WO2017141478A1

WO2017141478A1 - Vane pump

Info

Publication number: WO2017141478A1
Application number: PCT/JP2016/077578
Authority: WO
Inventors: 善也中村; 鈴木　一成
Original assignee: Ｋｙｂ株式会社
Priority date: 2016-02-15
Filing date: 2016-09-16
Publication date: 2017-08-24
Also published as: US20200392847A1; JP2017145699A; JP6670119B2; DE112016006428T5; CN108496007A

Abstract

A vane pump (100) is provided with annular recessed sections (23, 24) formed in an outer peripheral surface (20a) of a rotor (20), and in the recessed sections (23, 24), both side surfaces (23A, 23B, 24A, 24B) are sloped to be closer to each other toward bottom surfaces (23C, 24C).

Description

Vane pump

The present invention relates to a vane pump.

JP 2006-125210A describes a vane pump in which a notch portion is formed on a side surface of a cam ring that comes into contact with a side plate and that faces a suction recess formed in the side plate. In the vane pump described in JP2006-125210A, a suction port is constituted by a suction recess and a notch.

In the vane pump described in JP2006-125210A, hydraulic oil is sucked into a pump chamber partitioned between vanes through a suction port from a passage formed between the outer periphery of the cam ring and the inner periphery of the body bore as the rotor rotates. . However, in the vane pump described in JP2006-125210A, since the flow path of the working oil flowing into the pump chamber from the suction port is bent, pressure loss is likely to occur when the working oil is sucked. For this reason, there is a possibility that insufficient suction of hydraulic oil may occur when the vane pump rotates at high speed.

The present invention aims to improve the suction efficiency of the working fluid in the vane pump.

According to an aspect of the present invention, a vane pump includes a rotor that is rotationally driven, a plurality of vanes that are provided in the rotor so as to be capable of reciprocating in the radial direction of the rotor, and tip portions of the plurality of vanes as the rotor rotates. A cam ring having an inner peripheral cam surface that is in sliding contact, a first side member and a second side member that are disposed across the rotor and the cam ring, and a rotor, a cam ring, adjacent vanes, a first side member, and a second side member. The pump chamber, a suction port for guiding the working fluid to the pump chamber, and an annular recess formed on the outer peripheral surface of the rotor, the recesses approaching each other as both side surfaces go to the bottom surface Inclined.

FIG. 1 is a cross-sectional view of a vane pump according to an embodiment of the present invention. FIG. 2 is a front view of the rotor, the vane, and the cam ring according to the embodiment of the present invention, and shows the assembled state of the rotor, the vane, and the cam ring. FIG. 3 is a perspective view of the rotor according to the embodiment of the present invention. FIG. 4 is a side view of the rotor according to the embodiment of the present invention. FIG. 5 is an enlarged cross-sectional view of the vicinity of the pump chamber according to the embodiment of the present invention. FIG. 6 is a front view of the first side plate according to the embodiment of the present invention. FIG. 7 is a side view of the cam ring, the first side plate, and the second side plate according to the embodiment of the present invention, and shows a state in which the first side plate and the second side plate are assembled to the cam ring. FIG. 8 is a rear view of the cam ring according to the embodiment of the present invention. FIG. 9 is a front view of the second side plate according to the embodiment of the present invention. FIG. 10 is a diagram showing a modification of the embodiment of the present invention.

Hereinafter, a vane pump 100 according to an embodiment of the present invention will be described with reference to the drawings. The vane pump 100 is used as a hydraulic pressure supply source of a hydraulic device 1 (for example, a power steering device or a transmission) mounted on a vehicle. Here, although the vane pump 100 in which working oil is used as the working fluid will be described, other fluids such as working water may be used as the working fluid.

As shown in FIG. 1, the vane pump 100 includes a drive shaft 10, a rotor 20 coupled to the drive shaft 10, a plurality of vanes 30 provided on the rotor 20, a cam ring 40 that houses the rotor 20 and the vanes 30, Is provided.

The drive shaft 10 is rotatably supported by the pump body 50 and the pump cover 60. When the power of the engine or the electric motor (not shown) is transmitted to the drive shaft 10, the rotor 20 rotates as the drive shaft 10 rotates.

In the following, the direction along the rotation center axis of the rotor 20 is also referred to as “axial direction”, the radial direction of the rotor 20 is also simply referred to as “radial direction”, and the direction in which the rotor 20 rotates during normal operation of the vane pump 100 is simply “rotated”. Also referred to as “direction”.

Further, the vane pump 100 further includes first and

second side plates

70 and 80 as first and second side members disposed with the rotor 20 and the cam ring 40 sandwiched in the axial direction. The first and

second side plates

70 and 80 have

side surfaces

70a and 80a that abut against the rotor 20 and the cam ring 40, respectively. The pump chamber 41 is defined by the rotor 20, the cam ring 40, the adjacent vanes 30, the first side plate 70, and the second side plate 80.

Next, the shape of the rotor 20 will be described. FIG. 2 is a front view of the rotor 20, the vane 30 and the cam ring 40 as viewed from the assembled pump cover 60 side. FIG. 3 is a perspective view of the rotor 20. FIG. 4 is a side view of the rotor 20. FIG. 5 is an enlarged cross-sectional view in the vicinity of the pump chamber 41.

As shown in FIGS. 2 to 4, the rotor 20 is formed with a plurality of radial slits 22 having openings 21 on the outer peripheral surface 20a at predetermined intervals.

As shown in FIGS. 3 to 5, the rotor 20 is formed between two

annular recesses

23, 24 formed on the outer peripheral surface 20 a and the outer surface 20 a of the rotor 20 formed between the

recesses

23, 24 in the radial direction. And an annular ridge 25 projecting from the top.

The concave portion 23 includes a side surface 23A on the end surface 20b side facing the first side plate 70 of the rotor 20, a side surface 23B on the raised portion 25 side, and a bottom surface 23C formed by a concave curved surface between the side surface 23A and the side surface 23B. And comprising. The concave portion 23 is formed so as to be inclined so that the side surface 23A and the side surface 23B are closer to each other toward the bottom surface 23C. The bottom surface 23C is formed by a concave curved surface that is continuous with the side surface 23A and the side surface 23B.

The concave portion 24 includes a side surface 24A on the end surface 20c side facing the second side plate 80 of the rotor 20, a side surface 24B on the raised portion 25 side, and a bottom surface 24C formed by a concave curved surface between the side surface 24A and the side surface 24B. And comprising. The recess 24 is formed so as to be inclined so that the side surface 24A and the side surface 24B approach each other as it goes toward the bottom surface 24C. The bottom surface 24C is formed by a concave curved surface that is continuous with the side surface 24A and the side surface 24B.

As shown in FIG. 5, the side surface 23A of the recess 23 and the side surface 24A of the recess 24 are provided at

positions facing notches

43 and 44 formed in the cam ring 40 described later.

Refer to FIG. 2 again. The vane 30 is slidably inserted into each slit 22. The tip 31 of the vane 30 faces the inner peripheral surface 40 a of the cam ring 40. The base end portion 32 of the vane 30 is located in the slit 22, and the back pressure chamber 26 is formed by the slit 22 and the vane 30 on the base end portion 32 side of the vane 30.

When the rotor 20 rotates, centrifugal force acts on the vane 30. By this centrifugal force, the vane 30 is pushed out in a direction protruding from the slit 22, and the tip end portion 31 of the vane 30 is pressed against the inner peripheral surface 40 a of the cam ring 40.

The inner peripheral surface 40a of the cam ring 40 is formed in a substantially oval shape. Hereinafter, the inner peripheral surface 40a is also referred to as an “inner peripheral cam surface 40a”.

Since the inner peripheral cam surface 40a of the cam ring 40 is formed in a substantially oval shape, the vane 30 reciprocates in the radial direction with respect to the rotor 20 as the rotor 20 rotates. As the vane 30 reciprocates, the pump chamber 41 repeats expansion and contraction.

In this embodiment, the vane 30 reciprocates twice while the rotor 20 makes one rotation, and the pump chamber 41 repeats expansion and contraction twice. That is, the vane pump 100 alternately has two

expansion regions

42a and 42c in which the pump chamber 41 expands and two

contraction regions

42b and 42d in which the pump chamber 41 contracts in the rotation direction.

Refer to FIG. 1 again. The pump body 50 is formed with a housing recess 51 that houses the rotor 20, the cam ring 40, and the first side plate 70. The first side plate 70 is disposed on the bottom surface 51 a of the housing recess 51.

An annular groove 52 is formed on the bottom surface 51 a of the housing recess 51. The annular groove 52 and the first side plate 70 form a high-pressure chamber 53 into which hydraulic oil discharged from the pump chamber 41 flows. The hydraulic oil discharged from the pump chamber 41 is supplied to the hydraulic device 1 through the high pressure chamber 53.

FIG. 6 is a front view of the first side plate 70 as seen from the cam ring 40 side. As shown in FIGS. 1 and 6, the first side plate 70 has a through hole 71 that penetrates the first side plate 70 at the center thereof. The drive shaft 10 is inserted through the through hole 71.

The first side plate 70 is provided with two discharge ports 72 that guide the hydraulic oil discharged from the pump chamber 41 to the high-pressure chamber 53. The discharge port 72 is provided so as to be positioned in each of the

contraction regions

42b and 42d.

The pump chamber 41 contracts while the pump chamber 41 (see FIG. 2) passes through the

contraction regions

42b and 42d. As the pump chamber 41 contracts, the pressure of the hydraulic oil in the pump chamber 41 increases, and the hydraulic oil in the pump chamber 41 is discharged from the discharge port 72. That is, the hydraulic oil in the pump chamber 41 is discharged from the discharge port 72 while the pump chamber 41 passes through the

contraction regions

42b and 42d. Thus, since the hydraulic oil is discharged in the

contraction regions

42b and 42d, the

contraction regions

42b and 42d are also called “discharge regions”.

The vane 30 is pushed most into the slit 22 when moving from the contraction region 42d to the expansion region 42a and when moving from the contraction region 42b to the expansion region 42c. At this time, the volume of the pump chamber 41 is minimized. The minimum amount of hydraulic oil in the pump chamber 41 is not discharged from the pump chamber 41 while the pump chamber 41 passes through the

contraction regions

42 d and 42 b and remains in the pump chamber 41. Thus, the minimum volume of the pump chamber 41 does not function as a pump and is also called a dead volume.

The first side plate 70 is formed with two back pressure passages 73 (see FIGS. 1 and 6) for guiding the hydraulic oil from the high pressure chamber 53 to the back pressure chamber 26 (see FIGS. 1 and 2). As shown in FIG. 6, the back pressure passage 73 is formed in an arc shape centering on the through hole 71 so as to be positioned in the

expansion regions

42 a and 42 c. As a result, hydraulic oil is guided from the high pressure chamber 53 to the back pressure chamber 26 that passes through the

expansion regions

42 a and 42 c, so that the vane 30 that passes through the

expansion regions

42 a and 42 c is slit 22 by the pressure in the back pressure chamber 26. It protrudes from (refer FIG. 2), and is pressed by the internal peripheral surface 40a of the cam ring 40. FIG.

As described above, in this embodiment, the vane 30 is pressed in the direction in which the vane 30 protrudes from the slit 22 not only by the centrifugal force generated by the rotation of the rotor 20 but also by the pressure in the back pressure chamber 26.

Refer to FIG. 1 again. The inner diameter of the housing recess 51 of the pump body 50 is larger than the outer diameter of the cam ring 40. A fluid chamber 54 extending from the outer periphery of the second side plate 80 to the outer periphery of the first side plate 70 is formed between the cam ring 40 and the pump body 50.

The opening of the housing recess 51 is sealed by the pump cover 60. The pump cover 60 is fixed to the pump body 50 by bolts (not shown). A second side plate 80 is disposed between the pump cover 60 and the cam ring 40.

A low pressure chamber 61 is formed in the pump cover 60. The low pressure chamber 61 is connected to the tank 2 through a low pressure passage. When the vane pump 100 is operated, the hydraulic oil in the tank 2 is supplied to the low pressure chamber 61 through the low pressure passage. The low pressure chamber 61 communicates with the fluid chamber 54, and the hydraulic oil in the tank 2 is supplied to the fluid chamber 54 through the low pressure chamber 61.

The cam ring 40 and the second side plate 80 are provided with a side port 81 as a suction port that guides hydraulic oil in the low pressure chamber 61 to the pump chamber 41. Further, the cam ring 40 and the first side plate 70 are provided with a side port 74 as a suction port that guides hydraulic oil in the fluid chamber 54 to the pump chamber 41. The

side ports

74 and 81 are provided so as to be located in the

extended regions

42a and 42c.

The pump chamber 41 expands while the pump chamber 41 passes through the

expansion regions

42a and 42c (see FIG. 2). As the pump chamber 41 expands, the pressure in the pump chamber 41 decreases, and hydraulic oil is sucked into the pump chamber 41 from the

side ports

74 and 81. That is, the hydraulic oil is sucked into the pump chamber 41 from the

side ports

74 and 81 while the pump chamber 41 passes through the

expansion regions

42a and 42c. Thus, since the hydraulic oil is sucked into the pump chamber 41 in the

expansion regions

42a and 42c, the

expansion regions

42a and 42c are also called “suction regions”.

FIG. 7 is a side view of the first side plate 70 and the second side plate 80 assembled to the cam ring 40 and viewed from the outside in the radial direction. As shown in FIGS. 6 and 7, two depressions 75 are formed on the side surface 70 a of the first side plate 70. The recess 75 opens to the outer peripheral surface 70 b of the first side plate 70.

FIG. 8 is a rear view of the cam ring 40 as viewed from the first side plate 70 side. As shown in FIGS. 7 and 8, two notches 43 that communicate with the inner and outer peripheral surfaces of the cam ring 40 are provided on the end surface 40 b of the cam ring 40 that contacts the first side plate 70. The notch 43 is located in the

extended regions

42a and 42c, and is formed from the outer peripheral surface 40d of the cam ring 40 to the inner peripheral cam surface 40a.

As shown in FIG. 7, in a state where the first side plate 70 is assembled to the cam ring 40, the recess 75 of the first side plate 70 faces the notch 43 of the cam ring 40. The hydraulic oil in the fluid chamber 54 (see FIG. 1) is guided to the pump chamber 41 through a port formed by the recess 75 and the notch 43. That is, in the present embodiment, the recess 75 of the first side plate 70 and the notch 43 of the cam ring 40 correspond to the side port 74.

FIG. 9 is a front view of the second side plate 80 as viewed from the pump cover 60 side. As shown in FIGS. 7 and 9, two recessed portions 82 are provided on the outer peripheral surface 80 b of the second side plate 80. The recess 82 is formed from the side surface 80a of the second side plate 80 to the side surface 80c of the second side plate 80 opposite to the side surface 80a.

2 and 7, two end portions 40c of the cam ring 40 that are in contact with the second side plate 80 are provided with two notches 44 that communicate with the inner and outer peripheral surfaces of the cam ring 40. The notch 44 is formed from the outer peripheral surface 40d of the cam ring 40 to the inner peripheral cam surface 40a so as to be positioned in the

extended regions

42a and 42c.

As shown in FIG. 7, in a state where the second side plate 80 is assembled to the cam ring 40, the recessed portion 82 of the second side plate 80 faces the notch 44 of the cam ring 40. The hydraulic oil in the low pressure chamber 61 (see FIG. 1) is guided to the pump chamber 41 through a port formed by the recess 82 and the notch 44. Thus, in the present embodiment, the recessed portion 82 of the second side plate 80 and the notch 44 of the cam ring 40 correspond to the side port 81.

Next, the operation of the vane pump 100 will be described.

When the power of the engine or the electric motor (not shown) is transmitted to the drive shaft 10, the rotor 20 rotates as the drive shaft 10 rotates. As the rotor 20 rotates, the vane 30 reciprocates with respect to the rotor 20, and the pump chamber 41 repeats expansion and contraction.

The hydraulic oil in the tank 2 is sucked into the pump chamber 41 passing through the

expansion regions

42 a and 42 c through the low pressure chamber 61 and the

side ports

74 and 81, or through the low pressure chamber 61, the fluid chamber 54 and the side port 74. At this time, the hydraulic oil sucked through the

side ports

74 and 81 is centered in the axial direction of the pump chamber 41 by the

recesses

23 and 24 formed on the outer peripheral surface 20a of the rotor 20 as shown by arrows in FIG. Guided towards. Specifically, as indicated by an arrow A shown in FIG. 5, the flow of hydraulic oil is formed so as to be inclined even when the hydraulic oil is sucked from a direction substantially orthogonal to the outer peripheral surface 20 a of the rotor 20. The flow direction is smoothly changed toward the center side in the axial direction of the pump chamber 41 by the side surfaces 23A and 24A. Further, the hydraulic oil is guided toward the axial center of the pump chamber 41 by the bottom surfaces 23C and 24C and the side surfaces 23B and 24B of the

recesses

23 and 24. As described above, in the vane pump 100, by providing the

recesses

23 and 24 on the outer peripheral surface 20 a of the rotor 20, the sucked hydraulic oil can be smoothly guided to the axial center side in the pump chamber 41. Thereby, since the pressure loss at the time of suck | inhaling hydraulic fluid is reduced, the suction efficiency of the vane pump 100 improves.

The pump chamber 41 into which the hydraulic oil has been sucked in this way passes through the

contraction regions

42b and 42d as the rotor 20 rotates. At this time, the hydraulic oil in the pump chamber 41 is discharged from the discharge port 72.

In the vane pump 100, the

recesses

23 and 24 are formed on the outer peripheral surface 20 a of the rotor 20, so that the dead volume of the pump chamber 41 is increased, but a raised portion 25 that protrudes radially from the outer peripheral surface 20 a of the rotor 20 is provided. As a result, an increase in the dead volume of the pump chamber 41 is suppressed. Here, the dead volume is the volume of the pump chamber 41 during the transition from the

contraction regions

42b and 42d to the

expansion regions

42a and 42c (the pump chamber 41 is blocked while moving from the discharge port 72 to the side ports 74 and 81). The volume of the pump chamber 41 when it is in operation. The dead volume will be described in detail below.

When the

recesses

23 and 24 are formed on the outer peripheral surface 20a of the rotor 20, the dead volume in the vane pump 100 is increased accordingly. The dead volume contains high-pressure hydraulic oil that is in communication with the discharge port 72. For this reason, when the pump chamber 41 moves from the discharge port 72 to the

side ports

74 and 81 and communicates with the

side ports

74 and 81, the high-pressure hydraulic oil in the pump chamber 41 is transferred to the

side ports

74 and 81 having a low pressure. Flows in. At this time, the larger the dead volume, the greater the flow rate of the hydraulic oil flowing into the

side ports

74 and 81. In this way, if the hydraulic oil flows from the pump chamber 41 into the

side ports

74 and 81, the suction of the hydraulic oil into the pump chamber 41 is hindered, so that the pump suction efficiency decreases. For this reason, in the vane pump 100, by providing the raised portion 25, the volume increased by the

concave portions

23 and 24 is offset. That is, by providing the raised portion 25 on the outer peripheral surface 20 a of the rotor 20, the dead volume of the pump chamber 41 increased by the

recesses

23 and 24 can be reduced.

In addition, when the clearance enough to provide the protruding part 25 between the outer peripheral surface 20a of the rotor 20 and the inner peripheral surface 40a of the cam ring 40 cannot be secured, the protruding part 25 may not be provided. In the embodiment shown in FIG. 5, the raised portion 25 is formed so as to be continuous with the side surfaces 23 </ b> B and 24 </ b> B of the

recesses

23 and 24. However, as in the modification shown in FIG. It may be formed so as to be spaced from the

recesses

23 and 24.

In the embodiment shown in FIG. 5, the bottom surfaces 23C and 24C are formed by concave curved surfaces, but the bottom surfaces 23C and 24C may be flat as in the modification shown in FIG. Further, although not shown, a plane or a curved surface may be combined.

According to the above embodiment, the following effects are obtained.

The vane pump 100 includes

annular recesses

23 and 24 formed on the outer peripheral surface 20a of the rotor 20, and the

recesses

23 and 24 are formed as the side surfaces 23A, 23B, 24A, and 24B move toward the bottom surfaces 23C and 24C. Are inclined to approach each other. Therefore, the hydraulic oil sucked from the

side ports

74 and 81 is smoothly guided to the axial center side in the pump chamber 41 by the

recesses

23 and 24. Thereby, the suction efficiency of a pump improves.

Further, the side surfaces 23A and 24A of the two

recesses

23 and 24 are formed at positions facing the

notches

43 and 44, respectively. Further, the side surfaces 23A, 24A of the

recesses

23, 24 are formed with an inclination so that the flow of hydraulic oil sucked from the

notches

43, 44 can be controlled. As a result, the hydraulic oil sucked from the

notches

43 and 44 flows from a direction substantially orthogonal to the outer peripheral surface 20a of the rotor 20, but is pumped by the

inclined side surfaces

23A and 24A of the

recesses

23 and 24. It is smoothly guided into the chamber 41 (toward the axial center of the pump chamber 41). Therefore, since the pressure loss at the time of sucking the hydraulic oil from the

notches

43 and 44 is reduced, the suction efficiency of the vane pump 100 can be improved.

Furthermore, in the vane pump 100, since the bottom surfaces of the

recesses

23 and 24 are formed by concave curved surfaces, the hydraulic oil sucked from the

side ports

74 and 81 can be guided into the pump chamber 41 more smoothly. Thereby, the suction efficiency of the vane pump 100 further improves.

Moreover, the vane pump 100 can reduce the dead volume of the pump chamber 41 which is increased by providing the

concave portions

23 and 24 by providing the raised portion 25.

The configuration, operation, and effect of the embodiment of the present invention configured as described above will be described together.

The vane pump 100 includes a rotor 20 that is rotationally driven, a plurality of vanes 30 that are provided in the rotor 20 so as to be capable of reciprocating in the radial direction of the rotor 20, and tip portions 31 of the plurality of vanes 30 that slide with the rotation of the rotor 20. A cam ring 40 having an inner circumferential cam surface 40a in contact therewith, a first side member (first side plate 70) and a second side member (second side plate 80) disposed across the rotor 20 and the cam ring 40, and the rotor 20 , Cam ring 40, adjacent vane 30, pump chamber 41 defined by first side member (first side plate 70) and second side member (second side plate 80), and suction for guiding the working fluid to pump chamber 41 Ports (side ports 74 and 81) and

annular recesses

23 and 24 formed on the outer peripheral surface 20a of the rotor 20

Recesses

23 and 24, both side surfaces (side surfaces 23A and 23B, side surfaces 24A and 24B) are inclined towards each other brought toward its bottom 23C, 24C.

In this configuration, even if the hydraulic oil sucked from the suction ports (side ports 74 and 81) flows into the pump chamber 41 from a direction substantially orthogonal to the outer peripheral surface 20 a of the rotor 20, Since both side surfaces (side surfaces 23A and 23B, side surfaces 24A and 24B) of the

recesses

23 and 24 formed on the surface 20a are inclined so as to approach each other toward the bottom surfaces 23C and 24C, the sucked hydraulic oil is The both sides of the recesses 23 and 24 (side surfaces 23A and 23B, side surfaces 24A and 24B) are smoothly guided toward the axial center of the pump chamber 41. Therefore, the suction efficiency of the vane pump 100 is improved.

In the vane pump 100, the suction ports (side ports 74 and 81) are in contact with the end surface 40b of the cam ring 40 in contact with the first side member (first side plate 70) and the second side member of the cam ring 40 (second side plate 80). The

notches

43 and 44 are formed on at least one of the end faces 40c and communicate with the inner and outer peripheral faces of the cam ring 40. The side faces 23A and 24A of the

recesses

23 and 24 on the end faces 20b and 20c side of the rotor 20 are

notches

43 and 44. Is formed at a position opposite to.

In this configuration, the hydraulic oil sucked from the

notches

43 and 44 is smoothly guided into the pump chamber 41 by the side surfaces 23A and 24A of the

recesses

23 and 24 on the end surfaces 20b and 20c side of the rotor 20. Thereby, the suction efficiency of the vane pump 100 is improved.

In the vane pump 100, the bottom surfaces 23C and 24C of the

recesses

23 and 24 are formed by concave curved surfaces.

In this configuration, the bottom surfaces 23C and 24C of the

recesses

23 and 24 are formed by concave curved surfaces, so that the hydraulic oil can be guided into the pump chamber 41 more smoothly. Thereby, the suction efficiency of the vane pump 100 further improves.

In the vane pump 100, the rotor 20 includes two

concave portions

23 and 24 and an annular raised portion 25 that is formed between the two

concave portions

23 and 24 and protrudes in the radial direction from the outer peripheral surface 20a of the rotor 20.

In this configuration, the dead volume of the pump chamber 41 can be reduced by providing the raised portion 25 on the outer peripheral surface 20a of the rotor 20.

The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

In the above embodiment, the recess is provided with the two

recesses

23 and 24, but depending on how the hydraulic oil flows into the pump chamber 41, only one of the recesses may be provided.

This application claims priority based on Japanese Patent Application No. 2016-025853 filed with the Japan Patent Office on February 15, 2016, the entire contents of which are incorporated herein by reference.

Claims

A rotor that is driven to rotate;
A plurality of vanes provided in the rotor so as to be capable of reciprocating in the radial direction of the rotor;
A cam ring having an inner circumferential cam surface with which the tip portions of the plurality of vanes slide in contact with the rotation of the rotor;
A first side member and a second side member that are disposed across the rotor and the cam ring;
A pump chamber defined by the rotor, the cam ring, the adjacent vanes, the first side member, and the second side member;
A suction port for guiding the working fluid to the pump chamber;
An annular recess formed on the outer peripheral surface of the rotor,
The said recessed part is a vane pump which inclines so that both sides may approach mutually as it goes to a bottom face.
The vane pump according to claim 1,
The suction port is a notch that is formed on at least one of an end surface of the cam ring that contacts the first side member and an end surface of the cam ring that contacts the second side member, and communicates with the inner and outer peripheral surfaces of the cam ring;
The vane pump is formed such that a side surface of the recess on the end surface side of the rotor is opposed to the notch.
The vane pump according to claim 1,
The bottom surface of the concave portion is a vane pump formed by a concave curved surface.
The vane pump according to claim 1,
The rotor is a vane pump including the two concave portions and an annular ridge formed between the two concave portions and projecting radially from the outer peripheral surface of the rotor.