EP2359005B1 - Sliding vane pump - Google Patents

Description

The invention relates to vane pumps with a mounted in a pump housing, driven by a shaft rotor, a plurality of outer rotor blades mounted on this wing and an outer ring surrounding the rotor and the wing plates, this either directly in the pump housing, or in a pump housing along predetermined paths movable adjusting ring is arranged.

In the prior art, the most varied designs of vane pumps are described above. For example, describe the DE 29 14 282 C2 , as well as the DE 103 53 027 A1 in each case adjustable vane pumps with a linearly displaceable adjusting ring to achieve a variable delivery capacity.
In the DE 195 33 686 C2 Another type of variable vane pump is described above with a collar pivotally mounted about a pin.
In most cases, on both sides of the rotor of a vane pump on the one hand a suction kidney and on the other hand to this offset by 180 ° arranged a pressure kidney.

All the aforementioned designs have in common that the inner ring between the bearing points of the separating elements is always arcuate, that is formed as a circular arc corresponding to the outer diameter of the respective inner ring.
In other property rights / patent applications, such as in the DE 33 34 919 C2 , of the DE 44 42 083 A1 or in the DE 602 07 401 T2 and the WO2005 / 003562 , which can be considered as the closest prior art, are described designs of vane pumps with variable capacity, in which at / in the radially inner edge of each cell chamber, ie in the "cylinder surface" of the respective rotor, over the entire rotor width extending, parallel to the Lagernuten the wing plates arranged at the radially inner edge of each cell chamber, spaced from the Lagernuten, always symmetrical to the center axis of each cell chamber formed in cross-section trough-shaped, usually almost trapezoidal transverse grooves are arranged, which often the volume of the respective pump cell chambers to one for the respective design should increase possible maximum.
In another patent application, such as in the DE 10 2004 019 326 A1 Other cell pumps, such as roller cell pumps are described in which at / in the radially inner edge of each cell chamber, ie again in the "cylinder surface" of the rotor, symmetrically formed to the center axis of each cell chamber, extending over the entire rotor width, parallel to the bearings of the cylindrical rollers on the radial arranged inside the edge of each cell chamber, in its cross-section almost rectangular, trough-shaped transverse grooves are arranged, which also significantly increase the volume of the respective pump chamber, and even approximately doubled in the design presented here.
Another cell pump will be in the DE 10 2006 061 326 A1 presented. This is a variable-speed pendulum pusher machine, in which in the FIG. 1 both on / in the radially inner edge of each cell chamber, ie in the "cylinder surface" of the inner rotor, as well as in the "cylinder surface" of the outer rotor, also over the entire Rotor width extending to the center axis of each cell chamber also symmetrically formed, in the "cylinder surface" of the inner rotor in its cross-section half round and in the "cylinder surface" of the outer rotor in its cross section almost trapezoidal, trough-shaped transverse grooves are arranged, which also in this design a very special Wing cell pump to increase the volume of the respective pump chamber as possible to a maximum.
As the prior art described shows, the pump designers have been and are endeavoring for decades to provide the largest possible inflow cross sections for best possible filling of the displacer cells by means of symmetrically designed "clearances" arranged in the rotor walls of the most varied vane pump designs.
According to the respective eccentricity of the rotor relative to the outer ring, the respective pump design then pumps the delivery volume flow by means of these solutions from the suction kidney into the pressure kidney.
A major disadvantage of the aforementioned types of vane pumps of the current state of the art, however, is still that at drive speeds in the range of 4500 U / min to over 6000 U / min addition (ie when using these vane pumps, for example, as directly from the crankshaft of a Motor vehicle driven oil pumps) high power losses, a rising noise with increasing speed noise and also increasing with increasing speed wear occurs.

The object of the invention is now to develop vane pumps, which avoid the aforementioned disadvantages of the prior art and in addition to the power losses, the noise and wear compared to the prior art pump designs, especially in the speed range from 4,500 U / min to Beyond 6,000 rpm, significantly reduced, but manufacturing technology are easy to manufacture and are also characterized in all speed ranges by a high reliability, a long life, a high specific flow rate and high efficiency.

According to the invention, this object is achieved by a vane pump with a rotor (3), which is mounted in a pump housing (1) and driven by a shaft (2), a plurality of wing plates (5) mounted in bearing grooves (4) of the rotor (3) and one rotor ( 3) and the wing plates (5) surrounding the outer ring (6) arranged on a in the pump housing (1) suction kidney (8) and to this offset by 180 ° in the pump housing (1) Druckniere (9), with the radially inner Edge of each cell chamber (10), that in the cylinder surface of the rotor (3), between the bearing grooves (4) over the entire rotor width extending, parallel to the bearing grooves (4) of the wing plates (5) arranged by the bearing grooves (4) a lateral web (11) spaced transverse grooves (12), which according to the invention are characterized in that these transverse grooves (12) have an asymmetrical cross-sectional profile (13), which in each cell chamber (10) via a point (14) with a smallest Radius of the rotor has, as seen in the direction of rotation is always located after the cell chamber center axis (15).
By means of this invention, asymmetrical design of the cross-sectional profile (13) of the transverse groove (12) in vane pumps were surprisingly the power losses, noise and wear compared to the previously described in the prior art pump designs in the speed range from 4,500 U / min to over 6,000 U / min addition significantly reduced.
The solution according to the invention is easy to manufacture in terms of production and is characterized in all speed ranges by a high reliability, a long service life, a high specific volume flow and also a high degree of efficiency.
In test series it was found that the cell chambers of the vane pumps described in the prior art with symmetrically strong "enlarged" cell geometry, especially in the speed range from 4,500 rev / min to more than 6,000 rpm, during the "suction phase" no longer "completely" filled become.
As a result of this "incomplete" filling of the cell chambers occurs in the prior art described in the art vane pumps with symmetrically enlarged cell cavitation phenomena, which is a cause of the occurring in the speed range from 4,500 rev / min to over 6,000 rpm noise developments, the in occurring in this speed range wear, but also for the power losses occurring in this speed range.
Surprisingly, in the experiments carried out with the novel cell chamber geometry, according to the inventive solution, in contrast, even at speeds in the range of 4,500 U / min to more than 6,000 U / min, always an optimal, complete, cavitation-free filling of the cell chambers according to the invention ( 10) realized without problems.
The novel, according to the invention, an asymmetrical cross-sectional profile (13) having transverse grooves (12) having in each cell chambers (10) via a point (14) with a smallest radius of the rotor, which is always in the direction of rotation after the cell chamber center axis (15) , ensure in the entire speed range due to their optimal, very special fluidic design also a low-friction and aerodynamically optimal complete filling of the pump chambers.
It should also be emphasized that, in addition to a complete and optimal filling of the cell chambers (10) at the same time but also with respect to the previous state by means of the inventive solution even at the previously very critical speeds, in the range of 4,500 rev / min to more than 6,000 of the Technique optimal and fast, low-friction emptying of the cell chambers (10) is ensured.
In this context, it is furthermore very advantageous that the transverse grooves (12) according to the invention can also be produced very easily in terms of production engineering.
In the test series carried out with the solution according to the invention, it was found that surprising effects occur also by means of the asymmetrical pump cell cross-section according to the invention, which are presumably caused in connection with the reflection of the liquid flowing into the cell chambers on the wing plates.
All these surprising effects caused by the solution according to the invention ensure complete filling of the pump chambers even beyond the 5000 rpm, as well as their optimal emptying, while at the same time significantly reducing the power loss and wear in vane pumps.
Particularly advantageous embodiments, details and other features of the invention will become apparent from the dependent claims and the following description of an embodiment of the invention in conjunction with two drawings for the solution according to the invention.
The invention will now be explained in more detail with reference to an embodiment in conjunction with two figures.

Figur 1 :

die erfindungsgemäße Flügelzellenpumpe in der Seitenansicht (ohne die seitliche Abdeckung);

Figur 2 :

die Darstellung des Querschnittsverlaufes 13 der erfindungsgemäßen Querrille 12, gemäß Figur 1 (in Polarkoordinaten).

It shows:

FIG. 1:

the vane pump according to the invention in the side view (without the side cover);

FIG. 2:

the representation of the cross-sectional profile 13 of the transverse groove 12 according to the invention, according to FIG. 1 (in polar coordinates).

Dieser Funktionsverlauf, als einer der möglichen Querschnittsverläufe 13 der erfindungsgemäßen Querrille 12, ist in den vg. Grenzen in der Figur 2 dargestellt.
Auch die in der Figur 1 dargestellten Querrillen 12 der Zellenkammern 10 haben stets diesen in der Figur 2 dargestellten Querschnittsverlauf 13.
Bei der in der Figur 1 dargestellten 7-flügligen Flügelzellenpumpe beträgt die Breite eines Segmentes (einschließlich der zugehörigen Flügelplattenabschnitte) 51,4285 °.
Betrachtet man den Rotormantel in einer Zellenkammer 10 so folgt dieser zunächst unmittelbar neben den die Zellenkammer 10 beidseitig begrenzenden Lagernuten 4, d.h. im Bereich der Lagerstege 11 (in diesem Ausführungsbeispiel beidseitig über einen "Breitenbereich" der Zellenkammer 10 von ca. 5%) dem "ursprünglichen" Rotoraußendurchmesser.
Die dabei gebildeten, unmittelbar neben den Lagernuten 4 der Flügelplatten 5 angeordneten Lagerstege 11 gewährleisten die erforderliche Kraftübertragung und Steifigkeit des Rotors 3 selbst bei einer hohen Beanspruchung der Flügelzellenpumpe.
In Drehrichtung gesehen folgt dem "ersten" Lagersteg 11 der betrachteten Zellenkammer 10 dann über ca. 63 % der Breite der Zellenkammer 10 entlang des fiktiven "ursprünglichen" Rotoraußendurchmessers ein zweiter Bereich in dem der Querschnittsverlauf 13 der Querrille 12 bis zu einen Punkt 14, in diesem Ausführungsbeispiel auf den Radius 31,5 mm, d.h. um 1,9 mm (2,85% des ursprünglichen Rotoraußendurchmessers vom 66,8 mm) abfällt.
Diesem zweiten Sektor folgt nach dem Punkt 14 ein dritter Sektor in dem der Querschnittsverlauf 13 der Querrille 12 relativ rasch wieder ansteigt und bereits nach ca. 27 % der Breite der Zellenkammer 10 entlang des fiktiven Rotoraußendurchmessers den ursprünglichen Außendurchmesser des Rotors 3 wieder erreicht.
Wie bereits erläutert wird dann der Verlauf des ursprünglichen Außendurchmessers des Rotors 3 als zweiter Lagersteg 11, in diesem Ausführungsbeispiel über einen Bereich der Zellenkammer 10 von ca. 5% entlang des ursprünglichen Außendurchmessers des Rotors 3 bis zur Lagernut 4 beibehalten.
Mittels dieser erfindungsgemäßen, unsymmetrischen Ausbildung des Querschnittsverlaufes 13 der Querrille 12 wird bei Flügelzellenpumpen überraschenderweise stets eine reibungsarme und strömungstechnisch optimale vollständige Befüllung der Pumpenkammern gewährleistet.
Insbesondere kann durch die erfindungsgemäße Lösung selbst bei den bisher sehr kritischen Drehzahlen im Bereich von 4.500 U/min bis selbst über 6.000 U/min problemlos eine optimale vollständige Befüllung der Zellenkammern 10 wie auch eine optimale schnelle und reibungsarme Entleerung der Zellenkammern 10 gewährleistet werden.
Dabei sind die erfindungsgemäßen Querrillen 12 zudem auch einfach fertigungstechnisch herstellbar.
Die Flügelzellenpumpen mit den erfindungsgemäßen, unsymmetrischen Querrillen zeichnen sich dabei gegenüber den Bauformen des Standes der Technik auch durch einen geräuschärmeren Lauf selbst bei sehr hohen Drehzahlen aus.
Wie bereits erläutert, wurde in den mit der erfindungsgemäßen Lösung durchgeführeten Versuchsreihen festgestellt, dass mittels der hier vorgestellten Lösung auch der Verschleiß der Flügelzellenpumpen deutlich gesenkt und die Verlustleistungen minimiert werden konnten.
Zusammenfassend kann zudem auch festgestellt werden, dass mittels der erfindungsgemäßen Lösung bei hoher Zuverlässigkeit und hoher Lebensdauer ein hoher spezifischer Fördervolumenstrom mit hohem Wirkungsgrad sowohl bei niedrigen, wie aber insbesondere auch bei hohen Drehzahlen, d.h. im Bereich von 4.500 U/min bis über 6.000 U/min hinaus, gewährleistet werden kann.
In dem in der Figur 1 dargestellten Ausführungsbeispiel ist im Rotor 3 ein Führungsring 19 eingepasst der an den "innen liegenden" Stirnseiten 16 der Flügelplatten 5 anliegt, welche selbst wiederum mit ihren "außen liegenden" Stirnseiten 16 am Außenring 6 anliegen.
Kennzeichnend ist dabei, dass die Flügelplatten 5 der erfindungsgemäßen Flügelzellenpumpe an ihren Stirnseiten 16 abgerundet sind.
Im vorliegenden Ausführungsbeispiel entspricht der an den Stirnseiten 16 der Flügelplatten 5 angeordnete Radius dem halben Abstand zwischen den Stirnseiten 16 der Flügelplatten 5.
Dadurch wird neben einer optimalen und reibungs- und verschleißarmen Abdichtung der Zellenkammer am Außenring 6, gleichzeitig auch eine optimale, reibungs- und verschleißarme Führung am Führungsring 19 während des gesamten Umlaufs der Welle 2 gewährleistet.
Erfindungsgemäß ist auch, dass in den Wandungen 17 der im Rotor 3 angeordneten Lagernuten 4 der Flügelplatten 5 Schmiertaschen 18 angeordnet sind, welche den Verschleiß zwischen den Flügelplatten 5 und Lagernuten 4 deutlich minimieren.
Die in Verbindung mit der erfindungsgemäßen Lösung in der Figur 1 dargestellte Steuerdruckkammer 23 wird beidseitig jeweils von einer Dichtleiste 24 abgedichtet, wobei die Dichtleisten 24 in jeweils zugeordneten und vom Steuerdruck der Galerie druckbeaufschlagten Führungskammernuten 25 verschiebbar gelagert sind.
Vorteilhaft ist in diesem Zusammenhang, dass in den Führungskammernuten 25 (unterhalb der Dichtleisten 24) federnde Elemente, z.B. wie in der Figur 1 dargestellt, Blattfedern 27 angeordnet sind, welche gewährleisten, dass die Dichtleisten 24 auch dann noch an das Pumpengehäuse 1 angepresst werden wenn die Flügelzellenpumpe (der Motor) angehalten/gestoppt wird.
Erfindungsgemäß sind die Führungskammernuten 25 über Verbindungskanäle 26 mit der Steuerdruckkammer 23 verbunden, so dass diese sicher von dem über die Zuströmöffnung 22 einströmenden Steuerdruck der Galerie beaufschlagt werden können, und so auch unter extremen Bedingungen eine hoch zuverlässige und sehr sichere Abdichtung der Steuerdruckkammer 23 mittels der Dichtleisten 24 bei minimalem Bauraum gewährleisten.In the FIG. 1 the vane pump according to the invention in the side view, without cover with a mounted in a pump housing 1, by a shaft 2, in this embodiment of the crankshaft directly driven rotor 3, with a plurality of bearing grooves 4 of the rotor 3 radially displaceably mounted wing plates 5 and a the Rotor 3 and the wing plates 5 surrounding outer ring 6 shown.
This outer ring 6 is arranged in this embodiment in a rotatably mounted, provided with a control lever 20 lock slider 7.
On one side of the control lever 20 is mounted in the pump housing 1 compression spring 21 at.
On the opposite side of the actuating lever 20 via a feed opening 22 acted upon by the control pressure of the gallery control pressure chamber 23 is arranged.
In the pump housing 1, there is furthermore a suction kidney 8 and a pressure kidney 9 which is offset by 180 ° relative thereto.
At the radially inner edge of each cell chamber 10 of the rotor 3 are between the bearing grooves 4 of the wing plates 5, over the entire width, ie along the lateral surface of the rotor 3 extending, parallel to the bearing grooves 4 of the wing plates 5 arranged by the bearing grooves 4 to a bearing web 11 spaced transverse grooves 12 are arranged.
According to the invention, these transverse grooves 12, as already explained, an asymmetrical cross-sectional profile 13 which has a point 14 in each of the cell chambers 10 with a smallest radius of the rotor is always arranged in the direction of rotation of the cell chamber center axis 15, said point 14 in Embodiment about 1% to 8% of the outer diameter of the rotor 3 radially within this imaginary, the bearing webs 11 fictitious interconnecting outer diameter of the rotor 3 is located.
It is also characteristic that the asymmetrical cross-sectional profile 13 of the transverse grooves 12 on the rotor 3, as shown in this embodiment, can also be described by a polynomial of the 4th degree.
The polynomial underlying this embodiment is defined in the range of about - 0.42 radians to + 0.42 radians and reads: $$\mathrm{y}\mathrm{=}\mathrm{39}\mathrm{.}\mathrm{33695}{\mathrm{x}}^{\mathrm{4}}\mathrm{-}\mathrm{31}\mathrm{.}\mathrm{29170}{\mathrm{x}}^{\mathrm{3}}\mathrm{+}\mathrm{0}\mathrm{.}\mathrm{4913634}{\mathrm{x}}^{\mathrm{2}}\mathrm{+}\mathrm{5}\mathrm{.}\mathrm{285977}\mathrm{x}\mathrm{+}\mathrm{32}\mathrm{.}\mathrm{22,082th}$$

This functional course, as one of the possible cross-sectional profiles 13 of the transverse groove 12 according to the invention, is shown in FIGS. Borders in the FIG. 2 shown.
Also in the FIG. 1 shown transverse grooves 12 of the cell chambers 10 always have this in the FIG. 2 illustrated cross section course 13th
When in the FIG. 1 The illustrated 7-blade vane pump is the width of one segment (including the associated wing panel sections) 51.4285 °.
Considering the rotor shell in a cell chamber 10, it follows immediately next to the cell chamber 10 on both sides limiting bearing grooves 4, ie in the region of the bearing webs 11 (in this embodiment, on both sides over a "width range" of the cell chamber 10 of about 5%) the " original "rotor outside diameter.
The thus formed, immediately adjacent to the bearing grooves 4 of the wing plates 5 arranged bearing webs 11 ensure the required power transmission and rigidity of the rotor 3 even at high stress of the vane pump.
Seen in the direction of rotation follows the "first" bearing web 11 of the considered cell chamber 10 then about 63% of the width of the cell chamber 10 along the fictional "original" rotor outer diameter, a second region in which the cross-sectional profile 13 of the transverse groove 12 up to a point 14, this embodiment drops to the radius 31.5 mm, ie, 1.9 mm (2.85% of the original rotor outer diameter of 66.8 mm).
After the point 14, this second sector is followed by a third sector in which the cross-sectional profile 13 of the transverse groove 12 rises again relatively quickly and already after approximately 27% of the width of the cell chamber 10 along the notional Rotor outer diameter reaches the original outer diameter of the rotor 3 again.
As already explained, the course of the original outer diameter of the rotor 3 as the second bearing bar 11, in this exemplary embodiment over an area of the cell chamber 10 of approximately 5% along the original outer diameter of the rotor 3 up to the bearing groove 4, is then maintained.
By means of this invention, asymmetrical design of the cross-sectional profile 13 of the transverse groove 12 is surprisingly always ensured in vane pumps a low-friction and aerodynamically optimal complete filling of the pump chambers.
In particular, can be ensured by the inventive solution even at the previously very critical speeds in the range of 4,500 rev / min to even more than 6,000 rpm easily complete optimal filling of the cell chambers 10 as well as an optimal fast and low-friction emptying of the cell chambers 10.
In addition, the transverse grooves 12 according to the invention are also easy to manufacture.
The vane pumps with the asymmetrical transverse grooves according to the invention are distinguished from the designs of the prior art also by a quieter running even at very high speeds.
As already explained, it was found in the experimental series carried out with the solution according to the invention that by means of the solution presented here, the wear of the vane pumps could also be significantly reduced and the power loss minimized.
In summary, it can also be stated that by means of the solution according to the invention with high reliability and a long service life a high specific delivery volume flow with high efficiency both at low, but especially at high speeds, ie Range from 4,500 rpm to over 6,000 rpm.
In the in the FIG. 1 illustrated embodiment, a guide ring 19 is fitted in the rotor 3 which rests against the "inner" end faces 16 of the wing plates 5, which in turn rest with their "outer" end faces 16 on the outer ring 6.
It is characteristic that the wing plates 5 of the vane pump according to the invention are rounded at their end faces 16.
In the present exemplary embodiment, the radius arranged on the end faces 16 of the wing panels 5 corresponds to half the distance between the end faces 16 of the wing panels 5.
As a result, in addition to an optimal and low-friction and low-wear sealing of the cell chamber on the outer ring 6, at the same time ensures optimal, low-friction and low-wear guidance on the guide ring 19 during the entire circulation of the shaft 2.
It is also according to the invention that 5 lubrication pockets 18 are arranged in the walls 17 of the bearing grooves 4 of the wing plates arranged in the rotor 3, which clearly minimize the wear between the wing plates 5 and the bearing grooves 4.
In connection with the solution according to the invention in the FIG. 1 shown control pressure chamber 23 is sealed on both sides in each case by a sealing strip 24, wherein the sealing strips 24 are displaceably mounted in respectively associated and pressurized by the control pressure of the gallery Führungsungskammernuten 25.
It is advantageous in this context that in the Führungsungskammernuten 25 (below the sealing strips 24) resilient elements, eg as in the FIG. 1 represented, leaf springs 27 are arranged, which ensure that the sealing strips 24 are still pressed against the pump housing 1 when the vane pump (the motor) is stopped / stopped.
According to the invention, the guide chamber grooves 25 are connected via connecting channels 26 to the control pressure chamber 23, so that they are safe from the can be acted upon via the inflow opening 22 incoming control pressure of the gallery, and thus ensure a highly reliable and very secure sealing of the control pressure chamber 23 by means of the sealing strips 24 with minimal space under extreme conditions.

REFERENCE SYMBOL

1

pump housing

2

wave

3

rotor

4

bearing grooves

5

wing plates

6

outer ring

7

lock slider

8th

suction kidney

9

pressure kidney

10

cell chamber

11

bearing web

12

transverse grooves

13

Cross-sectional profile

14

nadir

15

Cell chamber center axis

16

front

17

wall

18

lubrication pocket

19

guide ring

20

lever

21

compression spring

22

inflow

23

Control pressure chamber

24

sealing strip

25

Führungskammernuten

26

connecting channel

27

leaf spring

Claims (10)

1. Sliding vane pump with a rotor (3) mounted in a pump housing (1) and driven by a shaft (2), several vane plates (5) mounted in bearing grooves (4) of the rotor (3) and an outer ring (6) surrounding the rotor (3) and the vane plates (5), with a suction kidney (8) arranged in the pump housing (1) and a pressure kidney (9) arranged in the pump housing (1) offset from this component by 180°, with at the radial inner edge of each cell chamber (10), i.e. in the radial outer cylinder liner surface of the rotor (3), between the bearing grooves (4), running over the complete rotor width, parallel to the bearing grooves (4) of the vane plates (5), transverse grooves (12) separated from the bearing grooves (4) by a bearing journal (11), characterised by the fact that these transverse grooves (12) have an asymmetrical cross-section progression (13), which in every cell chamber (10) has a point (14) with a smallest radius of the rotor (3), which viewed in the direction of rotation is always arranged after the cell chamber central axis (15).
2. Sliding vane pump in accordance with Claim 1, characterised by the fact that the point (14) with a smallest radius of the rotor lies radially within approx. 1 % to 8 % of the outer diameter of an intended outer diameter of the rotor (3) connecting the bearing journals (11) with each other.
3. Sliding vane pump in accordance with Claim 1, characterised by the fact that the vane plates (5) are rounded off (ball-shaped) on their front faces (16).
4. Sliding vane pump in accordance with Claim 3, characterised by the fact that the vane plates (5) are provided with radii on their front faces (16).
5. Sliding vane pump in accordance with Claim 4, characterised by the fact that the radius arranged on the front faces (16) of the vane plates (5) corresponds to half the distance between the front faces (16).
6. Sliding vane pump in accordance with Claim 1, characterised by the fact that lubrication pockets (18) are arranged in the walls (17) of the bearing grooves (4) of the vane plates (5) in the rotor (3).
7. Sliding vane pump in accordance with Claim 1, characterised by the fact that the outer ring (6) is mounted in a rotating setting slide (7) provided with a setting lever (20), which is in contact on one side of the setting lever (20) with a pressure spring (21) mounted in the pump housing (1), and on the other side of the setting lever (20) there is a control pressure chamber (23) pressurised by an inflow opening (22) by the control pressure of the gallery.
8. Sliding vane pump in accordance with Claim 7, characterised by the fact that the control pressure chamber (23) is sealed on both sides by a sealing strip (24), which are mounted in sliding mountings in facing, pressurised guide chamber grooves (25).
9. Sliding vane pump in accordance with Claim 8, characterised by the fact that the guide chamber grooves (25) are connected with the control pressure chamber (23) by means of connecting channels (26).
10. Sliding vane pump in accordance with Claim 8, characterised by the fact that leaf springs (27) are arranged in the guide chamber grooves (25) underneath the sealing strips (24).

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