • a pressure region is provided in at least one housing end wall 14,16, in which at least one pressure port 32 opens.
  • a pressure groove 34 which is elongate in the circumferential direction of the rotor 20 and is approximately kidney-shaped, is preferably formed in at least one housing end wall 14,16, into which the pressure opening 32 opens.
  • the pressure opening 32 opens into the pressure groove 34, preferably in its end region pointing in the direction of rotation 21 of the rotor 20.
  • the pressure port 32 is connected to a leading to the high-pressure pump drain.
  • the suction port 28, the suction groove 30, the pressure port 32 and the pressure groove 34 are arranged at a radial distance from the rotational axis 13 of the rotor 20 near the inside of the peripheral wall 18.
  • the wings 26 abut with their radially outer ends on the inside of the peripheral wall 18 and slide on this during the rotational movement of the rotor 20 in the direction of rotation 21 along.
  • the suction groove 30 and the suction opening is arranged in a peripheral region, in which the volume of the chambers 36 increases during the rotational movement in the direction of rotation 21 of the rotor 20, so that they are filled with fuel.
  • the pressure groove 34 and the pressure opening 32 is arranged in a peripheral region, in which the volume of the chambers 36 is reduced during the rotational movement in the direction of rotation 21 of the rotor 20, so that from this fuel into the pressure groove 34 and from this into the pressure port 32 is displaced ,
  • annular groove 38 is provided, which is connected to the pressure groove 34 via a connecting groove 40.
  • the annular groove 38 extends at such a radial distance from the axis of rotation 13 of the rotor 20, that this is opposite to the limited by the wings 26 in the grooves 24 of the rotor 20 radially inner interior regions.
  • the annular groove 38 is formed at least approximately concentric to the axis of rotation 13 of the rotor 20 and between this and the drive shaft 12, a sealing region 39 is formed, in which between the rotor 20 and the adjacent housing end wall 14,16 only a small axial distance is present.
  • the connecting groove 40 extends in such a way that it approaches the annular groove 38) in the direction of rotation 21 of the rotor 20. Furthermore, the connecting groove 40 is curved according to the invention, in particular helically curved.
  • the connecting groove 40 preferably opens on the one hand at least approximately tangentially in the pressure groove 34 and / or on the other hand at least approximately tangentially in the annular groove 38.
  • the connecting groove 40 opens in the counter to the direction of rotation 21 of the rotor 20 facing end portion of the pressure groove 34.
  • annular groove 38 and connecting them with the pressure groove 34 connecting groove 40 is arranged or it can be arranged in both housing end walls 14 and 16 each have an annular groove 38 and a connecting groove 40, which then preferably mirror images of each other in the housing end walls 14 and 16 are arranged. It can also be provided that an annular groove 38 is arranged in both housing end walls 14 and 16, but a connecting groove 40 is arranged only in a housing end wall 14 or 16.
  • the suction groove 30 and / or the pressure groove 34 is formed, the other housing end wall 16 and 14 is smooth, or that in both housing end walls 14 and 16 each have a suction 30th and / or pressure groove 34 is formed, which are then preferably arranged in mirror image to each other in the housing end walls 14 and 16.
  • the suction opening 28 and the pressure opening 32 is provided only in a housing end wall 14 or 16.
  • the rotor 20 and the wings 26 in the axial direction on both sides are loaded at least approximately equal, so that no or only a small resultant force acts on the rotor 20 and the wings 26 in the direction of the axis of rotation 13.
  • the depth of the annular groove 38 and the connecting groove 40 in the housing end wall 14,16 for example, about 0.1 to 2mm, preferably the width of the grooves 38 and 40 is greater than the depth.
  • FIG. 4 is the vane pump according to a second embodiment shown, in which the construction is substantially the same as in the first embodiment, but the arrangement of the annular groove 138 is modified. Notwithstanding the first embodiment, the annular groove 138 is arranged eccentrically to the axis of rotation 13 of the rotor 20.
  • the annular groove 138 is formed, for example, at least approximately circular, wherein the center M is arranged offset with respect to the axis of rotation 13 of the rotor 20 by a distance e forming the eccentricity.
  • the eccentricity e of the annular groove 138 is at least approximately equal and in the same direction as the eccentricity of the inner side of the peripheral wall 18 of the pump housing 10.
  • the center M of the annular groove 138 is seen in the direction of rotation 21 of the rotor 20 between the suction groove 30 and the pressure groove 34 lying portion of the peripheral wall 18 out with respect to the axis of rotation 13 arranged offset.
  • the radial extent s1 of the sealing region 139 within the annular groove 138 toward the drive shaft 12 on the side toward which the midpoint M is offset with respect to the axis of rotation 13 increases during the radial extent s2 of the sealing region 139 the opposite side is reduced.
  • annular groove 138 is not circular, but has an eccentric course with respect to the axis of rotation 13, wherein the radial extent s1 of Sealing region 139 in a region in the direction of rotation 21 of the rotor 20 between the suction groove 30 and the pressure groove 34 is greater than the radial extent s2 of the sealing region 139 in the opposite region.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Flügelzellenpumpe nach der Gattung des Anspruchs 1.The invention relates to a vane pump according to the preamble of claim 1.

Eine solche Flügelzellenpumpe ist durch die DE 199 52 167 A1 bekannt. Diese Flügelzellenpumpe weist ein Pumpengehäuse auf, in dem ein Rotor angeordnet ist, der durch eine Antriebswelle rotierend angetrieben wird. Der Rotor weist über seinen Umfang verteilt mehrere Nuten auf, die zumindest im wesentlichen radial zur Drehachse des Rotors verlaufen und in denen jeweils ein flügelförmiges Förderelement verschiebbar geführt ist. Das Pumpengehäuse weist eine den Rotor umgebende, zu dessen Drehachse exzentrische Umfangswand auf, an der die Flügel mit ihren radial äußeren Enden anliegen. Das Pumpengehäuse weist in Richtung der Drehachse des Rotors an diesen angrenzende Gehäusestirnwände auf. Bei der Rotation des Rotors werden infolge der exzentrischen Anordnung der Umfangswand zwischen den Flügeln sich vergrößernde und verkleinernde Kammern gebildet, zwischen denen das zu fördernde Medium unter Druckerhöhung von einem Saugbereich zu einem zu diesem in Umfangsrichtung versetzten Druckbereich gefördert wird. Die Flügel werden dabei infolge der Fliehkräfte bei rotierendem Rotor in Anlage an der Umfangswand gehalten, wobei jedoch insbesondere beim Anlaufen der Flügelzellenpumpe bei niedriger Drehzahl nur geringe Fliehkräfte wirken, so dass die Flügelzellenpumpe nur wenig fördert. Bei der bekannten Flügelzellenpumpe ist in einer Gehäusestirnwand eine sich über einen Teil des Umfangs des Rotors erstreckende ringförmige Nut vorgesehen, der von einer anderen Förderpumpe, die mit der Flügelzellenpumpe eine gemeinsame Pumpenanordnung bildet, verdichtetes Medium zugeführt wird. Die ringförmige Nut ist mit den von den Flügeln in den Nuten des Rotors durch die Flügel begrenzten radial innen liegenden Innenbereichen verbunden. Durch den erhöhten Druck in den Innenbereichen der Nuten werden die Flügel zusätzlich zur Fliehkraft radial nach außen zur Umfangswand hin gedrückt. Diese Maßnahme ist jedoch nur möglich, wenn die weitere Förderpumpe vorhanden ist. Darüberhinaus können durch die sich nur über einen Teil des Umfangs des Rotors erstreckende ringförmige Nut die Innenbereiche der Nuten des Rotors nur über einen entsprechenden Teil einer Umdrehung des Rotors druckbeaufschlagt werden, wodurch sich unter Umständen nur eine geringe Anpresskraft der Flügel an der Umfangswand ergibt.Such a vane pump is through the DE 199 52 167 A1 known. This vane pump has a pump housing, in which a rotor is arranged, which is driven in rotation by a drive shaft. The rotor has distributed over its circumference a plurality of grooves which extend at least substantially radially to the axis of rotation of the rotor and in each of which a wing-shaped conveying element is guided displaceably. The pump housing has a surrounding the rotor, to its axis of rotation eccentric peripheral wall, against which the wings with their radially outer ends. The pump housing has in the direction of the axis of rotation of the rotor to these adjacent housing end walls. During the rotation of the rotor, enlarging and reducing chambers are formed due to the eccentric arrangement of the peripheral wall between the wings, between which the medium to be conveyed is promoted by increasing the pressure from a suction to a circumferentially offset to this pressure range. The wings are held due to the centrifugal forces with a rotating rotor in abutment against the peripheral wall, but especially at start-up of the vane pump at low speed only small Centrifugal forces act, so that the vane pump promotes little. In the known vane pump, an annular groove extending over part of the circumference of the rotor is provided in a housing end wall, which is supplied with compressed medium from another feed pump, which forms a common pump arrangement with the vane pump. The annular groove is connected to the radially inner areas bounded by the vanes in the grooves of the rotor through the wings. Due to the increased pressure in the inner regions of the grooves, the wings are pressed in addition to the centrifugal force radially outward to the peripheral wall. However, this measure is only possible if the additional pump is present. Moreover, can be pressurized by the only over a part of the circumference of the rotor extending annular groove, the inner regions of the grooves of the rotor only over a corresponding part of a revolution of the rotor, which may result in only a small contact pressure of the wings on the peripheral wall.

JP 63 280883 A , die als nächotliegender Stand der Technik angesehen wird, offenbart eine Flügelzellenpumpe mit einem Rotor, deren Förderelemente bei einer Drehbewegung des Rotors Medium von einem Saugbereich in einen Druckbereich fördern, wobei in einer Gehäusestirnwand eine sich über einen Teil des Umfangs des Rotors erstreckende ringförmige Nut vorgesehen ist, die mit dem Druckbereich über eine Verbindungsnut in der Gehäusestirnwand verbunden ist. JP 63 280883 A , which is considered as a matter of prior art, discloses a vane pump with a rotor, the conveying elements promote during a rotational movement of the rotor medium from a suction to a pressure range, wherein provided in a housing end wall over a part of the circumference of the rotor extending annular groove is, which is connected to the pressure area via a connecting groove in the housing end wall.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Flügelzellenpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass eine Druckbeaufschlagung der radial innenliegenden Innenbereiche der Nuten des Rotors durch den von den Flügelzellenpumpe selbst erzeugten Druck erfolgt. Durch die sich über den gesamten Umfang des Rotors erstreckende Ringnut wird die Druckbeaufschlagung der Innenbereiche der Nuten des Rotors verbessert. In der nach innen verlaufenden gekrümmten Verbindungsnut entsteht darüber hinaus bei der Rotation des Rotors eine Schleppströmung, durch die eine Druckerhöhung in der Ringnut bewirkt wird, die wiederum zu einer Druckerhöhung in den mit der Ringnut in Verbindung stehenden Innenbereichen der Nuten des Rotors führt. Diese Schleppströmung wird mit zunehmender Drehzahl des Rotors verstärkt, so dass die Anpressung der Förderelemente an die Umfangswand mit zunehmender Drehzahl weiter verstärkt wird. Durch den Verlauf der Verbindungsnut wird außerdem erreicht, dass die Förderelemente diese nahezu rechtwinklig überstreichen, wodurch die Gefahr eines Verkippens und/oder Verkantens der Förderelemente beim Überstreichen der Verbindungsnut gering ist.The vane pump according to the invention with the features according to claim 1 has the advantage that a pressurization of the radially inner inner regions of the grooves of the rotor is effected by the pressure generated by the vane pump itself. By extending over the entire circumference of the rotor annular groove, the pressurization of the inner regions of the grooves of the rotor is improved. Moreover, in the inwardly extending curved connecting groove, during the rotation of the rotor, a drag flow is produced, through which an increase in pressure in the annular groove is effected, which in turn leads to an increase in pressure in the inner regions of the grooves of the rotor communicating with the annular groove. These Drag flow is amplified with increasing speed of the rotor, so that the contact pressure of the conveying elements is further reinforced with increasing speed to the peripheral wall. Through the course of the connecting groove is also achieved that the conveying elements sweep them almost at right angles, whereby the risk of tilting and / or tilting of the conveying elements when passing over the connecting groove is low.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Flügelzellenpumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 wird eine verlustarme Ein- und Ausströmung bei der Verbindungsnut ermöglicht. Durch die Ausbildung gemäß Anspruch 4 kann eine Leckage aus der Ringnut radial nach innen gering gehalten werden.In the dependent claims advantageous refinements and developments of the vane pump according to the invention are given. Due to the construction according to claim 2, a low-loss input and outflow is made possible in the connection groove. Due to the design according to claim 4, a leakage from the annular groove can be kept radially inward low.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Flügelzellenpumpe in vereinfachter Darstellung in einem Querschnitt entlang Linie I-I in Figur 2, Figur 2 die Flügelzellenpumpe gemäß einem ersten Ausführungsbeispiel in einem Querschnitt entlang Linie II-II in Figur 3, Figur 3 die Flügelzellenpumpe in einem Längsschnitt entlang Linie III-III in Figur 1 und Figur 4 die Flügelzellenpumpe in einem Querschnitt gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. Show it FIG. 1 a vane pump in a simplified representation in a cross section along line II in FIG. 2, FIG. 2 the vane pump according to a first embodiment in a cross section along line II-II in FIG. 3, FIG. 3 the vane pump in a longitudinal section along line III-III in FIG. 1 and FIG. 4 the vane pump in a cross section according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In den Figuren 1 bis 4 ist eine Flügelzellenpumpe dargestellt, die vorzugsweise zum Fördern von Kraftstoff, insbesondere Dieselkraftstoff, vorgesehen ist. Durch die Flügelzellenpumpe wird dabei Kraftstoff aus einem Vorratsbehälter zu einer Hochdruckpumpe gefördert. Die Flügelzellenpumpe kann getrennt von der Hochdruckpumpe angeordnet sein, an die Hochdruckpumpe angebaut oder in die Hochdruckpumpe integriert sein. Die Flügelzellenpumpe weist ein Pumpengehäuse 10 auf, das mehrteilig ausgebildet ist, und eine Antriebswelle 12, die in das Pumpengehäuse 10 hineinragt. Das Pumpengehäuse 10 weist zwei Gehäusestirnwände 14,16 auf, durch die in axialer Richtung, das heißt in Richtung der Drehachse 13 der Antriebswelle 12, eine Pumpenkammer begrenzt wird. In Umfangsrichtung wird die Pumpenkammer durch eine Umfangswand 18 begrenzt, die einstückig mit einer der Gehäusestirnwände 14,16 oder getrennt von diesen ausgebildet sein kann.In the FIGS. 1 to 4 a vane pump is shown, which is preferably provided for conveying fuel, in particular diesel fuel. Through the vane pump while fuel from a Reservoir fed to a high pressure pump. The vane pump may be arranged separately from the high pressure pump, attached to the high pressure pump or integrated into the high pressure pump. The vane pump has a pump housing 10, which is designed in several parts, and a drive shaft 12, which projects into the pump housing 10. The pump housing 10 has two housing end walls 14,16, is limited by the axial direction, that is, in the direction of the axis of rotation 13 of the drive shaft 12, a pump chamber. In the circumferential direction, the pump chamber is bounded by a peripheral wall 18, which may be formed integrally with one of the housing end walls 14,16 or separated from them.

In der Pumpenkammer ist ein Rotor 20 angeordnet, der mit der Antriebswelle 12 drehfest verbunden ist, beispielsweise über eine Nut/Federverbindung 22. Der Rotor 20 weist mehrere über seinen Umfang verteilt angeordnete, zumindest im wesentlichen radial zur Drehachse 13 des Rotors 20 verlaufende Nuten 24 auf. Die Nuten 24 erstrecken sich ausgehend vom Außenmantel des Rotors 20 zur Drehachse 13 hin in den Rotor 20 hinein. Es sind beispielsweise vier Nuten 24 vorgesehen, wobei auch weniger oder mehr als vier Nuten 24 vorgesehen sein können. In jeder Nut 24 ist ein scheibenförmiges Förderelement 26 verschiebbar angeordnet, das nachfolgend als Flügel bezeichnet wird und das mit seinem radial äußeren Endbereich aus der Nut 24 herausragt.In the pump chamber, a rotor 20 is arranged, which is rotatably connected to the drive shaft 12, for example via a tongue and groove connection 22. The rotor 20 has a plurality of distributed over its circumference, at least substantially radially to the axis of rotation 13 of the rotor 20 extending grooves 24th on. The grooves 24 extend, starting from the outer jacket of the rotor 20, towards the axis of rotation 13 and into the rotor 20. For example, four grooves 24 are provided, wherein fewer or more than four grooves 24 may be provided. In each groove 24, a disk-shaped conveying element 26 is slidably disposed, which is referred to below as a wing and protrudes with its radially outer end portion of the groove 24.

Die Innenseite der Umfangswand 18 des Pumpengehäuses 10 ist exzentrisch zur Drehachse 13 des Rotors 20 ausgebildet, beispielsweise kreisförmig oder mit anderer Form. In wenigstens einer Gehäusestirnwand 14,16 ist ein Saugbereich vorgesehen, in dem wenigstens eine Saugöffnung 28 mündet. Im Saugbereich ist vorzugsweise in wenigstens einer Gehäusestirnwand 14,16 eine in Umfangsrichtung des Rotors 20 langgestreckte, etwa nierenförmig gekrümmte Saugnut 30 ausgebildet, in die die Saugöffnung 28 mündet. Die Saugöffnung 28 mündet in die Saugnut 30 vorzugsweise in deren entgegen der Drehrichtung 21 des Rotors 20 weisenden Endbereich. Die Saugöffnung 28 ist mit einem vom Vorratsbehälter herführenden Zulauf verbunden. In wenigstens einer Gehäusestirnwand 14,16 ist außerdem ein Druckbereich vorgesehen, in dem wenigstens eine Drucköffnung 32 mündet. Im Druckbereich ist vorzugsweise in wenigstens einer Gehäusestirnwand 14,16 eine in Umfangsrichtung des Rotors 20 langgestreckte, etwa nierenförmig gekrümmte Drucknut 34 ausgebildet, in die die Drucköffnung 32 mündet. Die Drucköffnung 32 mündet in die Drucknut 34 vorzugsweise in deren in Drehrichtung 21 des Rotors 20 weisenden Endbereich. Die Drucköffnung 32 ist mit einem zur Hochdruckpumpe führenden Ablauf verbunden. Die Saugöffnung 28, die Saugnut 30, die Drucköffnung 32 und die Drucknut 34 sind mit radialem Abstand von der Drehachse 13 des Rotors 20 nahe der Innenseite der Umfangswand 18 angeordnet. Die Flügel 26 liegen mit ihren radial äußeren Enden an der Innenseite der Umfangswand 18 an und gleiten an dieser bei der Drehbewegung des Rotors 20 in Drehrichtung 21 entlang. Infolge der exzentrischen Ausbildung der Innenseite der Umfangswand 18 bezüglich der Drehachse 13 des Rotors 20 ergeben sich zwischen den Flügeln 26 Kammern 36 mit veränderlichem Volumen. Die Saugnut 30 und die Saugöffnung ist in einem Umfangsbereich angeordnet, in dem sich bei der Drehbewegung in Drehrichtung 21 des Rotors 20 das Volumen der Kammern 36 vergrößert, so dass diese mit Kraftstoff befüllt werden. Die Drucknut 34 und die Drucköffnung 32 ist in einem Umfangsbereich angeordnet, in dem sich bei der Drehbewegung in Drehrichtung 21 des Rotors 20 das Volumen der Kammern 36 verringert, so dass aus diesen Kraftstoff in die Drucknut 34 und von dieser in die Drucköffnung 32 verdrängt wird.The inside of the peripheral wall 18 of the pump housing 10 is formed eccentrically to the axis of rotation 13 of the rotor 20, for example circular or other shape. In at least one housing end wall 14,16 a suction area is provided, in which at least one suction opening 28 opens. In the suction region is preferably in at least one housing end wall 14,16 an elongated in the circumferential direction of the rotor 20, approximately kidney-shaped curved suction groove 30th formed, in which the suction opening 28 opens. The suction opening 28 opens into the suction groove 30, preferably in its counter to the direction of rotation 21 of the rotor 20 facing end region. The suction opening 28 is connected to an inlet leading from the reservoir. In addition, a pressure region is provided in at least one housing end wall 14,16, in which at least one pressure port 32 opens. In the pressure region, a pressure groove 34, which is elongate in the circumferential direction of the rotor 20 and is approximately kidney-shaped, is preferably formed in at least one housing end wall 14,16, into which the pressure opening 32 opens. The pressure opening 32 opens into the pressure groove 34, preferably in its end region pointing in the direction of rotation 21 of the rotor 20. The pressure port 32 is connected to a leading to the high-pressure pump drain. The suction port 28, the suction groove 30, the pressure port 32 and the pressure groove 34 are arranged at a radial distance from the rotational axis 13 of the rotor 20 near the inside of the peripheral wall 18. The wings 26 abut with their radially outer ends on the inside of the peripheral wall 18 and slide on this during the rotational movement of the rotor 20 in the direction of rotation 21 along. As a result of the eccentric formation of the inside of the peripheral wall 18 with respect to the axis of rotation 13 of the rotor 20 results between the wings 26 chambers 36 with variable volume. The suction groove 30 and the suction opening is arranged in a peripheral region, in which the volume of the chambers 36 increases during the rotational movement in the direction of rotation 21 of the rotor 20, so that they are filled with fuel. The pressure groove 34 and the pressure opening 32 is arranged in a peripheral region, in which the volume of the chambers 36 is reduced during the rotational movement in the direction of rotation 21 of the rotor 20, so that from this fuel into the pressure groove 34 and from this into the pressure port 32 is displaced ,

In wenigstens einer Gehäusestirnwand 14,16 ist eine Ringnut 38 vorgesehen, die mit der Drucknut 34 über eine Verbindungsnut 40 verbunden ist. Die Ringnut 38 verläuft in einem solchen radialen Abstand von der Drehachse 13 des Rotors 20, dass diese den durch die Flügel 26 in den Nuten 24 des Rotors 20 begrenzten radial inneren Innenbereichen gegenüberliegt. Die Ringnut 38 ist zumindest annähernd konzentrisch zur Drehachse 13 des Rotors 20 ausgebildet und zwischen dieser und der Antriebswelle 12 ist ein Dichtbereich 39 gebildet, in dem zwischen dem Rotor 20 und der angrenzenden Gehäusestirnwand 14,16 nur ein geringer axialer Abstand vorhanden ist. Im Bereich um die Antriebswelle 12 herrscht nur ein geringer Druck, so dass zwischen der Ringnut 38 und dem Bereich um die Antriebswelle 12 ein Druckgefälle besteht. Die Verbindungsnut 40 verläuft derart, dass diese sich in Drehrichtung 21 des Rotors 20 der Ringnut 38) annähert. Weiterhin verläuft die Verbindungsnut 40 erfindungsgemäß gekrümmt, insbesondere schneckenförmig gekrümmt. Die Verbindungsnut 40 mündet vorzugsweise einerseits zumindest annähernd tangential in die Drucknut 34 und/oder andererseits zumindest annähernd tangential in die Ringnut 38. Vorzugsweise mündet die Verbindungsnut 40 in den entgegen der Drehrichtung 21 des Rotors 20 weisenden Endbereich der Drucknut 34. Durch die Verbindung der Ringnut 38 mit der Drucknut 34 herrscht in der Ringnut 38 und damit in den mit dieser in Verbindung stehenden Innenbereichen der Nuten 24 des Rotors 20 ein erhöhter Druck, durch den die Anlagekraft der Flügel 26 an der Innenseite der Umfangswand 18 verstärkt wird, wodurch die Förderleistung der Flügelzellenpumpe verbessert wird. Durch den gekrümmten Verlauf der Verbindungsnut 40 wird außerdem bei der Drehbewegung des Rotors 20 in dieser eine Schleppströmung erzeugt, die zu einer weiteren Druckerhöhung in der Ringnut 38 und damit den Nuten 24 führt, wodurch die Anpresskraft der Flügel 26 an die Umfangswand 18 weiter erhöht wird. Insbesondere erfolgt infolge dieser Schleppströmung bereits beim Anlaufen der Flügelzellenpumpe ein Druckaufbau in der Ringnut 38, so dass die durch die Flügelzellenpumpe bereits beim Anlaufen eine ausreichende Kraftstoffmenge fördert. Durch den gekrümmten Verlauf der Verbindungsnut 40 ist außerdem sichergestellt, dass die Flügel 26 sich bei der Drehbewegung des Rotors 20 annähernd tangential über die Verbindungsnut 40 bewegen, wodurch der Verschleiß der Flügel 26 und der Gehäusestirnwand 14,16 gering gehalten wird.In at least one housing end wall 14,16 an annular groove 38 is provided, which is connected to the pressure groove 34 via a connecting groove 40. The annular groove 38 extends at such a radial distance from the axis of rotation 13 of the rotor 20, that this is opposite to the limited by the wings 26 in the grooves 24 of the rotor 20 radially inner interior regions. The annular groove 38 is formed at least approximately concentric to the axis of rotation 13 of the rotor 20 and between this and the drive shaft 12, a sealing region 39 is formed, in which between the rotor 20 and the adjacent housing end wall 14,16 only a small axial distance is present. In the area around the drive shaft 12, only a slight pressure prevails, so that there is a pressure gradient between the annular groove 38 and the area around the drive shaft 12. The connecting groove 40 extends in such a way that it approaches the annular groove 38) in the direction of rotation 21 of the rotor 20. Furthermore, the connecting groove 40 is curved according to the invention, in particular helically curved. The connecting groove 40 preferably opens on the one hand at least approximately tangentially in the pressure groove 34 and / or on the other hand at least approximately tangentially in the annular groove 38. Preferably, the connecting groove 40 opens in the counter to the direction of rotation 21 of the rotor 20 facing end portion of the pressure groove 34. By the connection of the annular groove 38 with the pressure groove 34 prevails in the annular groove 38 and thus in the associated with this inner regions of the grooves 24 of the rotor 20, an increased pressure by which the contact force of the wings 26 is reinforced on the inside of the peripheral wall 18, whereby the flow rate of the Vane pump is improved. Due to the curved course of the connecting groove 40 also in the rotational movement of the rotor 20 in this a drag flow is generated, which leads to a further pressure increase in the annular groove 38 and thus the grooves 24, whereby the contact pressure of the wings 26 to the Peripheral wall 18 is further increased. In particular, as a result of this drag flow, a pressure build-up in the annular groove 38 already takes place when the vane pump starts, so that the vaporizer pump already delivers a sufficient amount of fuel when it starts up. The curved course of the connecting groove 40 also ensures that the wings 26 move approximately tangentially over the connecting groove 40 during the rotational movement of the rotor 20, whereby the wear of the wings 26 and the housing end wall 14,16 is kept low.

Es kann vorgesehen sein, dass nur in einer Gehäusestirnwand 14 oder 16 die Ringnut 38 und die diese mit der Drucknut 34 verbindende Verbindungsnut 40 angeordnet ist oder es können in beiden Gehäusestirnwänden 14 und 16 jeweils eine Ringnut 38 und eine Verbindungsnut 40 angeordnet sein, die dann vorzugsweise spiegelbildlich zueinander in den Gehäusestirnwänden 14 und 16 angeordnet sind. Es kann auch vorgesehen sein, dass in beiden Gehäusestirnwänden 14 und 16 jeweils eine Ringnut 38 angeordnet ist, jedoch nur in einer Gehäusestirnwand 14 oder 16 eine Verbindungsnut 40 angeordnet ist. Es kann außerdem vorgesehen sein, dass nur in einer Gehäusestirnwand 14 oder 16 die Saugnut 30 und/oder die Drucknut 34 ausgebildet ist, wobei die andere Gehäusestirnwand 16 bzw. 14 glatt ausgebildet ist, oder dass in beiden Gehäusestirnwänden 14 und 16 jeweils eine Saugnut 30 und/oder Drucknut 34 ausgebildet ist, die dann vorzugsweise spiegelbildlich zueinander in den Gehäusestirnwänden 14 und 16 angeordnet sind. Die Saugöffnung 28 und die Drucköffnung 32 ist dabei jedoch nur in einer Gehäusestirnwand 14 oder 16 vorgesehen. Bei der spiegelbildlichen Anordnung der Saugnuten 30 und Drucknuten 34 sowie der Ringnuten 38 und Verbindungsnuten 40 in beiden Gehäusestirnwänden 14 und 16 wird erreicht, dass der Rotor 20 und die Flügel 26 in axialer Richtung beidseitig zumindest annähernd gleich belastet sind, so dass keine oder nur eine geringe resultierende Kraft auf den Rotor 20 und die Flügel 26 in Richtung der Drehachse 13 wirkt. Die Tiefe der Ringnut 38 und der Verbindungsnut 40 in der Gehäusestirnwand 14,16 beträgt beispielsweise etwa 0,1 bis 2mm, wobei vorzugsweise die Breite der Nuten 38 und 40 größer ist als deren Tiefe.It can be provided that only in a housing end wall 14 or 16, the annular groove 38 and connecting them with the pressure groove 34 connecting groove 40 is arranged or it can be arranged in both housing end walls 14 and 16 each have an annular groove 38 and a connecting groove 40, which then preferably mirror images of each other in the housing end walls 14 and 16 are arranged. It can also be provided that an annular groove 38 is arranged in both housing end walls 14 and 16, but a connecting groove 40 is arranged only in a housing end wall 14 or 16. It can also be provided that only in a housing end wall 14 or 16, the suction groove 30 and / or the pressure groove 34 is formed, the other housing end wall 16 and 14 is smooth, or that in both housing end walls 14 and 16 each have a suction 30th and / or pressure groove 34 is formed, which are then preferably arranged in mirror image to each other in the housing end walls 14 and 16. However, the suction opening 28 and the pressure opening 32 is provided only in a housing end wall 14 or 16. In the mirror image arrangement of the suction grooves 30 and pressure grooves 34 and the annular grooves 38 and connecting grooves 40 in the two housing end walls 14 and 16 is achieved that the rotor 20 and the wings 26 in the axial direction on both sides are loaded at least approximately equal, so that no or only a small resultant force acts on the rotor 20 and the wings 26 in the direction of the axis of rotation 13. The depth of the annular groove 38 and the connecting groove 40 in the housing end wall 14,16, for example, about 0.1 to 2mm, preferably the width of the grooves 38 and 40 is greater than the depth.

In Figur 4 ist die Flügelzellenpumpe gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem der Aufbau im wesentlichen gleich ist wie beim ersten Ausführungsbeispiel, jedoch die Anordnung der Ringnut 138 modifiziert ist. Abweichend zum ersten Ausführungsbeispiel ist die Ringnut 138 exzentrisch zur Drehachse 13 des Rotors 20 angeordnet. Der Ringnut 138 ist beispielsweise zumindest annähernd kreisförmig ausgebildet, wobei deren Mittelpunkt M bezüglich der Drehachse 13 des Rotors 20 um einen die Exzentrizität bildenden Abstand e versetzt angeordnet ist. Vorzugsweise ist die Exzentrizität e der Ringnut 138 zumindest annähernd gleich groß und gleichsinnig wie die Exzentrizität der Innenseite der Umfangswand 18 des Pumpengehäuses 10. Vorzugsweise ist der Mittelpunkt M der Ringnut 138 zu einem in Drehrichtung 21 des Rotors 20 gesehen zwischen der Saugnut 30 und der Drucknut 34 liegenden Bereich der Umfangswand 18 hin bezüglich der Drehachse 13 versetzt angeordnet. Durch diese exzentrische Ausbildung der Ringnut 138 ist die radiale Erstreckung s1 des Dichtbereichs 139 innerhalb der Ringnut 138 zur Antriebswelle 12 hin auf der Seite, zu der hin der Mittelpunkt M bezüglich der Drehachse 13 versetzt ist, vergrößert während die radiale Erstreckung s2 des Dichtbereichs 139 auf der gegenüberliegenden Seite verringert ist. Es kann auch vorgesehen sein, dass die Ringnut 138 nicht kreisförmig ausgebildet ist, sondern einen exzentrischen Verlauf bezüglich der Drehachse 13 aufweist, wobei die radiale Erstreckung s1 des Dichtbereichs 139 in einem Bereich in Drehrichtung 21 des Rotors 20 zwischen der Saugnut 30 und der Drucknut 34 größer ist als die radiale Erstreckung s2 des Dichtbereichs 139 im gegenüberliegenden Bereich.In FIG. 4 is the vane pump according to a second embodiment shown, in which the construction is substantially the same as in the first embodiment, but the arrangement of the annular groove 138 is modified. Notwithstanding the first embodiment, the annular groove 138 is arranged eccentrically to the axis of rotation 13 of the rotor 20. The annular groove 138 is formed, for example, at least approximately circular, wherein the center M is arranged offset with respect to the axis of rotation 13 of the rotor 20 by a distance e forming the eccentricity. Preferably, the eccentricity e of the annular groove 138 is at least approximately equal and in the same direction as the eccentricity of the inner side of the peripheral wall 18 of the pump housing 10. Preferably, the center M of the annular groove 138 is seen in the direction of rotation 21 of the rotor 20 between the suction groove 30 and the pressure groove 34 lying portion of the peripheral wall 18 out with respect to the axis of rotation 13 arranged offset. As a result of this eccentric design of the annular groove 138, the radial extent s1 of the sealing region 139 within the annular groove 138 toward the drive shaft 12 on the side toward which the midpoint M is offset with respect to the axis of rotation 13 increases during the radial extent s2 of the sealing region 139 the opposite side is reduced. It can also be provided that the annular groove 138 is not circular, but has an eccentric course with respect to the axis of rotation 13, wherein the radial extent s1 of Sealing region 139 in a region in the direction of rotation 21 of the rotor 20 between the suction groove 30 and the pressure groove 34 is greater than the radial extent s2 of the sealing region 139 in the opposite region.

Claims (6)

  1. Vane cell pump with a pump casing (10) in which is arranged a rotor (20) which is driven in rotation by a drive shaft (12), the rotor (20) having, distributed over its circumference, a plurality of grooves (24) which run at least essentially radially with respect to the axis of rotation (13) of the rotor (20) and in which in each case a vane-like conveying element (26) is guided displaceably, with a circumferential wall (18) of the pump casing (10), which circumferential wall surrounds the rotor (20) and runs eccentrically with respect to the axis of rotation (13) of the latter and against which circumferential wall the conveying elements (26) bear with their radially outer ends, and with casing end walls (14, 16) of the pump casing (10) which are adjacent to the rotor (20) in the direction of the axis of rotation (13) of the latter, during the rotational movement of the rotor (20) a medium being conveyed by the conveying elements (26) from a suction region (28, 30) to a delivery region (32, 34) offset with respect to the latter in the direction of rotation (21) of the rotor (20), there being provided in at least one of the casing end walls (14, 16) a ring-shaped groove (38; 138) which extends at least over part of the circumference of the rotor (20) and which lies opposite the inner regions (25) delimited by the conveying elements (26) in the grooves (24) of the rotor (20), the ring-shaped groove being designed as an annular groove (38; 138) running over the entire circumference of the rotor (20), the annular groove (38; 138) being connected to the delivery region (32, 34) via a connecting groove (40) in the casing end wall (14, 16), and the connecting groove (40) running from the delivery region (32, 34) radially inwards in the direction of rotation (21) of the rotor (20) to the annular groove (38; 138), characterized in that the connecting groove (40) runs in a curved, preferably helically curved manner.
  2. Vane cell pump according to Claim 1, characterized in that the connecting groove (40) issues at least approximately tangentially into the annular groove (38; 138) and/or into a curved delivery groove (34) arranged in the delivery region.
  3. Vane cell pump according to Claim 2, characterized in that the connecting groove (40) issues into that end region of the delivery groove (34) which points opposite to the direction of rotation (21) of the rotor (20).
  4. Vane cell pump according to one of Claims 1 to 3, characterized in that the annular groove (138) runs eccentrically with respect to the axis of rotation (13) of the rotor (20).
  5. Vane cell pump according to Claim 4, characterized in that the annular groove (138) runs at least approximately circularly, and in that its centre point (M) is arranged so as to be offset with respect to the axis of rotation (13) of the rotor (20) in relation to a region of the circumferential wall (18) of the pump casing (10), which region lies between the suction region (28, 30) and the delivery region (32, 34) in the direction of rotation (21) of the rotor (20).
  6. Vane cell pump according to Claim 4, characterized in that the annular groove (138) runs at a greater radial distance from the axis of rotation (13) of the rotor (20) in a circumferential region which lies between the suction region (28, 30) and the delivery region (32, 34) in the direction of rotation (21) of the rotor (20) than in the opposite circumferential region.
EP05813372A 2004-12-16 2005-11-16 Vane cell pump Expired - Lifetime EP1828609B1 (en)

Applications Claiming Priority (2)

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DE102004060554A DE102004060554A1 (en) 2004-12-16 2004-12-16 Vane pump
PCT/EP2005/056012 WO2006063913A1 (en) 2004-12-16 2005-11-16 Vane cell pump

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EP1828609A1 EP1828609A1 (en) 2007-09-05
EP1828609B1 true EP1828609B1 (en) 2013-03-27

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EP05813372A Expired - Lifetime EP1828609B1 (en) 2004-12-16 2005-11-16 Vane cell pump

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US (1) US7878779B2 (en)
EP (1) EP1828609B1 (en)
JP (1) JP2008524485A (en)
CN (1) CN101080572A (en)
DE (1) DE102004060554A1 (en)
WO (1) WO2006063913A1 (en)

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DE102005047175A1 (en) 2005-09-30 2007-04-05 Robert Bosch Gmbh Vane pump for feeding e.g. diesel fuel, has ring shaped groove designed at front sides of rotor opposite to front wall of pump housing, where ring shaped groove is connected to pressure area and extends over part of rotor circumference
CN101581301B (en) * 2009-06-15 2014-02-05 胡东文 Vane pump/motor
CN102072148B (en) * 2009-11-25 2015-03-25 博世汽车柴油系统有限公司 Vane pump
US20120045355A1 (en) * 2010-08-17 2012-02-23 Paul Morton Variable displacement oil pump
GB2486007B (en) * 2010-12-01 2017-05-10 Itt Mfg Enterprises Inc Sliding vane pump
CN103917748B (en) * 2011-11-04 2018-05-29 大陆汽车有限责任公司 For the pump installation of pumped (conveying) medium
US9605673B2 (en) 2013-10-17 2017-03-28 Tuthill Corporation Pump with pivoted vanes
JP7243528B2 (en) * 2019-08-29 2023-03-22 株式会社デンソー vane pump
DE102019127389A1 (en) * 2019-10-10 2021-04-15 Schwäbische Hüttenwerke Automotive GmbH Vane pump

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JPH0469686U (en) * 1990-10-25 1992-06-19
US5147183A (en) * 1991-03-11 1992-09-15 Ford Motor Company Rotary vane pump having enhanced cold start priming
DE19529806C2 (en) * 1995-08-14 1999-04-01 Luk Fahrzeug Hydraulik Vane pump
DE19952167A1 (en) 1998-12-24 2000-06-29 Mannesmann Rexroth Ag Pump arrangement with two hydraulic pumps
DE102005047175A1 (en) 2005-09-30 2007-04-05 Robert Bosch Gmbh Vane pump for feeding e.g. diesel fuel, has ring shaped groove designed at front sides of rotor opposite to front wall of pump housing, where ring shaped groove is connected to pressure area and extends over part of rotor circumference

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Publication number Publication date
CN101080572A (en) 2007-11-28
WO2006063913A1 (en) 2006-06-22
EP1828609A1 (en) 2007-09-05
US20090291010A1 (en) 2009-11-26
JP2008524485A (en) 2008-07-10
US7878779B2 (en) 2011-02-01
DE102004060554A1 (en) 2006-06-22

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