JP2005264906A - Vane pump rotor, vane pump - Google Patents

Abstract

A vane pump rotor capable of suppressing the occurrence of cavitation without lowering pump efficiency is provided.
A recess 1c that is recessed toward the center of the rotor 1 is provided, leaving the periphery of a pump section screen 1a partitioned by a vane receiving groove 1b on the outer periphery of the rotor 1.
[Selection] Figure 1

Description

  The present invention relates to a rotor for a vane pump used when supplying a working fluid to a steering device such as an automobile, and a vane pump including the rotor.

Normally, this type of vane pump has a large pressure difference of 7.84 to 16.2 MPa (80 to 165 kgf / Cm ² ) at the maximum between the low pressure suction side and the high pressure discharge side, and a maximum of 10,000 revolutions / minute. The suction / discharge of 2 times / rotation is repeated according to the rotor rotating at high speed.

  Recently, since this type of vane pump has been mounted on a larger vehicle, the discharge amount is as much as 15 ml / rev, and a stricter capacity than ever is required.

  In a vane pump in which such a large pressure difference occurs, cavitation is likely to occur in the axial center portion of the outer peripheral surface of the rotor, which will be described in detail later, in the central portion of the pump chamber, which causes vibration (pulsation) and noise. . In addition, erosion (erosion wear) may occur on the outer peripheral surface of the rotor where cavitation has occurred, and there is a concern that the performance of the vane pump will deteriorate.

  FIG. 9 (a1) is a plan view of an essential part for conceptually explaining the function of an example of a conventional vane pump rotor, (a2) is a sectional view thereof, and (b1) is another example of a conventional vane pump rotor. FIG. 9 is a plan view of the main part for conceptually explaining the function, and (b2) is a cross-sectional view thereof. The cause will be described below with reference to FIG.

  9A1 and 9A2, reference numeral 101 denotes a rotor for a vane pump, reference numeral 102 denotes a side plate that sandwiches the rotor 101 from one side, reference numeral 103 denotes a cover that sandwiches the rotor 101 from the other, and reference numeral 104 denotes an elliptical inner circumference. A cam ring having a surface in which the rotor 101 rotates, and a reference numeral 105 is a vane housed in a plurality of places so that the rotor 101 can be put in and out of the outer periphery of the rotor 101. The tip rotates while abutting, and these parts constitute the vane pump 110 as a whole.

  The rotor 101 has a cylindrical shape, and an outer circumference partitioned by the vane 105 is a pump section screen 101a, and a groove that accommodates the vane 105 in and out is a vane accommodation groove 101b.

With such a configuration, the vane pump 110 including the rotor 101 includes a pump chamber 106 surrounded by the pump section screen 101a of the rotor 101, both side surfaces of the adjacent vane 105, and the inner peripheral surface of the cam ring 104 with which the tip of the vane 105 abuts. Form. The pump chamber 106 rotates within the inner periphery of the elliptical cam ring 104 while the rotor 101 is kept coaxial with the cam ring 104 as indicated by an arrow D2 in FIG. 9 (a2). The distance between the outer peripheral surface, that is, the pump section screen 101a and the inner peripheral surface of the cam ring 104 increases and decreases, and the volume of the pump chamber 106 increases and decreases accordingly.

  The vane pump 110 is provided with a working fluid suction port (two places, not shown) at a predetermined position where the volume of the pump chamber 106 is increased, and a discharge port (two places, not shown) at a predetermined position where the volume is reduced. ) To inhale and discharge the working fluid, that is, exhibit the pump function.

  Thus, as shown by the arrow F in the figure, the working fluid is sucked from the side plate 102 and the cover 103 sandwiching the rotor 101 from both sides and discharged to one side. The low-pressure working fluid flows at high speed through the suction ports provided on both the cover 103 and the working fluid collides with each other in the axial central portion of the outer periphery of the rotor 101. Immediately after being inserted, this working fluid is pushed out from the side plate 102 side to a high-pressure chamber (not shown) on the discharge side at a high speed and a large capacity.

  The turbulent flow generated when the working fluid flows into the pump chamber 106 acts largely in the vicinity where the working fluids first collide with each other, so that cavitation tends to occur easily in the central portion in the axial direction of the pump chamber 106. Erosion (erosion wear) tends to occur easily at the central portion of the pump section screen 101a on the outer periphery of the rotor 101 corresponding to this portion (X marks in FIGS. 9A1 and 9A2) or the inner peripheral surface of the cam ring 104 corresponding thereto. is there.

  The rotors having the shapes shown in FIGS. 9A1 and 9A2 are general ones, and are described in, for example, Patent Document 1 and Patent Document 2. With this structure, the pump chamber itself is not particularly devised, and since the volume of the suction portion is small, the pressure fluctuation per unit volume generated in the working fluid in the pump chamber is large.

  Also, as can be seen in this figure, when the volume (volume) of the pump chamber is small, the buffering action against the pressure fluctuation of the working fluid in the pump chamber is small, and the cycle of the pressure fluctuation is fast as described above. In addition to the above-mentioned factors for generating cavitation due to working fluid collision, it is considered that the tendency of cavitation to occur in the pump chamber is promoted.

  Further, as shown in FIGS. 9 (b1) and 9 (b2), a vane pump 110A in which a recess 101c is formed in the pump section screen 101a of the rotor 101A over the entire length in the axial direction as having a rotor shape different from the above. Proposed. This pump 101A is described in, for example, Patent Document 3 and Patent Document 4. In addition, the same code | symbol is attached | subjected to the same part as FIG. 9 (a1) and (a2), and duplication description is abbreviate | omitted.

  This structure is a rotor 101A with improved suction performance compared to the structure of the rotor 101, and the volume of the pump chamber 106A at the time of suction is particularly greater than the structure of the rotor 101 by the amount of the recess 101c provided on the outer periphery of the rotor 101A. The feature is that (volume) is increased.

  As a result, the volume (volume) of the pump chamber 106A increases as a whole, so that the buffering action against the pressure fluctuation of the working fluid in the pump chamber 106A is larger than the structure of the rotor 101, and cavitation occurs in the pump chamber 106A. Is advantageous.

  However, when the recess 101c extending over the entire length of the rotor 101A is provided, the sliding area with the side plate 102 and the cover 103 is reduced, so that the pump efficiency, which is a very important point as a pump, is reduced accordingly. End up. Further, the contact surface pressure increases accordingly, which is disadvantageous for wear and seizure between the rotor 101A, the side plate 102, and the cover 103.

Therefore, in reality, it is difficult to enlarge the recess, and the present situation is that the cavitation cannot be completely eliminated in the entire rotation region where the vane pump is used.
Japanese Patent Laid-Open No. 5-44653 (FIG. 2) Japanese Patent Laid-Open No. 10-30580 (FIG. 1) Japanese Utility Model Publication No. 61-181888 (FIG. 1) Japanese Utility Model Laid-Open No. 5-12680 (FIG. 1) Japanese Patent Laid-Open No. 2001-323880 (FIGS. 4 and 10)

  An object of this invention is to provide the vane pump rotor which can suppress generation | occurrence | production of a cavitation, without reducing pump efficiency, and the vane pump provided with this rotor.

  The vane pump rotor according to the present invention is characterized in that a recess recessed in the rotor center direction is provided, leaving a peripheral edge of a pump section screen partitioned by a vane receiving groove on the outer periphery of the rotor. The vane pump of the present invention is characterized by including this rotor.

  The vane pump rotor of the present invention is provided with a recess that increases the volume of the pump chamber while leaving the periphery on the pump section screen partitioned by the vane receiving grooves on the outer periphery of the rotor forming the pump chamber. Even if the working fluid collides due to the suction of the working fluid or a large pressure fluctuation occurs due to the pump function, the pressure fluctuation per unit volume can be reduced, resulting in cavitation, vibration (pulsation), noise and erosion caused by it. Therefore, it is possible to realize a vane pump that is more difficult to generate.

  In addition, because the pump-shaped recess has left the periphery of the pump section screen, the volume of the pump chamber can be increased without reducing the contact area with the side plate and cover of the rotor. It is possible to suppress cavitation without reducing any wear resistance or seizure resistance.

  Moreover, the vane pump provided with the said rotor exhibits the effect of the said rotor as a vane pump.

  Hereinafter, embodiments (examples) of the present invention will be described with reference to the drawings.

  FIG. 1 is a perspective view showing an example of a rotor for a vane pump according to the present invention, FIG. 2 (a) is a plan view of a main part for conceptually explaining the operational effects of the rotor for a vane pump in FIG. 1, and FIG. FIG. 2C is a longitudinal sectional view thereof.

  The vane pump rotor 1 in FIG. 1 is used for a vane pump used when supplying a working fluid to a steering device such as an automobile, and has a cylindrical shape as a whole, and has a predetermined depth from the outer periphery thereof. A plurality of vane accommodating grooves 1b for accommodating the vanes 5 so as to be able to be taken in and out are provided at a plurality of locations (in this example, ten locations are not limited thereto) so as to divide the outer periphery.

  The outer peripheral surface of the rotor 1 partitioned by the vane housing groove 1b is referred to as a pump section screen 1a. As described in the conventional example, this is because the pump section screen 1a has the vane 5 side surface, the inner peripheral surface of the cam ring (reference numeral 4 in FIG. 2), and the vane pump having the rotor 1 (reference numeral 10 in FIG. 2). This is because a pump chamber (symbol 6 in FIG. 2) that accommodates the working fluid that is the processing target is formed.

  A shaft hole 1 d for fitting a shaft for rotating the rotor 1 is provided at the center of the cylindrical shaft of the rotor 1.

  The rotor 1 is characterized in that a recess 1c that is recessed toward the center of the rotor 1 is provided on the pump section screen 1a, leaving only its peripheral edge. The recess 1c is formed in the same shape (depth and surface shape) on all the pump section screens 1a.

  The operation and effect of the recess 1c will be described with reference to FIGS. 2 (a), (b), and (c) while comparing with FIGS. 9 (a1) and (a2) of the conventional example.

  FIG. 2A shows a place where the vane pump 10 having the rotor 1 of FIG. 1 is viewed through one pump section screen 1 a on the outer periphery of the rotor 1.

  The vane pump 10 has, in addition to the rotor 1 and the vane 5 described above, a side plate 2 that sandwiches the rotor 1 from one side, a cover 3 that sandwiches the rotor 1 from the other, and an elliptical inner peripheral surface. The rotating cam ring 4 has the same basic structure and function as the conventional vane pump 110 described in FIG. 9, and the structure of the rotor 1 is different as described above.

  The pump chamber 6 is formed by the pump section screen 1a of the rotor 1, the recess 1c, both side surfaces of the adjacent vanes 5, and the inner peripheral surface of the cam ring 4 with which the tips of the vanes 5 abut.

  When the rotor 1 is provided with the recess 1 c as described above, a collision of the working fluid occurs in the axial central portion (Δ mark in the figure) in the pump chamber 6 on the outer periphery of the rotor 1, and the pump chamber 6 is further pumped. Even if a large pressure fluctuation occurs, the volume of the pump chamber 6 is expanded by the provision of the recess 1c as shown in FIG. 9 (a1) and (a2). Therefore, it is possible to realize a vane pump in which cavitation, vibration (pulsation), noise, and erosion are less likely to occur.

  Further, since the concave portion 1c having the shape of the excavity leaving the periphery of the pump section screen 1a is provided, the volume of the pump chamber 6 can be increased without reducing the contact area of the rotor 1 with the side plate 2 and the cover 3. It is possible to suppress cavitation without reducing efficiency, wear resistance of sliding parts, and seizure resistance.

  Furthermore, in this embodiment, the volume of the pump chamber 6 can be increased without providing a recess communicating with a cut surface (a contact surface with the side plate 2 or the cover 3) in a plane orthogonal to the axial direction of the rotor 1. Therefore, no harmful burrs are generated when the rotor 1 is molded, and the workability is not changed at all.

  The shape of the concave portion 1c is such that the flow resistance generated by the working fluid flowing into the pump chamber 6 formed by the pump section screen 1a including the concave portion 1c is reduced, and the occurrence of cavitation due to this is prevented. Is good. Then, in addition to the effect of lowering the pressure fluctuation per unit volume simply by increasing the volume, cavitation can be further reduced.

  This shape can be determined by fluid engineering knowledge and trial and error. Moreover, all the various shapes described below are listed as specific examples of shapes that reduce the flow resistance.

  The first specific example relates to the depth as shown in FIGS. 2B and 2C, and the shape in the depth direction becomes deeper toward the center of the rotor 1 along the entire circumference of the recess 1 c. The gradient is gentle between the peripheral vicinity gradient 1ca and the deepest vicinity gradient 1cb. Here, the gradients of both gradients 1ca and 1cb gradually increase from the gradient zero toward the largest gradient portion in the intermediate portion, and return to zero.

  If it does in this way, the flow resistance accompanying the suction inflow of a working fluid will become smaller, and it is effective in cavitation suppression.

  FIG. 3A is a plan view of a principal part for conceptually explaining the operation and effect of another example of the vane pump rotor of the present invention, FIG. 3B is a sectional view thereof, and FIG. 3C is a longitudinal sectional view thereof. From here on, the parts already described are assigned the same reference numerals, and redundant description is omitted.

  The rotor 1A provided in the vane pump 10A is different from the rotor 1 of the vane pump 10 in FIG. 1 in that the concave portion 1e of the rotor 1A can secure a larger volume.

  Specifically, as can be seen more clearly in FIGS. 3B and 3C, the peripheral edge of the rotor section 1 </ b> A in the axial direction D <b> 1 side does not remain in the peripheral edge of the pump section screen 1 a where the concave part 1 e should be left. It is a part of 1e. However, the contact area between the rotor 1 </ b> A, the side plate 2, and the cover 3 is ensured similarly to the rotor 1.

  This is advantageous for suppressing cavitation as described above because the volume of the pump chamber 6A is larger than that of the rotor 1 of FIG.

  Also in the recess 1e, the gradient near the periphery 1ea of the rotor 1A and the gradient near the deepest part 1eb are gentle, and the same effect is exhibited.

  Moreover, when this point is compared with the recess 101c of the conventional example in FIGS. 9B1 and 9B2, in the conventional example, when considering the working fluid suction direction F, the recess 101c includes the side plate 102, Abrupt steps, that is, sudden pressure fluctuations are generated with respect to the cover 103. This point is disadvantageous for suppressing cavitation. However, as described above, cavitation suppression is considered as a part of the recess 1e. The problem of this conventional example can be solved by using a gentle gradient.

  4 (a), 4 (b), 4 (c), and 4 (d) are principal part plan views conceptually showing another example of the rotor for the vane pump of the present invention.

  The rotors 1B to 1E of the vane pumps 10B to 10E illustrated in FIGS. 4 (a), (b), (c), and (d) are shown in the same manner as in FIG. 2 (a). In addition, a specific example of a shape that suppresses cavitation is introduced with respect to the concave shape of the surface (rotor outer peripheral surface) portion of the pump section screen 1a.

  The shape of the concave portion 1f of the rotor 1B in FIG. 4A is a pointed shape in the axial direction D1 of the rotor 1B. As a result, the surface shape gradually increases with respect to the suction direction F of the working fluid. In addition to securing the same volume of the pump chamber as in the first and second embodiments, the flow resistance when the working fluid flows into the pump chamber can be reduced, which is effective in suppressing cavitation. .

  The shape of the concave portion 1g of the rotor 1C in FIG. 4B is pointed in both the axial direction D1 of the rotor 1C and the rotational direction D2 of the rotor 1C, and in addition to the effect of the rotor 1B, The sectional area of the recess 1g gradually increases with respect to the moving direction of the working fluid due to the rotation of the rotor 1C with respect to the suction of the working fluid, and the volume of the pump chamber equivalent to the first and second embodiments is increased. In addition, the flow resistance when the working fluid flows into the pump chamber and when the working fluid moves following the rotation of the rotor 1C can be reduced, which is effective in suppressing cavitation.

  Since the rotors 1B and 1C have the same recesses 1f and 1g with respect to the positive and negative (indicated by + and-in the drawing) in the rotation direction D2, the rotors 1B and 1C are rotated in either positive or negative directions. But it can also be used.

  On the other hand, the shape of the concave portion 1h of the rotor 1D in FIG. 4C is a sharp shape only on the positive side (+) of the rotational direction D2 of the rotor 1D. The cross-sectional area of the recess 1h due to the rotation of the rotor 1D with respect to the suction is effectively increased to suppress cavitation, but the rotation is limited only to the positive direction (+).

  The shape of the recess 1i of the rotor 1E in FIG. 4 (d) is a combination of the shape of the recess 1h of the rotor 1D in FIG. 4 (c) and the shape of the recess 1f of the rotor 1B in FIG. 4 (a). In this case, the rotation is limited to only the positive direction (+).

  The shape of the surface area of the pump section screen 1a of these recesses can also be applied to a recess of a type that does not leave the peripheral edge in the rotor axial direction D1, as in the recess 1e of FIG. Demonstrate.

  FIG. 5A is a plan view of a principal part for conceptually explaining the operation and effect of another example of the rotor for a vane pump of the present invention, FIG. 5B is a transverse sectional view thereof, and FIG. 5C is a longitudinal sectional view thereof.

  The rotor 1F provided in the vane pump 10F is obtained by applying the recess 1c described in FIG. 1 to the rotor 101A of FIG. 9 having a conventional structure.

  Specifically, as compared with the rotor 1 of FIGS. 1 and 2, a part of the pump section screen 1a of the rotor 1F is formed over the entire axial length of the rotor 1F, like the recess 101c of the rotor 101A of the conventional example. The difference is that it is a pump section screen 1a 'of the recessed portion. In addition, a recess 1c similar to the rotor 1 of FIG. 1 is formed so as to leave the periphery of the pump section screen 1a '.

  This is advantageous for suppressing cavitation as described above because the volume of the pump chamber 6 is larger than that of the rotor 1 of FIGS. Also in this recess 1c, the peripheral vicinity gradient 1ca and the deepest vicinity gradient 1cb are similarly gentle, and the same effect is exhibited.

  In addition, the rotor 1F is similar to the rotor 101A of the conventional structure in that the pump section screen 1a 'serving as the recess has a step with respect to the side plate 2 and the cover 3 in view of the working fluid suction direction F. Because of the recess, the working fluid can easily flow.

  In addition, the recessed part provided with respect to the pump area screen 1a 'of this recessed part is not limited only to 1c of this example, The various recessed parts 1e, 1f, 1g, 1h, 1i mentioned above can also be installed, Demonstrate the effect.

  FIG. 6 is a perspective view showing another example of the vane pump rotor of the present invention.

  This vane pump rotor 1G is a multi-layer type having the same structure as the multi-layer type rotor shown in Patent Document 5 (FIGS. 4 and 10), and the rotor layer plates 11A and 11B that form the rotor 1G by taking advantage of the characteristics thereof. According to the outer peripheral shape, the recess 1j is formed in the same shape as the recess 1c of the rotor 1 of FIG.

  The rotor layer plate 11A is a thick plate for both ends, and the rotor layer plate 11B is a thin plate sandwiched between the upper and lower rotor layer plates 11A. In this example, the rotor layer plate 11B The shape of the recess 1j is formed by the outer peripheral shape, and the fixing plates 1k are passed through the respective layer plates 11A and 11B so that the layer plates 11A and 11B do not shift. The rotor layer plate 11A can also participate in the formation of the concave shape.

  If it does in this way, since it can assemble after processing the peripheral shape of each rotor layer board 11B etc. previously, manufacture of rotor 1F can be made cheaper more easily. Further, the entire thickness of the rotor 1G can be dealt with by changing the number of the rotor layer plates 11B, and it becomes easy to deal with various pump capacities.

  In addition, since the rotor 1G includes the recess 1j, the same effect as the above-described recess 1c is exhibited, and the shape of the recess 1j can be the various recesses 1e to 1i described above. The effect of the recessed part of the shape can also be exhibited. Further, the shape of the pump section screen 1a 'of the above-described recess can be formed by the same method, and the same effect as that shape can be exhibited.

  FIG. 7 is a sectional view showing an example of the vane pump of the present invention, and FIG. 8 is a front view showing the internal structure of the vane pump of FIG. 7 and 8 show the vane pump 10 provided with the rotor 1 of FIG. 1 more specifically, but there is a characteristic in the configuration and operational effect of the rotor 1 provided with the recess 1c already described. Since the part is the same as a general vane pump, detailed description is abbreviate | omitted.

  As shown in FIGS. 7 and 8, the vane pump 10 includes a rotor body 1, a side plate 2, a cover 3, a cam ring 4, and a vane 5 which have already been described, A pump shaft 7 fitted in the shaft hole 1 d of the rotor 1, and a pulley 8 that is rotatably fitted to the other end of the pump shaft 7 and receives a rotational force to the pump shaft 7 are provided.

  The side plate 2 is provided with suction ports 2a (two places) for sucking working fluid and discharge ports 2b (two places) for discharging. Similarly, the cover 3 is provided with suction ports (two locations), but here, the suction ports (two locations) are not visible.

  The suction port 2a (the cover 3 side is not shown) communicates with the suction port 6a of the pump body 6, and the discharge port 2b communicates with the discharge port 6b of the pump body 6.

  With such a configuration, the vane pump 10 receives the rotational driving force applied to the rotor 1 and sucks the working fluid from the suction port 6a and discharges the high-pressure working fluid from the discharge port 6b. However, the above-described recess 1c is provided. The effect of the rotor 1 can be exhibited, and the occurrence of cavitation accompanying the pump operation can be suppressed without lowering the pump efficiency.

  Moreover, it replaces with the rotor 1 and exhibits the effect of these rotors 1 as a vane pump by providing the rotor 1A-1F with the above-mentioned various recessed parts 1f-1i.

  The rotor and vane pump for vane pumps of the present invention are compact, have little cavitation and are maintenance-free, such as when supplying working fluid to a steering device such as an automobile, and supply high-pressure working fluid stably for a long time. It can be used in all industrial fields that are required.

The perspective view which shows an example of the rotor for vane pumps of this invention (A) is a principal part top view which illustrates notionally the effect of the rotor for vane pumps of FIG. 1, (b) is the cross-sectional view, (c) is the longitudinal cross-sectional view. (A) is a principal part top view explaining notionally the effect of the other example of the rotor for vane pumps of this invention, (b) is the cross-sectional view, (c) is the longitudinal cross-sectional view (A), (b), (c), (d) is a principal part top view which shows conceptually the other example of the rotor for vane pumps of this invention. (A) is a principal part top view explaining notionally the effect of the other example of the rotor for vane pumps of this invention, (b) is the cross-sectional view, (c) is the longitudinal cross-sectional view The perspective view which shows the other example of the rotor for vane pumps of this invention Sectional drawing which shows an example of the vane pump of this invention The front view which shows the internal structure of the vane pump of FIG. (A1) is a plan view of an essential part for conceptually explaining the function of an example of a conventional vane pump rotor, (a2) is a sectional view thereof, and (b1) is a function of another example of a conventional vane pump rotor. Fig. 2 is a plan view of an essential part for conceptually explaining (b2) is a sectional view thereof.

Explanation of symbols

1-1F Vane pump rotor
1G Laminated rotor
1a Pump area screen
1a '(concave) pump section screen
1b Vane receiving groove
1c recess
1ca Edge gradient
1cb slope near the deepest part
1e recess
1ea Near edge gradient
1eb Gradient near the deepest part
1f to 1i recess
2 Side plate
3 Cover
4 Cam ring
5 Vane 10-10F Vane pump
D1 Rotor axial direction
D2 Rotor rotation direction
D2 + Positive side of rotor rotation direction

Claims (10)

  A rotor for a vane pump, characterized in that a recess recessed in the direction of the center of the rotor is provided, leaving a peripheral edge of a pump section screen partitioned by a vane receiving groove on the outer periphery of the rotor.   2. The rotor for a vane pump according to claim 1, wherein a shape of the pump section screen is a shape in which a portion other than the vicinity of the vane housing groove is recessed in a radial direction of the rotor.   The rotor for a vane pump according to claim 1 or 2, wherein a peripheral edge on the rotor axial direction side is not left out of the peripheral edge but is a part of the recess.   The shape of the concave portion is a shape that reduces cavitation caused by the working fluid flowing into the pump chamber formed by the pump section screen including the concave portion. The rotor for a vane pump as described.   5. The rotor for a vane pump according to claim 4, wherein the shape is a shape that becomes deeper toward the center of the rotor, and the gradient is gentle between the vicinity of the peripheral edge and the vicinity of the deepest portion.   The vane pump rotor according to claim 5, wherein a shape of the shape near the upper portion of the concave portion is a pointed shape in the axial direction of the rotor.   6. The vane pump rotor according to claim 5, wherein the shape of the shape near the upper portion of the recess is pointed in both the axial direction and the rotational direction of the rotor.   6. The vane pump rotor according to claim 5, wherein a shape of the shape in the vicinity of the upper portion of the concave portion is sharpened only on a positive side in a rotation direction of the rotor.   The vane pump rotor according to any one of claims 1 to 8, wherein the rotor is a laminated rotor, and the concave portion is formed by an outer peripheral shape of a rotor layer plate of the laminated rotor.   A vane pump comprising the vane pump rotor according to any one of claims 1 to 9.

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