JP2009156041A - Vane pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vane pump having a simple constitution capable of making a vane force act to one axial side. <P>SOLUTION: The vane pump has an inclined face 35A on an end face 8a on the other axial side of the vane 8 for making the vane 8 fluid force Fb act to one axial side (to the lower side in Fig.6) of a rotating shaft Ax accompanied by the rotation of a rotating part 4. Specifically, the inclined face 35A is formed extending toward one axial side so as progress to the forward side in a rotating direction RD from the front side. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a vane pump.

As a conventional vane pump, one disclosed in Patent Document 1 is known. In the vane pump disclosed in Patent Document 1, the slit that accommodates the vane formed in the rotor is inclined obliquely with respect to the rotation axis, and thereby the reaction force is directed from the side surface of the slit toward the one side in the axial direction with respect to the vane. And the vane is pressed against the casing. Thereby, the reciprocation of the vane in the axial direction is suppressed, and thus vibration and noise are suppressed.
JP 2006-132430 A

  However, in the vane pump disclosed in Patent Document 1, it is difficult to accurately form a slit that is inclined obliquely with respect to the rotation axis, which is a cause of an increase in manufacturing cost.

  Then, an object of this invention is to obtain the vane pump which can make the force to an axial direction one side act on a vane by simpler structure.

  In the invention of claim 1, a plurality of slits that extend radially with respect to the rotation axis of the rotating portion and that open radially outward are formed in the base portion of the rotating portion that rotates within the casing, The vane is housed in a retractable manner, an annular chamber formed around the base portion in the casing is partitioned by the plurality of vanes to form a plurality of pump chambers, and the rotating chamber is rotated to rotate the pump chamber. In the vane pump configured to discharge the fluid sucked into the pump chamber by periodically increasing / decreasing the volume of the rotary shaft, the surface of the vane is moved toward the one side in the axial direction of the rotating shaft as the rotating portion rotates. An inclined surface for applying a fluid force to the vane is provided.

  In the invention of claim 2, the inclined surface is formed on the end surface on the other side in the axial direction of the vane so as to go to the one side in the axial direction from the front side in the rotational direction to the front side. Features.

  According to the first aspect of the present invention, it is possible to apply a fluid force to the vane on one side in the axial direction of the rotary shaft by the inclined surface. Therefore, with a relatively simple configuration, the reciprocation of the vane in the axial direction can be suppressed, and the vibration and noise caused by the reciprocation can be suppressed.

  According to the second aspect of the present invention, it is only necessary to process the inclined surface on the end surface on the other side in the axial direction of the vane. Therefore, the above effect can be obtained with a relatively inexpensive configuration.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The following embodiment and the plurality of modifications include similar components. Therefore, below, about the same component, the overlapping description is abbreviate | omitted and suppose that a common code | symbol is provided.

  (First Embodiment) FIG. 1 is a cross-sectional view of a vane pump according to a first embodiment of the present invention in a cross-section orthogonal to the rotation axis, FIG. 2 is a cross-sectional view of the vane pump including a rotation axis, FIG. FIG. 4 is an exploded perspective view of the vane pump, FIG. 4 is an enlarged view of a part of FIG. 2, and FIG. 5 is a side view showing a rotating part included in the vane pump. In the following, the lower side of FIGS. 2, 3 and 4 is defined as one axial side of the rotation axis Ax, and the upper side is defined as the other axial side.

  First, with reference to FIG. 1, the structure regarding the suction | inhalation and discharge of the working fluid of the vane pump 1 is demonstrated.

  In the vane pump 1 according to the present embodiment, as shown in FIG. 1, in the casing 2, a substantially circular shape of the rotating portion 4 that rotates around the substantially cylindrical inner peripheral surface 3 a of the annular ring 3 and the rotation axis Ax. An annular chamber 6 for storing a working fluid (liquid) is formed between the outer peripheral surface 5 a of the columnar base portion 5. The width w of the annular chamber 6 changes along the circumferential direction of the rotation axis Ax. In the present embodiment, the center C of the inner peripheral surface 3a and the rotation axis Ax are shifted in parallel so that the inner peripheral surface 3a of the ring 3 and the base portion 5 of the rotating portion 4 are eccentric. For this reason, the width w of the annular chamber 6 is minimum at the right end position in FIG. 1, gradually increases in the clockwise direction from the right end position, and becomes maximum at the left end position, from the left end position to the right end position. It gradually becomes narrower gradually in the clockwise direction.

  A plurality of (four in the present embodiment) slits 7 are formed in the base portion 5 so as to extend radially outward with respect to the rotation axis Ax of the rotating portion 4 and open in the radially outward direction. A rectangular bar-like or substantially strip-like vane 8 is accommodated so as to protrude and retract. The vane 8 is urged radially outward in the slit 7 by the centrifugal force generated with the rotation of the rotating portion 4 and the pressurization of the working fluid introduced to the rotation axis Ax side in the slit 7. For this reason, the vane 8 rotates together with the rotating portion 4 while being in sliding contact with the inner peripheral surface 3a.

  The annular chamber 6 is divided into the same number (four in this embodiment) of pump chambers 9 by a plurality of vanes 8 arranged at a constant pitch in the circumferential direction. With the rotation of the rotating unit 4 and the vane 8, the volume of the pump chamber 9 changes according to the change in the width w of the annular chamber 6. That is, the volume of each pump chamber 9 is minimum at the right end position in FIG. And it increases gradually with the rotation to the rotation direction RD (clockwise direction of FIG. 1) of the rotation part 4, and becomes the maximum in the position of a left end. When the rotating unit 4 further rotates in the clockwise direction from that position, the volume of the pump chamber 9 gradually decreases and becomes the minimum at the right end position. That is, in this embodiment, the volume of the pump chamber 9 is expanded in the lower half section of FIG. 1 in one rotation of the rotating unit 4, and the volume of the pump chamber 9 is decreased in the upper half section. Therefore, the suction opening 11 is provided on the inner peripheral surface 3a of the ring 3 and the casing 2 (first casing 10) so as to face the section in which the volume of the pump chamber 9 increases, and the volume of the pump chamber 9 is reduced. A discharge opening 12 is provided facing the section. The suction opening 11 communicates with the suction passage 14 in the suction pipe 13 projecting on the side surface of the first casing 10, and the discharge opening 12 is in the discharge pipe 15 projecting in parallel with the suction pipe 13. It communicates with the discharge passage 16.

  Therefore, in FIG. 1, when the rotating unit 4 rotates in the rotation direction RD, the pump chamber 9 partitioned by the two adjacent vanes 8 moves from the right end position to the left end position while increasing the volume. Therefore, the working fluid flows into the pump chamber 9 from the suction passage 14 via the suction opening 11. The pump chamber 9 moves from the left end position to the right end position while reducing the volume. For this reason, the working fluid flows out from the pump chamber 9 to the discharge passage 16 through the discharge opening 12. Such inflow and outflow of the working fluid are sequentially performed with respect to the plurality of pump chambers 9, and thus continuous suction and discharge of the working fluid by the vane pump 1 is realized.

  Next, with reference to FIGS. 1-5, the structure of each part of the vane pump 1 concerning this embodiment is demonstrated in detail.

  As shown in FIG. 2, the slit 7 formed in the base portion 5 of the rotating portion 4 is closed by the bottom wall portion 17 on one side in the axial direction, and the vane 8 slides on the bottom wall portion 17. It reciprocates in the slit 7 in contact. That is, in the present embodiment, the bottom wall portion 17 corresponds to the guide wall portion. The bottom wall portion 17 is formed with a communication hole 17a that communicates with the inner diameter of the slit 7. The back wall (one side in the axial direction) of the bottom wall portion 17 is formed in the slit 7 through the communication hole 17a. From the above, a pressurized pressure of the working fluid is introduced.

  The bottom wall portion 17 is formed in a disc shape centering on the rotation axis Ax and orthogonal to the rotation axis Ax, and projects in a flange shape from the outer peripheral surface 5a of the base portion 5 to the outside. A substantially cylindrical skirt portion 18 projects from the outer peripheral edge of the bottom wall portion 17. The skirt portion 18 is concentric with the rotation axis Ax, and protrudes with a substantially constant thickness toward the side away from the base portion 5 (one side in the axial direction).

  The skirt portion 18 functions as a rotor (rotor) of the motor 19 that drives the rotating portion 4, and N poles and S poles are alternately magnetized along the circumferential direction of the stator core 20 around which the coil is wound. The magnetized portion 18a is included. At least a portion of the skirt portion 18 that functions as the magnetized portion 18a is made of a magnetic material. In this case, only a portion of the skirt portion 18 facing the teeth 20a may be made of a magnetic material (for example, a hard magnetic material such as a ferrite magnet or a samarium cobalt magnet), or the entire skirt portion 18 may be made of a magnetic material. Alternatively, the entire rotating unit 4 may be made of a magnetic material. In this case, the rotating part 4 and the skirt part 18 can be formed by mixing a resin material with a powdery or granular magnetic filler made of a magnetic material.

  As shown in FIGS. 1 and 3, the outer peripheral surface 5a of the base portion 5 is recessed in the radially inward direction at a constant pitch, whereby a blade portion 5b is formed. The blade portion 5 b rotates together with the base portion 5 (rotating portion 4), and enhances the performance of discharging the working fluid from the pump chamber 9 when facing the discharge opening 12.

  As shown in FIG. 2, a bearing portion 22 that rotatably supports the shaft 21 is fixed to the central portion of the base body portion 5 (rotating portion 4). The bearing portion 22 may be a sliding bearing such as a metal bush, or may be a rolling bearing such as a needle bearing.

  The rotating unit 4 is configured to rotate about the rotation axis Ax in an internal space 2a (see FIG. 2) formed by the casing 2. In the present embodiment, the casing 2 includes a first casing 10 located on the other axial side (the upper side in FIGS. 2 and 3) and a first casing 10 located on the one axial side (the lower side in FIGS. 2 and 3). 2 and a ring 3 forming the outer peripheral surface of the annular chamber 6 (the inner peripheral surface 3a of the ring 3).

  As shown in FIG. 3, the ring 3 includes a cylindrical portion 3 b that forms the outer peripheral surface of the annular chamber 6, and a flange portion 3 c that projects from the one side in the axial direction of the cylindrical portion 3 b in the radially outward direction of the rotation axis Ax. And a rib 3d that forms part of the side walls of the suction passage 14 and the discharge passage 16. The cylindrical portion 3b and the rib 3d are erected at substantially the same height in the axial direction of the rotation axis Ax from the disc-shaped annular flange portion 3c.

  As shown in FIG. 2, the ring 3 is accommodated in a recess 10 b formed in the first casing 10. That is, the concave portion 10b is formed in a shape that fits the cylindrical portion 3b of the ring 3 and the rib 3d. Further, the outer peripheral portion 3e of the flange portion 3c of the ring 3 is in contact with the annular wall portion 23a of the second casing 23 on the opposite side of the concave portion 10b, and this portion is in contact with the first casing 10 and the second casing 23. The ring 3 is fixed in the axial direction of the rotation axis Ax.

  The second casing 23 includes a substantially annular recess 23b that accommodates the skirt portion 18 of the rotating portion 4, and the second casing 23 side (one axial side, FIG. A recess 23c is formed to accommodate a portion projecting to the lower side of FIG.

  A region outside the annular wall portion 23a on the outer periphery of the concave portion 23b is a contact surface with the first casing 10. A groove portion 23d for the O-ring 34 is formed in a substantially annular shape on the abutting surface, and the O-ring 34 mounted in the groove portion 23d is used at the boundary portion between the first casing 10 and the second casing 23. The seal is secured. In addition, a seal member (for example, a gasket, an O-ring, or the like) is appropriately interposed also in a boundary portion (for example, a boundary surface between the flange portion 3c of the ring 3 and the first casing 10) between the members other than the boundary portion. The sealing performance of each boundary portion may be improved.

  A shaft 21 is installed between the bottom wall 23e of the recess 23c and the protrusion 10c of the first casing 10, and the center of the shaft 21 is a rotation axis Ax. The shaft 21 passes through a bearing portion 22 provided at the center of the rotating portion 4 and is rotatably supported by the bearing portion 22.

  In addition, as shown in FIG. 2, a protrusion is provided between the recess 23 b and the recess 23 c from the opposite side of the rotation unit 4 (one side in the axial direction, the lower side in FIG. 2) toward the rotation unit 4. An annular protrusion 23f is formed, and the stator core 20 constituting the motor 19 is accommodated in an annular recess 23j on the back side of the protrusion 23f.

  The stator core 20 is attached to the center of the surface 24a of the substrate 24, as shown in FIGS. 2 and 3, and extends radially from the cylindrical portion 20b concentrically with the rotational axis Ax and the cylindrical portion 20b. And a plurality of teeth 20a around which a coil is wound.

  Various electronic components (not shown) are mounted on the surface 24a of the substrate 24 on which the stator core 20 is provided, and a drive circuit for the motor 19 and other circuits are formed. In the present embodiment, the energization state of the coil wound around each tooth 20a is appropriately switched by the drive circuit formed on the substrate 24 to switch the polarity in the outer peripheral portion of the tooth 20a, and thereby the diameter relative to the tooth 20a. A circumferential thrust is applied to the magnetized portion 18a (skirt portion 18) opposed to the outer direction, so that the rotating portion 4 is rotated. Therefore, in the second casing 23, at least the partition wall portion 23 g interposed between the outer peripheral portion of the stator core 20 (the teeth 20 a) and the skirt portion 18 needs to have magnetic permeability. For this reason, the whole partition part 23g or the 2nd casing 23 is formed with the material (for example, stainless steel, resin material, etc.) which has magnetic permeability.

  The substrate 24 is attached so as to close the concave portion 23c from the opposite side (one axial direction side) of the rotating unit 4, and the substrate 24 is attached to the opposite side of the rotating unit 4 (one axial direction by the substrate cover 25). It is covered from the side). The board cover 25 is provided with ridges 25 a in order to secure an interval for arranging electronic components between the board 24 and the board 24.

  Both the first casing 10 and the second casing 23 have a substantially square outer shape when viewed in the axial direction along the rotation axis Ax. And the through-holes 10a and 23k of the screw 26 which fastens these at the four corners of these casings 10 and 23 are formed. The vane pump 1 is assembled by inserting the screws 26 into the through holes 10a and 23k and the through holes 25b formed at the four corners of the substrate cover 25 and screwing the nuts 27 together.

  The material and manufacturing method of each component constituting the vane pump 1 are appropriately selected in consideration of wear resistance, corrosion resistance, swelling resistance, moldability, component accuracy, etc. in addition to the above-described magnetization and permeability. Is done.

  Further, in the present embodiment, as the fluid force generating unit that causes the rotating unit 4 to generate a fluid force toward the other axial side of the rotating shaft Ax (the upper side in FIGS. 2, 3, and 5) along with the rotation. The inclined surface 28 is provided, and the rotating portion 4 is pressed against the first casing 10 located on the side opposite to the side on which the bottom wall portion 17 is provided.

  As shown in FIG. 5, in the present embodiment, an inclined surface 28 that is inclined with respect to the rotational direction RD of the rotating portion 4 is provided on the end surface 18 b on one axial side of the skirt portion 18. The inclined surface 28 is set so as to be inclined from one side (lower side in FIG. 5) to the other side (upper side) from the front side to the front side in the rotational direction RD. For this reason, the working fluid that hits the inclined surface 28 with the rotation of the rotating unit 4 applies a fluid force F to the rotating unit 4 and pushes it up to the other side in the axial direction (upper side in FIG. 5).

  And in order to slidably support the rotating part 4 that rotates while receiving the fluid force F (thrust force) acting toward the other side in the axial direction, the first casing 10 has, as shown in FIG. A thrust support portion 29 is provided. Specifically, in the first casing 10, a portion where the shaft 21 is inserted and supported is projected to one side in the axial direction to form a protruding portion 10 c, and a top surface 10 d of the protruding portion 10 c is provided with a washer 30. Thus, the bottom surface 4b of the recess 4a formed at the center of the rotating part 4 (base part 5) is abutted. In the present embodiment, the washer 30 is interposed in the thrust support portion 29, and the axial end surface 22a of the bearing portion 22 provided in the central portion of the rotating portion 4 (partly exposed on the bottom surface 4b of the recess 4a). It is easy to improve the wear resistance. That is, with this configuration, the wear resistance of this portion is adjusted by the specifications (material, dimensions, curing treatment, etc.) of the sliding contact portion between the washer 30 and the bearing portion 22, and the main body portion (base portion 5, The specifications of the bottom wall portion 17 etc. can be selected from the viewpoints of weight reduction, slidability of other sliding portions, corrosion resistance, and the like.

  As shown in FIG. 4, the diameter D <b> 2 of the sliding portion in the thrust support portion 29 is made smaller than the diameter D <b> 1 of the base portion 5. When the inclined surface 28 is provided, if there is no special thrust support portion, the end surface 5c of the base portion 5 comes into sliding contact with the first casing 10, and the sliding resistance may increase. . In this respect, in this embodiment, since the diameter D2 of the sliding portion is smaller than the diameter D1 of the base portion 5, the sliding resistance can be further reduced and the friction can be further reduced.

  As shown in FIG. 2, the gap 31 between the end surface 17b on the other side in the axial direction of the bottom wall portion 17 and the end surface 3f on the one side in the axial direction of the ring 3 is set narrow, and the space between these end surfaces 17b and 3f is set. The leak flow rate from the gap is reduced as much as possible. Also, a washer 30 is interposed on one side of the bearing portion 22 in the axial direction.

  FIG. 6 is a side view of a vane included in the vane pump according to the present embodiment as viewed from the inside of the diameter. As shown in FIG. 6, in the present embodiment, the end surface 8 a on the other side in the axial direction of the vane 8 is moved to the one side in the axial direction of the rotational axis Ax (downward in FIG. 6) as the rotating unit 4 rotates. An inclined surface 35 </ b> A for applying the fluid force Fb to the vane 8 is provided. The inclined surface 35A is inclined toward the one side in the axial direction from the front side to the front side in the rotation direction RD, and the relative flow of the working fluid generated along with the rotation of the rotating unit 4 and the vane 8 is inclined. When it hits the surface 35A, a fluid force Fb on one side in the axial direction (downward in FIG. 6) is applied to the vane 8.

  Therefore, according to this embodiment, the reciprocating motion of the vane 8 in the axial direction can be suppressed with a relatively simple configuration, and vibration and noise caused by the reciprocating motion can be suppressed. Moreover, since it is only necessary to process the inclined surface 35A on the end surface on the other side in the axial direction of the vane 8, the above effect can be obtained with a relatively inexpensive configuration.

  In particular, in the present embodiment, the vane 8 is pressed against the bottom wall portion 17 of the rotating portion 4 that rotates together with the vane 8 by the fluid force Fb, so that the vane 8 is pressed against the casing 2 (first casing 10). The rotational sliding resistance can be reduced as compared with the case of pressing. That is, in the configuration having the bottom wall portion 17 as a guide wall portion that slidably supports the vane 8 on one side in the axial direction as in this embodiment, the fluid force Fb is applied to the bottom wall portion 17 side. It is preferable to make it act toward.

  In the present embodiment, the rotating portion 4 is pushed up to one side in the axial direction of the rotation axis Ax by the inclined surface 28. With this configuration, the rotating unit 4 can be abutted against one side of the casing 2 in the axial direction (that is, the first casing 10), and the rotating unit 4 can be prevented from reciprocating in the axial direction during rotation. The reciprocating motion can suppress the occurrence of vibration and noise. As shown in FIG. 4, the gap g between the end surface 5c on the other axial side of the base body 5 and the end surface 10e on the one axial side of the first casing 10 is defined as the dimension d1 of the rotating portion 4 and the first The dimension d2 of the casing 10 can be defined more easily and more accurately, and an increase in the leakage flow rate and a decrease in the pump efficiency due to the expansion or fluctuation of the gap can be suppressed, and the vane pump can be suppressed. The variation (individual difference) of the discharge amount of 1 can be reduced.

  Further, in the present embodiment, by providing the inclined surface 28 that is inclined with respect to the rotation direction RD of the rotating unit 4, it is possible to apply the fluid force to the other side in the axial direction on the rotating unit 4 very easily. it can. In particular, the end surface 18b on one axial side of the skirt portion 18 provided with the inclined surface 28 according to the present embodiment is easy to secure a relatively large area and easily secure a wide gap with the second casing 23. The desired fluid force can be generated more easily. In addition, as a mechanism for generating a fluid force in the axial direction, other than the above-described configuration may be considered. For example, the outer peripheral surface of the rotating part 4 may be recessed in the radial direction, and an inclined surface similar to the above may be formed at the end in the axial direction. The part 4 may be provided with a groove or a ridge that is spirally wound in the axial direction.

  In the present embodiment, as shown in FIG. 2, substantially cylindrical gaps (annular gaps) 32 and 33 are provided between the skirt portion 18 and the second casing 23. The gap 32 is a gap between the outer peripheral surface 18c of the skirt portion 18 and the inner peripheral surface 23h of the annular wall portion 23a of the second casing 23, and the gap 33 is the outer peripheral surface 23i of the partition wall portion 23g and the skirt portion 18. This is a gap between the inner peripheral surface 18d. As described above, the skirt portion 18 is provided, and the cylindrical gaps 32 and 33 are formed between the second casing and the second casing over the predetermined section in the axial direction of the rotation axis Ax, and the size of the clearance is appropriately set. By making (a relatively small gap), the pump chamber 9 in the discharge stroke (the pump chamber 9 on the upper side in FIG. 1) to the pump chamber 9 in the suction stroke (the pump chamber 9 on the lower side in FIG. 1). In addition, the flow resistance of the working fluid that leaks through one side in the axial direction of the base portion 5 can be increased, and the leak flow rate can be reduced.

  In addition, since these gaps (small gaps) 32 and 33 are concentric with the rotation axis Ax, even when the rotary part 4 moves to the other side in the axial direction, the second part in the axial direction of the rotary part 4 and the second part The leakage flow rate of the working fluid between the casing 23 and the casing 23 can be reduced.

  The skirt portion 18 is a portion that functions as a rotor (rotor) constituting the motor 19. That is, according to the present embodiment, the skirt portion 18 that functions as a rotor and the surrounding structure are used effectively, and the cylindrical gaps (micro gaps) 32 on the radially outer side and the radially inner side of the skirt portion 18, 33 can efficiently reduce the leak flow rate.

  (Modified Example of the Inclined Surface Provided on the Vane) FIGS. 7 to 9 are side views (views from the inside of the diameter) of the vane showing modified examples of the inclined surface provided on the vane. As shown in FIGS. 7 to 9, the inclined surfaces 35 </ b> B to 35 </ b> D may be flat surfaces or curved surfaces. In addition, specifications such as the direction and size of the unevenness, radius of curvature, shape, inclination angle, flatness, and position can be changed as appropriate. Moreover, as shown in FIG. 7, it is good also considering a part of end surface 8a as the inclined surface 35B.

  As mentioned above, although embodiment and modification of this invention were described, this invention is not limited to said each embodiment and modification, A various deformation | transformation is possible. For example, the detailed configuration of the rotating part, ring, and casing of the vane pump is not limited to the above embodiment.

It is sectional drawing in the cross section orthogonal to the rotating shaft of the vane pump concerning 1st Embodiment of this invention. It is sectional drawing in the cross section containing the rotating shaft of the vane pump concerning 1st Embodiment of this invention. It is an exploded perspective view of the vane pump concerning a 1st embodiment of the present invention. FIG. 3 is an enlarged view of a part of FIG. 2. It is a side view of the rotation part contained in the vane pump concerning a 1st embodiment of the present invention. It is a side view of the vane contained in the vane pump concerning a 1st embodiment of the present invention. It is a side view of the vane contained in the vane pump concerning the modification of a 1st embodiment of the present invention. It is a side view of the vane contained in the vane pump concerning another modification of a 1st embodiment of the present invention. It is a side view of the vane contained in the vane pump concerning another modification of a 1st embodiment of the present invention.

Explanation of symbols

1 Vane pump 2 Casing 2a Internal space 3 Ring (casing)
DESCRIPTION OF SYMBOLS 4 Rotation part 5 Base | substrate part 6 Annular chamber 7 Slit 8 Vane 35, 35A-35D Inclined surface 9 Pump chamber 10 1st casing (casing)
23 Second casing (casing)
Ax Rotating shaft Fb Fluid force to one axial side

Claims (2)

A plurality of slits radially extending with respect to the rotation axis of the rotating part are formed in the base part of the rotating part that rotates in the casing, and vanes are accommodated in the slits so as to be able to project and retract. An annular chamber formed around the base portion is partitioned by the plurality of vanes to form a plurality of pump chambers, and the volume of the pump chamber is periodically increased or decreased by rotating the rotating portion. In the vane pump configured to discharge the fluid sucked into the pump chamber,
A vane pump characterized in that an inclined surface is provided on a surface of the vane to cause a fluid force to act on the one side in the axial direction of the rotating shaft as the rotating portion rotates.   2. The vane pump according to claim 1, wherein the inclined surface is formed on an end surface on the other side in the axial direction of the vane so as to go to one side in the axial direction from the front side in the rotational direction to the front side. .

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