JP2017166357A - Vane pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane pump which improves a starting property, by promptly projecting out a vane from a slit with centrifugal force at the time of rotation starting of a rotor.SOLUTION: A vane pump 1 is equipped with a pump housing 2 which has a rotor chamber 30 in which suction ports 41 and 42 and discharge ports 43 and 44 open; a disc-shaped rotor 5 radially formed with a plurality of slits 50; and a platy vane 6 stored in the slits 50 and capable of moving backward/forward in a diametrical direction of the rotor 5. The slit 50 is formed with a guide surface 50a which slides with a side surface 6a of the vane 6 to guide the backward/forward movement of the vane 6, and a first to a fourth thinned portions 511 to 514, on an inner surface on an outer diametrical side than a back pressure chamber 500. The guide surface 50a is formed so as to at least partially cross the inner surface of the slit 50 in an axial direction of the rotor 5, and the first to the fourth thinned portions 511 to 514 are opened to an outer peripheral surface 5a or axial end surfaces 5b and 5c of the rotor 5.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a vane pump in which fluid sucked from a suction port is discharged to a discharge port by rotation of a rotor in which a plurality of slits that accommodate a plurality of vanes are provided radially.

  Conventionally, a rotor that holds a plurality of vanes rotates in a cam ring having an inner peripheral cam surface, so that a vane pump that discharges hydraulic oil sucked from the suction port to the discharge port is used to operate various hydraulic devices, etc. It is used for. The plurality of vanes are accommodated in slits radially provided in the rotor and can move in the radial direction of the rotor, and a plurality of pump chambers are formed between the outer peripheral surface of the rotor and the inner peripheral cam surface. In such a vane pump, there is one in which the inner peripheral cam surface of the cam ring is formed in an elliptical shape and the first and second suction ports and the first and second discharge ports are opened in the rotor chamber in the cam ring ( For example, see Patent Document 1).

  In such a two-discharge type vane pump, the rotor rotates together with the plurality of vanes, so that the hydraulic oil sucked from the first suction port is discharged to the first discharge port and from the second suction port. The sucked hydraulic oil is discharged to the second discharge port. And it is possible to supply low-pressure and high-pressure hydraulic fluid to the supply destination of hydraulic fluid by making the amount of restriction | limiting in the flow path of the hydraulic fluid discharged to the 1st and 2nd discharge port mutually differ.

  In addition, the vane pump described in Patent Document 1 includes first and second communicating with the back side of the slit (center side of the rotor) in order to push the vane out of the slit and press the tip of the vane against the inner peripheral cam surface. It has a back pressure groove. The first back pressure groove communicates with a slit that accommodates a vane that forms a pump chamber communicating with the first suction port and the first discharge port, and the second back pressure groove includes the second suction port and the first suction port. It communicates with a slit that houses a vane that forms a pump chamber that communicates with the second discharge port. The pressure of the first discharge port is introduced into the first back pressure groove, and the pressure of the second discharge port is introduced into the second back pressure groove.

JP 2001-27186 A

  When a vane pump having two discharge ports, such as that described in Patent Document 1, is used for the operation of an automatic transmission of an automobile, for example, the rotor is rotated by the rotational force of the engine transmitted through the torque converter. Since it is driven, the rotation axis of the rotor is horizontal. In this case, the vane positioned above the rotation axis of the rotor may move to the back side of the slit due to its own weight.

  When some of the vanes move to the back side of the slit in this way, no pressure is generated in the upper discharge port of the first and second discharge ports, and therefore the first and second discharge ports communicate with the discharge port. No pressure is introduced into the back pressure groove. Therefore, for example, the pressure of the discharge port located above may not increase until the rotation of the rotor becomes high speed and the vane jumps out of the slit by centrifugal force. Such a phenomenon becomes conspicuous particularly when starting at an extremely low temperature of, for example, −30 ° C. or less where the viscosity of the oil becomes high.

  Further, the vane jumping out from the slit at the start is necessary not only in the vane pump in which a plurality of suction ports and discharge ports are opened in the rotor chamber, but also in the vane pump in which one suction port and one discharge port are opened in the rotor chamber. Thus, if the ability of the vane to protrude from the slit is improved at the time of start-up when the pressure in the back pressure groove is not sufficient, the discharge pressure from the vane pump is quickly increased.

  As a measure for improving the vane pop-out property, it is conceivable to widen the slit width to reduce the sliding resistance when the vane moves in the slit. However, in this case, the backlash of the vane increases, and the pressure in the back pressure groove leaks from the gap between the inner surface of the slit and the vane to the suction port, so that a sufficient back pressure cannot be obtained.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a vane pump having improved startability by causing a vane to quickly jump out of a slit by centrifugal force at the start of rotation of a rotor. .

  In order to achieve the above object, the present invention provides a pump housing having a rotor chamber in which a suction port and a discharge port are opened, a disk-shaped rotor disposed in the rotor chamber, and having a plurality of slits formed radially. A plate-like vane that is housed in the slit and protrudes from the outer peripheral surface of the rotor and is movable back and forth in the radial direction of the rotor. In the vane pump, the fluid sucked into the rotor chamber is discharged to the discharge port, and the slit is formed as a back pressure chamber to which a back pressure at which an inner diameter side pushes the vane is supplied, The inner surface of the slit closer to the outer diameter side than the back pressure chamber is in sliding contact with the side surface of the vane, and guides the movement of the vane in the radial direction of the rotor. And a stealing portion formed to be recessed from the guide surface in the plate thickness direction of the vane, and at least a part of the guide surface crosses the inner surface of the slit in the axial direction of the rotor. The meat stealing portion is provided as described above, and provides a vane pump that is open on an outer peripheral surface or an axial end surface of the rotor.

  According to the vane pump of the present invention, when the rotation of the rotor is started, the vane can be quickly ejected from the slit by the centrifugal force, and the startability is improved.

It is a block diagram which shows the schematic structure of the vane pump which concerns on the 1st Embodiment of this invention. It is sectional drawing of a vane pump. (A) is a top view which shows the side plate of a vane pump, (b) is a top view which shows the rotor of a vane pump. It is a perspective sectional view showing a part of a rotor. It is a perspective sectional view of the vane pump concerning a 2nd embodiment of the present invention. It is a perspective sectional view of the vane pump concerning the modification of a 2nd embodiment.

[First Embodiment]
A first embodiment of the present invention will be described with reference to FIGS. In addition, although embodiment described below is shown as a suitable specific example in implementing this invention, although there are some parts which have illustrated various technical matters that are technically preferable. The technical scope of the present invention is not limited to this specific embodiment.

  FIG. 1 is a configuration diagram showing a schematic configuration of a vane pump according to an embodiment of the present invention. FIG. 2 is a sectional view of the vane pump. Fig.3 (a) is a top view which shows the side plate of a vane pump. FIG. 3B is a plan view showing the rotor of the vane pump.

  The vane pump 1 is used in an automatic transmission that changes the output rotation of a drive source (engine) of an automobile in accordance with a vehicle speed or the like, and supplies hydraulic oil as a fluid to an actuator for the operation of the automatic transmission.

(Vane pump configuration)
The vane pump 1 includes a pump housing 2, a cam ring 3 and a side plate 4 accommodated in the pump housing 2, a rotor 5 rotatably disposed inside the cam ring 3, and a plurality of vanes 6 that rotate together with the rotor 5. A pump shaft 7 connected to the rotor 5 so as not to rotate relative to the rotor 5 is provided. The pump shaft 7 is a turbine runner which is an output member of a torque converter including a pump impeller connected to a crankshaft of an engine, a turbine runner disposed coaxially with the pump impeller, and a stator disposed between the pump impeller and the turbine runner. Rotational force is received from the drive shaft connected to the shaft via a chain or gear mechanism, and it rotates in the direction of arrow A shown in FIG. Hereinafter, a direction parallel to the rotation axis of the pump shaft 7 is referred to as an axial direction.

  As shown in FIG. 2, the pump housing 2 includes a housing body 21 in which a housing space 20 is formed, and a housing lid body 22 that closes an opening of the housing space 20 in the housing body 21. The lid 22 is fastened with a bolt (not shown). The housing body 21 and the housing lid body 22 are made of, for example, an aluminum-based metal material (aluminum alloy) and are die-cast. In FIG. 1, the housing lid body 22 is not shown and the inside of the accommodation space 20 is shown. 2, the cross section of the vane pump 1 in the AA line of FIG. 1 is shown.

  In the accommodation space 20, the cam ring 3 and the side plate 4 are accommodated. The side plate 4 is disposed on the bottom surface 20 a side of the accommodation space 20, and the cam ring 3 is disposed between the side plate 4 and the housing lid body 22. The cam ring 3 and the side plate 4 are made of, for example, an iron-based metal material and are formed by sintering.

  The housing body 21 is formed with first and second introduction portions 211 and 212 (see FIG. 1) into which hydraulic fluid is introduced from a suction passage (not shown) in communication with the accommodation space 20. The housing main body 21 is formed with first and second discharge passages 213 and 214 (see FIG. 2) that open to the bottom surface 20a of the housing space 20. The pump housing 2 supplies the hydraulic oil supplied from the oil reservoir to the first and second introduction parts 211 and 212 to the hydraulic pressure supply target from the first and second discharge passages 213 and 214 by increasing the pressure. To do. The pump housing 2 is disposed such that the lower side shown in FIGS. 1 and 2 is the lower side in the vertical direction, and the rotation axis of the pump shaft 7 is horizontal.

  The pump shaft 7 is inserted through an insertion hole 220 formed in the housing lid body 22, and one end thereof is accommodated in a blind hole 210 formed in the housing body 21. A sealing member 81 that seals between the inner peripheral surface of the insertion hole 220 and the outer peripheral surface of the pump shaft 7 is disposed in the insertion hole 220 of the housing lid body 22. Further, the pump shaft 7 is rotatably supported by a plurality of cylindrical rollers 82 accommodated in the insertion holes 220 of the housing lid body 22 and a plurality of cylindrical rollers 83 accommodated in the blind holes 210 of the housing body 21. Yes.

  The cam ring 3 has a circular outer peripheral surface and an elliptical inner peripheral surface when viewed from the axial direction along the rotation axis of the rotor 5. This inner peripheral surface serves as an inner peripheral cam surface 3a with which the tip of the vane 6 comes into sliding contact. That is, the cam ring 3 has an inner circumferential cam surface 3a that is elliptical when viewed in the axial direction. A rotor chamber 30 in which the rotor 5 is disposed is formed inside the cam ring 3 surrounded by the inner peripheral cam surface 3a.

  The cam ring 3 has a pair of through holes 31, 31. A pair of columnar protrusions 23 and 23 erected on the bottom surface 20 a of the housing space 20 in the housing main body 21 are inserted into the pair of through holes 31 and 31, respectively. As a result, the cam ring 3 cannot be rotated relative to the pump housing 2.

  As shown in FIG. 3A, the side plate 4 includes a first suction port 41, a second suction port 42, a first discharge port 43, a second discharge port 44, and a first back pressure groove. 45 and a second back pressure groove 46 are formed. These suction ports 41, 42, discharge ports 43, 44, and back pressure grooves 45, 46 are recessed in the axial direction from the flat surface 4 a of the side plate 4 that forms the inner surface of the rotor chamber 30 together with the inner peripheral cam surface 3 a of the cam ring 3. It is formed as a recess and opens into the rotor chamber 30. In the housing lid 22, an arc groove 222 is formed at a position facing the first back pressure groove 45, and an arc groove 221 is formed at a position facing the second back pressure groove 46.

  The first discharge port 43 communicates with the first discharge passage 213, and the second discharge port 44 communicates with the second discharge passage 214. The first discharge passage 213 communicates with the first back pressure groove 45 via the first back pressure introduction passage 47 provided in the side plate 4, and the second discharge passage 214 is connected to the side plate 4. The second back pressure groove 46 communicates with the second back pressure groove 46 through a second back pressure introduction path 48 provided in the first back pressure channel. In FIG. 2, the first and second back pressure introduction paths 47 and 48 are indicated by broken lines.

  The first back pressure groove 45 and the second back pressure groove 46 extend concentrically and semicircularly in different angular ranges along the rotation direction of the rotor 5. In the flat surface 4a of the side plate 4, portions between the opening of the first back pressure groove 45 and the opening of the second back pressure groove 46 are formed as first and second sealing surfaces 4b and 4c. . The first back pressure groove 45 and the second back pressure groove 46 are configured not to communicate directly with each other by the first and second seal surfaces 4b and 4c.

  In a state where the vane pump 1 is mounted on an automobile, the first discharge port 43 is positioned below the rotation axis of the pump shaft 7, and the second discharge port 44 is positioned above the rotation axis of the pump shaft 7. . Further, the side plate 4 has a first whisker groove 431 extending from the first discharge port 43 with the opening area gradually reduced in the direction opposite to the rotation direction of the rotor 5, and a second discharge port 44. A second whisker groove 441 is formed that extends while the opening area is gradually reduced in the direction opposite to the rotation direction of the rotor 5.

  Furthermore, the side plate 4 is formed with an insertion hole 490 through which the pump shaft 7 is inserted, and a pair of through holes 491 and 491 through which the columnar protrusions 23 and 23 are inserted. The side plate 4 is not rotatable relative to the pump housing 2.

  The cam ring 3 has a first communication passage 32 that communicates the first introduction portion 211 of the pump housing 2 and the first suction port 41 with an axial end surface facing the flat surface 4 a of the side plate 4, and a second A second communication passage 33 is formed to allow the introduction portion 212 and the second suction port 42 to communicate with each other. In FIG. 1, the outlines of the first communication path 32 and the second communication path 33 are indicated by broken lines.

  The rotor 5 is rotatably disposed in the rotor chamber 30 so that the outer peripheral surface 5 a faces the inner peripheral cam surface 3 a of the cam ring 3. The rotor 5 has a disk shape made of a sintered body obtained by firing a powder made of an iron-based metal, for example. A fitting hole 52 into which the pump shaft 7 is fitted is formed at the center of the rotor 5. In the present embodiment, the spline fitting portion 71 of the pump shaft 7 is spline fitted into the fitting hole 52 of the rotor 5. The rotor 5 cannot rotate relative to the pump shaft 7 and rotates together with the pump shaft 7.

  Further, as shown in FIG. 3B, the rotor 5 is formed with a plurality of (in this embodiment, twelve) slits 50 that are opened in the outer peripheral surface 5a in a radial pattern. The slit 50 penetrates the rotor 5 in the axial direction. Each slit 50 accommodates a flat vane 6 movably in the radial direction of the rotor 5. The vane 6 has a side surface 6 a that is in sliding contact with a guide surface 50 a (described later) on the inner surface of the slit 50 and is guided in the radial direction of the rotor 5, and a tip portion that protrudes from the outer peripheral surface 5 a of the rotor 5.

  A back pressure chamber 500 communicating with the first back pressure groove 45 and the second back pressure groove 46 is provided at the inner diameter side end of the slit 50 (end on the center side of the rotor 5). The back pressure chamber 500 communicates with the first back pressure groove 45 in a predetermined angle range in the rotation direction of the rotor 5, and communicates with the second back pressure groove 46 in another predetermined angle range. The width of the slit 50 in the circumferential direction of the rotor 5 is wider in the back pressure chamber 500 than in the outer diameter side of the back pressure chamber 500. Back pressure in the direction in which the vane 6 is pushed out of the rotor 5 from the slit 50 is supplied to the back pressure chamber 500 from the first back pressure groove 45 and the second back pressure groove 46. The vane 6 receives this back pressure, and the tip thereof comes into contact with the inner peripheral cam surface 3a.

  As shown in FIG. 3A, the first back pressure groove 45 is provided inside the first suction port 41, and a deep groove 451 through which the first back pressure introduction path 47 communicates, and the first discharge The shallow groove 452 provided inside the port 43, the communication groove 453 that communicates the deep groove 451 and the shallow groove 452, and the end of the shallow groove 452 opposite to the communication groove 453 extend in the rotational direction of the rotor 5. The extended groove 454 is formed. In the direction perpendicular to the plane 4 a of the side plate 4, the depth of the shallow groove 452 is shallower than the depth of the deep groove 451, and the depth of the communication groove 453 and the extension groove 454 is shallower than the depth of the shallow groove 452. In addition, the width of the communication groove 453 and the extension groove 454 is narrower than the width of the deep groove 451 and the shallow groove 452.

  Similarly, the second back pressure groove 46 is provided inside the second suction port 42, and is provided inside the deep groove 461 through which the second back pressure introduction path 48 communicates and the second discharge port 44. The shallow groove 462, the communication groove 463 that allows the deep groove 461 and the shallow groove 462 to communicate with each other, and the extension groove 464 that extends in the rotational direction of the rotor 5 from the end of the shallow groove 462 opposite to the communication groove 463. It consists of. In the direction perpendicular to the plane 4 a of the side plate 4, the depth of the shallow groove 462 is shallower than the depth of the deep groove 461, and the depth of the communication groove 463 and the extension groove 464 is shallower than the depth of the shallow groove 462. Further, the width of the communication groove 463 and the extension groove 464 is narrower than the width of the deep groove 461 and the shallow groove 462.

  The plurality of vanes 6 receive the back pressure supplied to the back pressure chamber 500 from the first back pressure groove 45 and the second back pressure groove 46, and between the inner peripheral cam surface 3 a and the outer peripheral surface 5 a of the rotor 5. A plurality of pump chambers P are formed. In other words, the rotor chamber 30 between the inner peripheral cam surface 3 a and the outer peripheral surface 5 a of the rotor 5 is partitioned into a plurality of pump chambers P by the plurality of vanes 6. The pump chamber P is a hydraulic oil storage space defined by the inner peripheral cam surface 3 a, the outer peripheral surface 5 a of the rotor 5, and a pair of vanes 6 adjacent in the circumferential direction of the rotor 5.

  The volume of the pump chamber P increases when going from the short diameter part to the long diameter part of the elliptical inner circumferential cam surface 3a, and the volume decreases when going from the long diameter part to the short diameter part. In addition, hydraulic oil flows into the pump chamber P from the first and second suction ports 41 and 42 as the volume increases, and the hydraulic fluid that flows into the pump chamber P decreases as the volume of the pump chamber P decreases. The ink is discharged to the second discharge ports 43 and 44.

  In the vane pump 1, the rotor 5 rotates in the direction of arrow A together with the plurality of vanes 6, whereby the hydraulic oil sucked into the pump chamber P from the first suction port 41 is discharged to the first discharge port 43. The pressure transition stroke and the second pressure transition stroke in which the hydraulic oil sucked into the pump chamber P from the second suction port 42 is discharged to the second discharge port 44 are simultaneously performed. The first pressure transition stroke includes a suction stroke for sucking hydraulic oil from the first suction port 41 into the pump chamber P and a discharge stroke for discharging the hydraulic oil sucked into the pump chamber P to the first discharge port 43. Become. Similarly, in the second pressure transition stroke, the suction stroke in which the hydraulic oil is sucked into the pump chamber P from the second suction port 42 and the hydraulic oil sucked in the pump chamber P is discharged to the second discharge port 44. It consists of a discharge stroke.

  The first back pressure groove 45 is located below the second back pressure groove 46. The first back pressure groove 45 supplies back pressure to the vane 6 forming the pump chamber P that performs the first pressure transition stroke. The second back pressure groove 46 supplies a back pressure to the vane 6 that forms the pump chamber P that performs the second pressure transition process. In the discharge stroke of the first pressure transition stroke, the vane 6 moves to the back side of the slit 50 (back pressure chamber 500 side) as the volume of the pump chamber P decreases. As a result, the hydraulic oil inside the slit 50 is discharged to the shallow groove 452 of the first back pressure groove 45, and the discharged hydraulic oil is supplied to the deep groove 451 through the communication groove 453. Similarly, in the discharge stroke of the second pressure transition stroke, as the volume of the pump chamber P decreases, the vane 6 moves to the back side of the slit 50 (the back pressure chamber 500 side), and the operation inside the slit 50 is performed. Oil is discharged into the shallow groove 462 of the second back pressure groove 46, and the discharged hydraulic oil is supplied to the deep groove 461 through the communication groove 463.

  The hydraulic oil discharged to the first discharge port 43 is discharged to the outside of the pump housing 2 through the first discharge passage 213, and the hydraulic oil discharged to the second discharge port 44 is discharged to the second discharge port 44. It is discharged to the outside of the pump housing 2 through the passage 214. The hydraulic fluid discharged from the first discharge passage 213 and the second discharge passage 214 is supplied to a hydraulic pressure supply target such as an actuator via a throttle valve. The throttle amount of the throttle valve is set according to the hydraulic pressure required for the hydraulic supply target. The discharge pressure at the first discharge port 43 and the discharge pressure at the second discharge port 44 are determined according to the throttle amount.

  As described above, since the pump shaft 7 is rotated by the driving force of the engine transmitted through the torque converter, the rotation of the rotor 5 is also stopped when the engine is stopped. At this time, as shown in FIG. 1, the vane 6 positioned above the rotation axis of the pump shaft 7 may move to the back side of the slit 50 due to its own weight. When the rotor 5 starts rotating from this state, the pump chamber P is not defined on the upper side of the rotor 5, so the second pressure transition process is not normally performed, and the back pressure is introduced from the second back pressure groove 46. Is not made. If this state continues, the vane 6 moved to the back side of the slit 50 at the short diameter portion of the inner peripheral cam surface 3a between the first discharge port 43 and the second suction port 42 protrudes outward. The state where the second discharge port 44 does not increase due to the rotation with the rotor 5 without being continued.

  In the vane pump 1 according to the present embodiment, due to the configuration of the rotor 5 described below, the sliding resistance when the vane 6 moves in the slit 50 of the rotor 5 is reduced, and the centrifugal force generated by the rotation of the rotor 5 reduces the sliding resistance. The vane 6 is easy to jump out of the slit 50. As a result, even if sufficient back pressure is not supplied to the back pressure chamber 500, the amount of protrusion of the vane 6 protruding from the outer peripheral surface 5a of the rotor 5 due to centrifugal force increases, and hydraulic oil is discharged to the second discharge port 44. Is done. When hydraulic oil is discharged to the second discharge port 44, the discharge pressure passes through the second back pressure introduction path 48 and the second back pressure groove 46, and the pump chamber P that performs the second pressure transition process is set in the pump chamber P. A back pressure is applied to the vane 6 to be formed. Thereby, the front-end | tip part of the vane 6 is pressed more strongly toward the inner peripheral cam surface 3a, and the discharge pressure of the 2nd discharge port 44 is further raised.

  FIG. 4 is a perspective sectional view showing the inner surface of the slit 50 by cutting the rotor 5 in the radial direction at the slit 50. As shown in FIG. 4, a guide surface that slides against the side surface 6 a of the vane 6 and guides the forward and backward movement of the vane 6 in the radial direction of the rotor 5 on the inner surface of the slit 50 on the outer diameter side of the back pressure chamber 500. 50a and the 1st thru | or 4th meat stealing parts 511-514 formed indented in the plate | board thickness direction (width direction of the slit 50) of the vane 6 from the guide surface 50a are formed. In addition, although illustration is abbreviate | omitted, the guide surface 50a and the 1st thru | or 4th meat stealing part 511-514 are similarly formed also in the other inner surface facing the one inner surface of the slit 50 shown in FIG. ing.

  The first meat stealing portion 511 has a groove shape that opens in one axial end surface 5 b of the rotor 5 (a surface facing the housing lid body 22) and extends in the axial direction. The second meat stealing portion 512 has a groove shape that opens in the other axial end surface 5c of the rotor 5 (the surface facing the side plate 4) and extends in the axial direction. The third and fourth meat stealing portions 513, 514 have a groove shape that opens on the outer peripheral surface 5 a of the rotor 5 and extends parallel to each other along the radial direction of the rotor 5 from the opening end surface of the slit 50. That is, in the present embodiment, the inner surface of the slit 50 on the outer diameter side of the back pressure chamber 500 is composed of the flat guide surface 50a and the groove surfaces of the first to fourth meat stealing portions 511 to 514, and the first The groove surfaces of the fourth meat stealing portions 511 to 514 do not contact the vane 6.

  These 1st thru | or 4th meat stealing parts 511-514 can be formed by the cutting process which used the drill and the end mill, for example as a cutting tool. When the rotor 5 is formed by sintering using a pair of molds facing in the axial direction, the first and second meat stealing portions 511 and 512 are formed by providing protrusions on the mold. be able to.

  In the present embodiment, the first to fourth meat stealing portions 511 to 514 have a semicircular cross section orthogonal to the extending direction, but the present invention is not limited thereto, and may be, for example, a rectangular cross section. That is, the 1st thru | or 4th meat stealing parts 511-514 should just be extended in the groove shape from at least any one of the outer peripheral surface 5a of the rotor 5, and axial direction end surface 5b, 5c.

  The guide surface 50 a is formed so that at least a part thereof crosses the inner surface of the slit 50 in the axial direction of the rotor 5. In the present embodiment, the belt-like portion on the inner diameter side of the virtual straight line L connecting the end portions of the first and second meat stealing portions 511 and 512 on the back pressure chamber 500 side, the inner surface of the slit 50 is connected to the rotor 5. Crossing in the axial direction. As a result, the hydraulic oil in the back pressure chamber 500 is prevented from leaking to the outer peripheral surface 5a side of the rotor 5 and the back pressure is released.

(Operation and effect of the first embodiment)
According to the present embodiment described above, since the first to fourth meat stealing portions 511 to 514 are formed on the inner surface of the slit 50, the area of the guide surface 50a that is in sliding contact with the side surface 6a of the vane 6 is increased. Get smaller. For this reason, the vane 6 easily moves to the outer peripheral side of the rotor 5 due to the centrifugal force generated by the rotation of the rotor 5, and the pressure of the hydraulic oil in the second discharge port 44 is easily increased at the time of starting. That is, the startability of the vane pump 1 is improved.

  Moreover, since the 1st thru | or 4th meat stealing part 511-514 is opened in either the outer peripheral surface 5a of the rotor 5, or the axial direction end surfaces 5b and 5c, the 1st thru | or 4th meat stealing part 511- The processing of 514 can be easily performed. In the present embodiment, the first to fourth meat stealing portions 511 to 514 extend in a groove shape from either the outer peripheral surface 5a of the rotor 5 or the axial end surfaces 5b and 5c. Is easy.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. The vane pump according to the present embodiment is the same as the first embodiment except that the configuration of the rotor is different from that of the first embodiment.

  FIG. 5 is a perspective sectional view showing the rotor 5A according to the present embodiment. In FIG. 5, components common to the rotor 5 according to the first embodiment described with reference to FIG. 4 are assigned the same reference numerals, and redundant description is omitted.

  In the rotor 5 </ b> A, first to third guide surfaces 50 b, 50 c, 50 d for guiding the forward and backward movement of the vane 6, and the first to third guides are provided on the inner surface of the slit 50 on the outer diameter side of the back pressure chamber 500. First and second meat stealing portions 515 and 516 formed so as to be recessed from the guide surfaces 50b, 50c and 50d in the thickness direction of the vane 6 are formed.

  In the present embodiment, the area occupied by the first and second meat stealing portions 515 and 516 on the inner surface of the slit 50 on the outer diameter side of the back pressure chamber 500 is the first to third guide surfaces 50b and 50c. , 50d is larger than the area occupied. The first to third guide surfaces 50b, 50c, 50d protrude in a land shape (island shape) from the bottom surfaces 515a, 516a of the first and second meat stealing portions 515, 516. In FIG. 5, the bottom surfaces 515 a and 516 a are illustrated as planes. However, these bottom surfaces 515 a and 516 a may be formed so as not to contact the vane 6, for example, cutting traces may be left. .

  The first guide surface 50 b is formed so as to cross the inner surface of the slit 50 in the axial direction of the rotor 5. The 2nd guide surface 50c is formed in the corner | angular part between the outer peripheral surface 5a in the rotor 5A, and one axial direction end surface 5b. The third guide surface 50d is formed at a corner between the outer peripheral surface 5a of the rotor 5A and the other axial end surface 5c. Similarly, the first to third guide surfaces 50b, 50c, 50d and the first and second meat stealing portions 515, 516 are also formed on the other inner surface facing the one inner surface of the slit 50 shown in FIG. Is formed.

  Also according to the present embodiment, the same operations and effects as those described in the first embodiment can be obtained. Further, since the area occupied by the first and second meat stealing portions 515, 516 is larger than the area occupied by the first to third guide surfaces 50b, 50c, 50d, the rotor 5 according to the first embodiment. Further, the sliding resistance when the vane 6 moves in the slit 50 can be further reduced.

[Modification of Second Embodiment]
FIG. 6 is a perspective sectional view showing a rotor 5B obtained by further modifying the rotor 5A according to the second embodiment. As with the rotor 5A according to the second embodiment, the rotor 5B includes first to third guide surfaces 50b, 50c, and 50d that guide the forward and backward movement of the vane 6, and first to third guide surfaces. The first and second meat stealing portions 515 and 516 are formed so as to be recessed in the plate thickness direction of the vane 6 from 50b, 50c and 50d, but the second guide surface 50c and the third guide surface 50d are formed. The position of is different.

  Specifically, the shape of the second guide surface 50c and the third guide surface 50d when the inner surface of the slit 50 is viewed in the width direction is a rectangular shape long in the radial direction of the rotor 5B, and the outer peripheral surface 5a of the rotor 5B. And are formed apart from the corners between the axial end faces 5b and 5c. Thereby, the space | interval between the 2nd guide surface 50c in the axial direction of the rotor 5B and the 3rd guide surface 50d is narrower than the rotor 5A which concerns on 2nd Embodiment. Also by this modification, the same operation and effect as those of the second embodiment can be obtained.

(Appendix)
Although the present invention has been described based on the above embodiments, the present invention is not limited to these embodiments, and can be appropriately modified and implemented without departing from the spirit of the present invention. It is.

DESCRIPTION OF SYMBOLS 1 ... Vane pump 2 ... Pump housing 30 ... Rotor chamber 41 ... 1st suction port 42 ... 2nd suction port 43 ... 1st discharge port 44 ... 2nd discharge port 5, 5A, 5B ... Rotor 50 ... Slit 500 ... back pressure chamber 50a ... guide surfaces 50b, 50c, 50d ... first to third guide surfaces 511 to 514 ... first to fourth meat stealing parts 515 and 516 ... first and second meat stealing parts 5a ... Outer peripheral surfaces 5b, 5c ... axial end face 6 ... vane 6a ... side face

Claims (2)

A pump housing having a rotor chamber in which a suction port and a discharge port are opened; a disk-shaped rotor disposed in the rotor chamber and having a plurality of slits formed radially; and an outer peripheral surface of the rotor housed in the slit And a plate-like vane that protrudes forward and backward in the radial direction of the rotor, and fluid that is sucked into the rotor chamber from the suction port when the rotor rotates together with the vane. A vane pump discharged into
The slit is formed as a back pressure chamber to which a back pressure that pushes out the vane at the end on the inner diameter side is supplied,
A guide surface that slides in contact with the side surface of the vane on the inner surface of the slit on the outer diameter side of the back pressure chamber and guides the movement of the vane in the radial direction of the rotor. A meat stealing part that is recessed in the thickness direction is formed,
The guide surface is formed so that at least a part thereof crosses the inner surface of the slit in the axial direction of the rotor,
The meat stealing portion is open to the outer peripheral surface or the axial end surface of the rotor,
Vane pump. The meat stealing portion extends in a groove shape from at least one of the outer peripheral surface and the axial end surface of the rotor,
The vane pump according to claim 1.

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