WO2020026410A1

WO2020026410A1 - Vane pump device

Info

Publication number: WO2020026410A1
Application number: PCT/JP2018/029025
Authority: WO
Inventors: 直哉多賀
Original assignee: 株式会社ショーワ
Priority date: 2018-08-02
Filing date: 2018-08-02
Publication date: 2020-02-06
Also published as: JPWO2020026410A1

Abstract

This vane pump device comprises: a rotor that rotates while supporting a plurality of vanes (30) so as to be movable in a turning radius direction; and a cam ring that has an inner peripheral surface facing an outer peripheral surface of the rotor. The vane pump device transitions to at least a suction step and an ejection step as the volume of a pump chamber defined by the outer peripheral surface of the rotor, the inner peripheral surface of the cam ring, and two adjacent vanes (30) among the plurality of vanes (30) changes in accordance with the rotation of the rotor. The suction step ends at a timing at which the volume of the pump chamber becomes maximum.

Description

Vane pump device

The present invention relates to a vane pump device.

Conventionally, vane pumps that can reduce the generation of abnormal noise have been proposed.
For example, a vane pump described in Patent Document 1 is disposed on a side of a cam ring and has a side plate having an opening formed in a discharge port, and a rotor rotatably housed in the cam ring and driven to rotate by a drive shaft. And a vane held in a plurality of slots formed in the outer peripheral portion of the rotor along the radial direction so as to be able to protrude and retract toward the inner peripheral surface of the cam ring. A beard groove communicating with the discharge port is formed on an inner surface of the side plate that is in sliding contact with the rotor, and the beard groove is gradually tapered from the discharge port along a direction opposite to a rotation direction of the rotor. The tip of the whisker is formed so as to be directed inward from the rotation trajectory passing through the base end of the whisker of each vane.

WO2005-005837

The high-pressure oil at the discharge port may flow back into the pump chamber during the transition from the suction process to the discharge process. When the oil flows backward, the noise generated when the oil flows backward increases as the pressure difference between the oil pressure of the discharge port and the oil pressure in the pump chamber increases.
SUMMARY OF THE INVENTION It is an object of the present invention to provide a vane pump device capable of reducing a pressure difference between a hydraulic pressure of a discharge port and a hydraulic pressure in a pump chamber in a process of shifting to a discharge step.

With this object in mind, the present invention includes a rotor that rotates while supporting a plurality of vanes movably in the rotational radius direction, and a cam ring having an inner peripheral surface facing the outer peripheral surface of the rotor, In accordance with the rotation of the rotor, the outer peripheral surface of the rotor, the inner peripheral surface of the cam ring, and the volume of the pump chamber defined by two adjacent vanes of the plurality of vanes change, The vane pump device transitions at least to the suction step and the discharge step, and ends the suction step when the volume of the pump chamber is the maximum.

According to the present invention, it is possible to provide a vane pump device capable of reducing the pressure difference between the oil pressure of the discharge port and the oil pressure in the pump chamber in the process of shifting to the discharge step.

It is an outline view of a vane pump concerning an embodiment. It is the perspective view which looked at some components of the vane pump from the cover side. It is the perspective view which looked at some components of the vane pump from the case side. It is sectional drawing for showing the flow path of the high pressure oil of a vane pump. It is sectional drawing for showing the flow path of the low-pressure oil of a vane pump. It is the figure which looked at a rotor, a vane, and a cam ring in one direction of a rotation axis direction, and the figure seen in the other direction. It is a figure which shows the distance from the rotation center for every rotation angle in the cam ring inner peripheral surface of a cam ring. It is the figure which looked at the inner plate in one direction of the rotation axis direction, and the other direction. It is the figure which looked at the outer plate in the other direction of a rotation axis direction, and one direction. It is the figure which looked at the case in one direction of the rotation axis direction. It is the figure which looked at the cover in the other direction of a rotation axis. It is a figure showing a flow of high pressure oil. It is a figure showing a flow of low pressure oil. It is the figure which looked at the cam ring and the inner plate in one direction. It is the figure which looked at the cam ring and the outer plate in the other direction. It is a figure which shows the volume of the pump chamber for every rotation angle. It is a figure which shows the volume of oil in the pump room for every rotation angle in the vane pump which concerns on a comparative structure. It is a figure showing the volume of oil in a pump room for every rotation angle in a vane pump concerning this embodiment.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 is an external view of a vane pump device 1 (hereinafter, referred to as “vane pump 1”) according to the present embodiment.
FIG. 2 is a perspective view of some of the components of the vane pump 1 as viewed from the cover 120 side.
FIG. 3 is a perspective view of some of the components of the vane pump 1 as viewed from the case 110 side.
FIG. 4 is a cross-sectional view illustrating a flow path of high-pressure oil of the vane pump 1. FIG. 4 is also a cross-sectional view taken along the line IV-IV of FIG.
FIG. 5 is a cross-sectional view for illustrating a flow path of low-pressure oil of the vane pump 1. FIG. 5 is also a cross-sectional view taken along the line VV of FIG.
The vane pump 1 is a pump driven by, for example, power from an engine of a vehicle to supply oil as an example of a working fluid to a device such as a hydraulic continuously variable transmission or a hydraulic power steering.

Further, the vane pump 1 according to the present embodiment increases the oil sucked from one suction port 116 to two different pressures, discharges high-pressure oil from the two pressures from the high-pressure side discharge port 117, and Is discharged from the low-pressure side discharge port 118. More specifically, the vane pump 1 according to the present embodiment increases the pressure of the oil sucked from the suction port 116 and sucked into the pump chamber from the high-pressure side suction port 2 (see FIG. 4). And discharged from the high pressure side discharge port 4 (see FIG. 4) to the outside through the high pressure side discharge port 117. In addition, the vane pump 1 increases the pressure in the pump chamber of the oil sucked from the suction port 116 and sucked into the pump chamber from the low-pressure side suction port 3 (see FIG. 5), and the low-pressure side discharge port 5 (FIG. 5). ) And discharged from the low pressure side discharge port 118 to the outside. The high pressure side suction port 2, the low pressure side suction port 3, the high pressure side discharge port 4, and the low pressure side discharge port 5 are portions facing (facing) the pump chamber.
Further, in the vane pump 1 according to the present embodiment, the volume Vp of the pump chamber for sucking the oil to be raised to a high pressure of the two different pressures is the volume of the pump chamber for sucking the oil to be raised to the low pressure of the two different pressures. It is smaller than Vp. In other words, the high pressure side discharge port 117 discharges high pressure, small volume oil, and the low pressure side discharge port 118 discharges low pressure, large volume oil.

The vane pump 1 includes a rotating shaft 10 that rotates by receiving a driving force from an engine or a motor of a vehicle, a rotor 20 that rotates with the rotating shaft 10, and a plurality of vanes 30 that are incorporated in grooves formed in the rotor 20. , And a cam ring 40 surrounding the outer periphery of the rotor 20 and the vane 30.
Further, the vane pump 1 is disposed on an inner plate 50 as an example of a one-side member disposed on one end side of the rotary shaft 10 with respect to the cam ring 40, and disposed on the other end side of the rotary shaft 10 with respect to the cam ring 40. And an outer plate 60 as an example of the other side member.
Further, the vane pump 1 includes a housing 100 that houses the rotor 20, the plurality of vanes 30, the cam ring 40, the inner plate 50, and the outer plate 60. The housing 100 has a bottomed cylindrical case 110 and a cover 120 that covers an opening of the case 110.

<Configuration of rotating shaft 10>
The rotating shaft 10 is rotatably supported by a later-described case-side bearing 111 provided on the case 110 and a later-described cover-side bearing 121 provided on the cover 120. A spline 11 is formed on the outer peripheral surface of the rotating shaft 10, and is connected to the rotor 20 via the spline 11. In the present embodiment, the rotating shaft 10 rotates by receiving power from a driving source disposed outside the vane pump 1 such as an engine of a vehicle, and rotates the rotor 20 via the spline 11.
In the vane pump 1 according to the present embodiment, the rotating shaft 10 (the rotor 20) is configured to rotate clockwise in FIG.

<Structure of rotor 20>
FIG. 6 is a view of the rotor 20, the vane 30, and the cam ring 40 as viewed in one direction and the other direction in the rotation axis direction.
The rotor 20 is a generally cylindrical member. On the inner peripheral surface of the rotor 20, a spline 21 into which the spline 11 (see FIG. 2) of the rotating shaft 10 is fitted is formed. A plurality of (in the present embodiment, ten) vane grooves 23 for accommodating the concave vanes 30 in the rotation center direction from the outermost peripheral surface 22 are formed at equal intervals (radially) in the outer peripheral portion of the rotor 20. Have been. In the outer peripheral portion of the rotor 20, a concave portion 24 recessed from the outermost peripheral surface 22 toward the center of rotation is formed between two adjacent vane grooves 23.
The vane groove 23 is a groove that opens on the outermost peripheral surface 22 of the rotor 20 and both end surfaces of the rotating shaft 10 in the rotation axis direction. When viewed in the direction of the rotation axis, the vane groove 23 has, as shown in FIG. 6, a rectangular shape on the outer peripheral side where the longitudinal direction of the rotational radius is the longitudinal direction, and a rotational center side that is in the lateral direction of the rectangle. It has a circular shape with a diameter larger than the length. In other words, the vane groove 23 has a rectangular parallelepiped groove 231 formed on the outer peripheral side in a rectangular parallelepiped shape, and a cylindrical groove 232 as an example of a central space formed on the rotation center side in a cylindrical shape. .

<Configuration of Vane 30>
The vanes 30 are rectangular parallelepiped members, and are incorporated one by one in each of the vane grooves 23 of the rotor 20. The length of the vane 30 in the rotation radius direction is smaller than the length of the vane groove 23 in the rotation radius direction, and the width thereof is smaller than the width of the vane groove 23. Then, the vane 30 is held in the vane groove 23 so as to be movable in the rotational radius direction.

<Configuration of cam ring 40>
The cam ring 40 is a generally cylindrical member, and includes a cam ring outer peripheral surface 41, a cam ring inner peripheral surface 42, an inner end surface 43 that is an end surface on the inner plate 50 side in the rotation axis direction, and an outer plate in the rotation axis direction. An outer end surface 44 which is an end surface on the 60 side is provided.
As shown in FIG. 6, the cam ring outer peripheral surface 41 has a substantially circular shape whose distance from the rotation center is substantially equal over the entire circumference (except for a part thereof) when viewed in the rotation axis direction.

FIG. 7 is a diagram showing the distance L from the rotation center for each rotation angle on the cam ring inner peripheral surface 42 of the cam ring 40.
As shown in FIG. 7, the cam ring inner peripheral surface 42 of the cam ring 40 has a distance L from the rotation center C (see FIG. 6) for each rotation angle (in other words, the vane groove of the vane 30). (Projection amount from the projection 23) has two projections. That is, assuming that the distance L from the rotation center C is zero degree on the positive vertical axis in the diagram viewed in one direction shown in FIG. 6, the distance L gradually increases from about 20 degrees to about 90 degrees in the counterclockwise rotation direction. The first convex portion 42a is formed by gradually decreasing to approximately 160 degrees, and gradually increasing from approximately 200 degrees to approximately 270 degrees, and gradually decreasing to approximately 340 degrees to form the second convex portion 42a. It is set so as to form the convex portion 42b. In the cam ring 40 according to the present embodiment, as shown in FIG. 7, the rotation at each rotation angle is such that the size of the first protrusion 42a is larger than the size of the second protrusion 42b. The distance L from the center C is set. The distance L from the rotation center C for each rotation angle is set so that the foot of the second protrusion 42b is gentler than the foot of the first protrusion 42a. That is, the change in the distance L from the rotation center C at each rotation angle at the foot of the second projection 42b is the change in the distance L from the rotation center C at each rotation angle at the foot of the first projection 42a. Less than. The portions other than the convex portions are set so that the distance L from the rotation center C becomes a minimum value. The minimum value is set to be slightly larger than the distance from the rotation center C on the outermost peripheral surface 22 of the rotor 20.
In the following description, when the positive vertical axis in the figure viewed in one direction shown in FIG. 6 is set to zero degree, the rotation angle range of 0 to 180 degrees in the counterclockwise rotation direction is set to the low pressure side, 180 degrees to 180 degrees. The rotation angle region of 360 degrees may be referred to as a high pressure side.

As shown in FIG. 6, the cam ring 40 has an inner recess 430 that is a plurality of recesses recessed from the inner end face 43 and an outer recess 440 that is a plurality of recesses recessed from the outer end face 44.
As shown in FIG. 6, the inner recess 430 forms a high-pressure suction recess 431 that forms the high-pressure suction port 2, a low-pressure suction recess 432 that forms the low-pressure suction port 3, and a high-pressure discharge port 4. It has a high-pressure side discharge recess 433 and a low-pressure side discharge recess 434 constituting the low-pressure side discharge port 5. When viewed in the rotation axis direction, the high-pressure side suction recess 431 and the low-pressure side suction recess 432 are formed to be point-symmetric with respect to the rotation center C, and the high-pressure side discharge recess 433 and the low-pressure side discharge The recess 434 is formed so as to be point-symmetric with respect to the rotation center C. Further, the high-pressure side suction concave portion 431 and the low-pressure side suction concave portion 432 are depressed over the entire area of the inner end face 43 in the radial direction of rotation, and are depressed from the inner end face 43 by a predetermined angle in the circumferential direction. The high-pressure side discharge concave portion 433 and the low-pressure side discharge concave portion 434 are recessed from the inner end surface 43 by a predetermined range from the cam ring inner peripheral surface 42 to the cam ring outer peripheral surface 41 in the radial direction of rotation. It is recessed from the inner end face 43 by an angle.

The outer recess 440 includes a high-pressure side suction recess 441 that forms the high-pressure side suction port 2 and a low-pressure side suction recess 442 that forms the low-pressure side suction port 3, as shown in FIG. And a high-pressure side discharge recess 443 forming the high-pressure side discharge port 4 and a low-pressure side discharge recess 444 forming the low-pressure side discharge port 5. When viewed in the rotation axis direction, the high-pressure side suction recess 441 and the low-pressure side suction recess 442 are formed to be point-symmetric with respect to the rotation center C, and the high-pressure side discharge recess 443 and the low-pressure side discharge recess 443 are formed. The recess 444 is formed so as to be point-symmetric with respect to the rotation center C. Further, the high-pressure side suction concave portion 441 and the low-pressure side suction concave portion 442 are depressed over the entire area of the outer end face 44 in the rotational radius direction, and are depressed from the outer end face 44 by a predetermined angle in the circumferential direction. The high-pressure side discharge concave portion 443 and the low-pressure side discharge concave portion 444 are recessed from the outer end surface 44 by a predetermined range from the cam ring inner peripheral surface 42 to the cam ring outer peripheral surface 41 in the radial direction of rotation. It is recessed from the outer end face 44 by an angle.

Further, when viewed in the rotation axis direction, the high pressure side suction recess 431 and the high pressure side suction recess 441 are provided at the same position, and the low pressure side suction recess 432 and the low pressure side suction recess 442 are provided at the same position. Have been. The low-pressure side suction recess 432 and the low-pressure side suction recess 442 are provided from about 20 degrees to about 90 degrees in the counterclockwise rotation direction when the positive vertical axis in the diagram viewed in one direction shown in FIG. The high pressure side suction recess 431 and the high pressure side suction recess 441 are provided from about 200 degrees to about 270 degrees.
Further, when viewed in the rotation axis direction, the high-pressure side discharge recess 433 and the high-pressure side discharge recess 443 are provided at the same position, and the low-pressure side discharge recess 434 and the low-pressure side discharge recess 444 are provided at the same position. Have been. The low-pressure side discharge concave portion 434 and the low-pressure side discharge concave portion 444 are provided from about 130 degrees to about 175 degrees in the counterclockwise rotation direction when the positive vertical axis in the one-direction view shown in FIG. The high-pressure side discharge concave portion 433 and the high-pressure side discharge concave portion 443 are provided from about 310 degrees to about 355 degrees.
The cam ring 40 has two high-pressure discharge through-holes 45 that penetrate in the direction of the rotation axis so as to communicate the high-pressure discharge recess 433 and the high-pressure discharge recess 443. The cam ring 40 has two low-pressure discharge through-holes 46 that penetrate in the direction of the rotation axis so as to communicate the low-pressure discharge recess 434 and the low-pressure discharge recess 444.

The cam ring 40 communicates with the inner end face 43 between the high-pressure suction recess 431 and the low-pressure discharge recess 434 and the outer end face 44 between the high-pressure suction recess 441 and the low-pressure discharge recess 444. A first through hole 47, which is a hole that penetrates in the direction of the rotation axis, is formed. Further, the cam ring 40 communicates with the inner end face 43 between the low pressure side suction recess 432 and the high pressure side discharge recess 433 and the outer end face 44 between the low pressure side suction recess 442 and the high pressure side discharge recess 443. A second through-hole 48, which is a hole that penetrates in the direction of the rotation axis, is formed at the bottom.

<Configuration of inner plate 50>
FIG. 8 is a view of the inner plate 50 viewed in one direction and the other direction in the rotation axis direction.
The inner plate 50 is a disk-shaped member having a through hole formed at a central portion, and has an inner outer peripheral surface 51, an inner inner peripheral surface 52, and an inner surface that is an end surface on the cam ring 40 side in the rotation axis direction. It has a cam ring side end surface 53 and an inner non-cam ring side end surface 54 which is an end surface opposite to the cam ring 40 side in the rotation axis direction.
The inner peripheral surface 51 is circular as shown in FIG. 8 when viewed in the rotation axis direction, and the distance from the rotation center C is equal to the distance from the rotation center C on the cam ring outer peripheral surface 41 of the cam ring 40. It is almost the same.
The inner inner peripheral surface 52 has a circular shape as shown in FIG. 8 when viewed in the direction of the rotation axis, and the distance from the rotation center C is the same as the spline 21 formed on the inner peripheral surface of the rotor 20 (see FIG. 8). 6) is substantially the same as the distance to the groove bottom.

The inner plate 50 has an inner cam ring side recess 530 formed from a plurality of recesses recessed from the inner cam ring side end surface 53 and an inner non-cam ring side recess 540 formed from a plurality of recesses recessed from the inner non-cam ring side end surface 54. Are formed.

The inner cam ring side recess 530 is formed at a position facing the high pressure side suction recess 431 of the cam ring 40 and constitutes the high pressure side suction recess 531 constituting the high pressure side suction port 2, and a position facing the low pressure side suction recess 432 of the cam ring 40. And a low-pressure side suction concave portion 532 constituting the low-pressure side suction port 3. The high-pressure suction recess 531 and the low-pressure suction recess 532 are formed to be point-symmetric with respect to the rotation center C.
The inner cam ring side recess 530 has a low pressure side discharge recess 533 formed at a position facing the low pressure side discharge recess 434 of the cam ring 40.
The inner cam ring side concave portion 530 is located at a position corresponding to the low pressure side suction concave portion 532 to the low pressure side discharge concave portion 533 in the circumferential direction, and faces the cylindrical groove 232 of the vane groove 23 of the rotor 20 in the radial direction of rotation. The inner low-pressure side concave portion 534 is provided at a position where the inner low-pressure side recess 534 is formed. The inner low-pressure side concave portion 534 includes a low-pressure side upstream concave portion 534a formed at a position corresponding to the low-pressure side suction concave portion 532 in the circumferential direction and a low-pressure side downstream concave portion formed at a position corresponding to the low-pressure side discharge concave portion 533 in the circumferential direction. 534b, and a low-pressure connection recess 534c that connects the low-pressure upstream recess 534a and the low-pressure downstream recess 534b.
The inner cam ring side concave portion 530 is located at a position corresponding to the high pressure side discharge concave portion 433 in the circumferential direction, and at a position opposed to the cylindrical groove 232 of the vane groove 23 of the rotor 20 in the radial direction of rotation. It has a recess 535.
The inner cam ring side concave portion 530 includes a first concave portion 536 formed at a position facing the first through hole 47 of the cam ring 40 and a second concave portion 537 formed at a position facing the second through hole 48. Have.

The inner non-cam ring side concave portion 540 is formed in the outer peripheral portion and is a groove into which the outer peripheral side O-ring 57 (see FIG. 4) is fitted, and the inner non-cam ring side concave portion 540 is formed in the inner peripheral portion and is formed in the inner peripheral portion. 4) and an inner peripheral groove 542 which is a groove into which the groove is fitted. The outer peripheral side O-ring 57 and the inner peripheral side O-ring 58 seal a gap between the inner plate 50 and the case 110.

In the inner plate 50, a high-pressure side discharge through-hole 55 which is a hole penetrating in the rotation axis direction is formed at a position facing the high-pressure side discharge concave portion 443 of the cam ring 40. The opening of the high pressure side discharge through hole 55 on the cam ring 40 side and the opening of the low pressure side discharge recess 533 are formed so as to be point-symmetric with respect to the rotation center C.
In the inner plate 50, a position corresponding to the high-pressure side suction concave portion 531 in the circumferential direction and a position facing the cylindrical groove 232 of the vane groove 23 of the rotor 20 in the radial direction of rotation are provided in the rotational axis direction. An inner high-pressure side through-hole 56 which is a hole penetrating through is formed.

<Configuration of outer plate 60>
FIG. 9 is a view of the outer plate 60 viewed in the other direction and the one direction of the rotation axis.
The outer plate 60 is a plate-like member having an outer peripheral surface 61, an outer inner peripheral surface 62, and an end surface on the cam ring 40 side in the rotation axis direction. It has a side end face 63 and an outer non-cam ring side end face 64 which is an end face opposite to the cam ring 40 side in the rotation axis direction.
When viewed in the direction of the rotation axis, the outer peripheral surface 61 has a shape obtained by cutting out two places from the circular shape of the base as shown in FIG. 9. The distance from the circular center of rotation C of the base is substantially the same as the distance from the center of rotation C of the cam ring outer peripheral surface 41 of the cam ring 40. The two cutouts are formed at positions facing the high-pressure suction recess 441 and are formed at positions facing the high-pressure suction cutout 611 constituting the high-pressure suction port 2 and the low-pressure suction recess 442. And a low-pressure side suction cutout portion 612 constituting the low-pressure side suction port 3. The outer peripheral surface 61 is formed so as to be point-symmetric with respect to the rotation center C, and the high-pressure side suction notch 611 and the low-pressure side suction notch 612 are point-symmetric with respect to the rotation center C. It is formed so that it becomes.
When viewed in the direction of the rotation axis, the outer inner peripheral surface 62 has a circular shape as shown in FIG. 9, and the distance from the rotation center C is equal to the groove of the spline 21 formed on the inner peripheral surface of the rotor 20. It is almost the same as the distance to the bottom.

The outer plate 60 has an outer cam ring side recess 630 formed by a plurality of recesses recessed from the outer cam ring side end surface 63.
The outer cam ring side concave portion 630 has a high pressure side discharge concave portion 631 formed at a position facing the high pressure side discharge concave portion 443 of the cam ring 40.
The outer cam ring side recess 630 is located at a position corresponding to the high pressure side suction notch 611 to the high pressure side discharge recess 631 in the circumferential direction, and the cylindrical groove 232 of the vane groove 23 of the rotor 20 in the radial direction of rotation. The outer high pressure side concave portion 632 is provided at a position facing the outer high pressure side. The outer high-pressure side concave portion 632 includes a high-pressure side upstream concave portion 632a formed at a position corresponding to the high-pressure side suction cutout portion 611 in the circumferential direction and a high-pressure side concave portion 632 formed at a position corresponding to the high-pressure side discharge concave portion 631 in the circumferential direction. It has a downstream recess 632b and a high-pressure connection recess 632c that connects the high-pressure upstream recess 632a and the high-pressure downstream recess 632b.
The outer cam ring side concave portion 630 is located at a position corresponding to the low pressure side discharge concave portion 444 of the cam ring 40 in the circumferential direction, and at a position facing the cylindrical groove 232 of the vane groove 23 of the rotor 20 in the radial direction of rotation. An outer low-pressure side concave portion 633 is provided.
The outer cam ring side concave portion 630 is parallel to the rotation axis direction, has a V-shaped cross section cut along a plane orthogonal to the outer peripheral surface 61, and has a concave depth as going from the upstream side to the downstream side in the rotation direction. Has a high-pressure side V-groove 634 that increases the size of the V-groove. The downstream end of the high-pressure side V groove 634 is connected to the upstream end of the high-pressure discharge recess 631.
The outer cam ring side concave portion 630 is parallel to the rotation axis direction, has a V-shaped cross section cut along a plane orthogonal to the outer peripheral surface 61, and has a concave depth as going from the upstream side to the downstream side in the rotation direction. Has a low-pressure side V-groove 635 that becomes larger. The downstream end of the low-pressure V-groove 635 is connected to the upstream end of the low-pressure discharge through-hole 65.

In the outer plate 60, a low-pressure side discharge through hole 65 which is a hole penetrating in the direction of the rotation axis is formed at a position facing the low-pressure side discharge concave portion 444 of the cam ring 40. The opening of the low pressure side discharge through hole 65 on the cam ring 40 side and the opening of the high pressure side discharge recess 631 are formed to be point-symmetric with respect to the rotation center C.
Further, the outer plate 60 is rotated at a position corresponding to the low pressure side suction cutout portion 612 in the circumferential direction and at a position facing the cylindrical groove 232 of the vane groove 23 of the rotor 20 in the radial direction of rotation. An outer low-pressure side through hole 66, which is a hole penetrating in the axial direction, is formed.
In the outer plate 60, a first through hole 67, which is a hole penetrating in the rotation axis direction, is provided at a position facing the first through hole 47 of the cam ring 40 at a position facing the second through hole 48 of the cam ring 40. , A second through hole 68 which is a hole penetrating in the direction of the rotation axis is formed.

<Configuration of the housing 100>
The housing 100 houses the rotor 20, the vane 30, the cam ring 40, the inner plate 50, and the outer plate 60. The housing 100 accommodates one end of the rotating shaft 10 therein, and projects the other end.
The case 110 and the cover 120 are fastened with bolts.

(Configuration of Case 110)
FIG. 10 is a view of the case 110 viewed in one direction of the rotation axis direction.
The case 110 is a cylindrical member with a bottom, and has a case-side bearing 111 that rotatably supports one end of the rotating shaft 10 at the center of the bottom.
The case 110 has an inner plate fitting portion 112 into which the inner plate 50 is fitted. The inner plate fitting portion 112 includes an inner diameter side fitting portion 113 located closer to the rotation center C (inner diameter side) and an outer diameter side fitting portion 114 located farther from the rotation center C (outer diameter side). Have.

As shown in FIG. 4, the inner diameter side fitting portion 113 is provided on the outer diameter side of the case side bearing 111, and covers the circumference of a part of the inner inner peripheral surface 52 of the inner plate 50. And an inner diameter side suppressing portion 113b for suppressing the inner plate 50 from moving to the bottom side. The inner diameter side cover portion 113a has a circular shape whose distance from the rotation center C is smaller than the distance from the rotation center C on the inner inner peripheral surface 52 when viewed in the rotation axis direction. The inner diameter side suppressing portion 113b is a donut-shaped surface orthogonal to the rotation axis direction, and the distance from the rotation center C in the inner circle is the same as the distance from the rotation center C in the inner diameter side covering portion 113a. The distance of the circle from the rotation center C is smaller than the distance of the inner inner peripheral surface 52 from the rotation center C.

As shown in FIG. 4, the outer diameter side fitting portion 114 includes an outer diameter side covering portion 114 a that covers a part of the inner outer peripheral surface 51 of the inner plate 50, and a movement of the inner plate 50 to the bottom side. And an outer-diameter-side suppressing portion 114b. The outer diameter side cover portion 114a has a circular shape whose distance from the rotation center C is larger than the distance from the rotation center C on the inner peripheral surface 51 when viewed in the rotation axis direction. The outer diameter side suppressing portion 114b is a donut-shaped surface orthogonal to the rotation axis direction, and the distance from the rotation center C in the outer circle is the same as the distance from the rotation center C in the outer diameter side covering portion 114a. The distance from the rotation center C on the inner circle is smaller than the distance from the rotation center C on the inner peripheral surface 51.

In the inner plate 50, the inner O-ring 58 fitted in the inner groove 542 of the inner plate 50 abuts against the inner diameter suppressing portion 113 b, and the outer O ring 57 fitted in the outer groove 541 prevents the outer O ring 57. It is inserted on the bottom side until it abuts on the portion 114b. Then, the inner peripheral side O-ring 58 contacts the inner peripheral side groove 542 of the inner plate 50, the inner diameter side covering portion 113 a and the inner diameter side suppressing portion 113 b of the case 110, and the outer peripheral side O ring 57 is connected to the outer periphery of the inner plate 50. The case 110 and the inner plate 50 are sealed by contacting the side groove 541, the outer diameter side covering portion 114a of the case 110, and the outer diameter side suppressing portion 114b. Thereby, space S1 on the opening side of inner plate fitting portion 112 in case 110 and space S2 on the bottom side of inner plate fitting portion 112 are defined. A space S1 closer to the opening than the inner plate fitting portion 112 forms a suction passage R1 through which oil sucked from the high-pressure suction port 2 and the low-pressure suction port 3 flows. A space S2 on the bottom side of the inner plate fitting portion 112 forms a high-pressure discharge passage R2 through which oil discharged from the high-pressure discharge port 4 flows.

In addition to the housing space for housing the rotor 20, the vane 30, the cam ring 40, the inner plate 50, and the outer plate 60, the case 110 has a rotational axis direction from the opening side outside the housing space in the radial direction of rotation. A case outer recess 115 is formed. The case outside concave portion 115 faces a cover outside concave portion 123 described later formed in the cover 120 and forms a case low pressure side discharge passage R3 through which oil discharged from the low pressure side discharge port 5 flows.

{Circle around (1)} As shown in FIGS. 1 and 2, the case 110 is formed with a suction port 116 that communicates the space S1 closer to the opening than the inner plate fitting portion 112 with the outside of the case 110. The suction port 116 is a cylindrical hole formed in the side wall of the case 110 and includes a hole whose column direction is orthogonal to the rotation axis direction. The suction port 116 forms a suction flow path R1 through which oil sucked from the high-pressure side suction port 2 and the low-pressure side suction port 3 flows.

{Circle around (1)} As shown in FIGS. 1 and 2, the case 110 is formed with a high-pressure side discharge port 117 that communicates the space S2 on the bottom side of the inner plate fitting portion 112 with the outside of the case 110. The high-pressure side discharge port 117 is configured to include a column-shaped hole formed in the side wall of the case 110 and having a column direction perpendicular to the rotation axis direction. The high-pressure discharge port 117 constitutes a high-pressure discharge passage R2 through which oil discharged from the high-pressure discharge port 4 flows.

Further, as shown in FIGS. 1 and 2, the case 110 is formed with a low-pressure side discharge port 118 that communicates between the case outside recess 115 and the outside of the case 110. The low-pressure side discharge port 118 is a column-shaped hole formed in the side wall of the case outer recess 115 of the case 110 and includes a hole whose column direction is orthogonal to the rotation axis direction. The low pressure side discharge port 118 forms a case low pressure side discharge passage R3 through which the oil discharged from the low pressure side discharge port 5 flows.
Note that the directions (column directions) of the cylindrical holes constituting the suction port 116, the high-pressure discharge port 117, and the low-pressure discharge port 118 of the case 110 according to the present embodiment are the same.

(Configuration of the cover 120)
FIG. 11 is a view of the cover 120 viewed in the other direction of the rotation axis.
The cover 120 has a cover-side bearing 121 that rotatably supports the rotating shaft 10 at the center.
In the cover 120, a cover low-pressure side discharge recess 122 is formed at a position facing the low-pressure side discharge through-hole 65 and the outer low-pressure side through-hole 66 of the outer plate 60. I have. The cover low-pressure side discharge recessed part 122 is formed at a position facing the low-pressure side discharge through-hole 65 and the second low-pressure side discharge formed at a position facing the outer low-pressure side through-hole 66. It has a recess 122b and a third low-pressure discharge recess 122c that connects the first low-pressure discharge recess 122a and the second low-pressure discharge recess 122b.

The cover 120 has a cover outer recess 123 recessed in the rotation axis direction from the end surface on the case 110 side in the rotation radial direction outside the cover low-pressure side discharge recess 122, and a first low-pressure side of the cover low-pressure side discharge recess 122. A cover recess connecting portion 124 that connects the discharge recess 122a and the cover outer recess 123 in the other direction of the rotation axis direction than the end surface on the case 110 side is formed. The cover outer recess 123 is formed so as to open at a position that does not face the above-described housing space formed in the case 110, and faces the case outer recess 115. The cover low-pressure side discharge recess 122, the cover recess connection portion 124, and the cover outside recess 123 constitute a cover low-pressure side discharge flow path R4 (see FIG. 5) through which oil discharged from the low-pressure side discharge port 5 flows. The oil discharged from the low-pressure side discharge port 5 flows into the case low-pressure side discharge flow path R3 via the cover concave-portion connecting portion 124, and via the second low-pressure side discharge concave portion 122b and the third low-pressure side discharge concave portion 122c. It flows into the outer low-pressure side through hole 66.
The second low-pressure discharge recess 122b and the third low-pressure discharge recess 122c are formed shallower and narrower than the first low-pressure discharge recess 122a, and the amount of oil flowing into the outer low-pressure side through hole 66 is It is smaller than the amount of oil flowing into the case low pressure side discharge passage R3.

Further, the cover 120 has a portion facing the high-pressure side suction cutout portion 611 and the low-pressure side suction cutout portion 612 of the outer plate 60, and a space S <b> 1 on the opening side of the inner plate fitting portion 112 of the case 110. A cover suction recess 125 is formed in a portion of the cam ring 40 facing the space outside the cam ring outer peripheral surface 41 in the radial direction of rotation from the end surface on the case 110 side in the rotation axis direction.
The cover suction recess 125 constitutes a suction passage R1 through which oil is sucked from the suction port 116 and is drawn into the pump chamber from the high pressure side suction port 2 and the low pressure side suction port 3.

The cover 120 has a first cover recess 127 recessed in the rotation axis direction from an end surface on the case 110 side at a position facing the first through hole 67 and the second through hole 68 of the outer plate 60, respectively. A recess 128 is formed.

<How to assemble the vane pump 1>
The vane pump 1 according to the present embodiment is assembled as follows.
The inner plate 50 is fitted into the inner plate fitting portion 112 of the case 110. The case 110 and the cover 120 are moved so that the inner cam ring side end surface 53 of the inner plate 50 contacts the inner end surface 43 of the cam ring 40 and the outer end surface 44 of the cam ring 40 contacts the outer cam ring side end surface 63 of the outer plate 60. They are connected by a plurality of (five in this embodiment) bolts.
One end of the cylindrical or columnar positioning pin passing through the first through hole 47 formed in the cam ring 40 and the first through hole 67 formed in the outer plate 60 is connected to the first recess of the inner plate 50. At 536, the other end is held in the first cover recess 127 of the cover 120. One end of a cylindrical or columnar positioning pin passing through the second through hole 48 formed in the cam ring 40 and the second through hole 68 formed in the outer plate 60 is connected to the second recess of the inner plate 50. At 537, the other end is held in the second cover recess 128 of the cover 120. With these, the positions among the inner plate 50, the cam ring 40, the outer plate 60, and the cover 120 are determined.
The rotor 20 and the vane 30 are housed inside the cam ring 40. One end of the rotating shaft 10 is rotatably supported by the case-side bearing 111 of the case 110, and the other end is exposed from the housing 100 between the one end and the other end. Are rotatably supported by the cover-side bearing 121 of the cover 120.

<Operation of vane pump 1>
The vane pump 1 according to the present embodiment has ten vanes 30, and the ten vanes 30 contact the inner peripheral surface 42 of the cam ring 40 of the cam ring 40, so that the two adjacent vanes 30 are adjacent to each other. The outer peripheral surface of the rotor 20 between the two vanes 30, the inner peripheral surface 42 of the cam ring between the two adjacent vanes 30, the inner cam ring side end surface 53 of the inner plate 50, and the outer cam ring side end surface 63 of the outer plate 60. There are 10 pump chambers formed. Focusing on one pump chamber, the pump chamber makes one rotation around the rotary shaft 10 as the rotary shaft 10 makes one rotation and the rotor 20 makes one rotation. In the course of one rotation of the pump chamber, the oil sucked from the high-pressure side suction port 2 is compressed to increase the pressure and discharged from the high-pressure side discharge port 4, and the oil sucked from the low-pressure side suction port 3 is compressed. The pressure is increased to discharge from the low pressure side discharge port 5. In the vane pump 1 according to the present embodiment, as shown in FIG. 7, the shape of the cam ring inner peripheral surface 42 of the cam ring 40 is one of the distance L from the rotation center C to the cam ring inner peripheral surface 42 at each rotation angle. Since the size of the second convex portion 42a is formed to be larger than the size of the second convex portion 42b, a large amount of the low-pressure oil is discharged from the high-pressure side discharge port 4. Oil is discharged from the low pressure side discharge port 5. Further, since the bottom of the second convex portion 42b is formed so as to be gentler than the bottom of the first convex portion 42a, the discharge pressure from the high pressure side discharge port 4 is reduced. 5 higher than the discharge pressure.

FIG. 12 is a diagram showing the flow of high-pressure oil.
Oil discharged from the high-pressure side discharge port 4 (hereinafter, referred to as “high-pressure oil”) flows through the high-pressure side discharge through hole 55 of the inner plate 50 into the space S2 on the bottom side of the inner plate fitting portion 112. Then, the liquid is discharged from the high pressure side discharge port 117. In addition, a part of the high-pressure oil that has flowed into the space S <b> 2 on the bottom side of the inner plate fitting portion 112 through the high-pressure side discharge through hole 55 of the inner plate 50 passes through the inner high-pressure side through hole 56, and faces the opposed rotor. 20 flows into the cylindrical groove 232 of the vane groove 23. In addition, a part of the high-pressure oil that has flowed into the cylindrical groove 232 of the vane groove 23 flows into the high-pressure side upstream recess 632 a of the outer plate 60. Part of the high-pressure oil that has flowed into the high-pressure-side upstream recess 632a of the outer plate 60 flows into the high-pressure-side downstream recess 632b via the high-pressure connection recess 632c (see FIG. 9). Part of the high-pressure oil that has flowed into the high-pressure-side downstream recess 632b of the outer plate 60 flows into the cylindrical groove 232 of the vane groove 23 of the opposed rotor 20, and flows into the inner high-pressure-side recess 535 of the inner plate 50. Since the high pressure side upstream recess 632a, the high pressure side connection recess 632c, and the high pressure side downstream recess 632b are provided from the high pressure side suction port 2 to the high pressure side discharge port 4, the circle of the vane groove 23 corresponding to the high pressure side pump chamber is provided. High-pressure oil flows into the columnar grooves 232. As a result, even if the vane 30 receives a force in the direction of the center of rotation due to the oil in the pump chamber on the high pressure side where the pressure has increased, since the high pressure oil flows into the cylindrical groove 232 of the vane groove 23, the vane 30 Is more likely to come into contact with the inner peripheral surface 42 of the cam ring.

FIG. 13 is a diagram showing the flow of low-pressure oil.
On the other hand, the oil discharged from the low-pressure side discharge port 5 (hereinafter, referred to as “low-pressure oil”) flows into the cover low-pressure side discharge recess 122 through the low-pressure side discharge through hole 65 of the outer plate 60, and the low-pressure side discharge It is discharged from the outlet 118. Further, part of the low-pressure oil that has flowed into the third low-pressure side discharge recess 122c of the cover low-pressure side discharge recess 122 through the low-pressure side discharge through hole 65 of the outer plate 60 passes through the second low-pressure side discharge recess 122b. After passing through the low-pressure side through hole 66, it flows into the cylindrical groove 232 of the vane groove 23 of the rotor 20 facing the same. In addition, part of the low-pressure oil that has flowed into the cylindrical groove 232 of the vane groove 23 flows into the low-pressure-side upstream concave portion 534a of the inner plate 50. Part of the low-pressure oil that has flowed into the low-pressure-side upstream recess 534a of the inner plate 50 flows into the low-pressure-side downstream recess 534b via the low-pressure connection recess 534c (see FIG. 8). Part of the low-pressure oil that has flowed into the low-pressure downstream recess 534b of the inner plate 50 flows into the cylindrical groove 232 of the vane groove 23 of the opposed rotor 20, and flows into the outer low-pressure recess 633 of the outer plate 60. Since the low pressure side upstream recess 534a, the low pressure side connection recess 534c, and the low pressure side downstream recess 534b are provided from the low pressure side suction port 3 to the low pressure side discharge port 5, the circle of the vane groove 23 corresponding to the low pressure side pump chamber is provided. Low-pressure oil flows into the columnar grooves 232. As a result, the low-pressure oil flows into the cylindrical groove 232 of the vane groove 23 corresponding to the vane 30 of the pump chamber on the low-pressure side. The contact pressure on the cam ring inner peripheral surface 42 is low.

<About the downstream end of the suction port>
Hereinafter, the ends of the high-pressure suction port 2 and the low-pressure suction port 3 on the downstream side in the rotation direction (hereinafter, referred to as “downstream ends”) will be described.
The high-pressure suction port 2 includes a high-pressure suction recess 431 and a high-pressure suction recess 441 formed in the cam ring 40, a high-pressure suction recess 531 formed in the inner plate 50, and a high-pressure suction formed in the outer plate 60. The cutout 611 is formed.
The low-pressure side suction port 3 includes a low-pressure side suction recess 432 and a low-pressure side suction recess 442 formed in the cam ring 40, a low-pressure side suction recess 532 formed in the inner plate 50, and a low-pressure side suction formed in the outer plate 60. The cutout 612 is formed.

The high-pressure discharge port 4 includes a high-pressure discharge recess 433 and a high-pressure discharge recess 443 formed in the cam ring 40, a high-pressure discharge through-hole 55 formed in the inner plate 50, and a high-pressure discharge recess 55 formed in the outer plate 60. It is composed of a discharge recess 631.
The low-pressure discharge port 5 includes a low-pressure discharge recess 434 and a low-pressure discharge recess 444 formed in the cam ring 40, a low-pressure discharge recess 533 formed in the inner plate 50, and a low-pressure discharge through-hole formed in the outer plate 60. 65.

In the following description, when it is not necessary to distinguish between the high-pressure side suction port 2 and the low-pressure side suction port 3, the high-pressure side suction port 2 and the low-pressure side suction port 3 may be collectively referred to as “suction port”. is there. When there is no need to distinguish between the high-pressure side discharge port 4 and the low-pressure side discharge port 5, the high-pressure side discharge port 4 and the low-pressure side discharge port 5 may be collectively referred to as a "discharge port". When there is no need to distinguish between the high-pressure side V-groove 634 and the low-pressure side V-groove 635, the high-pressure side V-groove 634 and the low-pressure side V-groove 635 may be collectively referred to as a “V-groove”.

The vane pump 1 according to the above-described embodiment includes the rotor 20 that rotates while supporting the ten vanes 30 movably in the rotational radius direction, and the cam ring 40 that has an inner peripheral surface facing the outer peripheral surface of the rotor 20. And the volume Vp of the pump chamber changes according to the rotation of the rotor 20. When the volume Vp of the pump chamber changes, at least a transition is made to the suction step and the discharge step.
The suction step is a step of sucking oil through a suction port. The section of the suction step is a section where the oil is sucked through the suction port. The discharge step is a step of discharging oil through a discharge port. The section of the discharge step is a section in which oil is discharged through the discharge port.
Then, in the vane pump 1 according to the present embodiment, after the suction process ends, before the discharge process starts, a compression process of compressing the sucked oil is performed. The section of the compression step is a section for compressing the sucked oil.

Hereinafter, the timing when the suction process ends and the timing when the discharge process starts will be described.
In the following description, the upstream vane 30 of the two vanes 30 forming the pump chamber is referred to as an upstream vane 31 (see FIG. 18), and the downstream vane 30 is referred to as a downstream vane 32 (see FIG. 18). Call it.
The timing at which the suction step ends is the timing at which the upstream vane 31 passes through the downstream end (downstream end) of the suction port. When the upstream vane 31 passes through the downstream end of the suction port, oil is not sucked into the pump chamber via the suction port.
The timing at which the discharge process starts is the timing at which the downstream vane 32 passes through the upstream end (upstream end) of the discharge port. The downstream vane 32 starts discharging oil from the pump chamber through the discharge port by passing through the upstream end of the discharge port.

FIG. 14 is a diagram in which the cam ring 40 and the inner plate 50 are viewed in one direction.
FIG. 15 is a view of the cam ring 40 and the outer plate 60 as viewed in the other direction.
The rotation angle at the downstream end of the high-pressure suction port 2 is determined by the high-pressure suction recess 431 and the high-pressure suction recess 441 formed on the cam ring 40 constituting the high-pressure suction port 2, and the high-pressure suction formed on the inner plate 50. Since the rotation angles at the downstream ends of the recess 531 and the high-pressure side suction cutout portion 611 formed on the outer plate 60 are all the same, the rotation angles at the downstream ends of these portions are obtained. For example, the downstream end of the cam ring 40 is the downstream end 431f (441f) of the high-pressure suction recess which is the downstream end of the high-pressure suction recess 431 (441) formed in the cam ring 40 shown in FIGS. The downstream end of the inner plate 50 is, for example, the downstream end 531f of the high-pressure suction recess 531 that is the downstream end of the high-pressure suction recess 531 formed in the inner plate 50 shown in FIG. In addition, the downstream end of the outer plate 60 is a downstream end 611f of the high-pressure suction notch portion, which is a downstream end of the high-pressure suction notch portion 611 formed in the outer plate 60, as shown in FIG.

The rotation angle at the downstream end of the low pressure side suction port 3 is the low pressure side suction recess 432 and the low pressure side suction recess 442 formed in the cam ring 40 constituting the low pressure side suction port 3, and the low pressure side suction formed in the inner plate 50. Since the rotation angles at the downstream ends of the concave portion 532 and the low-pressure side suction cutout portion 612 formed on the outer plate 60 are all the same, the rotation angles at the downstream ends of these portions are obtained. For example, the downstream end of the cam ring 40 is the downstream end 432f (442f) of the low pressure side suction recess 432 (442), which is the downstream end of the low pressure side suction recess 432 (442) formed in the cam ring 40 shown in FIGS. The downstream end of the inner plate 50 is, for example, a downstream end 532f of the low-pressure suction recess which is a downstream end of the low-pressure suction recess 532 formed in the inner plate 50 shown in FIG. In addition, the downstream end of the outer plate 60 is a downstream end 612f of the low-pressure side suction notch which is a downstream end of the low-pressure side suction notch 612 formed in the outer plate 60, as shown in FIG.

The rotation angle at the upstream end (upstream end) of the high-pressure discharge port 4 is determined by the high-pressure discharge recess 433 and the high-pressure discharge recess 443 formed on the cam ring 40 constituting the high-pressure discharge port 4, and the inner plate 50. Since the rotation angles of the upstream ends of the high-pressure side discharge through-hole 55 formed in the outer plate 60 and the high-pressure side discharge concave portion 631 formed in the outer plate 60 are all the same, the rotation angles of the upstream ends of these portions are obtained. For example, the upstream end of the cam ring 40 is the upstream end 433e (443e) of the high-pressure discharge recess 433 (443), which is the upstream end of the high-pressure discharge recess 433 (443) formed in the cam ring 40, as shown in FIGS. The upstream end of the inner plate 50 is, for example, an upstream end 55e of the high pressure side discharge through hole 55 which is an upstream end of the high pressure side discharge through hole 55 formed in the inner plate 50 shown in FIG. The upstream end of the outer plate 60 is the upstream end 631e of the high-pressure discharge recess 631, which is the upstream end of the high-pressure discharge recess 631 formed in the outer plate 60, as shown in FIG.

The rotation angle at the upstream end (upstream end) of the low-pressure discharge port 5 is determined by the low-pressure discharge recess 434 and the low-pressure discharge recess 444 formed in the cam ring 40 constituting the low-pressure discharge port 5, and the inner plate 50. Since the rotation angles of the upstream ends of the low-pressure side discharge concave portion 533 formed in the outer plate 60 and the low-pressure side discharge through hole 65 formed in the outer plate 60 are all the same, the rotation angles of the upstream ends of these portions are obtained. For example, the upstream end of the cam ring 40 is the upstream end 434e (444e) of the low-pressure discharge recess 434 (444e), which is the upstream end of the low-pressure discharge recess 434 (444) formed in the cam ring 40, as shown in FIGS. The upstream end of the inner plate 50 is, for example, a low-pressure discharge recess upstream end 533e which is an upstream end of the low-pressure discharge recess 533 formed in the inner plate 50 shown in FIG. Further, the upstream end of the outer plate 60 is a low-pressure side discharge through-hole 65e which is an upstream end of the low-pressure side discharge through-hole 65 formed in the outer plate 60 shown in FIG.

In the vane pump 1 according to the present embodiment, the timing at which the suction step ends is determined so as to be the timing at which the volume Vp of the pump chamber is maximized. The reason will be described below. In the following, the high pressure side will be described in detail, and the detailed description on the low pressure side will be omitted.

FIG. 16 is a diagram showing the volume Vp of the pump chamber for each rotation angle.
In the following description, the rotation angle of the upstream vane 31 of the two vanes 30 constituting the pump chamber will be referred to as the rotation angle of the pump chamber, and the volume Vp of the pump chamber including the upstream vane 31 will be described. Is the volume Vp at this rotation angle. That is, when the rotation angle of the upstream vane 31 is zero degree (when the center of the rotation direction of the upstream vane 31 is located on the positive vertical axis in the diagram viewed in one direction shown in FIG. 6), The volume V of the pump chamber including the upstream vane 31 is defined as a volume Vp at a rotation angle of zero degree. Since the vane 30 has a thickness in the rotation direction, the rotation angle of the vane 30 is based on the center in the rotation direction.

Then, the cam ring inner peripheral surface 42 of the cam ring 40 on the high pressure side (a range of 180 to 360 degrees in the counterclockwise rotation direction when the positive vertical axis in the diagram viewed in one direction shown in FIG. 6 is zero degree). The rotation angle at which the volume Vp of the pump chamber becomes the maximum (hereinafter, referred to as the “maximum volume”) is larger than the rotation angle of the maximum point of the distance L from the rotation center C (hereinafter, may be referred to as “maximum distance rotation angle”). The rotation angle is sometimes set to be smaller by a predetermined rotation angle. That is, when the upstream vane 31 has a rotation angle smaller than the maximum distance rotation angle of the distance L by a predetermined rotation angle, the volume Vp of the pump chamber including the upstream vane 31 is maximized. Is set. It should be noted that the predetermined rotation angle can be exemplified to be 9 degrees. In the following description, the rotation angle is a rotation angle rounded down to the nearest decimal point. Therefore, 9 degrees means 9.00 degrees to 9.99 degrees. In the vane pump 1 according to the present embodiment, the section of the rotation angle at the maximum point of the distance L (maximum distance rotation angle) and the rotation angle at which the volume Vp of the pump chamber is the maximum (maximum volume rotation angle) is less than 1 degree. And it is not the maximum more than once.

In the vane pump 1 according to the present embodiment, the timing at which the suction step ends is determined to be the timing at which the volume Vp of the pump chamber becomes the maximum. In other words, the end point of the suction port is determined to be a rotation angle smaller than the maximum distance rotation angle of the distance L by a predetermined rotation angle. In other words, the downstream end 431f (441f) of the high-pressure suction recess 431 of the high-pressure suction recess 431 (441) formed on the cam ring 40, the downstream end 531f of the high-pressure suction recess 531 formed on the inner plate 50, and The downstream end 611f of the high-pressure suction notch 611 formed on the outer plate 60 has a rotation angle smaller than the maximum rotation angle of the distance L by a predetermined rotation angle.

Hereinafter, advantages of the vane pump 1 according to the present embodiment will be described in comparison with a comparative configuration.
As the vane pump according to the comparative configuration, a configuration is considered in which the end point of the suction port is set to the rotation angle at which the distance L is the maximum (the maximum distance rotation angle) with respect to the vane pump 1 according to the present embodiment. That is, the rotation angle of the end point of the suction port in the comparative configuration is set to the discharge port side (downstream side) by a predetermined rotation angle from the rotation angle of the end point of the suction port in the present embodiment. Other points of the vane pump according to the comparative configuration are the same as those of the vane pump 1 according to the present embodiment. Since the shape of the discharge port of the vane pump according to the comparative configuration is the same as the shape of the discharge port of the vane pump 1 according to the present embodiment, the section of the compression step in the vane pump according to the comparative configuration is the same as the vane pump according to the present embodiment. 1 is shorter than the section of the compression step.

If the section of the compression step is short, the period for crushing bubbles (air) contained in the oil sucked into the pump chamber is short, so the pump chamber in the compression step (hereinafter, may be referred to as “compression step pump chamber”). The increase in the pressure (oil pressure) of the oil in the parentheses) is suppressed. Therefore, the pressure difference between the oil pressure in the compression process pump chamber and the oil pressure in the discharge port tends to increase. As a result, when the downstream vane 32 constituting the compression step pump chamber reaches the V groove before the discharge step of the compression step pump chamber starts, oil enters the compression step pump chamber from the discharge port through the V groove. The sound generated when flowing (backflow) increases. When oil flows (reversely flows) from the discharge port into the compression process pump chamber, the larger the pressure difference between the oil pressure in the compression process pump chamber and the oil pressure in the discharge port, the larger the oil flow rate and the more rapidly the bubbles are crushed. It is because there is much.

In the vane pump 1 according to the present embodiment, the section of the compression process is longer than the vane pump according to the comparative configuration by a predetermined rotation angle as compared with the vane pump according to the comparative configuration. As a result, according to the vane pump 1 according to the present embodiment, the period for crushing the bubbles contained in the oil in the compression process pump chamber becomes longer as compared with the vane pump according to the comparative configuration, so that the oil pressure in the compression process pump chamber is increased. be able to. Therefore, according to the vane pump 1 according to the present embodiment, the pressure difference between the oil pressure in the compression process pump chamber and the oil pressure at the discharge port is smaller than that of the vane pump according to the comparative configuration. As a result, when the downstream vane 32 constituting the compression process pump chamber reaches the V-groove before the discharge process of the compression process pump chamber starts, oil is discharged from the discharge port through the V-groove into the compression process pump chamber. It is possible to suppress the sound generated when flowing (backflow).

However, the longer the section of the compression step, the longer the period of crushing the bubbles contained in the oil in the pump chamber, which can increase the pressure of the oil in the pump chamber. It is desirable that the volume Vo of the oil is large.

FIG. 17 is a diagram illustrating a volume Vo of oil in the pump chamber for each rotation angle in the vane pump according to the comparative configuration.
As shown in FIG. 17, in the vane pump according to the comparative configuration, even if the end point of the suction port is set to the maximum distance rotation angle of the distance L, the oil volume Vo in the pump chamber becomes the maximum of the distance L. This indicates that the maximum value is not obtained at the distance rotation angle. This is because the volume Vp is reduced in a rotation angle region exceeding the rotation angle at which the volume Vp of the pump chamber is maximized, even though the suction port is open and oil can be sucked. I think it is because it is not possible to inhale oil. It can be seen that the volume Vo of the oil in the pump chamber does not increase even if the suction port is open in a rotation angle region exceeding the rotation angle at which the volume Vp of the pump chamber becomes maximum.
The difference between the volume Vp of the pump chamber and the volume Vo of the oil shown in FIG. 17 is the volume of bubbles (air).

As shown in FIG. 16, in the rotation angle region up to the rotation angle at which the volume Vp of the pump chamber reaches the maximum, the volume Vp of the pump chamber gradually increases, so that the volume Vo of the oil in the pump chamber becomes It has increased. Further, as shown in FIG. 17, in a region where the volume Vp of the pump chamber gradually increases, the volume Vo of the oil in the pump chamber increases. Therefore, even if the section of the compression step is extended by a predetermined rotation angle as compared with the vane pump according to the comparative configuration (even if the end point of the suction step is set to the maximum volume rotation angle), the pressure is sucked into the pump chamber. The volume Vo of the oil does not decrease.

In view of the above, in the vane pump 1 according to the present embodiment, the timing at which the suction process ends is determined to be the timing at which the volume Vp of the pump chamber becomes the maximum. In other words, the downstream end 431f (441f) of the high-pressure suction recess 431 of the high-pressure suction recess 431 (441) formed on the cam ring 40, the downstream end 531f of the high-pressure suction recess 531 formed on the inner plate 50, and The downstream end 611f of the high-pressure suction notch 611 formed in the outer plate 60 has a rotation angle smaller than the maximum rotation angle of the distance L by a predetermined rotation angle.

FIG. 18 is a diagram showing a volume Vo of oil in the pump chamber for each rotation angle in the vane pump 1 according to the present embodiment.
As shown in FIG. 18, in the vane pump 1 according to the present embodiment, the volume Vo of the oil in the pump chamber does not decrease even if the section of the compression process is made longer than that of the vane pump according to the comparative configuration. Further, since the pressure difference between the oil pressure in the compression process pump chamber and the oil pressure at the discharge port is small, the flow velocity of the oil flowing through the V groove is small. Therefore, it is possible to suppress a sudden increase in the amount of collapse of the bubbles. As a result, according to the vane pump 1 according to the present embodiment, the section of the compression process can be lengthened and noise can be suppressed while suppressing a decrease in pump efficiency.

In the vane pump 1 according to the present embodiment, the rotation at which the rotation angle (the maximum distance rotation angle) of the maximum point of the distance L from the rotation center C on the cam ring inner peripheral surface 42 of the cam ring 40 and the volume Vp of the pump chamber becomes maximum. The rotation angle difference from the angle (the maximum volume rotation angle) is set to approximately 9 degrees. Since the vane pump 1 according to the present embodiment is a pump having ten vanes 30, the rotational angle difference between the two vanes 30 forming the pump chamber (rotation angle between vanes) Is 9 / (360/10) = 0.25.

Therefore, in the vane pump 1 according to the present embodiment, the downstream end (end point) of the suction port is larger than the rotation angle (maximum distance rotation angle) of the maximum point of the distance L from the rotation center C of the cam ring inner peripheral surface 42. Is also set so as to be located on the upstream side in the rotation direction by a rotation angle of approximately 0.25 × (360/10 (number of vanes)). For example, when the number of vanes is 12, 0.25 × (360/12) = 7.5 degrees, and the downstream end of the suction port is located at a distance L from the rotation center C of the cam ring inner peripheral surface 42. It may be set so as to be located upstream of the rotation angle of the maximum point.

In addition, as a result of earnest research by the present inventors, in the vane pump 1 having ten vanes 30 according to the present embodiment, the downstream end (end point) of the suction port is smaller by one degree than the maximum volume rotation angle. In the case (on the upstream side), it was confirmed that the volume Vo of the oil sucked into the pump chamber was reduced beyond an allowable limit.
Further, if the section of the compression process is longer than that of the vane pump according to the comparative configuration, the pressure difference between the oil pressure in the compression process pump chamber and the hydraulic pressure at the discharge port can be made smaller than that of the vane pump according to the comparative configuration.
Therefore, the downstream end of the suction port is located at the same position as the maximum volume rotation angle or downstream of the maximum volume rotation angle and upstream of the maximum distance rotation angle (9 degrees in the present embodiment). It is preferable to set as follows.

In the vane pump 1 having ten vanes 30 according to the present embodiment, when the downstream end (end point) of the suction port is in a range of 3 degrees or less downstream of the maximum volume rotation angle, the compression is performed. The section of the process can be 1.5 times or more the vane pump of the comparative configuration. As a result of intensive studies made by the present inventors, when the downstream end (end point) of the suction port is in a range of 3 degrees or less downstream of the maximum volume rotation angle, the vane pump according to the comparative configuration is Thus, it was confirmed that the noise generated when oil flows (backflow) from the discharge port into the compression process pump chamber can be reduced to 1 / 1.15 or less. The ratio of the rotation angle difference of 3 degrees to the rotation angle between vanes is 3 / (360/10) = 0.083.

From the above, the downstream end (end point) of the suction port is rotated from 0 degree or more to 0.083 × (360 / (number of vanes)) at the downstream side in the rotation direction with respect to the maximum volume rotation angle. It is preferable that the angle is set to be within the angle range. Thus, it is possible to suppress the noise by lengthening the section of the compression process while suppressing a decrease in the pump efficiency.

On the other hand, the longer the section of the suction process, the more the surge pressure is suppressed, and the volume Vo of the oil sucked into the pump chamber particularly at high rotation increases. When the volume Vo of the oil increases, the suction efficiency particularly at high rotation increases, and the pump efficiency increases. As a result of the inventor's intensive research, when the downstream end of the suction port is located in a range from the rotation angle of 5 degrees to 9 degrees downstream of the maximum volume rotation angle, the downstream of the suction port is It has been confirmed that the oil volume Vo can be increased by 0.15% with respect to the case where the end is located at the maximum volume rotation angle. Therefore, especially in a vane pump mainly used in a high rotation region, in order to suppress a decrease in pump efficiency and suppress noise, the downstream end of the suction port is required to be 5 ° downstream of the maximum volume rotation angle. Preferably, it is set so as to be located in a range from the rotation angle to 9 degrees. Since the ratio of the rotation angle of 5 degrees to the inter-vane rotation angle is 5 / (360/10) = 0.14, the downstream end (end point) of the suction port is rotated in the rotation direction with respect to the maximum volume rotation angle. On the downstream side, the rotation angle is set so as to be within a rotation angle range of 0.14 × (360 / (number of vanes)) or more and less than 0.25 × (360 / (number of vanes)). preferable.

In the above-described vane pump 1 according to the present embodiment, when the section of the rotation angle at the maximum point of the distance L and the rotation angle at which the volume Vp of the pump chamber is the maximum is less than 1 degree, the maximum distance rotation angle It is illustrated that the difference between the rotation angle at which the volume Vp of the pump chamber is the maximum is a predetermined rotation angle (for example, 9 degrees). For example, when the section of the rotation angle where the volume Vp of the pump chamber is the maximum extends over 1 degree, the rotation angle when the volume Vp of the pump chamber is the maximum (when it becomes) and the maximum distance rotation It is desirable that the difference from the angle is a predetermined rotation angle (for example, 9 degrees). This makes it possible to lengthen the section of the compression process while keeping the volume Vo of the oil in the pump chamber from decreasing.

As described above, the vane pump 1 according to the present embodiment has the rotor 20 that supports and rotates the plurality of vanes 30 so as to be movable in the rotational radius direction, and the inner peripheral surface facing the outer peripheral surface of the rotor 20. And a plurality of vanes 30 defined by an outer peripheral surface of the rotor 20, an inner peripheral surface of the cam ring 40, and two adjacent vanes 30 among the plurality of vanes 30 in accordance with the rotation of the rotor 20. Pump chamber. The pump chamber changes at least to the suction step and the discharge step by changing the volume Vp, and the suction step ends when the volume Vp of the pump chamber is the maximum. Thus, for example, compared to the vane pump according to the comparative configuration in which the timing at which the suction step ends is the maximum distance rotation angle of the distance L, the compression of the oil in the pump chamber is prevented while the volume Vo is not reduced. The section of the process can be lengthened, and the pressure difference between the hydraulic pressure of the discharge port and the hydraulic pressure in the discharge pump chamber can be reduced.

Here, the timing at which the suction step ends is preferably when the volume Vp of the pump chamber becomes the maximum. For example, when the section of the rotation angle where the volume Vp of the pump chamber is the largest extends over 1 degree or more, the timing at which the suction process ends is set to the time when the volume Vp of the pump chamber becomes the maximum. The section of the process can be made longer.

Further, in the vane pump 1 according to the present embodiment, the volume Vp of the pump chamber changes according to the rotation of the rotor 20, so that at least a transition is made to the suction step and the discharge step. The start of the compression step as an example of the compression section until the start of the step is on the upstream side in the rotation direction from the rotation angle at which the distance L is maximum (the maximum distance rotation angle). Therefore, for example, compared with the vane pump according to the comparative configuration in which the start of the compression step is set to the maximum distance rotation angle of the distance L, the section of the compression step can be made longer. As a result, the pressure difference between the oil pressure of the discharge port and the oil pressure in the compression process pump chamber can be reduced.

In the above-described embodiment, the timing at which the suction steps on the high pressure side and the low pressure side of the vane pump 1 capable of discharging the oil sucked from the suction port 116 to two different pressures is set to the maximum. Although the volume rotation angle is set, it is not particularly limited to this mode. Only the timing at which either the high-pressure side or the low-pressure side suction step ends may be the maximum volume rotation angle.

Further, the timing at which the suction step ends is set to the maximum volume rotation angle by changing the shape of the cam ring inner peripheral surface 42 of the cam ring 40 without changing the suction port and the discharge port between the high pressure side and the low pressure side. Although the present invention is applied to a vane pump of a type that increases pressure to two pressures, the present invention is not particularly limited to such a type of vane pump. For example, the present invention is applied to a vane pump of a type in which the pressure of the oil discharged from the pump chamber such as the discharge port shape is changed to two different pressures without changing the shape of the cam ring inner peripheral surface 42 of the cam ring 40. Is also good.
The timing at which the suction step is completed may be set to the maximum volume rotation angle, which may be applied to a vane pump that discharges oil at the same pressure through two different discharge ports and flow paths.

In the above-described embodiment, the suction recesses (the high-pressure suction recess 431 and the high-pressure suction recess 441, or the low-pressure suction recess 432 and the low-pressure suction recess 442) of the cam ring 40, which constitute the suction port, The rotation angle of the downstream end of the suction recess of the plate 50 (the high-pressure side suction recess 531 or the low-pressure side suction recess 532) and the downstream end of the suction notch of the outer plate 60 (the high-pressure side suction notch 611 or the low-pressure side suction notch 612). Are all the same. Therefore, in order to set the rotation angle of the downstream end of the suction port to the maximum volume rotation angle, it is preferable that the rotation angles of the downstream ends of all these parts be the maximum volume rotation angle. However, when the downstream ends of these parts are not all the same, the rotation angle of the downstream end of the part constituting the downstream end may be set as the maximum volume rotation angle.

DESCRIPTION OF SYMBOLS 1 ... Vane pump, 2 ... High pressure side suction port, 3 ... Low pressure side suction port, 4 ... High pressure side discharge port, 5 ... Low pressure side discharge port, 10 ... Rotating shaft, 20 ... Rotor, 30 ... Vane, 40 ... Cam ring, 50 ... inner plate, 60 ... outer plate, 100 ... housing, 110 ... case, 120 ... cover

Claims

A rotor that supports and rotates a plurality of vanes movably in a rotational radial direction,
A cam ring having an inner peripheral surface facing the outer peripheral surface of the rotor,
Has,
In accordance with the rotation of the rotor, the outer peripheral surface of the rotor, the inner peripheral surface of the cam ring, and the volume of the pump chamber defined by two adjacent vanes of the plurality of vanes change, A vane pump device that transitions at least to a suction step and a discharge step, and ends the suction step when the volume of the pump chamber is maximum.
2. The vane pump device according to claim 1, wherein the suction step ends when the volume of the pump chamber is maximized. 3.
The volume of the pump chamber changes by changing the distance from the rotation center of the rotor to the inner peripheral surface of the cam ring according to the rotation angle of the rotor,
3. The vane pump device according to claim 1, wherein the rotation angle at which the suction step ends is upstream of the rotation angle at which the distance becomes maximum in the rotation direction. 4.
A rotor that supports and rotates a plurality of vanes movably in a rotational radial direction,
A cam ring having an inner peripheral surface facing the outer peripheral surface of the rotor,
Has,
In accordance with the rotation of the rotor, the outer peripheral surface of the rotor, the inner peripheral surface of the cam ring, and the volume of the pump chamber defined by two adjacent vanes of the plurality of vanes change, Transition to at least the inhalation step and the discharge step,
The ratio of the rotation angle difference between the rotation angle at which the suction process ends and the rotation angle at which the volume of the pump chamber is maximized to the interval between the rotation angles between the two adjacent vanes is 0 or more. A vane pump device that is less than 25.
The vane pump device according to claim 4, wherein a ratio of the rotation angle difference is 0 or more and 0.083 or less.
The vane pump device according to claim 5, wherein the rotation angle at which the suction step is completed is the same as the rotation angle at which the volume of the pump chamber is maximized.
The vane pump device according to claim 4, wherein a ratio of the rotation angle difference is 0.14 or more and less than 0.25.
A rotor that supports and rotates a plurality of vanes movably in a rotational radial direction,
A cam ring having an inner peripheral surface facing the outer peripheral surface of the rotor,
Has,
Since the distance from the rotation center of the rotor to the inner peripheral surface of the cam ring changes according to the rotation angle of the rotor, the outer peripheral surface of the rotor, the inner peripheral surface of the cam ring, and the plurality of vanes The volume of the pump chamber defined by the two adjacent vanes changes according to the rotation of the rotor, so that at least a transition is made to the suction step and the discharge step. A vane pump device in which the compression section is started before the discharge step is started, is located on the upstream side in the rotation direction from the rotation angle at which the distance becomes maximum.
The vane pump device according to claim 8, wherein the compression section starts at a time when the volume of the pump chamber is maximized.