EP1794457B1 - Vane cell pump - Google Patents

Vane cell pump Download PDF

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Publication number
EP1794457B1
EP1794457B1 EP06776763A EP06776763A EP1794457B1 EP 1794457 B1 EP1794457 B1 EP 1794457B1 EP 06776763 A EP06776763 A EP 06776763A EP 06776763 A EP06776763 A EP 06776763A EP 1794457 B1 EP1794457 B1 EP 1794457B1
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EP
European Patent Office
Prior art keywords
stator
cell pump
vane cell
pump according
piston
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 - Fee Related
Application number
EP06776763A
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German (de)
French (fr)
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EP1794457A1 (en
Inventor
Willi Schneider
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Joma Hydromechanic GmbH
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Joma Hydromechanic GmbH
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Filing date
Publication date
Priority claimed from DE200510048602 external-priority patent/DE102005048602B4/en
Priority claimed from DE102006021971A external-priority patent/DE102006021971B4/en
Application filed by Joma Hydromechanic GmbH filed Critical Joma Hydromechanic GmbH
Publication of EP1794457A1 publication Critical patent/EP1794457A1/en
Application granted granted Critical
Publication of EP1794457B1 publication Critical patent/EP1794457B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • 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

Definitions

  • the invention relates to a vane pump with an inner rotor and a plurality of vanes, which are mounted radially displaceable in substantially radial slots in the inner rotor and slides directly or indirectly along the inner peripheral surface of a stator, wherein the axis of the stator and the axis of the inner rotor offset to each other and the stator relative to the inner rotor in the radial direction adjustable and thereby the offset is variable, and the stator has a arranged in the housing of the vane pump pivot bearing.
  • a vane pump with an annular inner rotor known, in which a plurality of radially outwardly extending wing elements are received radially displaceable.
  • the radially inner end portions of the wing elements are supported on a non-rotatable central part, the radially outer end portions of a non-rotatable outer ring.
  • the rotor can be rotated about a rotation axis that is offset from the central axis of the central part and the outer ring. In this way, at a rotational movement of the rotor between the wing elements initially larger and then smaller again conveying cells. Due to the change in volume of the delivery cells fluid is first sucked into the delivery cells and then ejected again. The end regions of the wing elements slide on the central part or the outer ring.
  • Such a vane pump can be made simple and inexpensive.
  • Object of the present invention is to provide a vane cell machine which has a high efficiency and at the same time can be easily and inexpensively manufactured.
  • stator protrudes at least one curved piston portion whose piston axis extends in the circumferential direction of the stator to the pivot bearing.
  • a piston or piston portion which serves to adjust the stator and which protrudes from the stator and whose piston axis extends in the circumferential direction to the pivot bearing.
  • the piston movement thus runs in sections in a radius around the pivot bearing.
  • the piston portion has a defined piston surface, which also rotates in the circumferential direction about the pivot bearing, which has the advantage that the actuating forces on the stator are proportional to the compressive forces acting on the piston surface.
  • the piston section and the stator are integrally formed.
  • the piston portion and the stator are made Plastic or aluminum.
  • the piston portion loosely abuts the stator.
  • This variant has the advantage that the piston portion and the stator can be made of different materials and that they are easy to install.
  • the piston section is attached to the stator, in particular screwed.
  • the stator and the piston section can be made of different materials and pressure and suction forces can be transmitted.
  • stator is equipped with two piston sections.
  • stator in particular when the two piston sections with respect to the axis of the stator are opposite to each other, be adjusted in the direction of maximum delivery and in the direction of minimum funding, for which control pressures on the piston sections attack.
  • the cross section of the piston is rectangular.
  • This embodiment has the advantage that both the production of the piston and the production of the piston section receiving space in the housing can be relatively easily done by the stator receiving portion of the housing is plate-shaped, and provided the portion only with a piston portion receiving breakthrough must be, with the lateral sealing on other plates (end plates) takes place.
  • a cylinder receiving the piston portion is provided in that in the housing of the vane pump, a cylinder receiving the piston portion is provided.
  • This cylinder has not only the task of forming the piston chamber for the piston section, but also the task of guiding and supporting the stator, so that the pivot bearing has only the task to absorb the forces occurring in the circumferential direction of the pivot bearing, but not in radial Direction of tensile and compressive forces.
  • the cylinder supports the piston section at least over part of its length on the radially inner and outer running surfaces.
  • a defined piston chamber is created, which acts on a defined piston surface.
  • the running parallel to the pivot axis running surfaces simultaneously serve as support surfaces for perpendicular to the pivot axis acting on the stator forces. As a result, the pivot axis is relieved.
  • an overflow channel is provided on the outer circumference of the stator, which connects an outlet channel on the one end face of the vane pump with an outlet channel on the other end side of the vane pump.
  • the overflow channel runs axially parallel to the axis of the stator. This has the significant advantage that the overflow can be relatively easily manufactured, and that the overflow can be relatively easily connected to the outlet channels by provided in side lids arcuate flow channels.
  • the piston portion thus has the dual function of an adjusting member for the stator to adjust this between a maximum and a minimum promotion, and also connects the two outlet channels, which open on the two end faces of the interior of the stator.
  • an overflow channel is provided between the stator and the machine housing, which connects the inlet channel on one end face of the vane pump with the inlet channel on the other end face of the vane pump.
  • This overflow channel is formed by the space required for the displacement of the stator in the housing.
  • the overflow channels for both the inlet channel and the outlet channel offer the advantage that the vane pump can be flown from both end sides, whereby an optimal filling of the working spaces is made possible.
  • the pumped medium can flow off quickly and without loss, since it can leave the working space via both end faces.
  • a particularly preferred embodiment of the invention provides that protrudes from the stator, a support member for a printing element.
  • This support element is in particular one piece on Stator provided and serves to receive the force of a compression spring, in particular a coil spring.
  • the pressure element is a leaf spring, a leg spring or a pneumatic cushion.
  • This pressure element which is biased in particular, has the task of adjusting the stator in the direction of the maximum delivery of the pump. This is necessary if in a fault, the pneumatic or hydraulic control fails over the piston sections. The control by means of the pressure element ensures that the vane pump continues to operate at its maximum power in order to supply the connected system with the medium to be conveyed.
  • FIG. 1 schematically shows a housing 10 of a generally designated 12 vane pump, in which a drive shaft 14 is mounted.
  • This drive shaft 14 drives an inner rotor 16, which has a plurality of radial slots 18, in which wings 20 are mounted radially displaceable.
  • These wings 20 have a thickened end 22 to which sliding blocks 24 are pivotally mounted.
  • the sliding shoes 24 abut against the inner circumferential surface 26 of a stator 28, resulting in FIG. 2 is apparent.
  • the inner rotor 16, two wings 20, two sliding shoes 24 and the stator 28 each have a working space 30.
  • the working space 30 increases and decreases in rotating inner rotor 16, whereby a fluid is conveyed.
  • stator 28 has a bearing eye 32 which surrounds a pin 34 and a housing-fixed pivot bearing 36 forms.
  • the stator 28 can therefore be pivoted in the direction of the double arrow 38 within the housing 10 about the pivot bearing 36.
  • the stator 28 has two piston sections 40 and 42, which protrude from the outer periphery of the stator 28 and the piston axes 44 extend in the circumferential direction about the pivot bearing 36, that is concentric to this.
  • the piston sections 40 and 42 are each guided in a cylinder 46, which in the housing 10 of the vane pump 12th is provided.
  • the axis of the cylinder 46 also extends concentrically about the pivot bearing 36.
  • the cylinder 46 abuts over a portion of the length of the piston portions 40 and 42 at the radially inner and outer raceway surfaces of the piston portions 40 and 42.
  • the piston portions 40 and 42 each have a piston surface 48, which are acted upon by a pressure and exert a pivoting force about the pivot bearing 36 on the stator 28.
  • stator 28 is formed with its piston portions 40 and 42 substantially disc or plate-shaped, so that the piston portions 40 and 42 have rectangular cross-sections.
  • the sealing of the pressure chambers 50 and 52 takes place in each case via disc-shaped or plate-shaped elements which are placed on the end faces 54 and 56 of the stator 28. As a result, the work spaces 30 are closed at the front.
  • FIG. 2 can still be seen that from the stator 28, a support member 58 protrudes, which has a centering nose for a pressure element 62, for example a spiral spring 64.
  • the pressure element 62 exerts a force on the stator 28, which causes a pivoting of the stator 28 about the pivot bearing 36 in the clockwise direction. In this way, the stator 28 is permanently urged in the direction of maximum delivery, so that the vane pump 12 assumes its position for the maximum promotion in case of failure.
  • FIG. 4 shows the minimum promotion, in which the axis 66 of the stator 28 has almost no offset 70 to the axis 68 of the inner rotor 16. This offset 70, or the eccentricity of the inner rotor 16, determines the delivery volume of the vane pump 12.
  • an extension 72 is provided which has a substantially triangular cross-section.
  • This extension 72 has an overflow channel 74, which is clearly in FIG. 5 is shown, and connects the two end faces 54 and 56 with each other.
  • the outlet channels not shown in the drawing, which are provided in the front side mounted cover plates and in which the conveyed medium flows out of the working spaces 30, are connected to each other, so that the working spaces 30 can be emptied through both end faces 54 and 56.
  • an overflow channel 76 is provided which surrounds the stator 28 and connects the provided on both end faces 54 and 56 inlet channels together. In this way, the working spaces 30 can be filled from both end faces 54 and 56.
  • the two transfer ports 74 and 76 thus serve to increase the efficiency of the vane pump 12 by the working spaces 30 can be filled and emptied more effectively. Losses are thereby reduced.
  • the housing 10 of the vane pump 12 is formed substantially disc-shaped or plate-shaped, in which the receiving space for the stator 28 and the cylinder 46 are incorporated as openings.
  • the frontal sealing is done by placing one plate at a time.
  • the production of such components is relatively simple and the assembly can be done by machine.

Description

Die Erfindung betrifft eine Flügelzellenpumpe mit einem Innenrotor und einer Vielzahl von Flügeln, die in im Wesentlichen radialen Schlitzen im Innenrotor radial verschieblich gelagert sind und an der Innenumfangsfläche eines Stators direkt oder indirekt entlang gleitet, wobei die Achse des Stators und die Achse des Innenrotors einen Versatz zueinander aufweisen und der Stator bezüglich des Innenrotors in radialer Richtung verstellbar und dadurch der Versatz veränderbar ist, und der Stator ein im Gehäuse der Flügelzellenpumpe angeordnetes Schwenklager aufweist.The invention relates to a vane pump with an inner rotor and a plurality of vanes, which are mounted radially displaceable in substantially radial slots in the inner rotor and slides directly or indirectly along the inner peripheral surface of a stator, wherein the axis of the stator and the axis of the inner rotor offset to each other and the stator relative to the inner rotor in the radial direction adjustable and thereby the offset is variable, and the stator has a arranged in the housing of the vane pump pivot bearing.

Aus der DE 100 40 711 A1 ist eine Flügelzellenpumpe mit einem ringförmigen Innenrotor bekannt, in dem eine Mehrzahl von sich radial nach außen erstreckenden Flügelelementen radial verschieblich aufgenommen sind. Die radial inneren Endbereiche der Flügelelemente stützen sich an einem drehfesten Zentralteil ab, die radial außen liegenden Endbereiche an einem drehfesten Außenring. Der Rotor kann um eine Drehachse gedreht werden, die gegenüber der Mittelachse des Zentralteils und des Außenrings versetzt ist. Auf diese Weise bilden sich bei einer Drehbewegung des Rotors zwischen den Flügelelementen zunächst größer und dann wieder kleiner werdende Förderzellen. Durch die Volumenänderung der Förderzellen wird zunächst Fluid in die Förderzellen angesaugt und dann wieder ausgestoßen. Die Endbereiche der Flügelelemente gleiten auf dem Zentralteil bzw. dem Außenring. Eine solche Flügelzellenpumpe kann einfach und preiswert hergestellt werden.From the DE 100 40 711 A1 is a vane pump with an annular inner rotor known, in which a plurality of radially outwardly extending wing elements are received radially displaceable. The radially inner end portions of the wing elements are supported on a non-rotatable central part, the radially outer end portions of a non-rotatable outer ring. The rotor can be rotated about a rotation axis that is offset from the central axis of the central part and the outer ring. In this way, at a rotational movement of the rotor between the wing elements initially larger and then smaller again conveying cells. Due to the change in volume of the delivery cells fluid is first sucked into the delivery cells and then ejected again. The end regions of the wing elements slide on the central part or the outer ring. Such a vane pump can be made simple and inexpensive.

Zur Erhöhung des Wirkungsgrades ist aus der DE 195 32 703 C1 eine Flügelzellenmaschine in Form einer Pendelschieberpumpe bekannt. Bei dieser sind die Flügelelemente in einem Innenrotor verschieblich aufgenommen, wohingegen sie in einem ringförmigen Außenrotor schwenkbar gehalten sind. Die Drehachse des Innenrotors ist gegenüber der Drehachse des Außenrotors versetzt, wodurch im Betrieb ebenfalls sich zunächst vergrößernde und dann wieder verkleinernde Förderzellen gebildet werden. Die aus der DE 195 32 703 C1 bekannte Pendelschieberpumpe ist jedoch komplex und somit teuer in der Herstellung.To increase the efficiency is from the DE 195 32 703 C1 a vane machine in the form of a pendulum slide pump known. In this, the wing elements are in one Inner rotor slidably received, whereas they are pivotally held in an annular outer rotor. The axis of rotation of the inner rotor is offset with respect to the axis of rotation of the outer rotor, whereby in operation also initially magnifying and then shrinking conveyor cells are formed. The from the DE 195 32 703 C1 However, known pendulum slide pump is complex and therefore expensive to manufacture.

Aufgabe der vorliegenden Erfindung ist es, eine Flügelzellenmaschine zu schaffen, die einen hohen Wirkungsgrad aufweist und gleichzeitig einfach und preiswert hergestellt werden kann.Object of the present invention is to provide a vane cell machine which has a high efficiency and at the same time can be easily and inexpensively manufactured.

Diese Aufgabe wird durch eine Flügelzellenmaschine gelöst, bei der vom Stator wenigstens ein gekrümmter Kolbenabschnitt abragt, dessen Kolbenachse in Umfangsrichtung des Stators zum Schwenklager verläuft.This object is achieved by a vane machine in which the stator protrudes at least one curved piston portion whose piston axis extends in the circumferential direction of the stator to the pivot bearing.

Bei der erfindungsgemäßen Flügelzellenpumpe ist ein Kolben oder Kolbenabschnitt vorgesehen, der zur Verstellung des Stators dient und der vom Stator abragt und dessen Kolbenachse in Umfangsrichtung zum Schwenklager verläuft. Die Kolbenbewegung läuft demnach abschnittsweise in einem Umkreis um das Schwenklager. Der Kolbenabschnitt weist eine definierte Kolbenfläche auf, die ebenfalls in Umfangsrichtung um das Schwenklager umläuft, was den Vorteil besitzt, dass die Stellkräfte auf den Stator proportional zu den auf die Kolbenfläche wirkenden Druckkräften sind. Hierdurch können exakte Einstellungen des Stators und somit des zu fördernden Volumens der Flügelzellenpumpe vorgenommen werden, die proportional zum auf den Kolbenabschnitt wirkenden Druck sind. Dadurch wird eine feinfühlige Verstellung möglich.In the vane pump according to the invention, a piston or piston portion is provided which serves to adjust the stator and which protrudes from the stator and whose piston axis extends in the circumferential direction to the pivot bearing. The piston movement thus runs in sections in a radius around the pivot bearing. The piston portion has a defined piston surface, which also rotates in the circumferential direction about the pivot bearing, which has the advantage that the actuating forces on the stator are proportional to the compressive forces acting on the piston surface. As a result, exact settings of the stator and thus of the volume of the vane pump to be delivered can be made which are proportional to the pressure acting on the piston section. This makes a sensitive adjustment possible.

Bei einer Weiterbildung ist vorgesehen, dass der Kolbenabschnitt und der Stator einteilig ausgebildet sind. Insbesondere bestehen der Kolbenabschnitt und der Stator aus Kunststoff oder Aluminium. Hierdurch wird eine preiswerte Herstellung der Flügelzellenpumpe ermöglicht, und die Montage wird vereinfacht. Außerdem können am Kolbenabschnitt sowohl Druck- als auch Saugkräfte angreifen.In a further development it is provided that the piston section and the stator are integrally formed. In particular, the piston portion and the stator are made Plastic or aluminum. As a result, an inexpensive production of the vane pump is possible, and the assembly is simplified. In addition, both pressure and suction forces can act on the piston portion.

Bei einer Variante liegt der Kolbenabschnitt lose am Stator an. Diese Variante besitzt den Vorteil, dass der Kolbenabschnitt und der Stator aus unterschiedlichen Materialien bestehen können und dass sie einfach montierbar sind.In one variant, the piston portion loosely abuts the stator. This variant has the advantage that the piston portion and the stator can be made of different materials and that they are easy to install.

Bei einer anderen Variante ist der Kolbenabschnitt am Stator befestigt, insbesondere angeschraubt. Auch bei dieser Variante können der Stator und der Kolbenabschnitt aus unterschiedlichen Materialien bestehen und es können Druck- und Saugkräfte übertragen werden.In another variant, the piston section is attached to the stator, in particular screwed. In this variant too, the stator and the piston section can be made of different materials and pressure and suction forces can be transmitted.

Eine Weiterbildung der Erfindung sieht vor, dass der Stator mit zwei Kolbenabschnitten bestückt ist. Auf diese Weise kann der Stator, insbesondere dann, wenn die beiden Kolbenabschnitte bezüglich der Achse des Stators einander gegenüber liegen, in Richtung der Maximalförderung und in Richtung der Minimalförderung verstellt werden, wofür Steuerdrücke an den Kolbenabschnitten angreifen.A development of the invention provides that the stator is equipped with two piston sections. In this way, the stator, in particular when the two piston sections with respect to the axis of the stator are opposite to each other, be adjusted in the direction of maximum delivery and in the direction of minimum funding, for which control pressures on the piston sections attack.

Hierdurch wird eine sehr feinfühlige Einstellung bzw. Positionierung des Stators erzielt, was bei Kennfeldregelungen erforderlich ist. Insbesondere dann, wenn die beiden Kolbenabschnitte gegensinnig wirkend am Stator angeordnet sind, können schon kleinste Druckänderungen bei der Positionierung des Stators berücksichtigt werden. Insbesondere muss nicht gegen eine Federkonstante gearbeitet werden, was den Nachteil hat, dass gegen eine sich ändernde Kraft einer Feder, d.h. gegen eine Federkonstante, gearbeitet werden muss. Es können direkt die anfallenden Drücke zum Verlagern des Stators und zwar in beide Richtungen, verwendet werden.As a result, a very sensitive adjustment or positioning of the stator is achieved, which is required for map control. In particular, when the two piston sections are arranged in opposite directions acting on the stator, even the smallest pressure changes in the positioning of the stator can be considered. In particular, it is not necessary to work against a spring constant, which has the disadvantage that it is necessary to work against a changing force of a spring, ie against a spring constant. It can directly the resulting pressures for displacing the stator and that in both directions, can be used.

Mit Vorzug ist der Querschnitt des Kolbens rechteckförmig ausgebildet. Diese Ausgestaltung bietet den Vorteil, dass sowohl die Herstellung des Kolbens als auch die Herstellung des den Kolbenabschnitt aufnehmenden Raumes im Gehäuse relativ einfach erfolgen kann, indem der den Stator aufnehmende Abschnitt des Gehäuses plattenförmig ist, und der Abschnitt lediglich mit einem den Kolbenabschnitt aufnehmenden Durchbruch versehen werden muss, wobei die seitliche Abdichtung über weitere Platten (Stirnplatten) erfolgt.With preference, the cross section of the piston is rectangular. This embodiment has the advantage that both the production of the piston and the production of the piston section receiving space in the housing can be relatively easily done by the stator receiving portion of the housing is plate-shaped, and provided the portion only with a piston portion receiving breakthrough must be, with the lateral sealing on other plates (end plates) takes place.

Eine optimale Führung des Kolbens und somit des Stators im Gehäuse wird dadurch erzielt, dass im Gehäuse der Flügelzellenpumpe ein den Kolbenabschnitt aufnehmender Zylinder vorgesehen ist. Dieser Zylinder hat nicht nur die Aufgabe, den Kolbenraum für den Kolbenabschnitt zu bilden, sondern auch die Aufgabe, den Stator zu führen und abzustützen, so dass das Schwenklager lediglich die Aufgabe besitzt, die in Umfangsrichtung zum Schwenklager auftretenden Kräfte aufzunehmen, jedoch keine in radialer Richtung anfallenden Zug- und Druckkräfte.An optimal guidance of the piston and thus of the stator in the housing is achieved in that in the housing of the vane pump, a cylinder receiving the piston portion is provided. This cylinder has not only the task of forming the piston chamber for the piston section, but also the task of guiding and supporting the stator, so that the pivot bearing has only the task to absorb the forces occurring in the circumferential direction of the pivot bearing, but not in radial Direction of tensile and compressive forces.

Bei einer Weiterbildung der Erfindung ist vorgesehen, dass der Zylinder den Kolbenabschnitt zumindest über einen Teil seiner Länge an der radial inneren und äußeren Lauffläche abstützt. Hierdurch wird ein definierter Kolbenraum geschaffen, der auf eine definierte Kolbenfläche wirkt. Außerdem dienen die parallel zu Schwenkachse verlaufenden Laufflächen gleichzeitig als Stützflächen für senkrecht zur Schwenkachse am Stator angreifende Kräfte. Hierdurch wird die Schwenkachse entlastet.In a development of the invention, it is provided that the cylinder supports the piston section at least over part of its length on the radially inner and outer running surfaces. As a result, a defined piston chamber is created, which acts on a defined piston surface. In addition, the running parallel to the pivot axis running surfaces simultaneously serve as support surfaces for perpendicular to the pivot axis acting on the stator forces. As a result, the pivot axis is relieved.

Bei einer Weiterbildung der Erfindung ist vorgesehen, dass am Außenumfang des Stators ein Überströmkanal vorgesehen ist, der einen Auslasskanal auf der einen Stirnseite der Flügelzellenpumpe mit einem Auslasskanal auf der anderen Stirnseite der Flügelzellenpumpe verbindet. Hierdurch wird der Wirkungsgrad der Flügelzellenpumpe erhöht, da das geförderte Medium effektiver, d.h. verlustärmer abtransportiert werden kann.In a development of the invention, it is provided that an overflow channel is provided on the outer circumference of the stator, which connects an outlet channel on the one end face of the vane pump with an outlet channel on the other end side of the vane pump. This will be the Increased efficiency of the vane pump, since the pumped medium can be transported more effectively, ie loss of energy.

Dabei verläuft der Überströmkanal achsparallel zur Achse des Stators. Dies hat den wesentlichen Vorteil, dass der Überströmkanal relativ einfach hergestellt werden kann, und dass der Überströmkanal durch in seitlichen Deckeln vorgesehenen bogenförmigen Strömungskanälen relativ einfach an die Auslasskanäle angeschlossen werden kann.The overflow channel runs axially parallel to the axis of the stator. This has the significant advantage that the overflow can be relatively easily manufactured, and that the overflow can be relatively easily connected to the outlet channels by provided in side lids arcuate flow channels.

Mit Vorzug ist der Überströmkanal ein Teil des Kolbenabschnitts. Der Kolbenabschnitt besitzt demnach die Doppelfunktion eines Verstellglieds für den Stator, um diesen zwischen einer Maximal- und einer Minimalförderung zu verstellen, und außerdem verbindet er die beiden Auslasskanäle, die auf den beiden Stirnseiten aus dem Innenraum des Stators ausmünden.With preference, the overflow is part of the piston section. The piston portion thus has the dual function of an adjusting member for the stator to adjust this between a maximum and a minimum promotion, and also connects the two outlet channels, which open on the two end faces of the interior of the stator.

Mit Vorzug ist zwischen dem Stator und dem Maschinengehäuse ein Überströmkanal vorgesehen, der den Einlasskanal auf der einen Stirnseite der Flügelzellenpumpe mit dem Einlasskanal auf der anderen Stirnseite der Flügelzellenpumpe verbindet. Dieser Überströmkanal wird von dem Freiraum gebildet, der für die Verlagerung des Stators im Gehäuse erforderlich ist.With preference, an overflow channel is provided between the stator and the machine housing, which connects the inlet channel on one end face of the vane pump with the inlet channel on the other end face of the vane pump. This overflow channel is formed by the space required for the displacement of the stator in the housing.

Die Überströmkanäle sowohl für den Einlasskanal als auch für den Auslasskanal bieten den Vorteil, dass die Flügelzellenpumpe von beiden Stirnseiten angeströmt werden kann, wodurch eine optimale Befüllung der Arbeitsräume ermöglicht wird. Außerdem kann das geförderte Medium schnell und verlustfrei abströmen, da es über beide Stirnseiten den Arbeitsraum verlassen kann.The overflow channels for both the inlet channel and the outlet channel offer the advantage that the vane pump can be flown from both end sides, whereby an optimal filling of the working spaces is made possible. In addition, the pumped medium can flow off quickly and without loss, since it can leave the working space via both end faces.

Eine besonders bevorzugte Ausgestaltung der Erfindung sieht vor, dass vom Stator ein Abstützelement für ein Druckelement abragt. Dieses Abstützelement ist insbesondere einteilig am Stator vorgesehen und dient dazu, die Kraft einer Druckfeder, insbesondere einer Wendelfeder aufzunehmen. Es ist aber auch denkbar, dass das Druckelement eine Blattfeder, eine Schenkelfeder oder ein pneumatisches Kissen ist. Dieses Druckelement, welches insbesondere vorgespannt ist, hat die Aufgabe, den Stator in Richtung der Maximalförderung der Pumpe zu verstellen. Dies ist dann erforderlich, wenn in einem Störfall die pneumatische oder hydraulische Ansteuerung über die Kolbenabschnitte ausfällt. Durch die Ansteuerung mittels des Druckelements ist sichergestellt, dass die Flügelzellenpumpe weiterhin und dazu noch mit ihrer Maximalleistung arbeitet, um das angeschlossene System mit dem zu fördernden Medium zu versorgen.A particularly preferred embodiment of the invention provides that protrudes from the stator, a support member for a printing element. This support element is in particular one piece on Stator provided and serves to receive the force of a compression spring, in particular a coil spring. But it is also conceivable that the pressure element is a leaf spring, a leg spring or a pneumatic cushion. This pressure element, which is biased in particular, has the task of adjusting the stator in the direction of the maximum delivery of the pump. This is necessary if in a fault, the pneumatic or hydraulic control fails over the piston sections. The control by means of the pressure element ensures that the vane pump continues to operate at its maximum power in order to supply the connected system with the medium to be conveyed.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung zwei besonders bevorzugte Ausführungsbeispiele im einzelnen beschrieben sind. Dabei können die in der Zeichnung dargestellten sowie in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesendlich sein.Further advantages, features and details of the invention will become apparent from the following description in which two particularly preferred embodiments are described in detail with reference to the drawing. In this case, the features shown in the drawing and mentioned in the claims and in the description may each be individually invention itself or in any combination invention.

In der Zeichnung zeigen:

Figur 1
einen Querschnitt durch eine erste Ausführungsform der erfindungsgemäßen Flügelzellenpumpe;
Figur 2
eine perspektivische Ansicht des Stators mit eingesetztem Rotor, teilweise geschnitten;
Figur 3
einen Querschnitt durch eine zweite Ausführungsform der erfindungsgemäßen Flügelzellenpumpe, die Stellung des Innenrotors bei Maximalförderung zeigend;
Figur 4
einen Querschnitt gemäß Figur 3, die Stellung des Innenrotors bei Minimalförderung zeigend; und
Figur 5
eine perspektivische Darstellung der Flügelzellenpumpe gemäß Figur 3.
In the drawing show:
FIG. 1
a cross section through a first embodiment of the vane pump according to the invention;
FIG. 2
a perspective view of the stator with inserted rotor, partially cut away;
FIG. 3
a cross section through a second embodiment of the vane pump according to the invention, showing the position of the inner rotor at maximum promotion;
FIG. 4
a cross section according to FIG. 3 showing the position of the inner rotor at minimum conveyance; and
FIG. 5
a perspective view of the vane pump according to FIG. 3 ,

Zum besseren Verständnis der Erfindung wird auf die DE 10 2005 048 602 Bezug genommen, deren Inhalt hiermit eingeführt wird.For a better understanding of the invention is based on the DE 10 2005 048 602 Reference is made, the content of which is hereby introduced.

Die Figur 1 zeigt schematisch ein Gehäuse 10 einer insgesamt mit 12 bezeichneten Flügelzellenpumpe, in welcher eine Antriebswelle 14 gelagert ist. Diese Antriebswelle 14 treibt einen Innenrotor 16 an, welcher eine Vielzahl radialer Schlitze 18 aufweist, in welchen Flügel 20 radial verschieblich gelagert sind. Diese Flügel 20 besitzen ein verdicktes Ende 22, an welchem Gleitschuhe 24 schwenkbar befestigt sind. Die Gleitschuhe 24 liegen an der Innenumfangsfläche 26 eines Stators 28 an, was aus Figur 2 ersichtlich ist. Dabei bilden der Innenrotor 16, zwei Flügel 20, zwei Gleitschuhe 24 sowie der Stator 28 jeweils einen Arbeitsraum 30. Der Arbeitsraum 30 vergrößert und verkleinert sich bei sich drehendem Innenrotor 16, wodurch ein Fluid gefördert wird.The FIG. 1 schematically shows a housing 10 of a generally designated 12 vane pump, in which a drive shaft 14 is mounted. This drive shaft 14 drives an inner rotor 16, which has a plurality of radial slots 18, in which wings 20 are mounted radially displaceable. These wings 20 have a thickened end 22 to which sliding blocks 24 are pivotally mounted. The sliding shoes 24 abut against the inner circumferential surface 26 of a stator 28, resulting in FIG. 2 is apparent. In this case, the inner rotor 16, two wings 20, two sliding shoes 24 and the stator 28 each have a working space 30. The working space 30 increases and decreases in rotating inner rotor 16, whereby a fluid is conveyed.

Außerdem ist in den Figuren 1 und 2 erkennbar, dass der Stator 28 ein Lagerauge 32 aufweist, welches einen Zapfen 34 umgreift und ein gehäusefestes Schwenklager 36 bildet. Der Stator 28 kann demnach in Richtung des Doppelpfeils 38 innerhalb des Gehäuses 10 um das Schwenklager 36 verschwenkt werden. Hierfür weist der Stator 28 zwei Kolbenabschnitte 40 und 42 auf, die vom Außenumfang des Stators 28 abragen und deren Kolbenachsen 44 sich in Umfangsrichtung um das Schwenklager 36, d.h. konzentrisch zu diesem erstrecken. Die Kolbenabschnitte 40 und 42 sind jeweils in einem Zylinder 46 geführt, der im Gehäuse 10 der Flügelzellenpumpe 12 vorgesehen ist. Die Achse des Zylinders 46 verläuft ebenfalls konzentrisch um das Schwenklager 36. Der Zylinder 46 liegt über einen Teil der Länge der Kolbenabschnitte 40 und 42 an den radial inneren und äußeren Laufflächen der Kolbenabschnitte 40 und 42 an. Die Kolbenabschnitte 40 und 42 besitzen jeweils eine Kolbenfläche 48, die von einem Druck beaufschlagt werden und die eine Schwenkkraft um das Schwenklager 36 auf den Stator 28 ausüben.Moreover, in the FIGS. 1 and 2 recognizable that the stator 28 has a bearing eye 32 which surrounds a pin 34 and a housing-fixed pivot bearing 36 forms. The stator 28 can therefore be pivoted in the direction of the double arrow 38 within the housing 10 about the pivot bearing 36. For this purpose, the stator 28 has two piston sections 40 and 42, which protrude from the outer periphery of the stator 28 and the piston axes 44 extend in the circumferential direction about the pivot bearing 36, that is concentric to this. The piston sections 40 and 42 are each guided in a cylinder 46, which in the housing 10 of the vane pump 12th is provided. The axis of the cylinder 46 also extends concentrically about the pivot bearing 36. The cylinder 46 abuts over a portion of the length of the piston portions 40 and 42 at the radially inner and outer raceway surfaces of the piston portions 40 and 42. The piston portions 40 and 42 each have a piston surface 48, which are acted upon by a pressure and exert a pivoting force about the pivot bearing 36 on the stator 28.

Aus den Figuren 1 und 2 ist deutlich erkennbar, dass der Stator 28 mit seinen Kolbenabschnitten 40 und 42 im wesentlichen scheiben- oder plattenförmig ausgebildet ist, so dass die Kolbenabschnitte 40 und 42 rechteckförmige Querschnitte aufweisen. Die Abdichtung der Druckräume 50 und 52 erfolgt jeweils über Scheiben- oder plattenförmige Elemente, die auf die Stirnseiten 54 und 56 des Stators 28 aufgesetzt werden. Hierdurch werden auch die Arbeitsräume 30 stirnseitig verschlossen.From the FIGS. 1 and 2 is clearly visible that the stator 28 is formed with its piston portions 40 and 42 substantially disc or plate-shaped, so that the piston portions 40 and 42 have rectangular cross-sections. The sealing of the pressure chambers 50 and 52 takes place in each case via disc-shaped or plate-shaped elements which are placed on the end faces 54 and 56 of the stator 28. As a result, the work spaces 30 are closed at the front.

Aus Figur 2 ist noch ersichtlich, dass vom Stator 28 ein Abstützelement 58 abragt, welches eine Zentriernase für ein Druckelement 62, zum Beispiel eine Wendelfeder 64 aufweist. Das Druckelement 62 übt eine Kraft auf den Stator 28 aus, welche ein Verschwenken des Stators 28 um das Schwenklager 36 in Richtung des Uhrzeigersinns bewirkt. Auf diese Weise wird der Stator 28 permanent in Richtung der Maximalförderung gedrängt, so dass die Flügelzellenpumpe 12 im Störfall ihre Stellung für die Maximalförderung einnimmt.Out FIG. 2 can still be seen that from the stator 28, a support member 58 protrudes, which has a centering nose for a pressure element 62, for example a spiral spring 64. The pressure element 62 exerts a force on the stator 28, which causes a pivoting of the stator 28 about the pivot bearing 36 in the clockwise direction. In this way, the stator 28 is permanently urged in the direction of maximum delivery, so that the vane pump 12 assumes its position for the maximum promotion in case of failure.

In den Figuren 3 und 5, die ein zweites Ausführungsbeispiel der erfindungsgemäßen Flügelzellenpumpe 12 zeigen, ist der Stator 28 in der Maximalförderung dargestellt. Die Figur 4 zeigt die Minimalförderung, in welcher die Achse 66 des Stators 28 nahezu keinen Versatz 70 zur Achse 68 des Innenrotors 16 aufweist. Dieser Versatz 70, oder die Exzentrizitätdes Innenrotors 16, bestimmt das Fördervolumen der Flügelzellenpumpe 12.In the Figures 3 and 5 showing a second embodiment of the vane pump 12 according to the invention, the stator 28 is shown in the maximum funding. The FIG. 4 shows the minimum promotion, in which the axis 66 of the stator 28 has almost no offset 70 to the axis 68 of the inner rotor 16. This offset 70, or the eccentricity of the inner rotor 16, determines the delivery volume of the vane pump 12.

In den Figuren 3 bis 5 ist noch erkennbar, dass am Kolbenabschnitt 40 ein Fortsatz 72 vorgesehen ist, der einen im wesentlichen dreieckförmigen Querschnitt aufweist. Dieser Fortsatz 72 besitzt einen Überströmkanal 74, der deutlich in Figur 5 dargestellt ist, und der die beiden Stirnseiten 54 und 56 miteinander verbindet. Auf diese Weise können die in der Zeichnung nicht dargestellten Auslasskanäle, welche in stirnseitig angebrachten Deckplatten vorgesehen sind und in welche das geförderte Medium aus den Arbeitsräumen 30 ausströmt, miteinander verbunden werden, so dass die Arbeitsräume 30 über beide Stirnseiten 54 und 56 entleert werden können.In the FIGS. 3 to 5 is still recognizable that on the piston portion 40, an extension 72 is provided which has a substantially triangular cross-section. This extension 72 has an overflow channel 74, which is clearly in FIG. 5 is shown, and connects the two end faces 54 and 56 with each other. In this way, the outlet channels, not shown in the drawing, which are provided in the front side mounted cover plates and in which the conveyed medium flows out of the working spaces 30, are connected to each other, so that the working spaces 30 can be emptied through both end faces 54 and 56.

Außerdem ist in den Figuren 4 und 5 erkennbar, dass zwischen dem Stator 28 und dem Gehäuse 10 ein Überströmkanal 76 vorgesehen ist, der den Stator 28 umgibt und der die auf beiden Stirnseiten 54 und 56 vorgesehenen Einlasskanäle miteinander verbindet. Auf diese Weise können die Arbeitsräume 30 von beiden Stirnseiten 54 und 56 aus befüllt werden.Moreover, in the FIGS. 4 and 5 recognizable that between the stator 28 and the housing 10, an overflow channel 76 is provided which surrounds the stator 28 and connects the provided on both end faces 54 and 56 inlet channels together. In this way, the working spaces 30 can be filled from both end faces 54 and 56.

Die beiden Überströmkanäle 74 und 76 dienen also der Erhöhung des Wirkungsgrads der Flügelzellenpumpe 12, indem die Arbeitsräume 30 wirkungsvoller befüllt und entleert werden können. Verluste werden dadurch verringert.The two transfer ports 74 and 76 thus serve to increase the efficiency of the vane pump 12 by the working spaces 30 can be filled and emptied more effectively. Losses are thereby reduced.

Der Figur 5 kann noch entnommen werden, dass das Gehäuse 10 der Flügelzellenpumpe 12 im wesentlichen scheibenförmig bzw. plattenförmig ausgebildet ist, in welchem der Aufnahmeraum für den Stator 28 sowie die Zylinder 46 als Durchbrüche eingearbeitet sind. Die stirnseitige Abdichtung erfolgt durch Aufsetzen jeweils einer Platte. Die Herstellung derartiger Bauteile ist relativ einfach und die Montage kann maschinell erfolgen.Of the FIG. 5 can be found that the housing 10 of the vane pump 12 is formed substantially disc-shaped or plate-shaped, in which the receiving space for the stator 28 and the cylinder 46 are incorporated as openings. The frontal sealing is done by placing one plate at a time. The production of such components is relatively simple and the assembly can be done by machine.

Claims (17)

  1. A vane cell pump (12) with an inner rotor (16) and a plurality of vanes (20), which are essentially mounted radially displaceable in radial slots (18) in the inner rotor (16) and slide directly and indirectly on the internal circumferential surface (26) of a stator (28), the axis (66) of the stator (28) and the axis (68) of the inner rotor (16) being offset (70) in relation to one another, and the stator (28) being radially adjustable in relation to the inner rotor (16), and the offset (70) being consequently modifiable, and the stator (28) comprising a pivot bearing (36) arranged in the housing (10) of the vane cell pump (12), characterized in that at least one curved piston section (40 or 42) protrudes from the stator (28), whose piston axis (44) runs in the circumferential direction with respect to the pivot bearing (36).
  2. The vane cell pump according to claim 1, characterized in that the piston section (40 or 42) and the stator (28) are constructed in one piece.
  3. The vane cell pump according to claim 1, characterized in that the piston section (40 or 42) rests loosely on the stator (28).
  4. The vane cell pump according to claim 1, characterized in that the piston section (40 or 42) is attached, particularly screwed to the stator (28).
  5. The vane cell pump according to one of the preceding claims, characterized in that the stator (28) is equipped with two piston sections (40 or 42).
  6. The vane cell pump according to claim 5, characterized in that both piston sections (40 and 42) are opposite to one another in relation to the axis (66) of the stator (28).
  7. The vane cell pump according to claim 5 or 6, characterized in that both piston sections (40 and 42) act in opposite directions.
  8. The vane cell pump according to one of the preceding claims, characterized in that cross section of the piston section (40 and/or 42) has a rectangular shape.
  9. The vane cell pump according to one of the preceding claims, characterized in that a cylinder (46) is arranged in the housing (10) of the vane cell pump (12) to locate the piston section (40 or 42).
  10. The vane cell pump according to claim 9, characterized in that the cylinder (46) supports the piston section (40 or 42) at least over part of its length in an internal and an external radial tread surface.
  11. The vane cell pump according to one of the preceding claims, characterized in that on an external circumference of the stator (28) an overflow duct (74) is provided, which connects an outlet duct on one face side (54) of the vane cell pump (12) with an outlet duct on the other face side (56) of the vane cell pump (12).
  12. The vane cell pump according to claim 11, characterized in that the overflow duct (74) runs axially parallel to the axis (66) of the stator (28).
  13. The vane cell pump according to claim 11 or 12, characterized in that the overflow duct (74) is part of the piston section (40).
  14. The vane cell pump according to one of the preceding claims, characterized in that between the stator (28) and the housing (10) an overflow duct (76) is provided, which connects an inlet duct on one face side (54) of the vane cell pump (12) with an inlet duct on the other face side (56) of the vane cell pump (12).
  15. The vane cell pump according to one of the preceding claims, characterized in that a supporting element (58) for a compression element (62) protrudes from the stator (28).
  16. The vane cell pump according to claim 15, characterized in that the supporting element (58) and the stator (28) are constructed in one piece.
  17. The vane cell pump according to claim 15 or 16, characterized in that a compression spring, particularly a spiral coiled spring (64) meshes with the supporting element (58).
EP06776763A 2005-10-06 2006-08-11 Vane cell pump Expired - Fee Related EP1794457B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE200510048602 DE102005048602B4 (en) 2005-10-06 2005-10-06 Vane machine, in particular vane pump
DE102006021971A DE102006021971B4 (en) 2005-10-06 2006-05-03 Vane pump
PCT/EP2006/007944 WO2007039013A1 (en) 2005-10-06 2006-08-11 Vane cell pump

Publications (2)

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EP1794457A1 EP1794457A1 (en) 2007-06-13
EP1794457B1 true EP1794457B1 (en) 2009-07-08

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EP06776763A Expired - Fee Related EP1794457B1 (en) 2005-10-06 2006-08-11 Vane cell pump

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US (1) US7785087B2 (en)
EP (1) EP1794457B1 (en)
JP (1) JP4834734B2 (en)
KR (1) KR101146845B1 (en)
DE (1) DE502006004164D1 (en)
WO (1) WO2007039013A1 (en)

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JP2009510331A (en) 2009-03-12
WO2007039013A8 (en) 2007-09-27
WO2007039013A1 (en) 2007-04-12
EP1794457A1 (en) 2007-06-13
KR101146845B1 (en) 2012-05-16
US7785087B2 (en) 2010-08-31
US20080014108A1 (en) 2008-01-17
DE502006004164D1 (en) 2009-08-20
JP4834734B2 (en) 2011-12-14
KR20080049689A (en) 2008-06-04

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