JPH0932740A - Vane pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a small-sized vane pump which is light weight and ensure the strength of a body and a cam ring of a balance oil passage without necessitating the formation of a hollow passage and the cam ring by forming an introduction passage section which introduces hydraulic oil into a suction recessed section through a clearance on an end face on the cam ring side of a plate member in addition. SOLUTION: A back pressure introduction groove 31 is formed at a predetermined position which corresponds to a basic end of a vane 7 to introduce back pressure. An engaging face which engages with outer periphery of a side plate 4 is formed on inner periphery of a cover 2, and a recessed section 21 for forming an oil chamber 40 is formed. A clearance is formed between outer periphery of a cam ring 8 and the side plate 4 and inner periphery of the cover 2 to form a suction passage 20. A low pressure flow passage which is communicated with a supply communicating passage 12 which is opened on an end face 1A of a body 1 and surrounds an outer peripheral face which is semi-circular in its upper section of the cam ring 8 and the side plate 4 is constituted. Consequently, it is possible to reduce size and weight of a vane pump and ensure the strength of the cam ring.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a vane pump,
In particular, the present invention relates to a vane pump most suitable as a hydraulic power source for a vehicle power steering device or the like.

[0002]

2. Description of the Related Art Vehicles such as automobiles are equipped with a power steering device using hydraulic pressure.
A vane pump as shown in FIG. 13 to FIG. 15 is adopted, and it will be explained below.
Body 101 accommodating 10 and side plate 108
The end portion of the pump cartridge 110 is sealed with a cover 102, and a pump cartridge 110 includes a cylindrical cam ring 111, a rotor 112 coupled to the drive shaft 109, and a vane 113 slidably contacting the inner circumference of the cam ring 111. High-pressure hydraulic oil from 110 flows into the discharge passage 120 of the body 101 via the side plate 108, and is pressure-fed from the flow rate adjusting valve 105 to the outside.

On the other hand, excess hydraulic oil in the flow rate adjusting valve 105 and low-pressure hydraulic oil from the suction conduit 130 are transferred from the suction communication passage 131 formed in the body 101 to the cover 102.
And is supplied to the suction side of the pump cartridge 110 via a bifurcated branched suction passage 132 and a suction port 140 formed inside the cover 102.

Here, as shown in FIG. 15, the suction port of the pump cartridge 110 has a cam surface of the cam ring 111 and a suction port 140 formed in the cover 102 so as to face the vane 113, and also has a cam surface. Vane 113
A pair of suction recesses 141 formed as recesses on the side plate 108 facing each other, and balance oil passages 150, 150 communicating with the suction port 140 and the suction recess 141 facing each other are formed on the cam ring 111. A through hole is formed in parallel with 109.

The operating oil flowing from the branch suction passage 132 into the suction port 140 inside the cover 102 is supplied from the suction port 140 to the pump cartridge 110.
Part of the side plate 10 is through the balance oil passage 150.
It is also supplied from the suction recess 141 on the eighth side, and in FIG. 15, the vanes 113 are supplied with hydraulic oil from both end surfaces of the cam ring 111, respectively, to ensure suction efficiency.

[0006]

However, in the above-mentioned conventional vane pump, since the communication oil passage 150 is formed through the cam ring 111, the wall thickness is partially reduced, so that the wall thickness is increased in order to secure the strength. However, there is a problem in that the outer diameter of the cam ring 111 increases, which hinders the vane pump from becoming smaller and lighter.

Further, since it is necessary to form the branch suction passage 132 inside the cover 102, it is necessary to cast and mold using a core, and when molding, there is no need for sanding treatment of the core. In addition to the necessity of a process, which obstructs the reduction of the manufacturing cost, the cover 102 has the branch suction passage 13 inside.
Since 2 is formed in a bifurcated shape, there is a problem that strength is reduced when the thickness is reduced and the size is reduced.

Therefore, the present invention provides a vane pump which can be downsized while ensuring the suction efficiency and the strength of the cam ring and the cover, and which can easily form the cover without using a core to reduce the manufacturing cost. The purpose is to provide.

[0009]

According to a first aspect of the present invention, a rotor coupled to a drive shaft, a cam ring rotatably accommodating a vane provided in and out of the rotor, and a shaft support for the drive shaft are provided. , A suction port corresponding to the suction region of the cam ring and a discharge port corresponding to the discharge region are respectively provided on the end surface that abuts against one end surface of the cam ring, and the upper semicircular outer peripheral portion of the outer circumference of the cam ring. A first body in which a low pressure distribution groove portion bifurcated toward the suction port is provided in an end surface portion corresponding to, and a cam ring is arranged so as to sandwich the cam ring in cooperation with the first body. The plate member, the rotor, the cam ring, and the plate member are housed inside, and the peripheral edge portion of the opening end surface that engages with the first body engages with the end surface of the plate member. A second body that surrounds the outer periphery of the cam ring and the plate member and abuts the lower semicircular outer peripheral surface of the cam ring and the plate member while forming a predetermined bifurcated gap between the cam ring and the plate member and the upper semicircular outer peripheral surface. A suction communication passage formed at the top of the low pressure distribution groove portion of the first body end surface facing the gap, and a predetermined position on the cam ring side end surface of the plate member so as to communicate with the gap. A suction recess formed to face the suction port of the first body end surface and a discharge recess formed to face the discharge port of the first body end surface are provided, and the cam ring side end surface of the plate member is further provided. An introduction passage portion for guiding hydraulic oil from the gap to the suction recess is additionally formed.

In a second aspect of the present invention, one of the introduction passages with respect to the suction recesses symmetrically arranged in the plate member is formed so as to extend along the rotational direction of the rotor and the other is provided in the rotational direction. It is extended in the opposite direction.

According to a third aspect of the invention, the introduction passage portion of the plate member is formed by a tapered chamfered portion provided on the end surface of the plate member.

[0012]

Therefore, according to the first aspect of the present invention, the pump cartridge is sandwiched between the end surface of the first body and the plate member, and the cam ring and the plate member forming the pump cartridge are in contact with each other at the end surface of the plate member. It is mounted and supported on the inner circumference of the body.

A suction port corresponding to the suction area of the cam ring and a discharge port corresponding to the discharge area are symmetrically provided on the contact surface of the first body with which the cam ring contacts, and the upper semicircular outer circumference of the outer circumference of the cam ring. A low-pressure distribution groove that is bifurcated toward the suction port is provided in the end face portion corresponding to the portion, while the second body surrounds the outer periphery of the cam ring and the plate member, and its upper semicircular outer peripheral surface. A predetermined forked gap is formed between the plate member and the cam ring side end face of the plate member so as to communicate with the gap and face a suction port of the first body end face. And a discharge recess formed so as to face the discharge port on the end surface of the first body, and further facilitates the inflow of hydraulic oil from the gap into the suction recess. Forming a guide passage portion.

When the drive shaft is rotated and the rotor is rotated,
The hydraulic oil on the suction side is
Flowed through the bifurcated low-pressure distribution passage on the end face of the first body from the suction port, and on the other end face, from the supply communication passage of the first body into the bifurcated gap on the inner circumference of the second body. After that, it is sucked into the suction region of the cam ring from the suction recess formed at the predetermined position of the end face of the cam ring side of the plate member, respectively, and is sucked substantially evenly from both end faces of the cam ring, so that suction efficiency can be secured. At this time, the hydraulic oil into the suction recess of the plate member is made to easily flow in by the introduction passage portion of the end surface of the plate member that abuts against the cam ring, and these low pressure side passages should accommodate the cam ring and the plate member in the second body. Since it is configured by using the gap formed by, it is not necessary to form a hollow passage by molding a hollow core, etc. and to connect both end surfaces of the cam ring. Since it is not necessary to form a balance oil passage for hydraulic oil in the cam ring, size and weight can be promoted and the strength of the second body and the cam ring can be easily ensured. Since it is formed as a part, any molding method can be adopted without being limited to casting using a core,
The processing cost can be reduced.

According to a second aspect of the present invention, the shape of the introduction passage portion with respect to the suction recesses symmetrically arranged on the plate member is matched with the rotation direction of the rotor, one is extended along the rotation direction, and the other is rotated. Because it was formed extending in the opposite direction,
While increasing the area of each passage on the suction side, the suction characteristics of the vane pump due to the rotation direction of the rotor can be made uniform.

Further, in the third aspect of the invention, since the introduction passage portion of the plate member is formed by the tapered chamfered portion provided on the end surface of the plate member, the strength of the plate member is impaired to secure each passage area on the suction side. It is possible to improve the suction efficiency and reduce the size and weight without causing any trouble.

[0017]

1 to 11 show an embodiment in which the present invention is applied to a vane pump.

1 to 7, reference numeral 1 is a first body of a vane pump for supporting a drive shaft 9 and accommodating a flow rate adjusting valve 5, and a rotor 6 is rotatably accommodated in the body 1. A pump cartridge 3 including a cam ring 8 and the like, and a cover 2 as a second body for accommodating a side plate 4 as a plate member formed of a substantially disc-shaped member are coupled.

A drive shaft 9 penetrating substantially the center of the body 1.
Is rotatably supported by a bearing metal 16, and a hydraulic pipe line (not shown) is connected to an intake connector 10 which is integrally provided so as to project from an upper portion of the body 1. A pulley (not shown) or the like is connected to the right end of the drive shaft 9 in the figure.

The flow rate adjusting valve 5 is provided inside the body 1.
Is accommodated and the flow rate of the hydraulic oil is adjusted to be sent to the outside of the vane pump from the discharge port 5A shown in FIGS.

As shown in FIG. 1, the pump cartridge 3 is in contact with the end surface 1A of the body 1 facing the cover 2, and the pump cartridge 3 is a circle engaged with the bottom of the cover 2 formed in a concave shape. Plate-shaped side plate 4 and end face 1
It is sandwiched with A.

As shown in FIG. 2, the pump cartridge 3 has a rotor 6 that is spline-coupled to the drive shaft 9 at the inner circumference of a tubular cam ring 8 and a rotor 6 that is supported by the rotor 6 and slides on the inner circumference of the cam ring 8. The cam ring 8 is composed of a vane 7 in contact with the body 1, and the rotation of the cam ring 8 is restricted by a pair of dowel pins 18, 18 protruding from the body 1. The inner circumference of the cam ring 8 faces the pump cartridge 3 as described later. The end ports 1A communicate with the suction ports 14, 14 and the discharge ports 15, 15 in a predetermined phase. In addition,
The displacement of the rotor 6 to the left in FIG. 1 is restricted by a circlip 17 provided on the drive shaft 9.

On the other hand, in FIG. 1, the hydraulic oil passage formed in the body 1 is such that the lower portion of the supply passage 11 formed vertically in the inner circumference of the suction connector 10 is arranged substantially horizontally in the figure. It communicates with the supply communication passage 12 that opens to the end face 1A, and the right end of this supply communication passage 12 has a flow rate adjusting valve 5
End face 1A in communication with the bypass side that discharges the excess flow rate of
The hydraulic oil flows into the inner circumference of the cover 2 from the supply communication passage 12 that is open to the inside.

Then, as shown in FIG. 3, the end surface 1A is
A pair of suction ports 14, 14 are formed as grooves having a predetermined depth on the horizontal diameter across the drive shaft 9.

The bifurcated recessed groove passage portions 12A and 12B for connecting the suction port 14 and the supply communication passage 12 are shown in FIG.
As shown in FIG. 3, the suction port 14 is formed in a groove shape with a predetermined depth so as to connect the intake port 14 with the supply communication passage 12 that is open to the end face 1A in the upper semicircular outer peripheral portion along the outer periphery of the cam ring 8. The concave groove passage portions 12A and 12B form an integrated groove portion. Here, “upper” means the supply communication passage 12 side than the diameter in the horizontal direction passing through the axis of the drive shaft 9 in FIG. 3, and “side” means also in FIG.
The left and right directions on the horizontal diameter passing through the axis of the drive shaft 9 are shown, and the same applies hereinafter.

The concave groove passage portions 12A and 12B and the suction ports 14 and 14 form a gap between the end surface of the cam ring 8 and the end surface 1A of the body 1 which are in contact with each other, and the supply communication passage 12 opened to the end surface 1A. From one side to the side of the pump cartridge 3 to form one low-pressure distribution path for supplying hydraulic oil to the suction ports 14 and 14 via the bifurcated concave groove paths 12A and 12B.

The discharge area of the cam ring 8 is a predetermined position determined by the rotation direction of the rotor 6 and the enclosed space formed by housing the rotor 6 on the inner circumference of the cam surface of the cam ring 8, and FIGS. As shown in FIG. 2, a pair of discharge ports 1 opened vertically in the figure at the end faces of the body 1 sandwiching the drive shaft 9 therebetween.
5, 15 communicate with each other at opposite positions, and these discharge ports 15,
15 communicates with each other through an annular communication passage 19 formed inside the body 1, and also communicates with the flow rate adjusting valve 5 through the discharge passage 13, so that the pressure oil whose excess flow rate is adjusted by the flow rate adjusting valve 5 is It is pressure-fed to the outside from the discharge port 5A shown in FIG.

An annular back pressure introducing groove 31 is formed at a predetermined position on the end face 1 of the body 1 corresponding to the base end of the vane 7 in the rotor 6, and a back pressure introducing hole of the side plate 4 described later is formed. Back pressure to the base end of the vane 7 is introduced via 44.

Here, as shown in FIGS. 1, 5 and 6, the cover 2 has a concave shape capable of forming a gap, which will be described later, between the outer periphery of the pump cartridge 3 and the side plate 4 accommodated therein. Is formed, and the peripheral edge portion of the opening end face is fastened to the end face on the body 1 side via a seal 26.

A cylindrical boss portion 23 for pivotally supporting the drive shaft 9 penetrating the pump cartridge 3 is provided at a substantially central portion of an inner peripheral bottom portion of the cover 2 facing the end portion of the drive shaft 9.
Projecting in the axial direction toward the side (axial direction of the drive shaft 9),
A bearing metal 27 is provided on the inner circumference of the boss portion 23.

At the bottom of the cover 2 on the outer periphery of the boss portion 23, a bottom surface 28 is formed as a plane orthogonal to the drive shaft 9 and contacts the end surface 40A of the side plate 4.

On the inner circumference of the cover 2 adjacent to the bottom surface 28,
An annular engagement surface 22 that engages with the outer periphery of the side plate 4 is formed in the axial direction and fits to approximately half the thickness of the side plate 4, and between the bottom surface 28 and the boss portion 23 the side plate 4 is provided. The recess 21 having a predetermined depth is formed in an annular shape so as to form the oil chamber 40 between the end surface 40A and the end surface 40A.

The cover 2 has a predetermined inner diameter,
As shown in FIGS. 1 and 5, a predetermined gap is formed between the outer circumference of the cam ring 8 and the side plate 4 and the inner circumference of the cover 2 to define a suction passage 20. Communicating with the supply communication passage 12 opened to the end face 1A,
A low-pressure flow path that surrounds the upper semicircular outer peripheral surfaces of the cam ring 8 and the side plate 4 is formed.

On the other hand, the cam ring 8 and the side plate 4
The lower outer peripheral surface on the side opposite to the gap is abutted and supported by the inner peripheral surface of the cover 2 at a substantially semicircular lower outer peripheral surface portion.

The side plate 4 interposed between the cover 2 and the pump cartridge 3 is constructed as shown in FIGS.

In FIG. 7, the side plate 4 is provided with a through hole for inserting the drive shaft 9 in the central portion thereof so that the inner periphery is fitted to the outer periphery of the boss portion 23 of the cover 2, and as described above. , The outer periphery is fitted to the engaging surface 22 of the cover 2.

The side of the side plate 4 facing the cover 2 is the end surface 40A, and the side of the side plate 4 contacting the cam ring 8 is the end surface 40B.
As shown in FIG. 1, a step portion 40C is formed in an annular shape on the outer circumference of the end surface 40A that abuts the bottom surface 28 of the cover 2.
The seal 25 is housed between the cover 2 and the end face 40.
A seal 24 is interposed between the inner circumference of A and the outer circumference of the boss portion 23, and an oil chamber 40 is defined between the end surface 40A and the recess 21 of the cover 2, and the oil chamber 40 Is a seal 2
It is sealed by 4, 25.

The side plate 4 is provided with engaging holes 45, 45 at predetermined positions on the outer circumference, engages with the dowel pins 18, 18 penetrating the cam ring 8, and is coupled with the cam ring 8 and the body 1 at a predetermined phase. .

An end surface 40B is provided at a position facing the discharge ports 15, 15 formed on the end surface 1A of the body 1.
And the end surface 1A are communicated with the pressure communication holes 41, 41 so that the discharge port of the pump and the oil chamber 40 communicate with each other.

Further, an annular back pressure introducing groove 42 is formed in a predetermined depth on the inner peripheral side (drive shaft 9 side) of the pressure communicating hole 41 at a position facing the back pressure introducing groove 31 of the body 1. At a predetermined position of the back pressure introducing groove 42, back pressure introducing holes 44, 44 communicating with the oil chamber 40 are formed through the side plate 4, so that the oil pressure of the oil chamber 40 is applied to the base end of the vane 7. Introduced as pressure.

An end surface 40B of the side plate 4 facing the suction ports 14, 14 formed on the end surface 1A of the body 1.
As shown in FIGS. 7A, 7B, and 8, suction recesses 43L and 43R are formed with a predetermined depth as steps from the outer circumference to the inner circumferential surface of the cam surface in the suction area of the cam ring 8. The suction recesses 43L and 43R as the opposed suction ports are opened at the outer circumference of the side plate 4 with a gap formed between the contact surface with the cam ring 8 and the inner circumference of the cam surface.

These suction recesses 43L and 43R are shown in FIG.
9 are arranged symmetrically on the horizontal diameter and open on the outer peripheral sides of the side plates 4 that sandwich the drive shaft 9, respectively. The shape of the cam ring 8 and the shape of the hydraulic oil inflow passage and the vane rotation direction are shown. In consideration of the above, the suction recesses 43L and 43R are formed in different shapes so that the suction characteristics of the vane pump are optimized.

The contact surface between the cam ring 8 and the side plate 4 is, as shown by the diagonal lines in FIG. 8, a side surface of the side plate 4 facing the suction region of the cam ring 8, that is, a substantially horizontal direction with the drive shaft 9 interposed therebetween. Pair of suction recesses 4 arranged in the
The upper contact surface 30A and the lower contact surface 3 are separated by 3L and 43R.
0B, the upper semicircular outer peripheral portion of the cam ring 8 on the lower contact surface 30B side and the outer periphery of the side plate 4 are contacted and supported by the inner circumference of the cover 2, while the upper contact surface 3
The upper semicircular outer peripheral portions of the side plate 4 and the cam ring 8 corresponding to 0A form a predetermined gap 20 with the cover 2, and suction and 43L, 43R as shown in FIG. Bifurcated passage 20 towards
A and 20B are formed. Since the lower semicircular outer circumference of the cam ring 8 and the side plate 4 contacts the inner circumference of the cover 2, the inner diameter of the lower semicircular portion of the cover 2 in FIGS. 8 and 9 is substantially equal to the outer diameter of the side plate 4 or the cam ring 8. It can be set, and the passage of hydraulic oil is secured while reducing the outer diameter of the cover 2.

In FIGS. 8 and 9, the opening edge 4 of the suction recesses 43L and 43R of the side plate 4 on the bifurcated passage side.
In 3A and 43B, the taper portion 46 as an introduction passage portion for facilitating the inflow of the low pressure hydraulic oil from the forked passages 20A20B in accordance with the rotation directions of the rotor 6 and the vane 7.
U and 46L are formed respectively. Note that these tapered portions may have any cross-sectional shape.

These taper portions 46U, 46L, 47 form groove-like passage portions 46A as shown in FIGS. 10 and 11 on the outer circumference of the contact surface between the side plate 4 and the cam ring 8.
47A is formed, and the low-pressure hydraulic oil in the suction passage 20 formed between the inner circumference of the cover 2 and the inner circumference of the cover 2 is sucked after branching in the circumferential direction of the side plate 4 from above as shown in FIG. At this time, the suction passage 20 is sucked into the recesses 43L, 43R. At this time, the suction passage 20 branches from the upper part in the drawing into bifurcated passages 20A, 20B that wrap around in the circumferential direction of the side plate 4, and in these passages 20A, 20B the side plate 4 and the cam ring. And passage portions 46A, 47A formed between
The cross-sectional area of the flow channel is enlarged by.

Here, the difference between the shapes of the suction concave portions 43L and 43R is that, as shown in FIG. 8, the suction concave portions 43L and 43R are each formed as a step portion from the outer circumference toward the radial center to a predetermined distance W. However, the suction concave portion 43L includes a tapered portion 47 that rises from the opening end 43A toward the upper outer periphery at an angle α in the figure, whereas the suction concave portion 43R includes
As a tapered portion 46L inclined from the opening end 43A toward the outer periphery at a predetermined angle β, and as an introduction passage portion extending from the opening end 43B along the outer periphery of the side plate 4 to a predetermined position in the rotation direction of the vane rotor. Taper part 46U
Is provided. It should be noted that the angles α and β are angles formed by the horizontal plane passing through the axis and the tapered portion in the radial direction, and the shapes of the suction recesses 43L and 43R are set according to the shape of the cam surface of the cam ring 8.

The configuration is as described above. Next, the operation will be described.

When the rotor 6 of the pump cartridge 3 is driven by the rotation of the drive shaft 9, the working oil in the supply passage 11 of the suction connector 10 and the surplus working oil from the flow rate adjusting valve 5 are supplied to the supply communication passage 12. Through a suction passage 20 as a low-pressure passage defined inside the case 2.

The hydraulic oil flowing into the suction passage 20 has bifurcated concave groove passage portions 12A, 12B formed in groove shapes on the end surface 1A of the body 1, the outer periphery of the cam ring 8 and the outer periphery of the cover 2 and the side plate 4, respectively. It flows into the suction ports 14, 14 and the suction recesses 43L, 43R via the passages 20A, 20B.

The cam ring 8 sandwiched between the body 1 and the side plate 4 has two sets of suction ports 14 and 14 and suction recesses 43L and 43R formed on the end surface 1A of the body 1 and the end surface 40B of the side plate 4, respectively. Hydraulic oil from the cam ring 8 to the suction area on the inner periphery of the cam ring 8,
In FIG. 1, the hydraulic oil can be sucked substantially uniformly from both end surfaces (left and right direction in the drawing) of the cam ring 8 and from the left and right on the horizontal diameter in FIGS. 3 and 9.

As shown in FIG. 12, the low-pressure hydraulic oil supplied to the suction passage 20 passes downward from the upper portion of the suction passage 20 through the bifurcated passages 20A, 20B, 12A, 12B from inside the cover 2. Flows toward the outer peripheral side of the cam ring 8 and then flows into the inner peripheral surface of the cam surface of the cam ring 8 in a direction substantially parallel to the axis, so that the cam ring 8 operates almost uniformly from the front and rear in the axial direction. Along with sucking the oil, the suction recesses 43L and 43R, which have different shapes and are arranged axially symmetrically in accordance with the rotation direction of the rotor 6, can suck the working oil substantially evenly from the left and right sides of the outer circumference. It is possible to improve the suction efficiency by making the contents uniform by being influenced by the rotation direction of the rotor 6.

At this time, in the present embodiment, the suction passage 20 formed so as to surround the side plate 4 and the cam ring 8 above and to the side is branched into the passages 20A and 20B formed by the bifurcated gap, and the side plate 4 Since low-pressure hydraulic oil is supplied to the suction side of the vane 7 from the suction recesses 43L and 43R that are open to the side, it is not necessary to form a balance oil passage inside the cam ring 8 as in the conventional example, It is possible to suppress the unevenness of the strength of the cam ring 8 and to secure the strength while reducing the wall thickness of the cam ring 8, and it is possible to reduce the outer diameter of the cam ring 8 by reducing the wall thickness. The vane pump can be made smaller and lighter.

Further, it is not necessary to form the bent hollow low pressure passage inside the cover 2 as in the conventional example, and the size in the axial direction can be reduced to promote the downsizing of the vane pump. Also, since the cover 2 is molded by casting, since there is no bent oil passage, a core is not required, which simplifies the molding process and promotes a reduction in manufacturing cost. It is possible to select a processing method according to the constituent material such as press, injection, etc., and to reduce the manufacturing cost by simplifying the molding process.

Here, in FIG. 9, the side plate 4
The suction recesses 43L and 43R formed on the outer surface of the side plate 4 open toward the outer peripheral side, but the lower semicircular outer peripheral portion of the side plate 4 bordering the opening position of the suction recesses 43L and 43R contacts the inner periphery of the cover 2. Since they are in contact with each other, the inner diameter of the case 2 in the radial direction can be set equal to the outer diameter of the side plate 4 or the cam ring 8 to reduce the size and weight, while
Since the bifurcated passages 20A and 20B are formed along the outer periphery of the upper semicircle of the side plate 4 as the gaps communicating with the suction recesses 43L and 43R, the suction efficiency is maintained by securing the low pressure passage area on the suction side of the vane pump. Then
It is a small but highly efficient vane pump.

The intake passage 43R has a branched passage 2
By providing the taper portion 46U for securing the introduction area of the low-pressure hydraulic oil along the rotation direction of the rotor 6 facing 0B, the flow passage cross-sectional area can be expanded, and the vane pump rotor 6 rotation direction can be increased. Accordingly, the suction resistance of the low-pressure hydraulic oil can be reduced, and the suction recess 4 on the opposite side can be reduced.
With respect to 3L, it is possible to eliminate the difference in the introduction effect due to the rotation direction of the hydraulic oil and obtain a suction action with a good left-right balance.

On the other hand, the hydraulic oil pressure-fed from the discharge port 15 passes through the communication passage 19 inside the body 1 and the flow rate adjusting valve 5
And only the required flow rate is supplied from the discharge port 5A,
The surplus flow rate is returned to the supply communication passage 12.

The discharge pressure of the pump cartridge 3 is guided to the oil chamber 40 through the pressure communication hole 41, the side plate 4 is urged toward the body 1 according to the oil pressure applied to the oil chamber 40, and the cam ring 8 is Pressed by the end surface 1A of the body 1,
The gap between the vane 7 and the rotor 6 and the end surface 1A and the end surface 40B of the guide plate 4 can be maintained at a predetermined value to maintain smooth rotation while reducing the leakage of hydraulic oil.

At this time, the cover 2 moves from the oil chamber 40 to the recess 2
Any material can be used as long as it can support the discharge pressure applied to 1, and the material is not limited to a metal material, and can be made of resin or the like, and it is possible to reduce the manufacturing cost while promoting further weight reduction. it can.

[0059]

As described above, according to the present invention, since the hydraulic oil in the suction passage is sucked substantially evenly from both end surfaces of the cartridge along the drive shaft, the suction efficiency can be ensured. The hydraulic oil to both end faces of the cartridge is carried out through a bifurcated suction passage formed by the gap formed on the outer circumference of the cam ring and the side plate, so that the cam ring itself or the cam ring is sandwiched between the suction port and the suction recess. Since it is not necessary to form a hydraulic oil passage for communication, the size and weight of the pump can be reduced, and the strength of the cam ring can be easily ensured.
Since the suction recess of the plate member is formed as a step,
Any molding method can be adopted without being limited to casting using a core. Moreover, since the play passage and the cam ring side end surface of the member are formed with the introduction passage portion for facilitating the flow of the hydraulic oil from the bifurcated suction passage due to the outer peripheral gap to the suction concave portion of the plate member, the suction characteristic of the low pressure oil is formed. Will not hurt.

Further, in the second invention, the shape of the introduction passage portion with respect to the suction concave portion symmetrically arranged in the plate member is such that one is extended along the rotation direction of the rotor and the other is formed in the rotation direction. Due to the different shapes that extend in the opposite direction, it is possible to increase the passage area on the suction side of the pump cartridge and at the same time make the suction characteristics of the pump uniform due to the rotation direction of the vane rotor. It is possible to provide a vane pump that is lightweight and highly efficient.

Further, according to the third aspect of the invention, since the introduction passage portion of the plate member is formed by the tapered chamfered portion provided on the end surface of the plate member, the plate member is ensured for each passage area on the suction side. It is possible to improve the suction efficiency and reduce the size and weight without impairing the strength.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a vane pump showing an embodiment of the present invention.

FIG. 2 is a view taken along the line C-C of FIG.

FIG. 3 is a view taken along the line AA of FIG.

FIG. 4 is a sectional view taken along the line BB of FIG.

FIG. 5 is a sectional view of the cover.

FIG. 6 is a front view of the same cover.

7A and 7B also show side plates, FIG. 7A is a side view on the pump cartridge side, FIG. 7B is a sectional view taken along the line EE of FIG. 7A, and FIG.

8 is a cross-sectional view taken along the line DD of FIG.

9 is a cross-sectional view taken along the line EE of FIG.

10 is a sectional view taken along arrow G in FIG.

11 is a cross-sectional view taken along arrow H in FIG.

FIG. 12 is a conceptual diagram showing an intake passage.

FIG. 13 is a cross-sectional view of a conventional vane pump.

14 is a sectional view taken along line JJ of FIG.

15 is a sectional view taken along line KK of FIG.

[Explanation of symbols]

 1 Body 2 Cover 3 Pump Cartridge 4 Side Plate 6 Rotor 7 Vane 8 Cam Ring 11 Supply Passage 12 Supply Communication Passage 13 Discharge Passage 14 Suction Port 15 Discharge Port 20 Suction Passage 20A, 20B Gap Passage 28 Bottom 40 Oil Chamber 40A End Face 40B End Face 43L , 43R Suction recesses 46U, 46L, 47 Tapered parts 46A, 47A Groove-shaped passage parts

Claims (3)

[Claims] 1. A cam ring rotatably accommodating a rotor coupled to a drive shaft, and a vane provided in and out of the rotor, and pivotally supporting the drive shaft to abut one end surface of the cam ring. The end face is provided with a suction port corresponding to the suction region of the cam ring and a discharge port corresponding to the discharge region, respectively, and the suction port is provided at the end face portion corresponding to the upper semicircular outer periphery of the cam ring outer periphery. A first body in which a low pressure distribution groove portion bifurcated toward the side is provided, a plate member arranged to hold the cam ring in cooperation with the first body, and the rotor, the cam ring and the plate. The member is housed inside, and has an opening end face peripheral portion that engages with the first body and a bottom portion that engages with the end face of the plate member. And a second body that surrounds the outer periphery of the plate member and abuts the lower semicircular outer peripheral surface of the plate member while forming a predetermined bifurcated gap between the plate body and the upper semicircular outer peripheral surface. 1 a suction communication passage formed at the top of the low pressure distribution groove portion on the end face of the body, and a suction port formed on the end face of the cam ring side of the plate member at a predetermined position so as to communicate with the gap. The suction recess is formed so as to face each other, and the discharge recess is formed so as to face the discharge port of the first body end surface. Further, the cam ring side end surface of the plate member operates from the gap to the suction recess. A vane pump characterized in that an introduction passage portion for guiding oil is additionally formed. 2. The shape of the introduction passage with respect to the suction concave portion symmetrically arranged in the plate member is such that one of the introduction passages extends along the rotation direction of the rotor and the other extends in the direction opposite to the rotation direction. The vane pump according to claim 1, wherein the vane pump is formed. 3. The vane pump according to claim 2, wherein the introduction passage portion of the plate member is formed by a tapered chamfered portion provided on an end surface of the plate member.