Patent Description:
<CIT> discloses a cartridge vane pump that is configured so as to be attachable and detachable to/from a main body portion to be fixed to a base, a frame, and so forth.

<CIT> discloses a variable displacement pump. This pump comprises a rotor on a driving shaft; a plurality of vanes at the rotor; a cam ring having an inner circumference cam face with which the plurality of vanes are brought into sliding contact; a housing body in which the rotor is arranged; a cover member brought into contact with end surfaces of the rotor and the cam ring, the cover member that is attached to the body; and an O-ring. The pump further comprises a side plate. The O-ring is interposed between the outer peripheral corner portion of the side plate housed in a accommodating space of the body, and a bottom surface of the body.

<CIT> discloses a vane pump. This vane pump comprises a rotor on a driving shaft; a plurality of vanes at the rotor; a cam ring having an inner circumference cam face facing the plurality of vanes; a housing body in which the rotor is arranged; a cover member brought into contact with end surfaces of the rotor and the cam ring, the cover member being attached to the body (<NUM>); and two sealing rings. In one example, a lid member is set on the outer surface of the cover member.

<CIT> discloses a vane pump having a rotor connected to a drive shaft (<NUM>), vanes provided at the rotor, and a cam ring. The vane pump further has a control plate at a bottom side from the rotor and the cam ring.

With such a cartridge vane pump as in <CIT>, it is required to bring a side plate, which is provided between a cam ring and a body accommodating the cartridge vane pump, into close contact with the cam ring, thereby preventing leakage of working oil from between the cam ring and the side plate. In order to achieve the above-mentioned object, it is considered to provide a spring between the body and the side plate such that the side plate is biased towards the cam ring.

However, with such a configuration, there is a risk in that the size of the cartridge vane pump and the pump device is increased due to the presence of the spring. In addition, in this case, assembly is performed by arranging the spring in the body, and thereafter, arranging the cartridge vane pump in the body. Therefore, there is a risk in that assemblability of the cartridge vane pump is deteriorated.

An object of the present invention is to, while reducing the size, improve the assemblability of a cartridge vane pump and a pump device including the same.

According to one aspect of the present invention, a cartridge vane pump configured to be accommodated in a body in an attachable and detachable manner, the cartridge vane pump includes a rotor linked to a driving shaft, the rotor being configured to be rotationally driven; a plurality of vanes provided in the rotor so as to be able to reciprocate in a radial direction of the rotor; a cam ring having an inner circumference cam face with which the plurality of vanes are brought into sliding contact; a plurality of pump chambers defined in the cam ring by an outer circumferential surface of the rotor, the inner circumference surface of the cam ring, and the adjacent vanes, a side member brought into contact with first end surfaces of the rotor and the cam ring; a cover member brought into contact with second end surfaces of the rotor and the cam ring, the cover member being configured to be attached to the body; and a sealing member provided in an outer circumference of the side member, the sealing member being configured to seal a gap between the outer circumference of the side member and an inner circumference of the body, wherein the side member has: a suction port for guiding the working fluid into the pump chambers, the suction port being formed so as to form cut-out shapes that open at an end surface of the side member facing the cam ring and at an outer circumferential surface of the side member; a first restricting portion configured to restrict movement of the sealing member towards the rotor side; a second restricting portion configured to restrict movement of the sealing member towards an opposite side from the rotor; and an accommodating space defined by the first restricting portion and the second restricting portion, the sealing member being configured to be accommodated in the accommodating space, and wherein the first restricting portion is formed to have an outer diameter larger than an outer diameter of the second restricting portion so as to be able to compress the sealing member with the body in an axial direction of the driving shaft.

A cartridge vane pump (hereinafter, simply referred to as "vane pump") <NUM> according to the embodiment of the present invention and a pump device <NUM> including the same are used as a fluid pressure source for a fluid pressure device mounted on a vehicle, such as, for example, a power steering apparatus, a transmission, and so forth. In the following, an explanation will be given of the vane pump <NUM> that uses working oil as working fluid. The working fluid is not limited to the working oil, and other working fluid may also be used.

As shown in <FIG>, the pump device <NUM> includes the vane pump <NUM> and a body <NUM> in which an accommodating concave portion <NUM> for accommodating the vane pump <NUM> is formed. The body <NUM> of the pump device <NUM> is used as a body of the fluid pressure device in a shared manner.

In an assembled state (a state shown in <FIG>), the vane pump <NUM> is accommodated in the accommodating concave portion <NUM> formed in the body <NUM> in an attachable and detachable manner. A motive force from an engine (not shown) is transmitted to an end portion of a driving shaft <NUM>, and a rotor <NUM> linked to the driving shaft <NUM> is rotated.

As shown in <FIG> and <FIG>, the vane pump <NUM> is provided with the rotor <NUM> that is rotationally driven by being linked to the driving shaft <NUM>, a plurality of slits 2a that are formed in a radiating pattern so as to open at an outer circumference of the rotor <NUM>, a plurality of vanes <NUM> that are respectively inserted into the slits 2a in a freely slidable manner so as to be capable of reciprocating in the radial direction of the rotor <NUM>, and a cam ring <NUM> that accommodates the rotor <NUM> and that has an inner circumference cam face 4a on which tip end portions of the vanes <NUM> slide by rotation of the rotor <NUM>.

As shown in <FIG>, at the base-end side of the slits 2a, back pressure chambers <NUM> into which discharge pressure from the vane pump <NUM> is guided are defined. The vanes <NUM> are pushed by the pressure in the back pressure chambers <NUM> in the directions in which the vanes <NUM> are drawn out from the slits 2a, and the tip end portions of the vanes <NUM> are brought into contact with the inner circumference cam face 4a of the cam ring <NUM>. With such a configuration, a plurality of pump chambers <NUM> are defined in the cam ring <NUM> by an outer circumferential surface of the rotor <NUM>, the inner circumference cam face 4a of the cam ring <NUM>, and the adjacent vanes <NUM>.

The cam ring <NUM> is an annular member whose inner circumference cam face 4a has a substantially oval shape, and the cam ring <NUM> has suction regions 4b at which the volumes of the pump chambers <NUM> are expanded as the rotor <NUM> is rotated and discharge regions 4c at which the volumes of the pump chambers <NUM> are contracted as the rotor <NUM> is rotated. The respective pump chambers <NUM> are expanded/contracted by the rotation of the rotor <NUM>. The vane pump <NUM> is a so-called balanced vane pump in which the cam ring <NUM> has two suction regions 4b and two discharge regions 4c. In both end surfaces of the cam ring <NUM>, cut-out portions 4d are formed at the positions corresponding to the two suction regions 4b such that an outside and an inside of the cam ring <NUM> are communicated therethrough.

As shown in <FIG>, the vane pump <NUM> is further provided with a cover (cover member) <NUM> that is brought into contact with first end surfaces of the rotor <NUM> and the cam ring <NUM> (on the upper side in <FIG>) so as to be attached to the body <NUM> to close the accommodating concave portion <NUM> and a side plate <NUM> serving as a side member that is brought into contact with second end surfaces of the rotor <NUM> and the cam ring <NUM> (the lower side in <FIG>). In this embodiment, the cover member is formed of a single cover <NUM>. The configuration is not limited thereto; a cover-side plate, which is brought into contact with the first end surfaces of the rotor <NUM> and the cam ring <NUM>, may be provided between the cover <NUM> and each of rotor <NUM> and the cam ring <NUM>, and the cover member may be formed of the cover <NUM> and the cover-side plate.

The cover <NUM> and the side plate <NUM> are arranged such that the rotor <NUM> and the cam ring <NUM> are held therebetween. Because both end surfaces of the rotor <NUM> and the cam ring <NUM> are held between the cover <NUM> and the side plate <NUM>, the pump chambers <NUM> are sealed.

As shown in <FIG> and <FIG>, the cover <NUM> has a closing portion <NUM> that is brought into contact with an end surface of the body <NUM> and that closes an opening of the accommodating concave portion <NUM>, an inserted portion <NUM> that is formed so as to protrude from the closing portion <NUM> and that is inserted into the accommodating concave portion <NUM>, a contacting portion <NUM> that is formed so as to protrude from the inserted portion <NUM> and that is brought into contact with the cam ring <NUM>, suction ports 10a (see <FIG>) that are formed such that parts of an outer edge portion of the contacting portion <NUM> are cut away for guiding the working oil into the pump chambers <NUM>, and a through hole 10b into which the driving shaft <NUM> is inserted.

The suction ports 10a are respectively formed at positions corresponding to the two suction regions 4b. The respective suction ports 10a are formed to have an arc shape centered at the through hole 10b.

The through hole 10b is formed coaxially with the rotation center axis of the rotor <NUM>. The driving shaft <NUM> is rotatably supported by the cover <NUM> via a bearing (not shown).

As shown in <FIG>, in the side plate <NUM>, discharge ports 20a are formed so as to penetrate the side plate <NUM> in the axial direction such that the pump chambers <NUM>(see <FIG>) are communicated with a high-pressure chamber <NUM>, which will be described below. The discharge ports 20a are formed at positions corresponding to the two discharge regions 4c. As the rotor <NUM> is rotated, the working oil in the pump chambers <NUM> is discharged from the discharge ports 20a.

In addition, also in the side plate <NUM>, suction ports 20b for guiding the working oil into the pump chambers <NUM> are formed at positions corresponding to the two suction regions 4b (see <FIG>). The suction ports 20b are formed so as to form cut-out shapes that open at an end surface of the side plate <NUM> facing the cam ring <NUM> and at an outer circumferential surface 20c.

As shown in <FIG> and <FIG>, an outer circumference of the side plate <NUM> is provided with an O-ring <NUM> serving as a sealing member for sealing a gap between the outer circumference of the side plate <NUM> and an inner circumference of the accommodating concave portion <NUM> formed in the body <NUM>.

In addition, the side plate <NUM> has a first flange portion <NUM> that is formed so as to protrude radially outward from the outer circumferential surface 20c, a second flange portion <NUM> that is formed so as to protrude radially outward from the outer circumferential surface 20c (see <FIG>), and an accommodating space <NUM> that is defined by the first flange portion <NUM> and the second flange portion <NUM> so as to accommodate the O-ring <NUM>. The first flange portion <NUM> serves as a first restricting portion that restricts movement of the O-ring <NUM> to the rotor <NUM> side (the upper side in <FIG>), and the second flange portion <NUM> serves as a second restricting portion that restricts movement of the O-ring <NUM> to the opposite side from the rotor <NUM> (the lower side in <FIG>). The first flange portion <NUM> is formed to have an outer diameter larger than that of the second flange portion <NUM>.

The second flange portion <NUM> has a tapered guide surface 22a that is formed such that the outer diameter is gradually increased towards the accommodating space <NUM> for guiding insertion of the O-ring <NUM> into the accommodating space <NUM> (see <FIG>). Because the second flange portion <NUM> has the guide surface 22a, it is possible to easily insert the O-ring <NUM> into the accommodating space <NUM> from an end portion of the side plate <NUM> on the opposite side from the cam ring <NUM>. The shape of the guide surface 22a is not limited to the tapered shape, and it may have other shapes such as a curved shape, for example.

As shown in <FIG> and <FIG>, the accommodating concave portion <NUM> has an accommodating main body portion <NUM> that opens at an end surface of the body <NUM>, a first accommodating portion <NUM> that is formed so as to have an inner diameter smaller than that of the accommodating main body portion <NUM> and that accommodates the first flange portion <NUM> of the side plate <NUM>, a second accommodating portion <NUM> that is formed so as to have an inner diameter smaller than that of the first accommodating portion <NUM> and that accommodates the second flange portion <NUM>, and a tapered portion <NUM> that is formed between the first accommodating portion <NUM> and the second accommodating portion <NUM> so as to have a tapered surface that is inclined relative to the driving shaft <NUM>.

The inserted portion <NUM> and the contacting portion <NUM> of the cover <NUM>, the cam ring <NUM>, the rotor <NUM>, and a part of the side plate <NUM> on the rotor <NUM> side are accommodated in the accommodating main body portion <NUM>. A sealing member (not shown) for preventing leakage of the working oil is provided between the accommodating main body portion <NUM> and the inserted portion <NUM> of the cover <NUM>.

An inner circumferential surface of the accommodating main body portion <NUM> faces an outer circumferential surface of the cam ring <NUM> and the outer circumferential surface 20c of the side plate <NUM> with a gap therebetween. An annular low pressure chamber (pressure chamber) <NUM> is formed by the accommodating main body portion <NUM>, the cam ring <NUM>, and the cover <NUM>.

The low pressure chamber <NUM> is communicated with the pump chambers <NUM> through the suction ports 10a and 20b of the cover <NUM> and the side plate <NUM> (see <FIG>), and the low pressure chamber <NUM> is also communicated with a tank (not shown) through a suction passage <NUM> formed in the body <NUM>. When the vane pump <NUM> is operated, the working oil in the tank is sucked into the pump chambers <NUM> through the suction passage <NUM>, the low pressure chamber <NUM>, and the suction ports 10a and 20b.

A bottom surface of the second accommodating portion <NUM> faces the end surface of the side plate <NUM> (the lower surface in <FIG>) with a gap therebetween. The high-pressure chamber <NUM> is formed by the second accommodating portion <NUM> and the side plate <NUM>.

The high-pressure chamber <NUM> is communicated with the pump chambers <NUM> through the discharge ports 20a, and the high-pressure chamber <NUM> is also communicated with a discharge passage 50a formed in the body <NUM>. When the vane pump <NUM> is operated, the working oil in the pump chambers <NUM> is discharged to the discharge passage 50a through the discharge ports 20a and the high-pressure chamber <NUM>.

The high-pressure chamber <NUM> is also communicated with the back pressure chambers <NUM> (see <FIG>), and the working oil in the high-pressure chamber <NUM> is guided to the back pressure chambers <NUM>. Therefore, the vanes <NUM> are biased radially outward not only by the centrifugal force, but also by the pressure in the back pressure chambers <NUM>.

The first flange portion <NUM> of the side plate <NUM> is formed to have substantially the same outer diameter as the inner diameter of the first accommodating portion <NUM> of the accommodating concave portion <NUM>, and the first flange portion <NUM> fits into the first accommodating portion <NUM>. The second flange portion <NUM> is formed to have substantially the same the outer diameter as the inner diameter of the second accommodating portion <NUM> of the accommodating concave portion <NUM>, and the second flange portion <NUM> fits into the second accommodating portion <NUM>.

As described above, the outer diameter of the first flange portion <NUM> is larger than the outer diameter of the second flange portion <NUM>, and the inner diameter of the first accommodating portion <NUM> is larger than the inner diameter of the second accommodating portion <NUM>. There is a difference between the outer diameters of the first flange portion <NUM> and the second flange portion <NUM>, and correspondingly, there is a difference between the inner diameters of the first accommodating portion <NUM> and the second accommodating portion <NUM>. Thus, as shown in <FIG>, in a state in which the cover <NUM> is attached to the body <NUM>, the second accommodating portion <NUM> is formed such that an inner circumference thereof is positioned at the inner side of an outer circumference of the first flange portion <NUM> in the radial direction, and the tapered portion <NUM> faces the first flange portion <NUM> such that the O-ring <NUM> provided in the accommodating space <NUM> is located therebetween. The O-ring <NUM> is provided between the tapered portion <NUM> of the accommodating concave portion <NUM> in the body <NUM> and the first flange portion <NUM> in a compressed state in the axial direction of the driving shaft <NUM>.

With such a configuration, the gap between the side plate <NUM> and the body <NUM> is closed. With the O-ring <NUM>, it is possible to prevent flow of the working oil between the low pressure chamber <NUM> and the high-pressure chamber <NUM> through this gap.

In addition, because the O-ring <NUM> is compressed by the tapered portion <NUM> of the accommodating concave portion <NUM> between the tapered portion <NUM> and the first flange portion <NUM> of the side plate <NUM> in the axial direction, the side plate <NUM> is biased upwards in <FIG> and <FIG> towards the rotor <NUM> and the cam ring <NUM> by the reaction force (elastic force). Therefore, the side plate <NUM> is pressed against the cam ring <NUM> by the biasing force exerted by the O-ring <NUM>, and it is possible to prevent leakage of the working oil in the pump chambers <NUM> (see <FIG>) from between the side plate <NUM> and the cam ring <NUM>. Especially, even in a case in which the pressing force exerted to the side plate <NUM> against the cam ring <NUM> by the pressure of the working oil in the high-pressure chamber <NUM> is small soon after the vane pump <NUM> has started, the leakage of the working oil in the pump chambers <NUM> can be prevented by the biasing force exerted by the O-ring <NUM>. Therefore, it is possible to improve a discharge performance of the vane pump <NUM>.

As described above, the O-ring <NUM> not only exhibits a function as the sealing member for sealing the gap between the side plate <NUM> and the body <NUM>, it also functions as a biasing member for pressing the side plate <NUM> against the cam ring <NUM>. Thus, there is no need to provide other biasing members, such as a spring, etc., and so, it is possible to reduce the overall length thereof to reduce the size. In addition, because the number of parts can be reduced, it is possible to reduce the cost.

In addition, because the O-ring <NUM> is compressed by the tapered portion <NUM> having the tapered surface, the O-ring <NUM> is pressed against the side plate <NUM> in the axial direction and also in the radial direction. Therefore, it is possible to seal the gap between the outer circumference of the side plate <NUM> and an inner circumference of the body <NUM> with a higher reliability by biasing the side plate <NUM> towards the cam ring <NUM> by the O-ring <NUM> and by pressing the O-ring <NUM> against the outer circumferential surface 20c of the side plate <NUM>. With such a configuration, it is possible to improve the sealing performance between the side plate <NUM> and the body <NUM>. By adjusting the taper angle of the tapered portion <NUM>, it is possible to adjust a balance between the pressing force exerted by the O-ring <NUM> against the first flange portion <NUM> (in other words, the biasing force exerted to the side plate <NUM> towards the cam ring <NUM>) and the pressing force exerted to the O-ring <NUM> against the outer circumferential surface 20c of the side plate <NUM> (in other words, the sealing performance between the side plate <NUM> and the body <NUM>).

Next, a method of assembling the vane pump <NUM> and the pump device <NUM> will be described.

Dowel pins <NUM> are first press-fitted into the cover <NUM> (see <FIG> and <FIG>). After the dowel pins <NUM> are inserted into the cam ring <NUM>, the dowel pins <NUM> are also inserted into the side plate <NUM>. By doing so, a state in which the cover <NUM>, the cam ring <NUM>, are the side plate <NUM> are stacked is achieved. Here, the driving shaft <NUM>, the rotor <NUM>, and the vanes <NUM> are assembled inside the cam ring <NUM> when the cam ring <NUM> is to be inserted. As described above, the dowel pins <NUM> penetrate through the cam ring <NUM>, and both ends thereof are supported by the cover <NUM> and the side plate <NUM>, and thereby, relative rotation of the cover <NUM> and the side plate <NUM> with respect to the cam ring <NUM> is prevented. In other words, the dowel pins <NUM> not only function as positioning parts for these members during the assembly, but also function as rotation stoppers for preventing the relative rotation of the cover <NUM> and the side plate <NUM> with respect to the cam ring <NUM> after the assembly.

Next, two head pins <NUM> serving as linking members are inserted into the cover <NUM>, the cam ring <NUM>, and the side plate <NUM> that have been stacked in this order, and thereby, these members are integrally held by the head pins <NUM>. Specifically, tip ends 32a of the head pins <NUM> are press-fitted into the side plate <NUM>. By doing so, the cover <NUM>, the cam ring <NUM>, and the side plate <NUM> are integrated by the head pins <NUM>. In <FIG>, for the sake of convenience of description, single dowel pin <NUM> and single head pin <NUM> are illustrated in the same plane. In addition, the head pins <NUM> are not limited to those press-fitted into the side plate <NUM>. For example, the tip ends 32a may be threaded, and the cover <NUM>, the cam ring <NUM>, and the side plate <NUM> may be integrated by screwing the head pins <NUM> into the side plate <NUM>.

Next, the O-ring <NUM> is accommodated into the accommodating space <NUM> from the end portion of the side plate <NUM>. At this time, the insertion of the O-ring <NUM> into the accommodating space <NUM> is guided by the guide surface 22a of the side plate <NUM>. Thus, it is possible to attach the O-ring <NUM> to the side plate <NUM> with ease. The O-ring <NUM> accommodated in the accommodating space <NUM> is prevented from being dismounted by the second flange portion <NUM>. Thus, the O-ring <NUM> is held integrally to the side plate <NUM>. As described above, the vane pump <NUM> is assembled.

Next, the vane pump <NUM> that has been assembled as described above is accommodated in the accommodating concave portion <NUM> of the body <NUM>. At this time, the vane pump <NUM> is accommodated such that the second flange portion <NUM> of the side plate <NUM> is fitted to the second accommodating portion <NUM> of the accommodating concave portion <NUM> and such that the first flange portion <NUM> is fitted to the first accommodating portion <NUM>. The O-ring <NUM> is then compressed in the axial direction by the first flange portion <NUM> of the side plate <NUM> and the tapered portion <NUM> of the accommodating concave portion <NUM> in the body <NUM>. In this state, the cover <NUM> is fixed to the body <NUM> with bolts (not shown). By doing so, the side plate <NUM> is pressed against the cam ring <NUM> by the biasing force exerted by the O-ring <NUM>.

As described above, with the cartridge vane pump <NUM>, even in a case in which only the cover <NUM> is lifted up in a state in which the cover <NUM> is not attached to the body <NUM>, separation of the rotor <NUM>, the vanes <NUM>, the cam ring <NUM>, and the side plate <NUM> from the cover <NUM> is prevented, and they are configured in the integrated state. Therefore, it is possible to attach the vane pump <NUM> to the body <NUM> by moving the respective members in the integrated state at once, and thereby, it is possible to improve the assemblability of the vane pump <NUM>.

Even when the vane pump <NUM> is to be detached from the body <NUM>, only by moving the cover <NUM> away from the body <NUM>, it is possible to take out the rotor <NUM>, the vanes <NUM>, the cam ring <NUM>, and the side plate <NUM> from the accommodating concave portion <NUM>. Therefore, it is possible to detach the vane pump <NUM> from the body <NUM> with ease.

In a case in which the side plate is to be pressed against the cam ring by other biasing members such as the spring, etc. in the cartridge vane pump, in which respective members are integrated, the spring is accommodated in an accommodating concave portion first, the vane pump is then accommodated in the accommodating concave portion, and thereby, the vane pump is assembled to the body. In such a case, because assembly steps such as alignment of the body and the vane pump with the spring is required, for example, the number of the assembly steps is increased, and the assemblability of the vane pump is deteriorated.

In contrast, in this embodiment, the movement of the O-ring <NUM>, which is provided in the accommodating space <NUM> of the side plate <NUM> and that biases the side plate <NUM>, towards the opposite side from the rotor <NUM> is restricted by the second flange portion <NUM>, and thereby, the O-ring <NUM> is prevented from being dismounted from the accommodating space <NUM>. Thus, it is possible to insert the entire vane pump <NUM> into the accommodating concave portion <NUM> in a state in which the O-ring <NUM> is accommodated in the accommodating space <NUM> and the O-ring <NUM> is integrated with the vane pump <NUM>. As described above, with the vane pump <NUM>, because the O-ring <NUM> is integrated by being held on the side plate <NUM>, attachment to the body <NUM> can be performed at once, and so, it is not necessarily to perform alignment, etc. Therefore, it is possible to press the side plate <NUM> against the cam ring <NUM> by the O-ring <NUM> while improving the assemblability.

Next, a modification of this embodiment will be described.

In the above-mentioned embodiment, the first restricting portion is the first flange portion <NUM> that protrudes radially outward from the outer circumferential surface 20c of the side plate <NUM>, and the second restricting portion is the second flange portion <NUM> that protrudes radially outward from the outer circumferential surface 20c of the side plate <NUM>. However, the configuration is not limited thereto; the O-ring <NUM> may be compressed in the axial direction between the first restricting portion and the body <NUM>, and the second restricting portion may take any shape so long as the compression of the O-ring <NUM> by the first restricting portion and the body <NUM> is not disturbed and the dismount of the O-ring <NUM> is prevented.

In addition, in the above-mentioned embodiment, a step portion is formed between the first accommodating portion <NUM> and the second accommodating portion <NUM> of the accommodating concave portion <NUM> as the tapered portion <NUM> having a tapered surface. In contrast, as long as the O-ring <NUM> can be compressed by the first flange portion <NUM> and the step portion between the first accommodating portion <NUM> and the second accommodating portion <NUM>, the step portion may be formed to have other shapes than the tapered portion <NUM>, such as, for example, a curved surface, a flat surface perpendicular to the driving shaft <NUM>, and so forth. In addition, the step portion may be formed to have a shape formed by appropriately combining a tapered surface, a curved surface, and a flat surface.

According to the embodiment mentioned above, the advantages described below are afforded.

In the vane pump <NUM>, because the O-ring <NUM> is compressed in the axial direction between the first flange portion <NUM> of the side plate <NUM> and the tapered portion <NUM> of the body <NUM>, the side plate <NUM> is biased towards the rotor <NUM> and the cam ring <NUM> by the reaction force (elastic force). Therefore, the side plate <NUM> is pressed against the cam ring <NUM> by the biasing force exerted by the O-ring <NUM>, and so, it is possible to prevent leakage of the working oil in the pump chambers <NUM> from between the side plate <NUM> and the cam ring <NUM>. Especially, even in a case in which the pressing force exerted to the side plate <NUM> against the cam ring <NUM> by the pressure of the working oil in the high-pressure chamber <NUM> is small, the leakage of the working oil in the pump chambers <NUM> can be prevented by the biasing force exerted by the O-ring <NUM>. Therefore, it is possible to improve the discharge performance of the vane pump <NUM>.

In addition, the O-ring <NUM> is integrally configured with the vane pump <NUM> so as to be prevented from being dismounted from the accommodating space <NUM> by the second flange portion <NUM> of the side plate <NUM>. Therefore, as described above, the O-ring <NUM> not only exhibits a function as the sealing member for sealing the gap between the side plate <NUM> and the body <NUM>, it also functions as the biasing member for pressing the side plate <NUM> against the cam ring <NUM>. Thus, there is no need to provide other biasing members, such as the spring, etc., and so, it is possible to reduce the overall length thereof to reduce the size. In addition, because the number of parts can be reduced, it is possible to reduce the cost.

In addition, in this embodiment, the movement of the O-ring <NUM> towards the opposite side from the rotor <NUM> is restricted by the second flange portion <NUM>, and thereby, the O-ring <NUM> is prevented from being dismounted from the accommodating space <NUM>. Thus, because the vane pump <NUM> can be attached to the body <NUM> in a state in which the O-ring <NUM> is held on the side plate <NUM>, it is possible to press the side plate <NUM> against the cam ring <NUM> by the O-ring <NUM> while improving the assemblability.

In addition, in this embodiment, because the O-ring <NUM> is compressed by the tapered portion <NUM> having the tapered surface, the O-ring <NUM> is pushed in the axial direction such that the side plate <NUM> is pressed against the cam ring <NUM>, and at the same time, the O-ring <NUM> is pushed in the radial direction to the outer circumferential surface 20c of the side plate <NUM>. Thus, it is possible to press the side plate <NUM> against the cam ring <NUM> and to improve the sealing performance between the side plate <NUM> and the body <NUM>.

Configurations, operations, and effects of the embodiment according to the present invention will be collectively described below.

The vane pump <NUM> accommodated in the body <NUM> in an attachable and detachable manner includes: the rotor <NUM> linked to the driving shaft <NUM>, the rotor <NUM> being configured to be rotationally driven; the plurality of vanes <NUM> provided in the rotor <NUM> so as to be able to reciprocate in the radial direction of the rotor <NUM>; the cam ring <NUM> having the inner circumference cam face 4a with which the plurality of vanes <NUM> are brought into sliding contact; the side plate <NUM> brought into contact with the first end surfaces of the rotor <NUM> and the cam ring <NUM>; the cover <NUM> brought into contact with the second end surfaces of the rotor <NUM> and the cam ring <NUM>, the cover <NUM> being attached to the body <NUM>; and the O-ring <NUM> provided in the outer circumference of the side plate <NUM>, the O-ring <NUM> being configured to seal the gap between the outer circumference of the side plate <NUM> and the inner circumference of the body <NUM>, wherein the side plate <NUM> has: the first flange portion <NUM> configured to restrict the movement of the O-ring <NUM> towards the rotor side; the second flange portion <NUM> configured to restrict the movement of the O-ring <NUM> towards the opposite side form the rotor <NUM>; and the accommodating space <NUM> defined by the first flange portion <NUM> and the second flange portion <NUM>, the O-ring <NUM> being configured to be accommodated in the accommodating space <NUM>, and wherein the first flange portion <NUM> is formed to have the outer diameter larger than the outer diameter of the second flange portion <NUM> so as to be able to compress the O-ring <NUM> with the body <NUM> in the axial direction of the driving shaft <NUM>.

With such a configuration, although the second flange portion <NUM> is formed to have the outer diameter smaller than that of the first flange portion <NUM> and a difference in the outer diameter is caused between them, the second flange portion <NUM> restricts the movement of the O-ring <NUM>, which is provided in the outer circumference of the side plate <NUM>, towards the anti-rotor side. Thus, while the dismount of the O-ring <NUM> from the accommodating space <NUM> is prevented, because a part of the body <NUM> (the tapered portion <NUM>) is formed so as to face the first flange portion <NUM> such that the O-ring <NUM> is sandwiched therebetween at the inner side of the outer circumference of the first flange portion <NUM> in the radial direction, it is possible to compress the O-ring <NUM> in the axial direction between the part of the body <NUM> and the first flange portion <NUM>. As the O-ring <NUM> is compressed in the driving shaft direction by the first flange portion <NUM> of the side plate <NUM> and the body <NUM>, the biasing force is exerted to the side plate <NUM> by the O-ring <NUM> in the direction towards the cam ring <NUM>. Thus, the O-ring <NUM> sealing the gap between the side plate <NUM> and the body <NUM> also functions as the biasing member that presses the side plate <NUM> against the cam ring <NUM>, and so, there is no need to separately provide the biasing member, such as the spring, etc. In addition, because the dismount of the O-ring <NUM> is prevented by the second flange portion <NUM>, it is possible to assemble the vane pump <NUM> to the body <NUM> as a unit by keeping the O-ring <NUM> held on the side plate <NUM>. Therefore, the size of the vane pump <NUM> and the pump device <NUM> is reduced, and at the same time, the assemblability is improved.

In addition, in the vane pump <NUM>, the second flange portion <NUM> has the guide surface 22a configured to guide the insertion of the O-ring <NUM> into the accommodating space <NUM>, the guide surface 22a being formed such that the outer diameter is gradually increased towards the accommodating space <NUM>.

With such a configuration, the O-ring <NUM> can be accommodated into the accommodating space <NUM> with ease by being guided by the guide surface 22a.

In addition, the pump device <NUM> includes: the above-described the vane pump <NUM>; and the body <NUM> having the accommodating concave portion <NUM> configured to accommodate the vane pump <NUM>, wherein the accommodating concave portion <NUM> has: the first accommodating portion <NUM> configured to accommodate the first flange portion <NUM>; the second accommodating portion <NUM> formed to have the inner diameter smaller than the inner diameter of the first accommodating portion <NUM>, the second accommodating portion <NUM> being configured to accommodate the second flange portion <NUM>; and the tapered portion <NUM> formed between the first accommodating portion <NUM> and the second accommodating portion <NUM> so as to have the tapered surface inclined with respect to the driving shaft <NUM>, the O-ring <NUM> being configured to be compressed in an axial direction between the tapered portion <NUM> and the first flange portion <NUM>.

Claim 1:
A cartridge vane pump (<NUM>) configured to be accommodated in a body (<NUM>) in an attachable and detachable manner, the cartridge vane pump (<NUM>) comprising:
a rotor (<NUM>) linked to a driving shaft (<NUM>), the rotor (<NUM>) being configured to be rotationally driven;
a plurality of vanes (<NUM>) provided in the rotor (<NUM>) so as to be able to reciprocate in a radial direction of the rotor (<NUM>);
a cam ring (<NUM>) having an inner circumference cam face (4a) with which the plurality of vanes (<NUM>) are brought into sliding contact;
a plurality of pump chambers (<NUM>) defined in the cam ring (<NUM>) by an outer circumferential surface of the rotor (<NUM>), the inner circumference surface (4a) of the cam ring (<NUM>), and the adjacent vanes (<NUM>),
a side member (<NUM>) brought into contact with first end surfaces of the rotor (<NUM>) and the cam ring (<NUM>);
a cover member (<NUM>) brought into contact with second end surfaces of the rotor (<NUM>) and the cam ring (<NUM>), the cover member (<NUM>) being configured to be attached to the body (<NUM>); and
a sealing member (<NUM>) provided in an outer circumference of the side member (<NUM>), the sealing member (<NUM>) being configured to seal a gap between the outer circumference of the side member (<NUM>) and an inner circumference of the body (<NUM>),
a first restricting portion (<NUM>) configured to restrict movement of the sealing member (<NUM>) towards the rotor (<NUM>) side;
a second restricting portion (<NUM>) configured to restrict movement of the sealing member (<NUM>) towards an opposite side from the rotor (<NUM>); and
an accommodating space (<NUM>) defined by the first restricting portion (<NUM>) and the second restricting portion (<NUM>), the sealing member (<NUM>) being configured to be accommodated in the accommodating space (<NUM>), and wherein
the first restricting portion (<NUM>) is formed to have an outer diameter larger than an outer diameter of the second restricting portion (<NUM>) so as to be able to compress the sealing member (<NUM>) with the body (<NUM>) in an axial direction of the driving shaft (<NUM>),
characterized in that:
the side member (<NUM>) further has a suction port (20b) for guiding the working fluid into the pump chambers (<NUM>), the suction port (20b) being formed so as to form cut-out shapes that open at an end surface of the side member (<NUM>) facing the cam ring (<NUM>) and at an outer circumferential surface (20c) of the side member (<NUM>).