KR20200081270A - Compressor - Google Patents

Abstract

Provided is a compressor capable of suppressing overcompression and reducing usage space. A cylinder unit accommodates a rotor and a stator. A vane rotates while moving in the axial direction along with rotation of the rotor. A compression chamber is partitioned by the rotor surface, the stator surface, and the cylinder inner peripheral surface. A discharge chamber is disposed outside the compression chamber in the radial direction of a rotary shaft through the cylinder unit. A plurality of discharge ports connect the compression chamber and the discharge chamber by penetrating the cylinder unit in the radial direction of the rotary shaft. The plurality of discharge ports are arranged in a circumferential direction at a position opposite to a rotational direction side of the rotor rather than the flat surface of the stator within the cylinder unit.

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor.

For example, as shown in Japanese Unexamined Patent Publication No. 2018-44483, a compressor having a rotating shaft, a rotor as a rotating body having a plurality of slit grooves, and a plurality of vanes fitted in a slit groove is known. The compressor further includes a side plate on which a cam surface for displacing the plurality of vanes in the axial direction, a compression chamber, and a discharge chamber as the plurality of vanes are rotationally displaced. In the above document, the discharge chamber and the compression chamber face the axial direction of the rotating shaft through the side plate as a fixed body. It is described in the said document that the side plate is provided with a plurality of discharge refrigerant passages as a plurality of discharge ports penetrating in the axial direction of the rotating shaft. The plurality of discharge refrigerant passages are formed in the corresponding portion of the side plate on the top and bottom flat surfaces, which are the thickest portions.

In addition, in the above document, it is described that a discharge valve for opening and closing the openings of the plurality of discharge refrigerant passages is formed on the back side of the cam surface in the side plate.

As described above, in the configuration of discharging the compressed fluid using the discharge port penetrating the fixed body in the axial direction, the passage length of the discharge port is likely to be long. For this reason, there is a concern that the dead volume, which is a loss generated when the compressed fluid flows through the discharge port, becomes large. Particularly, as shown in the above document, if the discharge port is formed in the thick portion in the fixed body, the passage length of the discharge port tends to be long, and the problem is likely to occur.

In addition, in general, when the flow path cross-sectional area of the discharge port is large, the serviceability is likely to increase. However, if the flow path cross-sectional area of the discharge port is excessively small, overcompression may occur in which the pressure in the compression chamber is excessively high.

Japanese Patent Publication No. 2018-44483

The present invention has been made in view of the above-described circumstances, and its object is to provide a compressor capable of suppressing overcompression and reducing use.

The compressor according to one embodiment of the present disclosure has a rotating shaft and a rotating body that rotates with rotation of the rotating shaft, and has a rotating body surface that intersects an axial direction of the rotating shaft. In addition, the compressor is a fixed body having a fixed body surface opposite to the axial direction to the rotating body surface, wherein the fixed body surface is a fixed body flat surface contacting the rotating body surface and a main axis of the rotating shaft with respect to the fixed body flat surface. It includes a pair of curved surfaces formed on both sides in the (周) direction, and the pair of curved surfaces are curved in the axial direction so as to gradually move away from the rotating body surface as they move away from the stationary flat surface in the main direction. One, the fixed body, and the cylinder portion accommodating the rotating body and the fixed body, the cylinder portion having an inner circumferential surface of the cylinder, and being inserted into a vane groove formed in the rotating body, accompanied by rotation of the rotating body Thus, as the vane rotating while moving in the axial direction, the rotating body surface, the fixed body surface, and a compression chamber which is a seal partitioned by the inner circumferential surface of the cylinder, the volume change of the compression chamber is generated by the vane. The compression chamber is provided in which fluid is sucked and compressed. In addition, the compressor is a discharge chamber disposed in the radial direction outside of the rotating shaft with respect to the compression chamber through the cylinder portion, the discharge chamber in which compressed fluid compressed in the compression chamber is present, and the cylinder portion in the radial direction of the rotating shaft A plurality of discharge ports for communicating the compression chamber and the discharge chamber by penetrating therethrough, wherein the cylinder portion is arranged in the main direction at a position opposite to the rotation direction side of the rotating body than the flat surface of the fixed body. It is characterized by comprising a plurality of discharge ports, and a valve for blocking the plurality of discharge ports.

According to such a structure, the discharge chamber is disposed outside the compression chamber in the radial direction through the cylinder portion. And a plurality of discharge ports are formed in the cylinder portion, not the fixed body. Accordingly, the passage length of each discharge port is likely to be shortened. Therefore, the use volume which is a loss accompanying the movement of the compressed fluid from the compression chamber to the discharge chamber can be reduced.

Further, a plurality of discharge ports are formed. For this reason, compared with a configuration in which only one discharge port is formed, for example, the passage cross-sectional area can be secured wide. Accordingly, it is possible to suppress, for example, overcompression in which the pressure in the compression chamber is excessively high due to the narrow cross-sectional area of the discharge port. In view of the above, it is possible to suppress overcompression and reduce use.

For the compressor, the rotating body surface is a flat surface orthogonal to the axial direction, and the plurality of discharge ports are provided in the main direction from the first discharge port and the fixed body flat surface than the first discharge port. As a second discharge port formed at a distant position, it may be configured to include the second discharge port having a larger flow path cross-sectional area than the first discharge port.

According to such a structure, the rotating body surface is a flat surface orthogonal to the axial direction of the rotating shaft. On the other hand, the curved surface of the fixed body surface is curved in the axial direction gradually away from the rotating body surface as it moves away from the flat surface of the fixed body. For this reason, the compression chamber is widened in the axial direction as it moves away from the flat surface of the fixed body. For this reason, the second discharge port formed at a position away from the flat surface of the stationary body than the first discharge port exists in a place where the compression chamber is wider than the first discharge port. In the above configuration, the cross-sectional area of the flow passage of the second discharge port is larger than the cross-sectional area of the flow passage of the first discharge port. For this reason, many compressed fluids can be made to flow to a discharge chamber through a 2nd discharge port. Therefore, suppression of overcompression can be aimed at more suitably.

In addition, the first discharge port is formed on the flat surface side of the fixed body than the second discharge port. For this reason, in the compression chamber, the compressed fluid in the portion on the rotational direction side of the second discharge port is discharged to the discharge chamber through the first discharge port. Thereby, it can suppress that the compressed fluid in the part of a compression chamber located in the rotation direction side than a 2nd discharge port is a loss.

In particular, the compression chamber is narrowed in the axial direction as it faces the flat surface of the fixture. For this reason, the ratio occupied by the volume of the portion on the side of the rotation direction to the entire volume of the compression chamber is relatively small. For this reason, even if the cross-sectional area of the flow path of the first discharge port is smaller than that of the second discharge port, overcompression can be suppressed.

With respect to the compressor, the cylinder portion has a cylindrical shape having a curved cylinder outer circumferential surface, and on the outer circumferential surface of the cylinder, a left surface of a flat surface that is struck from the outer circumferential surface of the cylinder and orthogonal to the radial direction is formed. , The plurality of discharge ports and the valve may be configured as formed on the seat surface.

According to such a structure, it is not necessary to bend the valve along the outer peripheral surface of the cylinder, for example. Accordingly, the complexity of the shape of the valve can be suppressed.

For the compressor, the cylinder portion has an attachment seat that is a portion between the seat surface and the inner cylinder surface, and the thickness of the attachment seat differs along the main direction, and the plurality of discharge ports are the attachment seat. Among them, the thicknesses are formed at positions different from each other, and include a thick portion port and a thin portion port, and the flow path cross-sectional area of the thin portion port may be larger than the flow path cross-sectional area of the thick portion port.

According to such a structure, the cross-sectional area of the flow path of the thin-walled port is larger than that of the thick-walled port. For this reason, since the flow rate of the compressed fluid discharged through the thin portion port can be increased, overcompression can be suppressed. Moreover, the side of the thin portion pot is formed in the thin portion than the rear portion port. For this reason, the passage length of the hexagonal port is shorter than the passage length of the hexagonal port. Therefore, even if the cross-sectional area of the flow path of the thin-walled portion is increased, use is unlikely to occur. Therefore, overcompression can be more suitably suppressed while suppressing the use.

With respect to the compressor, the rotating body surface is a flat surface orthogonal to the axial direction, and a fixed body edge that is an outer periphery of the curved surface is displaced in the axial direction along the main direction, and the plurality of discharge ports May be configured to be arranged in the main direction while displaced in the axial direction along the edge of the fixture when viewed from the outside in the radial direction.

According to such a structure, in correspondence with the fixed body edge being displaced axially along the main direction, a plurality of discharge ports are displaced axially along the fixed body edge. Accordingly, it is possible to secure a wide area facing the compression chamber, which is an area contributing to the discharge of the compressed fluid in the plurality of discharge ports. Therefore, overcompression can be suppressed more suitably.

With respect to the compressor, a center line connecting the centers of the plurality of discharge ports, as viewed from the outside in the radial direction, is provided with the rotating body edge, rather than with each of the rotating body edge and the fixed body edge that are the outer peripheries of the rotating body surface. It may be configured to be arranged on the middle line side of the fixture edge.

According to this configuration, the centers of the plurality of discharge ports are arranged on the middle line side. For this reason, it is possible to secure a wide area of the plurality of discharge ports facing the compression chamber.

With respect to the compressor, the valve includes a base portion extending in an arrangement direction of the plurality of discharge ports, and a plurality of arm portions extending from the base portion in a direction orthogonal to both of the arrangement direction and the radial direction. As, it is provided with the plurality of arm portions covering the plurality of discharge ports, the length of each arm portion extending installation direction, it may be configured to be the same.

According to such a structure, the length of each arm part in the extension installation direction is the same. For this reason, it is possible to achieve uniformity in the pressure at which the plurality of discharge ports covered by the plurality of arm portions are opened.

In particular, according to this configuration, the base portion extends in the arrangement direction of the plurality of discharge ports in correspondence with the arrangement of the plurality of discharge ports in the axial direction while being displaced in the axial direction. Thereby, the length of the extending direction of each arm part can be made equal. That is, in a configuration in which a plurality of discharge ports are displaced in the axial direction, it is possible to achieve a uniform pressure in which the plurality of discharge ports are opened.

According to the present invention, suppression of overcompression and reduction of use can be achieved.

1 is a cross-sectional view showing an outline of the compressor of the first embodiment disclosed herein.
FIG. 2 is an exploded perspective view of the main configuration of the compressor of FIG. 1.
FIG. 3 is an exploded perspective view of the main configuration of the compressor of FIG. 1 seen from the opposite side to FIG. 2.
4 is a partially enlarged view of the compressor of FIG. 1.
5 is an exploded perspective view of the front cylinder, the front valve, and the front retainer in the compressor of FIG. 1;
6 is a side view of a front cylinder showing a plurality of front discharge ports in the compressor of FIG. 1.
7 is a side view of the front cylinder showing the front valve in the compressor of FIG. 1;
8 is a sectional view taken along line 8-8 in FIG. 7.
9 is a sectional view taken along line 9-9 in FIG. 7.
FIG. 10 is a side view of the front cylinder showing the rear valve in the compressor of FIG. 1;
11 is a sectional view taken along line 11-11 in FIG. 10.
12 is an exploded view showing the state of both fixed bodies and vanes in a certain phase in the compressor of FIG. 1.
FIG. 13 is an exploded view showing the state of both fixed bodies and vanes in a phase different from that of FIG. 12 in the compressor of FIG. 1.
14 is an exploded perspective view showing a main configuration of a second embodiment disclosed herein.
15 is a cross-sectional view schematically showing a relationship between a plurality of vanes and a front fixture in the compressor of FIG. 14.
16 is a cross-sectional view schematically showing a relationship between a plurality of vanes and a rear fixture in the compressor of FIG. 14.
FIG. 17 is an exploded view schematically showing both the fixed body, the rotating body, and the vane in the compressor of FIG. 14.
FIG. 18 is an exploded view schematically showing both fixed bodies, rotation bodies, and vanes in a phase different from that of FIG. 17 in the compressor of FIG. 14.
19 is a cross-sectional view schematically showing another example compressor.

(Form for carrying out the invention)

(First embodiment)

Hereinafter, the first embodiment of the disclosed compressor will be described with reference to FIGS. 1 to 13 of the drawings. In addition, the compressor of this embodiment is a vehicle, for example, It is mounted in a vehicle in detail, and is used. The compressor is used, for example, in a vehicle air conditioner, and the fluid to be compressed by the compressor is a refrigerant containing oil.

In addition, for convenience of illustration, the rotary shaft 12 is shown in side view in FIG. 1, and the valves 150 and 170 and retainers 155 and 175 are omitted in FIGS. 2 and 3, and FIGS. 1 and 4 are shown. The part of vane 120 is shown by breaking.

As shown in Fig. 1, the compressor 10 includes a housing 11, a rotating shaft 12, an electric motor 13, an inverter 14, a front cylinder 30 as a cylinder, and a rear plate ( 40), a front fixing body 60, a rear fixing body 80, and a rotating body 100 are provided.

The housing 11 has, for example, a cylindrical shape as a whole, and has an inlet 11a through which suction fluid from the outside is sucked, and an outlet 11b through which compressed fluid is discharged. The rotating shaft 12, the electric motor 13, the inverter 14, the front cylinder 30, the rear plate 40, both fixed bodies 60, 80 and the rotating body 100 are accommodated in the housing 11 It is done.

The housing 11 is provided with a front housing 21, a rear housing 22, and an inverter cover 25.

The front housing 21 has a bottomed cylindrical shape and opens toward the rear housing 22. The suction port 11a is, for example, formed at a position on the lower side of the side wall portion of the front housing 21 than the opening end of the front housing 21. However, the position of the suction port 11a is arbitrary.

The rear housing 22 is a bottomed cylindrical shape having a rear housing bottom portion 23 and a rear housing side wall portion 24 standing up from the rear housing bottom 23 toward the front housing 21. The rear housing 22 is opened toward the front housing 21. The discharge port 11b is formed in the rear housing side wall portion 24. However, the position of the discharge port 11b is arbitrary.

The front housing 21 and the rear housing 22 are united with the openings facing each other.

The inverter cover 25 is disposed with respect to the front housing 21 on the opposite side to the rear housing 22 side. The inverter cover 25 is fixed to the front housing 21 in a state that is against the bottom of the front housing 21.

Inverter 14 is accommodated in inverter cover 25. The inverter 14 drives the electric motor 13.

As shown in FIG. 1, the front cylinder 30 accommodates both the fixed bodies 60, 80 and the rotating body 100 in cooperation with the rear plate 40. As shown in FIG. The front cylinder 30 has a bottomed cylindrical shape formed smaller than the rear housing 22 and opens toward the rear housing bottom 23.

The front cylinder 30 has a front cylinder bottom part 31 and a front cylinder side wall part 32 standing up from the front cylinder bottom part 31 toward the rear housing bottom part 23.

1 and 2, the front cylinder bottom portion 31 has a stepped shape in the axial direction Z, and is disposed on the center side of the first bottom portion 31a and the first bottom portion 31a. It is outside the radial direction R of the rotating shaft 12, and has a second bottom portion 31b disposed on the rear housing bottom portion 23 side than the first bottom portion 31a. In the first bottom portion 31a, a front insertion hole 31c through which the rotation shaft 12 can be inserted is formed, and the rotation shaft 12 is inserted through the front insertion passage hole 31c.

As shown in FIG. 1, the front cylinder side wall part 32 enters inside the rear housing 22. As shown in FIG. The front cylinder side wall portion 32 has a front cylinder inner circumferential surface 33 as an inner circumferential surface, and a front cylinder outer circumferential surface 34 as an outer circumferential surface disposed on the opposite side to the front cylinder inner circumferential surface 33.

The front cylinder inner peripheral surface 33 and the front cylinder outer peripheral surface 34 are, for example, cylindrical surfaces extending in the axial direction Z. The front cylinder outer peripheral surface 34 abuts on the inner peripheral surface of the rear housing side wall portion 24 in the radial direction R.

In the present embodiment, the discharge concave portion 35 for dividing the discharge chamber A1 is formed on the front cylinder outer circumferential surface 34. The discharge concave portion 35 is formed between both ends in the axial direction Z of the outer circumferential surface 34 of the front cylinder, and is recessed toward the inside in the radial direction R. A discharge chamber A1 in which compressed fluid is present is partitioned by the discharge concave portion 35 and the rear housing side wall portion 24. The discharge chamber A1 in the present embodiment is formed in a cylindrical shape with the axial direction Z in the axial direction. The discharge chamber A1 communicates with the discharge port 11b. The compressed fluid in the discharge chamber A1 is discharged from the discharge port 11b.

In the front cylinder 30, an expansion portion 36 extending outward in the radial direction R of the rotating shaft 12 is formed. The bulging portion 36 is formed at a position across both the front cylinder bottom portion 31 and the front end side (front cylinder bottom portion 31 side) of the front cylinder side wall portion 32. The bulging portion 36 is bulged outward in the radial direction R from the front cylinder outer circumferential surface 34. The front housing 21 and the rear housing 22 are unitized in a state where the bulging portion 36 is sandwiched. The displacement of the axial direction Z of the front cylinder 30 is regulated by both the housings 21 and 22.

As shown in FIG. 1, in this embodiment, the motor chamber A2 is divided by the front housing 21 and the front cylinder bottom part 31, and the electric motor 13 is accommodated in the motor chamber A2. have. The electric motor 13 is supplied with drive electric power from the inverter 14, so that the rotating shaft 12 is rotated in the direction indicated by the arrow M, and in particular, the two fixed bodies 60, 80 from the electric motor 13 are provided. Boa rotates clockwise.

In addition, since the suction port 11a is formed in the front housing 21 that divides the motor chamber A2, the suction fluid sucked from the suction port 11a is sucked into the motor chamber A2 in the housing 11 do. That is, intake fluid exists in the motor chamber A2. In other words, it can be said that the motor chamber A2 is a suction chamber through which suction fluid is sucked.

In the compressor 10 of the present embodiment, the inverter 14, the electric motor 13, the front fixture 60, the rotating body 100, and the rear fixture 80 are ordered in the axial direction (Z). As listed. However, the position of each of these parts is arbitrary, and for example, the inverter 14 may be arranged outside the radial direction R of the rotating shaft 12 with respect to the electric motor 13.

The rear plate 40 has a plate shape (in the present embodiment, a disc shape), and is accommodated in the rear housing 22 so that the plate thickness direction coincides with the axial direction Z. The outer diameter of the rear plate 40 is the same diameter as, for example, the front cylinder outer circumferential surface 34 (or the inner circumferential surface of the rear housing side wall portion 24). The rear plate 40 is fitted to the rear housing 22.

In the central portion of the rear plate 40, a rear plate insertion passage 41 through which the rotation shaft 12 is inserted is formed. In the present embodiment, the rear plate insertion passage 41 is formed to have the same size as the rotating shaft 12. However, the present invention is not limited to this, and the rear plate insertion through hole 41 may be larger than the rotating shaft 12.

The front cylinder 30 and the rear plate 40 are joined so that the front end of the side wall portion 32 of the front cylinder is in contact with the rear plate 40, and the opening portion of the front cylinder 30 by the rear plate 40 This is blocked.

Specifically, in the rear plate 40, a recess 42 is formed at a portion of the front cylinder side wall portion 32 facing the axial direction Z at the distal end portion. The depression 42 is formed over the entire circumference of the rear plate 40. The front cylinder 30 and the rear plate 40 are attached to each other in a state where the front end of the side wall portion 32 of the front cylinder fits into the recess 42.

In addition, the rear plate 40 is held by the front cylinder 30 supported by the housing 11 and the rear housing bottom 23 which is a part of the housing 11. Thereby, the rear plate 40 is supported by the housing 11. In addition, the rear plate 40 should just be supported by the housing 11, and the specific support embodiment is arbitrary.

The rear plate 40 is a plate surface orthogonal to the axial direction Z, and has a first plate surface 43 and a second plate surface 44. The first plate surface 43 is disposed on the front cylinder bottom 31 side. The second plate surface 44 is disposed on the rear housing bottom 23 side, and faces the rear housing bottom 23 in the axial direction Z. In addition, in the present embodiment, the first plate surface 43 is smaller than the second plate surface 44 because of the formation of the recesses 42.

In addition, in this specification, "opposite" (A opposes B), unless otherwise specified, within a range not technically contradictory, A and B face each other through a gap, and both are in agreement. Includes a touched aspect. For example, the second plate surface 44 and the rear housing bottom 23 may be spaced apart or may be in contact with each other. In addition, "opposite" (C-plane opposes D-plane) includes an aspect in which two parts are in contact with each other and the other parts are separated.

As shown in FIG. 1, the compressor 10 is provided with two radial bearings 51 and 53 that rotatably support the rotating shaft 12 with respect to the housing 11.

Of both radial bearings 51 and 53, the front radial bearing 51 is attached to the boss portion 52 formed at the bottom of the front housing 21. The boss portion 52 is a ring shape protruding from the bottom of the front housing 21. The front radial bearing 51 is disposed inside the radial direction R of the rotating shaft 12 with respect to the boss portion 52, and rotates a first end, which is one end of both ends of the rotating shaft 12, I support it as much as possible.

Of the radial bearings 51 and 53, the rear radial bearing 53 is attached to the radial accommodating recess 54 formed in the rear plate 40. The radial accommodating recess 54 is a portion of the inner wall surface of the rear plate insertion passage 41 on the second plate surface 44 side than the first plate surface 43, and further, the second plate surface 44 It is formed in the peripheral part of the rear plate insertion hole 41 in. The radial accommodating recessed part 54 is open toward both of the radial direction R inside and the rear housing bottom part 23 side. The rear radial bearing 53 is disposed in the radial accommodating concave portion 54, and supports the second end of the both ends of the rotating shaft 12 opposite to the first end so as to be rotatable.

As shown in Fig. 1, a space is formed by the front cylinder 30 and the rear plate 40, and both fixed bodies 60, 80 and the rotating body 100 are accommodated in the space. In detail, both fixtures 60 and 80 are arranged opposite to each other in the axial direction Z, and between both fixtures 60 and 80, and both fixtures 60 and 80 and the rotating shaft 12 ), the rotating body 100 is disposed.

Both fixed bodies 60 and 80 are supported by the front cylinder 30 (in other words, the housing 11) so as not to rotate with rotation of the rotating shaft 12. In addition, in this embodiment, both fixing bodies 60 and 80 are the same shape.

Both fixed bodies 60 and 80 are demonstrated.

1 to 3, of the two fixed bodies 60 and 80, the front fixed body 60 disposed on the electric motor 13 side has, for example, a ring shape (circular annular shape in this embodiment) ), and has a front fixture insert hole 61 into which the rotating shaft 12 is inserted. In the present embodiment, the front fixture insertion hole 61 is a through hole penetrating in the axial direction Z. The rotating shaft 12 is inserted into the front fixture insertion hole 61, and the front fixture 60 is disposed in the front cylinder 30.

The front fixture 60 has a front cylinder outer circumferential surface 62 facing the radial direction R on the front cylinder inner circumferential surface 33. In this embodiment, the front fixed body outer circumferential surface 62 and the front cylinder inner circumferential surface 33 abut, and the front fixed body 60 is supported by the front cylinder 30 by the abutment. However, the present invention is not limited to this, and the front cylinder inner circumferential surface 33 and the front fixture outer circumferential surface 62 may be separated.

The front fixture 60 is provided with a front rear surface 63 facing the axial direction Z at the bottom of the front cylinder 31. The front rear surface 63 and the front cylinder bottom 31 may be separated from each other or may be in contact with each other.

The front fixed body 60 has a front fixed body surface 70 as a fixed body surface. The front fixed body surface 70 is a plate surface on the opposite side to the front rear surface 63. The front fixed body surface 70 is ring-shaped, and in this embodiment, it is annular.

As shown in FIG. 3, the front fixture surface 70 is provided with the first front flat surface 71 and the second front flat surface 72, which both intersect (orthogonally in this embodiment) with the axial direction Z. , A pair of front curved surfaces 73 as curved surfaces connecting both front flat surfaces 71 and 72 is provided.

4, both front flat surfaces 71 and 72 are shifted in the axial direction Z. As shown in FIG. Specifically, the second front flat surface 72 is disposed at a position closer to the rear fixture 80 (in other words, the front rotating surface 103) than the first front flat surface 71. In other words, the distance between the second front flat surface 72 and the front rotating body surface 103 is smaller than the distance between the first front flat surface 71 and the front rotating body surface 103. In addition, the front rotating body surface 103 will be described later.

Both front flat surfaces 71 and 72 are arranged spaced apart in the main direction of the front fixing body 60, for example, both are shifted by 180 degrees. In this embodiment, both front flat surfaces 71 and 72 are fan-shaped. In addition, in the following description, the circumferential positions of both fixing bodies 60 and 80 are also called angular positions.

Each pair of front curved surfaces 73 is fan-shaped. As shown in FIG. 3, the pair of front curved surfaces 73 are arranged opposite to the direction perpendicular to both of the axial direction Z and opposite directions of both front flat surfaces 71, 72. As shown in FIG. Specifically, the inner peripheries of the pair of front curved surfaces 73 face each other with the rotating shaft 12 sandwiched therebetween. Both front curved surfaces 73 have the same shape.

The pair of front curved surfaces 73 connect both front flat surfaces 71 and 72, respectively. Specifically, one of the pair of front curved surfaces 73 connects one end portion in the main direction of both front flat surfaces 71 and 72, and the other of the pair of front curved surfaces 73 is connected. Silver connects the other ends of the front flat surfaces 71 and 72 opposite to the one end in the main direction.

Here, for convenience of explanation, the angular position of the boundary between the front curved surface 73 and the first front flat surface 71 is set to the first angle position θ1, and the front curved surface 73 and the second front flat surface are used. The angular position of the boundary portion of the surface 72 is taken as the second angular position (θ2). In addition, for the sake of illustration, in Fig. 3, each angular position θ1, θ2 is indicated by a broken line, but in reality, the boundary portions continue smoothly. In other words, the front curved surface 73 and the first front flat surface 71 are smoothly continuous with each other at the first angular position θ1, and the front curved surface 73 and the second front flat surface 72 are, At the second angular position θ2, they are smoothly continuous with each other.

The front curved surface 73 is a curved surface displaced in the axial direction Z along the main direction (in other words, depending on the angular position of the front fixture 60). Specifically, the front curved surface 73 gradually approaches the rear fixture 80 as it moves from the first angular position θ1 to the second angular position θ2 (in other words, the front rotator surface 103 )), and it is curved in the axial direction (Z). In addition, "according to the main direction" includes the meaning "according to the main position". That is, the position of the axial direction Z of each part of the front curved surface 73 is different for each main position of the part. Similarly, "according to the radial direction (R)" includes the meaning "according to the radial direction (R) position".

That is, the pair of front curved surfaces 73 are formed on both sides in the main direction with respect to the second front flat surface 72, and gradually move toward the front rotating body surface as they move away from the second front flat surface 72 in the main direction. It curves in the axial direction Z so that it is away from (103).

In the present embodiment, the front curved surface 73 is convex toward the front rotating surface 73a and the front concave surface 73a curved in the axial direction Z so as to be concave with respect to the front rotating surface 103. It has a front convex surface 73b curved in the axial direction Z so as to be made.

The front concave surface 73a is disposed on the first front flat surface 71 side than the second front flat surface 72, and the front convex surface 73b is second than the first front flat surface 71. It is arranged on the front flat surface 72 side. The front concave surface 73a and the front convex surface 73b are connected. That is, the front curved surface 73 is a curved surface having an inflection point.

In addition, the angular range occupied by the front convex surface 73b and the angular range occupied by the front concave surface 73a may be the same or different. In addition, the position of the inflection point is arbitrary. In addition, since the front curved surface 73 can also be referred to as a curved surface that curves in a wavy shape, paying attention to this point, the front fixture surface 70 is also called a wave surface that includes a portion curved in a wavy shape. can do.

Here, the front fixture edge 73c, which is the outer periphery of the front curved surface 73, is displaced in the axial direction Z along the main direction. In the present embodiment, since the front curved surface 73 has a shape having a front concave surface 73a and a front convex surface 73b, the front fixture edge 73c is a sinusoidal wave when viewed from outside in the radial direction R It is made.

2 to 4, the rear fixed body 80 disposed on the rear plate 40 side of both fixed bodies 60 and 80, like the front fixed body 60, has a ring shape (bone In the embodiment, it has an annular shape) and has a rear fixture insert hole 81 into which the rotating shaft 12 is inserted. In the present embodiment, the rear fixture insertion hole 81 is a through hole that penetrates in the axial direction Z. The rear fixture 80 is disposed in the front cylinder 30 with the rotary shaft 12 inserted into the rear fixture insertion hole 81.

The rear fixture 80 has a rear fixture outer circumferential surface 82 facing the radial direction R on the front cylinder inner circumferential surface 33. In this embodiment, the outer peripheral surface 82 of the rear fixed body and the inner peripheral surface 33 of the front cylinder abut, and the rear fixed body 80 is supported by the front cylinder 30 by the abutment. However, the present invention is not limited to this, and the front cylinder inner circumferential surface 33 and the rear fixture outer circumferential surface 82 may be separated.

The rear fixture 80 is provided with a rear rear surface 83 facing the axial direction Z on the first plate surface 43 of the rear plate 40. The rear rear surface 83 and the first plate surface 43 may be separated from each other or may be in contact with each other.

The rear fixed body 80 has a rear fixed body surface 90 as a fixed body surface. The rear fixed body surface 90 is a plate surface opposite to the rear rear surface 83. The rear fixture surface 90 is ring-shaped, and is annular in this embodiment.

In this embodiment, the rear fixed body surface 90 has the same shape as the front fixed body surface 70. As shown in FIG. 2, the rear fixed surface 90 intersects (orthogonally in this embodiment) the axial direction Z, and the first rear flat surface 91 and the second rear flat surface 92 are both A pair of rear curved surfaces 93 are provided as curved surfaces connecting the rear flat surfaces 91 and 92.

4, both rear flat surfaces 91 and 92 are shifted in the axial direction Z. As shown in FIG. Specifically, the second rear flat surface 92 is a fixed flat surface that is disposed closer to the front fixture 60 (in other words, the rear rotating surface 104) than the first rear flat surface 91. to be. In other words, the distance between the second rear flat surface 92 and the rear rotating surface 104 is smaller than the distance between the first rear flat surface 91 and the rear rotating surface 104. In addition, both rear flat surfaces 91 and 92 are arranged spaced apart in the main direction of the rear fixing body 80, for example, both are shifted by 180 degrees. In this embodiment, both rear flat surfaces 91 and 92 are fan-shaped.

Each pair of rear curved surfaces 93 is fan-shaped. The pair of rear curved surfaces 93 are arranged opposite to the direction perpendicular to both of the axial direction Z and opposite directions of both rear flat surfaces 91 and 92. Specifically, the inner peripheries of the pair of rear curved surfaces 93 face each other with the rotating shaft 12 sandwiched therebetween.

One of the pair of rear curved surfaces 93 connects one end portion in the main direction of both rear flat surfaces 91 and 92, and the other of the pair of rear curved surfaces 93 has both rear surfaces. The other ends on the opposite side to the one end in the main direction of the flat surfaces 91 and 92 are connected.

The two fixed body surfaces 70 and 90 are spaced apart from each other in the axial direction Z in the state where the angular positions are shifted by 180° from each other through the rotating body 100.

The opposing distances of the two fixed body surfaces 70 and 90 are made constant regardless of the angular position (in other words, the main position). Specifically, as shown in FIG. 4, the first front flat surface 71 and the second rear flat surface 92 face the axial direction Z, and the second front flat surface 72 and the first The rear flat surface 91 faces the axial direction Z. In addition, the amount of shift Z1 in the axial direction Z between both front flat surfaces 71 and 72 and the amount of shift between both rear flat surfaces 91 and 92 are the same. Hereinafter, the amount of displacement in the axial direction Z between both front flat surfaces 71 and 72 and the amount of displacement between both rear flat surfaces 91 and 92 are simply referred to as "shift amount Z1".

In addition, the degree of curvature of the front curved surface 73 and the degree of curvature of the rear curved surface 93 are the same. Specifically, a pair of rear curved surfaces 93 are formed on both sides in the circumferential direction with respect to the second rear flat surfaces 92, like the front curved surfaces 73, and the second rear flat surfaces 92 ), it is curved in the axial direction (Z) so as to gradually move away from the rear rotating surface 104 as it moves away from the main direction. That is, the front curved surface 73 and the rear curved surface 93 are curved in the same direction so that the opposing distance between them does not change depending on the angular position. Accordingly, the opposing distances between the two fixed body surfaces 70 and 90 are constant at any angular position.

In addition, for the specific shapes of the first rear flat surface 91, the second rear flat surface 92, and the rear curved surface 93, the first front flat surface 71, the second front flat surface 72, and , Since it is the same as the front curved surface 73, detailed description is omitted. In addition, like the front curved surface 73, the rear curved surface 93 can also be referred to as a curved surface that is curved in a wavy shape, so paying attention to this point, the rear fixed surface 90 is curved in a wavy shape. It can also be said to be a wave surface that includes the part being performed.

Here, the rear fixture edge 93c, which is the outer periphery of the rear curved surface 93, is displaced in the axial direction Z along the main direction. In the present embodiment, the rear fixture edge 93c has a sinusoidal shape when viewed from the outside in the radial direction R, like the front fixture edge 73c.

The rotating body 100 rotates with rotation of the rotating shaft 12. The rotating body 100 is disposed in the housing 11 so that the rotating central axis of the rotating body 100 is the same as the central axis of the rotating shaft 12. That is, the rotating body 100 is disposed so as to be coaxial with the rotating shaft 12. For this reason, the compressor 10 has a structure of an axial center movement, not an eccentric movement.

Here, the main directions of both the fixed bodies 60 and 80 and the rotating body 100 coincide with the main directions of the rotating shaft 12, and the diameters of both the fixed bodies 60 and 80 and the rotating body 100 The direction and the radial direction R of the rotating shaft 12 coincide. In addition, the axial direction of both the fixed bodies 60 and 80 and the rotating body 100 coincides with the axial direction Z of the rotating shaft 12. For this reason, the main direction, the radial direction (R), and the axial direction (Z) of the rotating shaft (12) may be appropriately substituted in the main direction, the radial direction, and the axial direction of the rotating body (100). You may apply|replace in the main direction, the radial direction, and the axial direction of the stagnation 60,80.

2 to 4, the rotating body 100 includes a cylindrical portion 101 through which the rotating shaft 12 is inserted, and a ring portion 102 protruding toward the outside in the radial direction R from the cylindrical portion 101. ).

The cylindrical portion 101 is, for example, a cylindrical shape with the axial direction Z in the axial direction, and has an inner diameter equal to or slightly larger than the rotating shaft 12, and smaller than both fixed body insertion holes 61 and 81. It has an outer diameter.

The cylinder part 101 is attached to the rotating shaft 12 so as to integrally rotate with the rotating shaft 12. Accordingly, with the rotation of the rotating shaft 12, the rotating body 100 rotates. In addition, the attachment mode of the cylindrical part 101 to the rotating shaft 12 is arbitrary, for example, the cylindrical part 101 may be fixed to the rotating shaft 12 by press-fitting, or to the rotating shaft 12 and the cylindrical part 101 The cylindrical portion 101 may be fixed to the rotating shaft 12 by a fixing pin inserted over. Further, a configuration in which the cylinder portion 101 and the rotating shaft 12 are connected by a connecting member such as a key may be used, and the concave portion formed on the other side of the concave portion formed on one of the cylindrical portion 101 and the rotating shaft 12 is engaged. It may be configured.

The cylinder part 101 is arrange|positioned over both the fixed bodies 60,80. Specifically, the first end of both ends in the axial direction Z of the cylindrical portion 101 enters the front fixture insertion hole 61, and the second end opposite to the first end is a rear fixture It enters the insertion hole 81.

The ring portion 102 is formed at a predetermined position (near the center portion in the present embodiment) between both ends in the axial direction Z in the cylinder portion 101, and is disposed between the two fixed bodies 60 and 80. have. In other words, both fixing bodies 60 and 80 are arranged opposite to the axial direction Z through the ring portion 102.

The ring portion 102 is an annular plate shape with the axial direction Z in the plate thickness direction, and has both ring-shaped front rotator surfaces 103 and rear rotator surfaces 104 as both cross-sections in the axial direction Z. have. Both rotating body surfaces 103 and 104 are flat surfaces intersecting with respect to the axial direction Z, and in this embodiment, they are flat surfaces orthogonal to the axial direction Z. For this reason, both rotating body edges 103a and 104a, which are the outer circumferential edges of both rotating body surfaces 103 and 104, have a linear shape when viewed from the outside of the radial direction R, and are axial regardless of the main direction (main position). The position of (Z) is made constant. In addition, the front rotating body surface 103 and the rear rotating body surface 104 may also be referred to as a first rotating body surface and a second rotating body surface.

As shown in Fig. 4, the front rotating body surface 103 faces the front fixing body surface 70 in the axial direction Z. In the present embodiment, the front rotating body surface 103 and the second front flat surface 72 are in contact with each other, and a surface (part) other than the second front flat surface 72 of the front fixed body surface 70 and the front The rotating body surface 103 is separated.

The rear rotating body surface 104 faces the rear fixing body surface 90 in the axial direction Z. In the present embodiment, the rear rotating body surface 104 and the second rear flat surface 92 are in contact, and among the rear fixed body surfaces 90, surfaces other than the second rear flat surface 92 and the rear rotating body surface 104 ) Is separated.

The ring outer circumferential surface 105, which is the outer circumferential surface of the ring portion 102, is a surface that intersects with the radial direction R, and faces the radial direction R with the inner circumferential surface 33 of the front cylinder. The ring outer circumferential surface 105 and the front cylinder inner circumferential surface 33 may be in contact with each other, or may be separated through a small gap.

As shown in FIG. 4, the compressor 10 is provided with rotating body bearings 111 and 112 as radial bearings that rotatably support the cylindrical parts 101 with respect to both fixed bodies 60 and 80. .

The rotating body bearings 111 and 112 are disposed in the fixed body insertion holes 61 and 81. The rotating body bearings 111 and 112 have a cylindrical shape with the axial direction Z in the axial direction, and extend in the axial direction Z. The specific types of both rotating body bearings 111 and 112 are arbitrary.

The front rotating body bearing 111 is disposed between the cylindrical portion 101 and the inner wall surface of the front fixture inserting hole 61, includes a first end, and includes a front fixture inserting hole in the cylindrical portion 101 The part contained in (61) is rotatably supported.

The rear rotator bearing 112 is disposed between the cylindrical portion 101 and the inner wall surface of the rear fixture insertion hole 81, and includes a second end, and the rear fixture insertion hole in the cylindrical portion 101 ( 81) The part contained in the inside is rotatably supported.

In this embodiment, the rotating body 100 is a state in which the rotating body surfaces 103 and 104 and the fixed body surfaces 70 and 90 face the axial direction Z by both rotating body bearings 111 and 112. , It is supported with respect to both fixtures (60, 80). Accordingly, the posture of the rotating body 100 is held. In particular, in this embodiment, both ends of the rotating body 100 are supported by both rotating body bearings 111 and 112. Accordingly, the rotating body 100 is stably held.

In addition, the outer circumferential surfaces of the rotating body bearings 111 and 112 are curved so as to be convex toward the outside in the radial direction R. The outer circumferential surfaces of the rotating body bearings 111 and 112 are in contact with the inner wall surfaces of the fixed body insertion holes 61 and 81, and the curvatures of both of them are the same.

As shown in FIG. 4, the compressor 10 is provided with thrust bearings 113 and 114 that support the rotating body 100 from the axial direction Z. Both thrust bearings 113 and 114 are disposed on both sides of the axial direction Z of the cylindrical portion 101, and sandwich the cylindrical portion 101 from the axial direction Z.

Specifically, the front thrust bearing 113 is arranged in a space generated by the front cylinder bottom 31 being formed in a stepped shape. The front thrust bearing 113 supports the first end face in the axial direction Z of the cylinder portion 101 in a state supported by the front cylinder bottom portion 31.

The rear thrust bearing 114 is disposed in the thrust receiving recess 115 formed in the rear plate 40. The thrust accommodating recess 115 is a portion of the inner wall surface of the rear plate insertion passage 41 that is on the side of the first plate surface 43 than the second plate surface 44, and is also provided on the first plate surface 43. It is formed in the periphery of the rear plate insertion hole 41 in the above. In this embodiment, the thrust accommodation recess 115 and the radial accommodation recess 54 are formed separately, and the rear plate 40 is interposed between them. The rear thrust bearing 114 is disposed in the thrust receiving concave portion 115 and supports the second end face in the axial direction Z of the cylindrical portion 101 in a state supported by the rear plate 40. .

Both thrust bearings 113 and 114 have a cylindrical shape, and the rotation shaft 12 is inserted through both thrust bearings 113 and 114. In the present embodiment, the inner circumferential surfaces of both thrust bearings 113 and 114 are in contact with the outer circumferential surfaces of rotation shaft 12. In this case, it can be said that both thrust bearings 113 and 114 support the rotating shaft 12 by contacting the rotating shaft 12 with the radial direction R. However, the present invention is not limited to this, and both thrust bearings 113 and 114 and the rotating shaft 12 may be separated in the radial direction R.

As shown in FIG. 4, the compressor 10 is equipped with the compression chambers A4 and A5 in which fluid suction and compression are performed. Both compression chambers A4 and A5 are disposed on both sides of the axial direction Z in the rotating body 100.

The front compression chamber A4 is divided by a front fixed body surface 70, a front rotating body surface 103, an outer peripheral surface of the front rotating body bearing 111, and an inner inner surface 33 of the front cylinder. The rear compression chamber A5 is divided by a rear fixed body surface 90, a rear rotating body surface 104, an outer peripheral surface of the rear rotating body bearing 112, and an inner inner surface 33 of the front cylinder. In this embodiment, the front compression chamber A4 and the rear compression chamber A5 are the same size.

Here, both of the compression chambers A4 and A5 and the discharge chamber A1 face the radial direction R through the front cylinder side wall portion 32. That is, the discharge chamber A1 is disposed outside the radial direction R of both compression chambers A4 and A5 through the front cylinder side wall portion 32.

Incidentally, in the present embodiment, the discharge chamber A1 faces the radial direction R with respect to a part of the front compression chamber A4, while the radial direction R with respect to the entire rear compression chamber A5. It is opposed to, but is not limited to. In other words, the discharge chamber A1 is axially oriented so that at least a portion of the front compression chamber A4 faces the radial direction R and at least a portion of the rear compression chamber A5 faces the radial direction R. Z).

2 to 4, the compressor 10 includes a vane 120 inserted into the vane groove 125 formed in the rotating body 100.

The vane 120 is a rectangular plate shape, for example. For example, so that the plate surface of the vane 120 is orthogonal to the main direction of the rotating shaft 12, the vane 120 is between both fixed bodies 60, 80 (in other words, both fixed body surfaces 70, 90). Are deployed. That is, the vane 120 is a plate shape with the direction orthogonal to both of the axial direction Z and the radial direction R (the main direction of the rotating shaft 12) in the thickness direction.

The vane 120 has a first vane end 121 and a second vane end 122 as both ends in the axial direction Z, and a vane outer circumferential end surface 123 as both cross-sections in the radial direction R. And a vane inner circumferential end face 124.

As shown in FIG. 4, the 1st vane end part 121 contacts the front fixed body surface 70, and the 2nd vane end part 122 contacts the rear fixed body surface 90. That is, the vane 120 of this embodiment abuts both fixed body surfaces 70 and 90. In addition, although the specific shape of both vane end parts 121 and 122 is arbitrary, it is good if it curves so that it may be convex toward both fixed body surfaces 70 and 90, for example.

2 to 4, the vane groove 125 is formed in the ring portion 102 of the rotating body 100. The vane groove 125 penetrates the ring portion 102 in the axial direction Z, and opens on both the rotating body surfaces 103 and 104. The vane groove 125 of this embodiment opens toward the outside in the radial direction R. On the other hand, the vane groove 125 is not opened inside the radial direction R.

Further, the vane groove 125 is formed using, for example, an end mill. As an example, the vane groove 125 is formed by forming the rotating body 100 in which the vane groove 125 is not formed, and then moving the end mill from the outside in the radial direction R toward the inside. However, the method of forming the vane groove 125 is not limited to this and is arbitrary.

The vane grooves 125 have both sides facing each other in the main direction. Both side surfaces of the vane groove 125 and both plate surfaces of the vane 120 face each other. The width of the vane groove 125 (in other words, the opposing distances on both sides of the vane groove 125. The main distance) may be equal to or slightly larger than the plate thickness of the vane 120. The vane 120 inserted in the vane groove 125 is sandwiched between both sides of the vane groove 125. The vane 120 is allowed to move along the vane groove 125 in the axial direction Z.

According to such a structure, the vane 120 rotates as the rotating body 100 rotates. In this case, since both fixed body surfaces 70 and 90 are curved, the vane 120 moves along both fixed body surfaces 70 and 90 in the axial direction Z (in other words, swings). That is, the vane 120 rotates while moving in the axial direction Z. Accordingly, the first vane end 121 of the vane 120 enters the front compression chamber A4, or the second vane end 122 enters the rear compression chamber A5. That is, the vane groove 125 is such that the vanes 120 are disposed across both compression chambers A4 and A5 while rotating the vanes 120 with the rotation of the rotating body 100.

In addition, in both compression chambers A4 and A5, the periodic volume change of both compression chambers A4 and A5 is caused by the vanes 120 with rotation of the rotating shaft 12, respectively, so that fluid is sucked and compressed. This is done. That is, the vane 120 can also be said to generate a volume change in both compression chambers A4 and A5. This point will be described later.

The travel distance (in other words, swing distance) of the vane 120 is the amount of displacement in the axial direction Z between the two front flat surfaces 71 and 72 (or between the two rear flat surfaces 91 and 92), that is, the displacement amount (Z1). In addition, the vane 120 maintains the state in contact with both fixed body surfaces 70 and 90 during rotation of the rotating body 100. That is, the vane 120 continues to abut against both the fixed body surfaces 70 and 90 during rotation of the rotating body 100, and intermittent contact (in detail, the vane 120 is fixed body surface 70 , 90).

Here, the vane outer circumferential end face 123 abuts against the front cylinder inner circumferential surface 33 regardless of the movement of the vane 120. In other words, the front cylinder inner circumferential surface 33 is longer than the length of the axial direction Z of the vane 120 so as to contact the vane outer circumferential end face 123 regardless of the movement of the vane 120 in the axial direction Z. It can be said to be extended.

In addition, the shape of the vane outer circumferential end surface 123 is arbitrary, but is curved so as to be convex toward the outside in the radial direction R so as to be continuous with the ring outer circumferential surface 105, for example, and the vane outer circumferential end surface 123 ) May be the same as the curvature of the inner circumferential surface 33 of the front cylinder.

The compressor 10 is provided with the abutting member 130 abutting on the vane inner circumferential end face 124. In this embodiment, the abutting member 130 is a separate body from the rotating body 100, and the abutting member 130 is attached to the rotating body 100. The abutting member 130 and the vane inner circumferential end face 124 will be described below. In addition, the abutting member 130 is hidden behind the cylinder 101 in FIGS. 2 and 3.

As shown in Fig. 4, a concave tank 131 extending in the axial direction Z is formed on the outer circumferential surface of the cylindrical portion 101. The concave tank 131 is open toward the outside in the radial direction R, and communicates with the vane groove 125.

The abutment member 130 is a rod shape (in other words, a column shape) extending in the axial direction Z, so that the abutment member 130 fits into the concave tank 131 so that the abutment member 130 The cross-sectional shape is formed in accordance with the cross-sectional shape of the concave tank 131. The abutting member 130 is attached to the rotating body 100 by being fitted into the concave tank 131. The abutting member 130 is formed in the concave tank 131 at a position communicating with the vane groove 125. A part of the abutting member 130 protrudes outward in the radial direction R in the vane groove 125, and is sandwiched between the axial directions Z by both rotating body bearings 111 and 112.

The abutting member 130 has an abutting surface 132 abutting in the radial direction R on the vane inner circumferential end face 124. The abutting surfaces 132 are continuous to the outer circumferential surfaces of both rotating body bearings 111 and 112. The abutment surfaces 132 are curved so as to be convex toward the outside in the radial direction R, for example, like the outer circumferential surfaces of the rotating body bearings 111 and 112, and the outer circumferential surfaces of the two rotating body bearings 111 and 112 It is supposed to face. In detail, the curvature of the abutment surface 132 is set equal to the curvature of the outer circumferential surfaces of both rotating body bearings 111 and 112 (in other words, curvature of the inner wall surfaces of both fixture insertion holes 61 and 81). It is done.

The vane inner circumferential end surface 124, which is a cross section inside the radial direction R of the vane 120, is formed in correspondence with the abutment surfaces 132 and the outer circumferential surfaces of both rotating body bearings 111 and 112, in detail. The vane inner circumferential end face 124 is curved so as to face toward the outside in the radial direction R.

According to this configuration, by the outer circumferential surface and the abutting surface 132 of both rotating body bearings 111 and 112, one sliding surface through which the vane 120 slides is configured, and the vane 120 is axially ( When moving to Z), the vane inner circumferential end face 124 moves in the axial direction Z while sliding relative to the sliding surface. Accordingly, while the movement of the axial direction Z of the vane 120 is smoothly performed, formation of a gap inside the radial direction R of the vane 120 can be suppressed.

In addition, since the vane 120 is sandwiched between the inner circumferential surface 33 of the front cylinder and the abutting surface 132 of the abutting member 130 from the radial direction R, the vane 120 is in the radial direction The positional shift of (R) can be suppressed. In addition, it is possible to suppress the fluid from flowing out from the boundary portion between the vane 120 (the vane outer circumferential end face 123) and the front cylinder inner circumferential surface 33.

Next, with reference to Figs. 2 to 11, the configuration according to suction of the suction fluid into the front compression chamber A4 and discharge of the compressed fluid from the front compression chamber A4 will be described. In addition, for convenience of illustration, the illustration of the front retainer 155 is omitted in FIG. 7, while the front retainer 155 is illustrated in FIGS. 8 and 9. In addition, in FIG. 8, the housing 11 is also shown.

2 to 4, the compressor 10 is provided with a front suction port 140 for sucking suction fluid into the front compression chamber A4. The front suction port 140 is formed in the front cylinder 30, for example, and in detail, the front suction port 140 spans both the front cylinder bottom part 31 and the front cylinder side wall part 32. Is formed. The front suction port 140 opens in the motor chamber A2 and extends in the axial direction Z, and opens toward the front compression chamber A4. The motor chamber A2 and the front compression chamber A4 communicate with each other by the front suction port 140.

In particular, the front suction port 140 communicates with the front compression chamber A4 in a phase where the volume of the front compression chamber A4 is increased, while the front suction port 140 is in a phase where the volume of the front compression chamber A4 is decreased. It is opened at a position not in communication with the compression chamber A4. For example, as shown in FIG. 8, the front suction port 140 is provided on the second front flat surface 72 among the parts defining the front compression chamber A4 on the inner inner surface 33 of the front cylinder. With respect to the direction of rotation M. In this embodiment, the front suction port 140 has an oval shape in cross section, and, for example, compared to a circular shape, the flow path cross-sectional area of the front suction port 140 is large.

3 to 6, the compressor 10 is provided with a plurality of front discharge ports 141 to 143 for discharging compressed fluid compressed in the front compression chamber A4.

The plurality of front discharge ports 141 to 143 are formed at positions opposite to the rotational direction M side of the rotating body 100 than the second front flat surface 72 of the side wall portions 32 of the front cylinder. And are arranged in the main direction.

Specifically, on the curved front cylinder outer circumferential surface 34, a front seat surface 144 recessed from the front cylinder outer circumferential surface 34 is formed. As shown in FIG. 8, the front seat surface 144 is between the front compression chamber A4 and the discharge chamber A1 of the front cylinder outer circumferential surface 34, and the rotating body 100 is larger than the second front flat surface 72. ) Is formed on the part opposite to the rotation direction (M) side. The front seat surface 144 is a flat surface orthogonal to the radial direction R, and extends in the axial direction Z.

Here, the portion between the front seat surface 144 and the front cylinder inner circumferential surface 33 in the front cylinder side wall portion 32 is referred to as a front mounted seat portion 145. That is, it can be said that the front cylinder side wall part 32 is provided with the front attaching seat 145 on which the front seat surface 144 is formed.

As shown in FIG. 8, the thickness of the front left seat 145 differs depending on the main direction, because the front cylinder inner circumferential surface 33 is curved while the front seat surface 144 is a flat surface. In detail, the thickness of the front left surface 145 is thinner than the both ends of the front left surface 144 when viewed from the axial direction Z, as viewed from the axial direction Z.

As shown in FIGS. 5, 6, and 8, a plurality of front discharge ports 141 to 143 are formed on the front seat surface 144 of the seat 145 attached to the front. The plurality of front discharge ports 141 to 143 are first front discharge ports 141 to second front discharge ports 142 to third front discharge ports 143 in order from the second front flat surface 72. It is arranged in the main direction so as to move away. For this reason, the 1st front discharge port 141 is formed in the position closest to the 2nd front flat surface 72 compared with the other front discharge ports 142,143. That is, the second front discharge port 142 and the third front discharge port 143 are farther away from the second front flat surface 72 than the first front discharge port 141 in the main direction. In the present embodiment, when the first front discharge port 141 is considered to correspond to the "first discharge port", the second front discharge port 142 or the third front discharge port 143 is the "second discharge port". Corresponds to

The plurality of front discharge ports 141 to 143 communicate with the front compression chamber A4 and the discharge chamber A1 by penetrating the front-mounted left portion 145 in the radial direction R. As already described, since the thickness of the front attaching left portion 145 differs along the main direction, at least a portion of each of the front discharge ports 141 to 143 is formed at a position where the thickness is relatively different. For this reason, the passage length (in detail, the length of the radial direction R) of at least a part of each front discharge port 141-143 differs depending on the main direction.

In the present embodiment, since the second front discharge port 142 is disposed at the center of the front left surface 144 than the first front discharge port 141, the second front discharge port 142 is the first front discharge. More than the port 141, it is formed in the thin portion of the front-facing seat 145. For this reason, the passage length of the second front discharge port 142 is shorter than the passage length of the first front discharge port 141. That is, the second front discharge port 142 is a thin-walled portion port formed at a location where the thickness of the left portion 145 attached to the front is thinner than the location where the first front discharge port 141 is formed in the left portion 145 attached to the front. Can. Similarly, the first front discharge port 141 may be referred to as a thick rear port formed in a location where the thickness of the left portion 145 attached to the front is thicker than the location where the second front discharge port 142 is formed among the left portion 145 attached to the front. Can.

Incidentally, in this embodiment, the thickness of the first front discharge port 141 and the second front discharge port 142 (in detail, the length of the radial direction R) differs depending on the position in the main direction. In this case, the maximum thickness of the second front discharge port 142 as a thin portion port is thinner than the minimum thickness of the first front discharge port 141 as a thick portion port. That is, in the present embodiment, the maximum thickness of the thin foil port is thinner than the minimum thickness of the thick foil port.

However, not limited to this, in a configuration in which the thickness of the thin portion port or the thickness of the thick portion port is different depending on the position in the main direction, the thickness of the thickest portion of the thin portion port is the thickness of the thickest portion of the thick portion port A thinner configuration may be used. In addition, the thickness of the thinnest portion of the thin portion may be thinner than the thickness of the thinnest portion of the thick portion. Moreover, the structure in which the average thickness of the thin-walled portion port is thinner than that of the thick-walled portion port may be used.

5 and 6, the plurality of front discharge ports 141 to 143 are, for example, circular. The diameter of the first front discharge port 141 is constant regardless of the radial direction (R). That is, the flow path cross-sectional area of the first front discharge port 141 of the present embodiment is constant without changing along the radial direction R. The same applies to the second front discharge port 142 and the third front discharge port 143.

The flow path cross-sectional area of the second front discharge port 142 and the third front discharge port 143 is larger than that of the flow path of the first front discharge port 141. In detail, the diameter of the second front discharge port 142 and the third front discharge port 143 is larger than the diameter of the first front discharge port 141. In addition, in this embodiment, the 2nd front discharge port 142 and the 3rd front discharge port 143 are formed in the same size.

As shown in Fig. 6, the plurality of front discharge ports 141 to 143 are displaced in the axial direction Z along the front fixture edge 73c displaced in the axial direction Z along the main direction, It is arranged in the main direction corresponding to the front fixture edge 73c.

Specifically, a line connecting a plurality of intermediate points of the front fixed body edge 73c and the front rotating body edge 103a is referred to as a front intermediate line La. The front intermediate line La is displaced along the front fixture edge 73c in the axial direction Z along the main direction, and is in a sinusoidal shape when viewed from the outside in the radial direction R in detail.

In this configuration, a line passing between the centers of the front discharge ports 141 to 143 is referred to as a front center line L1. In this case, a plurality of front center lines L1 are arranged on the front intermediate line La side than the front fixed body edge 73c and front rotating body edge 103a, respectively, when viewed from the outside in the radial direction R. The front discharge ports 141 to 143 are arranged. For this reason, in the present embodiment, the plurality of front discharge ports 141 to 143 are arranged while slightly shifting from each other in the axial direction Z. That is, the arrangement direction of the plurality of front discharge ports 141 to 143 is inclined with respect to the main direction (in other words, the rotation direction M). In other words, the arrangement direction and the axial direction Z are not orthogonal, but inclined.

In addition, for convenience of description, in the following description, the arrangement direction of the plurality of front discharge ports 141 to 143 is simply referred to as the "arrangement direction". The arrangement direction is a curve passing between the centers of the front discharge ports 141 to 143, or an approximate straight line of the curve. In this embodiment, since the front fixture edge 73c around the second front flat surface 72 is the outer periphery of the front convex surface 73b, the front center line L1 is the front convex surface 73b It can be said that he is following his outsourcing role.

Incidentally, in the present embodiment, the front center line L1 and the front middle line La coincide substantially. Here, the front center line L1 is disposed on the front intermediate line La side of each of the front fixture edge 73c and the front rotor edge 103a, so that the front center line L1 is the front intermediate line (La).

The size of the first front discharge port 141 is, for example, in a position where the first front discharge port 141 is formed, in the axial direction between the front fixed body edge 73c and the front rotating body edge 103a. It is larger than the distance of (Z). For this reason, the 1st front discharge port 141 overlaps the both sides of the axial direction Z with respect to the front compression chamber A4. In this case, an area facing the front compression chamber A4 among the first front discharge ports 141, specifically, the front fixture edge 73c as viewed from the radial direction R among the first front discharge ports 141 ) And the area between the front rotor edge 103a greatly contributes to the discharge of the compressed fluid. The same is true for the second front discharge port 142 and the third front discharge port 143.

5, 7 to 9, the compressor 10 includes a front valve 150 that blocks the plurality of front discharge ports 141 to 143, and a front retainer 155 that adjusts the opening degree of the front valve 150. ).

The front valve 150 is formed on the front seat surface 144. The front valve 150 is a thin plate shape that can be elastically deformed. In correspondence with the front seat surface 144 being a flat surface, the front valve 150 is formed in a flat shape. Specifically, the front valve 150 is a flat plate formed along the front seat surface 144.

The front valve 150 is provided in both the arrangement direction and the radial direction R from the front base portion 151 and the front base portion 151 extending in the arrangement direction of the plurality of front discharge ports 141 to 143. It has a plurality of front arm portions 152 to 154 extending in an orthogonal direction.

The front base portion 151 is disposed on the side away from the front fixing body 60 than the plurality of front discharge ports 141 to 143. The front base portion 151 is a rectangular shape in which the arrangement direction is a longitudinal direction.

In the front base portion 151, two front attachment holes 151a for attaching the front valve 150 to the front seat surface 144 are formed. The two front attachment holes 151a are formed at both ends of the front base portion 151 in the extension installation direction, and penetrate the front valve 150 in the thickness direction.

5 and 6, on the front seat surface 144, a front bolt hole 144a communicating with the front attachment hole 151a is formed. While the bolt B is inserted into the front attachment hole 151a, the bolt B is screwed into the front bolt hole 144a, so that the front valve 150 is fixed to the front seat surface 144. .

Here, as already described, the arrangement direction of the plurality of front discharge ports 141 to 143 is inclined with respect to the main direction. For this reason, as shown in FIG. 7, the front base part 151 is inclined with respect to the main direction.

5 and 7, the front arm portions 152 to 154 extend from the front base portion 151 toward the front discharge ports 141 to 143. The front arm portions 152 to 154 are arranged in the array direction through the gaps.

The first front arm portion 152 extends from both ends in the longitudinal direction of the front base portion 151 toward the first front discharge port 141 from the ends on the second front flat surface 72 side. . In addition, the first front arm portion 152 has a first front end portion 152a covering the first front discharge port 141. In the present embodiment, the first front end portion 152a has a semicircular shape, and the center of the semicircle is arranged to coincide with the center of the first front discharge port 141.

The second front arm portion 153 extends from the vicinity of the central portion in the longitudinal direction of the front base portion 151 toward the second front discharge port 142. In addition, the second front arm portion 153 has a second front end portion 153a covering the second front discharge port 142. In the present embodiment, the second front end portion 153a is circular, and the center thereof is arranged to coincide with the center of the second front discharge port 142.

The third front arm portion 154 extends from both ends of the front base portion 151 in the longitudinal direction opposite to the second front flat surface 72 side toward the third front discharge port 143. It is done. And the 3rd front arm part 154 has the 3rd front front end part 154a which covers the 3rd front discharge port 143. In the present embodiment, the third front end portion 154a is circular, and the center thereof is arranged to coincide with the center of the third front discharge port 143.

As shown in FIG. 7, the length of each front arm part 152-154 in the extension installation direction is the same. Specifically, the distance from the front base portion 151 to the center of the semicircle of the first front end portion 152a is the first arm length X1, and from the front base portion 151 to the second front end portion 153a. The distance to the center point is the second arm length X2, and the distance from the front base portion 151 to the center point of the third front end portion 154a is the third arm length X3. In this case, each arm length (X1 to X3) is set equally.

In other words, the front valve 150 is attached to the front seat surface 144 (in other words, the front cylinder side wall portion 32) in a state inclined with respect to the main direction so that the respective arm lengths X1 to X3 are the same. It can be said to be.

5 and 9, the front retainer 155 is a plate shape thicker than the front valve 150, and the front valve 150 is interposed between the front retainer 155 and the front seat surface 144. In the fitted state, it is fixed to the front seat surface 144 by a bolt B. The front retainer 155 is the same shape as the front valve 150 when viewed from a direction perpendicular to the front seat surface 144 and overlaps the front valve 150. The portion of the front retainer 155 that overlaps with the front base portion 151 is pressed against the front valve 150 toward the front seat surface 144 by receiving the tightening force of the bolt B. On the other hand, each front arm portion 152 to 154 in the front retainer 155 is such that a portion overlapping the front end portions 152a to 154a in the front retainer 155 is moved away from the front end portions 152a to 154a. The overlapping part is curved. For this reason, each front-end|tip part 152a-154a can rock between the front seat surface 144 and the front retainer 155.

According to this configuration, when the pressure in the front compression chamber A4 exceeds the threshold, the compressed fluid in the front compression chamber A4 pushes out each front end portion 152a to 154a, and each front discharge port 141 to 143). Accordingly, the compressed fluid is discharged to the discharge chamber A1. That is, the front valve 150 opens and closes the front discharge ports 141 to 143.

In this case, the opening angle of each front end portion 152a to 154a is regulated by the front retainer 155. On the other hand, the movement of the compressed fluid from the discharge chamber A1 to the front compression chamber A4 (that is, reverse flow) is suppressed by the front valve 150.

Here, in this embodiment, each arm length X1-X3 is set equally. For this reason, the threshold value of the pressure of the compressed fluid, which is the trigger for opening the front end portions 152a to 154a, is the same or close to each other in each of the front discharge ports 141 to 143.

Next, with reference to Figs. 2 to 4, 10, and 11, a configuration according to suction of suction fluid into the rear compression chamber A5 and discharge of compressed fluid from the rear compression chamber A5 will be described. In addition, for the sake of illustration, the illustration of the rear retainer 175 is omitted in FIG. 10, while the illustration of the rear retainer 175 is illustrated in FIG. 11. In addition, in FIG. 11, the housing 11 is also shown.

2 to 4, the compressor 10 is provided with a rear suction port 160 for sucking the suction fluid into the rear compression chamber A5.

The rear suction port 160 is formed in the front cylinder 30, for example, and is formed in detail over both the front cylinder bottom part 31 and the front cylinder side wall part 32. The rear suction port 160 opens in the motor chamber A2 and extends in the axial direction Z to a position outside the radial direction R with respect to the rear compression chamber A5, and the rear compression chamber (A5). The motor chamber A2 and the rear compression chamber A5 communicate with each other by the rear suction port 160.

In particular, the rear suction port 160 communicates with the rear compression chamber A5 in a phase in which the volume of the rear compression chamber A5 is increased, while the rear in the rear compression chamber A5 is in a phase in which the volume of the rear compression chamber A5 is decreased. It is opened at a position not in communication with the compression chamber A5. For example, as shown in FIG. 11, the rear suction port 160 is provided on the second rear flat surface 92 among the portions partitioning the rear compression chamber A5 on the front cylinder inner circumferential surface 33. With respect to the direction of rotation M. In the present embodiment, the rear suction port 160 has an elliptical cross section, and the flow path cross-sectional area of the rear suction port 160 is larger than that of the circular shape.

The compressor 10 is provided with a plurality of rear discharge ports 161 to 163 for discharging compressed fluid compressed in the rear compression chamber A5.

As shown in FIGS. 10 and 11, the plurality of rear discharge ports 161 to 163 have a rotational direction (M) of the rotating body 100 than the second rear flat surface 92 among the front cylinder side wall portions 32. It is formed at the position opposite to the) side and is arranged in the main direction.

In detail, the rear seat surface 164 which is recessed from the front cylinder outer peripheral surface 34 is formed in the curved front cylinder outer peripheral surface 34. The rear seat surface 164 is located between the rear compression chamber A5 and the discharge chamber A1 among the front cylinder outer circumferential surfaces 34 and rotates the rotating body 100 more than the second rear flat surface 92. It is formed in the part opposite to the direction M side. The rear seat surface 164 is a flat surface orthogonal to the radial direction R, and extends in the axial direction Z.

Here, in the front cylinder side wall portion 32, the portion between the rear seat surface 164 and the front cylinder inner circumferential surface 33 is referred to as a rear seat 165. In other words, it can be said that the front cylinder side wall part 32 is provided with the rear-attached seat part 165 having the rear seat surface 164.

As shown in FIG. 11, the thickness of the rear seat 165 differs along the main direction, and specifically, the thickness of the rear seat 165 is seen from the axial direction Z, and the rear seat surface 164 ), the center side of the rear seat surface 164 is thinner than the both ends.

A plurality of rear discharge ports 161 to 163 are formed on the rear seat surface 164 of the rear seat 165. The plurality of rear discharge ports 161 to 163 are in the order of the first rear discharge port 161 → the second rear discharge port 162 → the third rear discharge port 163, and the second rear flat surface 92. It is arranged in the main direction to move away from. That is, the second rear discharge port 162 and the third rear discharge port 163 are farther away from the second rear flat surface 92 in the main direction than the first rear discharge port 161 is. In this embodiment, when it is considered that the first rear discharge port 161 corresponds to the "first discharge port", the second rear discharge port 162 or the third rear discharge port 163 is the "second discharge port". Corresponds to

The plurality of rear discharge ports 161 to 163 communicate with the rear compression chamber A5 and the discharge chamber A1 by penetrating through the rear left portion 165 in the radial direction R. As already described, since the thickness of the rear-attached seat 165 is different along the main direction, at least a portion of each rear discharge port 161 to 163 is relatively positioned at a position where the thickness of the rear-attached seat 165 is different. Is formed.

In the present embodiment, since the second rear discharge port 162 is disposed at the center of the rear seat surface 164 than the first rear discharge port 161, the second rear discharge port 162 discharges the first rear. More than the port 161, it is formed in the thin part of the seat 165 with a rear. For this reason, the passage length of the second rear discharge port 162 is shorter than the passage length of the first rear discharge port 161. That is, in the present embodiment, it can be said that the second rear discharge port 162 corresponds to the thin portion port, and the first rear discharge port 161 corresponds to the thick portion port.

The shapes of the plurality of rear discharge ports 161 to 163 are the same as the plurality of front discharge ports 141 to 143. For this reason, detailed description of the shape of the plurality of rear discharge ports 161 to 163 is omitted.

The plurality of rear discharge ports 161 to 163 displace in the axial direction Z along the rear fixture edge 93c displaced in the axial direction Z along the main direction, while the rear fixture edges 93c are displaced. Corresponding to it is arranged in the main direction. Specifically, a line connecting a plurality of intermediate points of the rear fixed body edge 93c and the rear rotating body edge 104a is referred to as a rear intermediate line Lb, and the plurality of rear discharge ports 161 to 163 The line passing between the centers is referred to as the rear center line L2. In this case, the plurality of rear discharge ports 161 to 163 are arranged such that the rear center line L2 is disposed on the rear intermediate line Lb side, respectively, than the rear fixed body edge 93c and the rear rotating body edge 104a, respectively. Is arranged. In this embodiment, the rear center line L2 and the rear middle line Lb are almost identical.

10 and 11, the compressor 10 includes a rear valve 170 that blocks a plurality of rear discharge ports 161 to 163, and a rear retainer 175 that adjusts the opening degree of the rear valve 170. It is equipped with.

The rear valve 170 is a thin plate shape elastically deformable, and is formed on the rear seat surface 164. The rear valve 170 is provided in both the arrangement direction and the radial direction R from the rear base portion 171 and the rear base portion 171 extending in the arrangement direction of the plurality of rear discharge ports 161 to 163. It extends in an orthogonal direction, and is also provided with a plurality of rear arm portions 172 to 174 having rear tip portions 172a to 174a. The rear retainer 175 has the same shape as the rear valve 170 when viewed from a direction orthogonal to the rear seat surface 164 and overlaps the rear valve 170.

The specific configuration of the rear valve 170 and the rear retainer 175 is the same as the front valve 150 and the front retainer 155. Specifically, the rear base portion 171 and the rear arm portions 172 to 174 are the same as the front base portion 151 and the front arm portions 152 to 154. For this reason, detailed description of the rear valve 170 and the rear retainer 175 is omitted.

According to this configuration, when the pressure in the rear compression chamber A5 exceeds the threshold, the compressed fluid in the rear compression chamber A5 pushes out each rear tip portion 172a to 174a, and each rear discharge port 161 to 163). Accordingly, the compressed fluid is discharged to the discharge chamber A1. That is, the rear valve 170 opens and closes the rear discharge ports 161 to 163.

Incidentally, in correspondence with the second front flat surface 72 and the second rear flat surface 92 being shifted 180° in the main direction, the front left surface 144 and the rear seat surface 164 are shifted by 180°. , The plurality of front discharge ports 141 to 143 and the plurality of rear discharge ports 161 to 163 are shifted by 180 degrees. In addition, while both the left and right surfaces 144 and 164 are shifted in the axial direction Z, the plurality of front discharge ports 141 to 143 and the plurality of rear discharge ports 161 to 163 are shifted in the axial direction Z. have. For this reason, the front valve 150 and the rear valve 170 are arrange|positioned shifted in the axial direction Z.

Next, using Figs. 12 and 13, the positional relationship between the ports 140 to 143, 160 to 164 in this embodiment and the vanes 120 in the compression chambers A4 and A5 are generated. The volume change to be described will be described in detail.

12 and 13 are exploded views showing a state of the fixed bodies 60 and 80, the rotating body 100, and the vanes 120, and the phases of both of FIGS. 12 and 13 are different from each other. 12 and 13, the ports 140 to 143 and 160 to 164 are schematically shown.

12, the vane 120 is arrange|positioned over both compression chambers A4 and A5. In this case, a part of the vane 120 on the first vane end 121 side enters the front compression chamber A4. Accordingly, the front compression chamber A4 is divided into two with the vane 120 as a border. For convenience of explanation, one front compression chamber A4 is referred to as a first front compression chamber A4a, and the other front compression chamber A4 is referred to as a second front compression chamber A4b. The first front compression chamber (A4a) and the second front compression chamber (A4b) are divided by a contact point between the second front flat surface (72) and the front rotating body surface (103), and a vane (120). It is adjacent in the direction.

While the vane 120 moves from the front suction port 140 to the plurality of front discharge ports 141 to 143, the first front compression chamber A4a communicates with the front suction port 140, while a plurality of It is not in communication with the front discharge ports 141 to 143. The second front compression chamber A4b communicates with the plurality of front discharge ports 141 to 143, but does not communicate with the front suction ports 140.

That is, in most of the rotational phase of the rotating body 100, the vane 120 has a front suction port 140 so that the front suction port 140 and the plurality of front discharge ports 141 to 143 do not communicate with each other. It can also be said that the first front compression chamber A4a communicating with the second front compression chamber A4b communicating with the plurality of front discharge ports 141 to 143 communicates with each other. When the vane 120 passes through the second front flat surface 72 by rotating the rotating body 100 in the rotational direction M, the yarn that has been the first front compression chamber A4a so far is the second front compression chamber. (A4b). Further, a first front compression chamber A4a is newly created. That is, the fluid sucked into the first front compression chamber A4a is compressed in the second front compression chamber A4b and discharged from the second front compression chamber A4b.

Here, as described above, the front curved surface 73 is curved in the axial direction Z to gradually move away from the front rotating surface 103 as it moves away from the second front flat surface 72. For this reason, the distance between the front curved surface 73 and the front rotating body surface 103 is widening as it moves away from the second front flat surface 72. That is, the second front compression chamber A4b (in other words, the front compression chamber A4) is widened in the axial direction Z as it moves away from the second front flat surface 72. For this reason, it can be said that the plurality of front discharge ports 141 to 143 are arranged in order from the narrow position of the front compression chamber A4 to the wide position.

Similarly, since the part of the vane 120 on the second vane end 122 side enters the rear compression chamber A5, the rear compression chamber A5 is divided into two with the vane 120 as a boundary. have. For convenience of explanation, one rear compression chamber A5 is referred to as a first rear compression chamber A5a, and the other rear compression chamber A5 is referred to as a second rear compression chamber A5b. The first rear compression chamber (A5a) and the second rear compression chamber (A5b) are separated by a contact point between the second rear flat surface (92) and the rear rotating surface (104), and the vane (120), It is adjacent in the main direction.

While the vane 120 moves from the rear suction port 160 to the plurality of rear discharge ports 161 to 163, the first rear compression chamber A5a communicates with the rear suction port 160 while the plurality of It is not in communication with the rear discharge ports 161 to 163. The second rear compression chamber A5b communicates with the plurality of rear discharge ports 161 to 163, but does not communicate with the rear suction ports 160.

That is, in most of the rotation phase of the rotating body 100, the vane 120 has a rear suction port 160 so that the rear suction port 160 and the plurality of rear discharge ports 161 to 163 do not communicate with each other. It can also be said that the first rear compression chamber A5a communicating with the second rear compression chamber A5b communicating with the plurality of rear discharge ports 161 to 163 is separated.

Here, as already described, the rear curved surface 93 is curved in the axial direction Z so as to gradually move away from the rear rotating surface 104 as it moves away from the second rear flat surface 92. For this reason, as the distance from the second rear flat surface 92 increases, the distance between the rear curved surface 93 and the rear rotating surface 104 increases. That is, the second rear compression chamber A5b (in other words, the rear compression chamber A5) is widened in the axial direction Z as it moves away from the second rear flat surface 92. For this reason, it can be said that the plurality of rear discharge ports 161 to 163 are arranged in order from the narrow position of the rear compression chamber A5 to the wide position.

Then, when the rotating shaft 12 is rotated by the electric motor 13, the rotating body 100 and the vane 120 rotate accordingly. In addition, in FIG. 12, the rotating body 100 and the vane 120 move in the direction below the ground.

Accordingly, as shown in Fig. 13, when the vanes 120 move in the axial direction Z (left and right directions of the ground), volume changes occur in both compression chambers A4 and A5.

Specifically, in the first front compression chamber A4a, suction of the suction fluid from the front suction port 140 is performed by increasing the volume of the first front compression chamber A4a, while the second front compression chamber A4a ( In A4b), the suction fluid is compressed by reducing the volume of the second front compression chamber A4b. And, when the pressure in the second front compression chamber (A4b) exceeds the threshold, the front valve 150 is opened, so that the compressed fluid compressed in the second front compression chamber (A4b) has a plurality of front discharge ports ( 141 to 143) to the discharge chamber (A1).

Likewise, in the first rear compression chamber A5a, suction of the suction fluid from the rear suction port 160 is performed by increasing the volume, while in the second rear compression chamber A5b, the compression of the fluid is reduced. Is done. Then, when the pressure in the second rear compression chamber (A5b) exceeds a threshold value, the rear valve 170 opens, and the compressed fluid compressed in the second rear compression chamber (A5b) has a plurality of rear discharge ports (161). -163) to the discharge chamber A1.

As described above, by rotating the rotating body 100 and the vane 120, in both compression chambers A4 and A5, a cycle of suction and compression with 720° (for two rotations of the rotating body 100) as one cycle The operation is repeated.

Here, for convenience of explanation, the two front compression chambers A4a and A4b are distinguished and described. Note that, in the front compression chamber A4, a cycle operation with 720° as one cycle is performed. (A4a) may be referred to as a front compression chamber (A4) having a phase of 0° to 360°, and the second front compression chamber (A4b) may be referred to as a front compression chamber (A4) having a phase of 360° to 720°. Can. That is, the space divided by the front fixed body surface 70, the front rotating body surface 103, the front circumferential bearing 111, and the front cylinder inner circumferential surface 33 has a phase that is 0 by the vane 120. It can be said that the front compression chamber A4 of ° to 360° and the front compression chamber A4 of 360° to 720° are phased. In other words, the vane 120, in the state of dividing the space into a first chamber where fluid is sucked and a second chamber where fluid is compressed, is accompanied by rotation of the rotating body 100 and the vane 120, It can be said that the volume change of the first and second rooms (detailed increase in volume for the first room and reduced volume for the second room) occurs. The same applies to the first rear compression chamber A5a and the second rear compression chamber A5b.

According to the present embodiment described above, the following operational effects are exhibited. In addition, for convenience of explanation, only the front side will be described below, but the same effect is exerted on the rear side.

(1-1) The compressor 10 is a rotating shaft 12 and a rotating body 100 that rotates with rotation of the rotating shaft 12, and front rotation intersecting the axial direction Z of the rotating shaft 12 A rotating body 100 having a body surface 103 and a front fixing body 60 having a front fixing body surface 70 facing the axial direction Z on the front rotating body surface 103 are provided. The front fixed body surface 70 has both sides of the second front flat surface 72 as a fixed body flat surface contacting the front rotating body surface 103 and the main direction of the rotation shaft 12 with respect to the second front flat surface 72 It includes a pair of front curved surface 73 formed on. The front curved surface 73 is curved in the axial direction Z so as to gradually move away from the front rotating surface 103 as it moves away from the second front flat surface 72 in the main direction.

The compressor 10 includes a front cylinder side wall portion 32 having a front cylinder inner circumferential surface 33 as a front cylinder side wall portion 32 as a cylinder portion accommodating the rotating body 100 and the front fixture 60. do. In addition, the compressor 10 includes a vane 120 inserted into the vane groove 125 formed in the rotating body 100, a front compression chamber A4, and a discharge chamber A1. The vane 120 rotates while moving in the axial direction Z as the rotating body 100 rotates. The front compression chamber A4 is divided by the front rotating body surface 103, the front fixing body surface 70, and the front cylinder inner peripheral surface 33. In the front compression chamber A4, the volume change occurs by the vane 120, so that the fluid is sucked and compressed. The discharge chamber A1 is disposed outside the radial direction R with respect to the front compression chamber A4 through the front cylinder side wall portion 32.

In this configuration, the compressor 10 penetrates the front cylinder side wall portion 32 in the radial direction R, thereby providing a plurality of front discharge ports 141 communicating the front compression chamber A4 and the discharge chamber A1. ~143). The plurality of front discharge ports 141 to 143 are located in a position opposite to the rotational direction M of the rotating body 100 than the second front flat surface 72 of the front cylinder side wall portion 32 is the main Arranged in the direction. Then, the compressor 10 is provided with a front valve 150 that blocks the plurality of front discharge ports 141 to 143.

According to this structure, the discharge chamber A1 is disposed outside the radial direction R with respect to the front compression chamber A4 through the front cylinder side wall portion 32. Then, a plurality of front discharge ports 141 to 143 are not formed in the front fixing body 60, but are formed in the front cylinder side wall portion 32. Accordingly, the passage length of each front discharge port 141 to 143 is likely to be shortened. Therefore, the loss (hereinafter, referred to as "usage") accompanying the movement of the compressed fluid from the front compression chamber A4 to the discharge chamber A1 can be reduced.

Specifically, in order to discharge the compressed fluid in the front compression chamber A4 partitioned by the front rotating body surface 103, the front fixing body surface 70, and the front cylinder inner peripheral surface 33, for example, the front fixing body ( It is conceivable to form the discharge port to penetrate 60) in the axial direction Z. In this case, the length of the discharge port tends to be long. In particular, since the second front flat surface 72 or its periphery corresponds to the thick portion in the front fixture 60, the length of the discharge port passing through the thick portion is likely to be long, and the passage length is increased. easy.

At this point, in this embodiment, a plurality of front discharge ports 141 to 143 are arranged in the main direction, and are formed in the front cylinder side wall portion 32, and the front cylinder side wall portion 32 is radially ( R). Thereby, the passage length of each front discharge port 141-143 can be made into the thickness of the side wall part 32 of the front cylinder. For this reason, the passage length of each front discharge port 141-143 can be shortened. Therefore, reduction in use can be achieved.

Further, a plurality of front discharge ports 141 to 143 are formed. For this reason, compared with a configuration in which only one discharge port is formed, for example, the cross-sectional area of the flow path of the discharge port in the front compression chamber A4 can be secured. Accordingly, it is possible to suppress, for example, overcompression, in which the pressure in the front compression chamber A4 is excessively high due to the narrow cross-sectional area of the discharge port.

In view of the above, it is possible to suppress overcompression and reduce use.

Particularly, in the present embodiment, the plurality of front discharge ports 141 to 143 are arranged in the main direction of the front fixture 60, which has a longer margin than the radial direction R of the front fixture 60. have. For this reason, the space and size of each front discharge port 141-143 can be adjusted relatively freely. Accordingly, for example, in consideration of overcompression and usage, a plurality of front discharge ports 141 to 143 can be set to appropriate positions or sizes.

(1-2) The front rotating body surface 103 is a flat surface orthogonal to the axial direction Z. The plurality of front discharge ports 141 to 143 include a first front discharge port 141 and a third front formed at a position farther away from the second front flat surface 72 than the first front discharge port 141 in the main direction. A discharge port 143 is provided. The passage cross-sectional area of the third front discharge port 143 is larger than the passage cross-sectional area of the first front discharge port 141.

While the front rotating surface 103 is a flat surface orthogonal to the axial direction Z, the front curved surface 73 gradually moves away from the front rotating surface 103 as it moves away from the second front flat surface 72. It is curved in the axial direction Z so as to lose. For this reason, the front compression chamber A4 is widened in the axial direction Z as it moves away from the second front flat surface 72. For this reason, the third front discharge port 143 formed at a position farther from the second front flat surface 72 than the first front discharge port 141 has a front compression chamber than the first front discharge port 141. (A4) is present in a wide location. In addition, the cross-sectional area of the flow passage of the third front discharge port 143 is larger than the cross-sectional area of the flow passage of the first front discharge port 141. For this reason, through the third front discharge port 143, a large amount of compressed fluid can be flowed into the discharge chamber A1. Therefore, suppression of overcompression can be achieved.

In addition, the first front discharge port 141 is formed on the second front flat surface 72 side than the third front discharge port 143. For this reason, in the front compression chamber A4, the compressed fluid in the portion on the side of the rotational direction M (hereinafter referred to as "the discharging end portion") of the third front discharge port 143 is first front discharge. Through the port 141, it is discharged to the discharge chamber A1. Thereby, it can suppress that the compressed fluid in the discharge end part becomes a loss.

In particular, the front compression chamber A4 is narrowed in the axial direction Z as it faces the second front flat surface 72. For this reason, the ratio occupied by the volume of the discharge end portion to the entire volume of the front compression chamber A4 is relatively small. For this reason, even if the flow path cross-sectional area of the first front discharge port 141 is smaller than the flow path cross-sectional area of the third front discharge port 143, it is possible to suppress the occurrence of overcompression. In addition, for convenience of explanation, the relationship between the first front discharge port 141 and the third front discharge port 143 has been described, but the relationship between the first front discharge port 141 and the second front discharge port 142 is described. The same is also true.

(1-3) The front cylinder side wall portion 32 is a cylindrical shape having a curved front cylinder outer circumferential surface 34. The front cylinder outer circumferential surface 34 is formed with a front seat surface 144 of a flat surface, which is cut from the front cylinder outer circumferential surface 34 and orthogonal to the radial direction R. The plurality of front discharge ports 141 to 143 are formed on the front seat surface 144.

According to this configuration, it is not necessary to curve the front valve 150 along the outer circumferential surface 34 of the front cylinder, for example. Accordingly, complexity of the shape of the front valve 150 can be suppressed.

(1-4) The front cylinder side wall portion 32 is provided with a front-mounted left portion 145 that is a portion between the front left surface 144 and the front cylinder inner circumferential surface 33. Since the front seat surface 144 is a flat surface, the thickness of the front seat 145 is different along the main direction.

In this configuration, the plurality of front discharge ports 141 to 143 are formed at positions where the thicknesses of the front attachment left portions 145 are relatively different from each other, and the first front discharge port 141 as a thick rear port and the thin foil portion A second front discharge port 142 as a port is provided. The passage cross-sectional area of the second front discharge port 142 is larger than the passage cross-sectional area of the first front discharge port 141.

According to this configuration, the cross-sectional area of the flow passage of the second front discharge port 142 is larger than the cross-sectional area of the flow passage of the first front discharge port 141. For this reason, since the flow rate of the compressed fluid discharged through the second front discharge port 142 can be increased, overcompression can be suppressed. In addition, the side of the second front discharge port 142 is formed in the thin portion of the left portion 145 attached to the front than the first front discharge port 141. For this reason, the passage length of the second front discharge port 142 is shorter than the passage length of the first front discharge port 141. Therefore, even if the cross-sectional area of the flow path of the second front discharge port 142 is increased, usage is unlikely to occur. Therefore, overcompression can be more suitably suppressed while suppressing the use.

(1-5) The front rotating body surface 103 is a flat surface orthogonal to the axial direction Z. For this reason, the front rotating body edge 103a which is the outer peripheral edge of the front rotating body surface 103 does not displace in the axial direction Z irrespective of a main direction. On the other hand, the front fixture edge 73c, which is the outer periphery of the front curved surface 73, is displaced in the axial direction Z along the main direction. The plurality of front discharge ports 141 to 143 are arranged in the main direction while displaced in the axial direction Z along the front fixture edge 73c.

Among the plurality of front discharge ports 141 to 143, the compressed fluid is unlikely to flow to a portion of the front fixed body facing the outer peripheral surface 62 and a portion of the ring facing the ring outer peripheral surface 105. For this reason, an area facing the front compression chamber A4 among the plurality of front discharge ports 141 to 143 contributes to the discharge of the compressed fluid. Here, the area of the front discharge ports 141 to 143 facing the front compression chamber A4 is a front fixed body edge 73c and a front in a plurality of front discharge ports 141 to 143. It is an area between the outer periphery of the rotating body surface 103 (front rotating body edge 103a).

In this respect, in this embodiment, in correspondence with the front fixture edge 73c being displaced in the axial direction Z along the main direction, a plurality of front discharge ports 141 to 143 are provided with the front fixture edge ( 73c) in the axial direction (Z). Accordingly, in the plurality of front discharge ports 141 to 143, a region contributing to discharge of the compressed fluid, in other words, a region facing the front compression chamber A4 can be secured widely. Therefore, overcompression can be suppressed.

Here, when attention is paid to the viewpoint of suppressing overcompression, for example, the plurality of front discharge ports 141 to 143 can be increased without displacing the plurality of front discharge ports 141 to 143 in the axial direction Z. You can also think. However, in this case, the use becomes large.

According to this point and this embodiment, several front discharge ports 141-143 are arrange|positioned, shifting in the axial direction Z. Accordingly, the area contributing to the discharge of the compressed fluid can be enlarged, and overcompression can be suppressed without excessively increasing the plurality of front discharge ports 141 to 143.

(1-6) The line connecting the centers of the plurality of front discharge ports 141 to 143 is referred to as the front center line L1. The front center line L1 is seen from the outside in the radial direction R, and the front fixture edge 73c and the front rotor edge 103a, respectively, than the front fixture edge 73c and the front rotor edge 103a, respectively. ) Is arranged on the front middle line (La) side.

According to such a structure, the centers of each of the front discharge ports 141 to 143 are arranged on the front middle line La side. For this reason, the area facing the front compression chamber A4 among the plurality of front discharge ports 141 to 143 can be secured wide.

(1-7) The front valve 150 includes an arrangement direction and a radial direction (from the front base portion 151 and the front base portion 151 extending in the arrangement direction of the plurality of front discharge ports 141 to 143 ( As a plurality of front arm portions 152 to 154 extending in a direction orthogonal to both sides of R), a plurality of front arm portions 152 to 154 covering a plurality of front discharge ports 141 to 143 are provided. . Each arm length X1 to X3, which is the length of each front arm portion 152 to 154 in the extended installation direction, is the same.

According to this structure, each arm length (X1-X3) becomes the same. For this reason, it is possible to achieve uniformity in the pressure at which the plurality of front discharge ports 141 to 143 covered by the plurality of front arm portions 152 to 154 are opened.

In particular, in the present embodiment, in response to the arrangement of the plurality of front discharge ports 141 to 143 arranged in the main direction while being displaced in the axial direction Z, the front base portion 151 includes a plurality of front discharge ports ( 141 to 143). Thereby, the length of the extending installation direction of each front arm part 152-154 can be made equal. That is, in a configuration in which the plurality of front discharge ports 141 to 143 are displaced in the axial direction Z, it is possible to achieve uniform pressure in which the plurality of front discharge ports 141 to 143 are opened.

(Second embodiment)

In this embodiment, the number of vanes 120 is different from the first embodiment. This point will be explained.

As shown in FIGS. 14-16, the compressor 10 of this embodiment is provided with a plurality of sets of vanes 120 and vane grooves 125, and in detail three (three sets). The plurality of vane grooves 125 are arranged at equal intervals in the circumferential direction, and in detail, they are arranged at positions deviated from each other by 120 degrees. In response to this, a plurality of vanes 120 are arranged at equal intervals in the main direction.

Further, in correspondence with the plurality of vanes 120 and vane grooves 125 being formed, a plurality of abutting members 190 and concave tanks 191 are also formed. The abutting member 190 and the concave tank 191 are respectively formed inside the radial direction R of the plurality of vanes 120, and are arranged at equal intervals in the main direction. In addition, the abutting member 190 and the concave tank 191 of this embodiment are formed only in the portion corresponding to the ring portion 102, and extends in the axial direction Z from both rotating body surfaces 103 and 104. There is not.

According to this configuration, as shown in FIG. 15, the front compression chamber A4 is composed of three chambers by three vanes 120, that is, the first front compression chamber A4a and the second front compression chamber A4b. And, a third front compression chamber (A4c).

Each of the front compression chambers A4a to A4c is formed over an angle range of 120°, respectively. That is, each of the front compression chambers A4a to A4c extends in the main direction, and the extension installation length (in detail, the length in the main direction) is a length corresponding to an angular range of 120°.

At least a portion of the first front compression chamber (A4a) is disposed in the rotational direction (M) side with respect to the second front flat surface (72), and space inside the radial direction (R) of the front suction port (201) Includes all or part of.

The 2nd front compression chamber A4b is arrange|positioned in the rotation direction M side than the 1st front compression chamber A4a. At least a part of the second front compression chamber A4b is disposed on the side opposite to the rotation direction M side with respect to the second front flat surface 72, and the radial direction R of the front discharge ports 141 to 143 ) Includes some or all of the space inside.

The third front compression chamber A4c is disposed between the first front compression chamber A4a and the second front compression chamber A4b in the main direction. The third front compression chamber A4c is located in the rotational direction M with respect to the first front compression chamber A4a, and is disposed on the side opposite to the rotational direction M with respect to the second front compression chamber A4b. It is done. If the first front compression chamber (A4a) deviates from the inside of the radial direction (R) of the front suction port (201) by rotating the rotating body (100) toward the rotational direction (M), so far the first front compression chamber (A4a) ) Was the third front compression chamber A4c. At this time, the yarn that has been the third front compression chamber A4c so far becomes the second front compression chamber A4b. Further, a first front compression chamber A4a is newly created. That is, the fluid sucked into the first front compression chamber A4a is compressed in the third front compression chamber A4c and the second front compression chamber A4b, and is discharged from the second front compression chamber A4b.

The front suction port 201 of this embodiment extends in the main direction corresponding to the front cylinder side wall portion 32, and is formed in an arc shape as viewed from the axial direction Z. The front suction port 201 has a front suction opening 201a opened to the front compression chamber A4. The front suction opening 201a is a rotational direction M from a position corresponding to the central portion of the second front flat surface 72 among the parts defining the front compression chamber A4 on the inner circumferential surface 33 of the front cylinder. ).

In this embodiment, the length in the main direction of the front suction port 201 (in other words, an angular range) and the length in the main direction of the front suction opening 201a are set to be the same. The length of each of the front suction ports 201 and the front suction openings 201a in the main direction may be substantially the same as the extended installation length (length in the main direction) of the front compression chambers A4a to A4c, for example. That is, the front suction opening 201a is in the main direction by a length substantially equal to the interval of each vane 120 from a position corresponding to the central portion of the second front flat surface 72 of the inner inner surface 33 of the front cylinder. May be extended.

In addition, when the angular position of the central portion of the second front flat surface 72 is 0°, the front suction opening 201a of the present embodiment is at least in the rotational direction (M) side of the second front flat surface 72. It can be said that it is formed over the range from the end to the angular position of 120° in the rotation direction M.

When one of the plurality of vanes 120 is in contact with the second front flat surface 72, the vanes 120 do not enter the front compression chamber A4. In this case, the spaces (specifically, the first front compression chamber A4a) and the second front compression chamber (A4b) on both sides (in the circumferential direction) of the vane 120 contacting the second front flat surface 72 )) is divided by the contact point between the front rotating surface 103 and the second front flat surface 72, and is sealed by the contact point.

The front suction port 201 and the front discharge ports 141 to 143 are mutually circumferentially in the main direction through a portion outside the radial direction R of the second front flat surface 72 of the side wall portions 32 of the front cylinder. It is formed in a separated position. Accordingly, in the main direction, between the space inside the radial direction R of the front suction ports 201 and the space inside the radial direction R of the front discharge ports 141 to 143, the front rotation There is a contact point between the body surface 103 and the second front flat surface 72. Accordingly, regardless of the positions of the plurality of vanes 120, both spaces (the space inside the radial direction R of the front suction port 201 and the radial direction R of the front discharge ports 141-143) The space on the inside) is sealed by the contact point.

That is, the first front compression chamber A4a may be in communication with the front suction ports 201, while being configured not to communicate with the front discharge ports 141 to 143.

The second front compression chamber A4b is a chamber communicating with the front discharge ports 141 to 143. However, in the present embodiment, the length of the second front compression chamber A4b in the main direction is longer than the length of the second front flat surface 72 in the main direction. For this reason, depending on the phase, the second front compression chamber A4b is both inside the radial direction R of the front suction port 201 and inside the radial direction R of the front discharge ports 141 to 143. It may be placed across. Even in this case, the inside of the radial direction R of the front suction port 201 and the diameter of the front discharge ports 141 to 143, due to the contact point between the front rotating surface 103 and the second front flat surface 72, Since the inside of the direction R is sealed, the communication between the front suction port 201 and the front discharge ports 141 to 143 is restricted.

The third front compression chamber A4c is a chamber configured not to communicate with the front suction port 201, and from the state of not communicating with the front discharge ports 141 to 143 with the rotation of the rotating body 100, It shifts to the state which communicates with the front discharge ports 141-143.

As shown in FIG. 16, similar to the front compression chamber A4, the rear compression chamber A5 includes three vanes 120, the first rear compression chamber A5a, and the first rear compression chamber A5a. ) Is disposed between the second rear compression chamber A5b disposed on the rotational direction M and the first rear compression chamber A5a and the second rear compression chamber A5b in the main direction. It is divided into a third rear compression chamber (A5c). The first rear compression chamber (A5a), the second rear compression chamber (A5b), and the third rear compression chamber (A5c) are the first front compression chamber (A4a), the second front compression chamber (A4b), and the third Since it is the same as the front compression chamber A4c, detailed description is omitted.

In addition, the rear suction port 202 of the present embodiment is formed in an arc shape extending in the circumferential direction, similarly to the front suction port 201, and is arranged opposite to the front suction port 201 by inserting the rotating shaft 12. It is done. The rear suction port 202 has a rear suction opening 202a opened to the rear compression chamber A5. The rear suction opening 202a is formed in a portion of the front cylinder inner peripheral surface 33 that divides the rear compression chamber A5.

As shown in FIG. 16, in this embodiment, the rear suction port 202 and the rear suction opening 202a are located at the front discharge port (from the position corresponding to the central portion in the main direction of the second rear flat surface 92). 141 to 143), as long as it does not interfere with the front valve 150 and the front retainer 155, it is sufficient to extend in the rotational direction M.

However, the present invention is not limited to this, and the lengths in the main direction of the rear suction port 202 and the rear suction opening 202a may be the same as the lengths in the main direction of the front suction port 201 and the front suction opening 201a. . In this case, the length of the axial direction Z of the front valve 150 or the like is shortened so that the rear suction port 202 and the rear suction opening 202a and the front discharge ports 141 to 143 do not interfere, or The positions of the front discharge ports 141 to 143 may be shifted, or the angle range of the second front flat surface 72 may be narrowed.

Next, the compression operation of the compressor 10 of the present embodiment will be described.

17 and 18, when the rotating shaft 12 is rotated by the electric motor 13, the rotating body 100 rotates accordingly. Accordingly, the plurality of vanes 120 rotate while moving in the axial direction Z (left and right directions) along both fixed body surfaces 70 and 90 while maintaining their relative positions. Accordingly, a volume change occurs in each of the front compression chambers A4a to A4c and each of the rear compression chambers A5a to A5c, whereby fluid is sucked, compressed, or expanded.

Specifically, in the first front compression chamber A4a, suction volume is suctioned from the front suction port 201 by increasing the volume of the first front compression chamber A4a. In this case, since the front suction opening 201a extends in the rotational direction M from a position corresponding to the central portion of the second front flat surface 72, the front suction opening 201a is the first front compression chamber ( The area opened toward A4a) (hereinafter, simply referred to as "opening area") gradually increases. Accordingly, the suction amount sucked from the front suction port 201 to the first front compression chamber A4a increases with the volume of the first front compression chamber A4a.

On the other hand, in the second front compression chamber A4b, specifically, in the second front compression chamber A4b, the part on the side opposite to the rotation direction M side than the second front flat surface 72, and the third front The compression chamber A4c is a chamber whose volume decreases. For this reason, in the part opposite to the rotation direction M side than the 2nd front flat surface 72 in the 3rd front compression chamber A4c and the 2nd front compression chamber A4b, suction fluid is compressed. This is done. Specifically, the suction fluid is compressed in the third front compression chamber A4c, and the fluid compressed in the third front compression chamber A4c is the second front flat surface in the second front compression chamber A4b ( It is further compressed in the portion opposite to the rotation direction M side than 72).

Then, when the pressure in the portion of the second front compression chamber A4b opposite to the rotational direction M side than the second front flat surface 72 exceeds the threshold, the front valve 150 is turned on. Is open. Therefore, the compressed fluid compressed in the second front compression chamber A4b flows through the plurality of front discharge ports 141 to 143 to the discharge chamber A1. The same is true for the rear compression chamber A5.

As described above, by rotating the rotating body 100 and the vane 120, in both compression chambers A4 and A5, a cycle operation of suction and compression with 480° as one cycle is repeatedly performed. Specifically, in both compression chambers A4 and A5, suction or expansion of suction fluid is performed over a phase of 0° to 240°, and compression of suction fluid over a phase of 240° to 480° is performed.

For example, if the angular position of the central portion of the second front flat surface 72 is 0° and the first vane 120 is disposed in the central part, the first vane 120 is the angular position of 0°. Until the angular position of from 240° is reached, suction of the suction fluid is performed in the front compression chamber A4 opposite to the rotation direction M side with respect to the first vane 120.

In particular, the front suction opening 201a is formed over a range from at least the second front flat surface 72 end portion in the rotational direction M to an angular position of 120° in the rotational direction M. have. For this reason, the front compression chamber A4 (specifically, the first front compression chamber A4a and the second) through the front suction opening 201a until the first vane 120 reaches an angular position of 240°. The suction fluid is sucked into the front compression chamber A4b. Accordingly, expansion of the fluid in the front compression chamber A4 can be avoided, and efficiency can be improved.

And, until the second vane 120 on the side opposite to the rotational direction M than the first vane 120 reaches the angular position of 360° from the angular position of 120°, the second vane ( With respect to 120, in the front compression chamber A4 (specifically, the second front compression chamber A4b and the third front compression chamber A4c) on the rotational direction M side, the suction fluid is compressed.

Here, for convenience of explanation, each of the front compression chambers A4a to A4c has been separately described, and each of the front compression chambers A4a to A4c can be said to be a plurality of front compression chambers A4 having different phases. That is, it may be said that the space partitioned by using the front fixed body surface 70 and the front rotating body surface 103 is divided into a plurality of front compression chambers A4 having different phases by a plurality of vanes 120. Can.

According to the present embodiment described above, the following operational effects are exhibited.

(2-1) Three vanes 120 and vane grooves 125 are formed at equal intervals in the main direction. The compression chambers A4 and A5 include first compression chambers A4a and A5a communicating with the suction ports 201 and 202 by a plurality of vanes 120, and discharge ports 141 to 143 and 161 to 163. A second compression chamber (A4b, A5b) communicating with the third compression chamber (A4c) arranged between the first compression chamber (A4a, A5a) and the second compression chamber (A4b, A5b) in the main direction. A5c). In the first compression chambers A4a and A5a, suction of suction fluid is performed as the rotating body 100 rotates. On the other hand, in the third compression chambers A4c and A5c, the suction fluid is compressed with the rotation of the rotating body 100, and in the second compression chambers A4b and A5b, the third compression chambers A4c and A5c In the compressed fluid, further compression is performed.

According to this configuration, the fluid is sucked and compressed in a state in which the compression chambers A4 and A5 are divided into three chambers by the plurality of vanes 120. As a result, the volume per one thread is reduced, while the entire volume of the compressor 10 can be secured, so that the volume of three times the volume reduced yarn can be secured, so that the overall volume of the compressor 10 can be improved. .

In addition, for example, compared with the case where there is only one vane 120, in this embodiment, it is re-ejected from the discharge ports 141 to 143, 161 to 163 communicating with the second compression chambers A4b and A5b. The loss due to can be reduced.

More specifically, in the second compression chambers A4b and A5b, when the next compression is started after the previous compression is finished, it is caused by the previous compression through the discharge ports 141 to 143 and 161 to 163. The compressed fluid is sprayed back into the second compression chambers A4b and A5b in the initial stage of compression. Accordingly, losses occur. The loss tends to increase as the pressure difference between the initial stage and the final stage of compression in the second compression chambers A4b and A5b increases.

Here, if the third compression chambers A4c and A5c are not formed as in the first embodiment, the pressure in the second compression chambers A4b and A5b in the initial stage of compression is equal to the pressure of the suction fluid. Since it becomes almost the same, the pressure change of the second compression chambers A4b and A5b is large. For this reason, loss tends to increase. In addition, the inflow destination of the compressed fluid ejected from the discharge ports 141 to 143 and 161 to 163 is a space in which the suction fluid is present and the open space (second compression chambers A4b and A5b in the initial stage of compression) Therefore, loss occurs due to a decrease in the circulating flow rate.

According to this point and the present embodiment, since the third compression chambers A4c and A5c are compressed before the second compression chambers A4b and A5b, the second compression chambers A4b and A5b are formed. The pressure in the initial stage of compression is not the pressure of the suction fluid, but the pressure of the fluid compressed in the third compression chambers A4c and A5c. Thereby, the pressure difference between the initial stage and the final stage in the second compression chambers A4b and A5b can be reduced, and the loss can be reduced. In addition, the inflow destination of the compressed fluid ejected from the discharge ports 141 to 143 and 161 to 163 becomes the second compression chambers A4b and A5b that are not in communication with the suction ports 201 and 202. It is possible to suppress the loss caused by the decrease in the flow rate.

Each of the above-described embodiments may be changed as follows. In addition, each of the above-described embodiments and the following individual examples may be combined with each other within a range that is not technically contradictory. In the following, for convenience of explanation, the front side (for example, the plurality of front discharge ports 141 to 143, etc.) is mainly described, but the rear side (for example, the plurality of rear discharge ports 161 to 163), etc. ) Can be changed similarly.

○ In the present embodiment, the accommodation chambers for accommodating both the fixed bodies 60 and 80 and the rotating body 100 are partitioned by the front cylinder 30 and the rear plate 40, but are not limited thereto. The specific configuration for dividing the accommodation room is arbitrary.

For example, the compressor 10 may be provided with a plate-shaped front plate instead of the front cylinder 30 and a bottom-shaped cylindrical rear cylinder instead of the rear plate 40. In this case, the rear cylinder and the front plate are brought into contact with each other, so that the accommodating chambers accommodating both the fixed bodies 60 and 80 and the rotating body 100 are partitioned. In this distinct example, the side wall portion of the rear cylinder corresponds to the "cylinder portion", and the inner peripheral surface of the rear cylinder corresponds to the "cylinder inner peripheral surface".

In addition, the compressor 10 may be provided with two cylinders in the shape of a cylinder, and a configuration in which the accommodating chambers accommodating both the fixed bodies 60 and 80 and the rotating body 100 are partitioned by both may be employed. In this case, the side wall portions of both cylinders correspond to the "cylinder portion", and the inner circumferential surfaces of both cylinders correspond to the "cylinder inner circumferential surface". That is, the "cylinder portion" and the "cylinder inner peripheral surface" may be composed of one member or may be composed of a plurality of members. Further, the rear plate 40 may be omitted, and the accommodation chamber may be divided by the front cylinder 30 and the rear housing bottom 23.

○ The compression chambers A4 and A5 should be at least divided by the rotating body surfaces 103 and 104, the fixed body surfaces 70 and 90, and the front cylinder inner circumferential surface 33, and divide the compression chambers A4 and A5. The other side used is arbitrary. For example, the compression chambers A4 and A5 may be partitioned by the outer circumferential surface of the cylindrical portion 101 instead of the outer circumferential surfaces of the rotating body bearings 111 and 112.

○ The number of front discharge ports is arbitrary if they are plural, for example, two or more, or four or more.

○ The sizes of the plurality of front discharge ports 141 to 143 are arbitrary.

For example, the diameter of the first front discharge port 141 is the distance between the front fixed body edge 73c and the front rotating body edge 103a at the place where the first front discharge port 141 is formed. It may be as follows. In other words, the discharge port does not need to overlap the front compression chamber A4 so that the discharge port faces the front compression chamber A4 in the axial direction Z. .

For example, among the plurality of front discharge ports 141 to 143, the flow path cross-sectional area of the third front discharge port 143 at a position farthest from the second front flat surface 72 is the second front flat surface ( It may be larger than the flow path cross-sectional area of the first front discharge port 141 close to 72). That is, a configuration in which a plurality of front discharge ports are formed is a first front discharge port and a second front discharge port located at a position farther away from the second front flat surface 72 than the first front discharge port, and the flow path cross-sectional area The second front discharge port may be larger than the first front discharge port.

For example, even if the size (for example, the port diameter) of the second front discharge port 142 formed in the thin portion of the front attaching left portion 145 is smaller than the size of the first front discharge port 141 formed in the thick portion, It may be good or the same.

For example, the sizes of the plurality of front discharge ports 141 to 143 may be the same.

○ The shape of the plurality of front discharge ports 141 to 143 is not limited to a circular shape and is arbitrary. For example, the plurality of front discharge ports 141 to 143 may have an elliptical shape or other shapes. Further, the shapes of the plurality of front discharge ports 141 to 143 may be different from each other. For example, the first front discharge port 141 may have an elliptical shape with the main direction in the longitudinal direction, and the third front discharge port 143 may be circular.

○ The plurality of front discharge ports 141 to 143 may have a shape gradually expanded from the inside of the radial direction R toward the outside of the radial direction R, or vice versa. In this case, the cross-sectional area of the flow path changes along the radial direction R.

In this configuration, the minimum flow path cross-sectional area of the second front discharge port 142 may be larger than the minimum flow path cross-sectional area of the first front discharge port 141. Similarly, the minimum flow path cross-sectional area of the third front discharge port 143 may be larger than the minimum flow path cross-sectional area of the first front discharge port 141.

○ The front seat surface 144 may be omitted. In this case, the front valve 150 and the front retainer 155 may be curved along the front cylinder outer peripheral surface 34. However, it is preferable to form the front seat surface 144, noting that the complexity of the shape of the front valve 150 can be suppressed.

○ The plurality of front discharge ports 141 to 143 may be arranged in the main direction without shifting in the axial direction Z.

○ Each arm length (X1 to X3) may be different. In this case, the front valve 150 may be attached along the main direction so that the extension installation direction of the front base portion 151 coincides with the main direction.

In this distinct example, the front retainer 155 may be configured such that the front base portion 151 and a portion of each front arm portions 152 to 154 are pressed. In this case, the lengths of the swing portions of the front arm portions 152 to 154 that are not pressed against the front retainer 155 are the same in the front retainers 155 so that the lengths of the swing portions of the front arm portions 152 to 154 are the same. The pressing area for each front arm portion 152 to 154 may be adjusted. Thereby, even when the arm lengths X1 to X3 are different, the opening pressure of each front discharge port 141 to 143 can be made uniform.

○ When the front base portion 151 extends in the main direction, the width of the front base portion 151 (length in the shorter direction, in other words, the shaft, so that the length of each front arm portion 152 to 154 is the same The length of the direction Z) may be different depending on the main direction.

○ Both the fixed bodies 60 and 80 were of the same shape, but are not limited to this, for example, the front fixed body 60 may have a large diameter with respect to the rear fixed body 80, and vice versa. In this case, the front cylinder inner circumferential surface 33 may have a stepped shape in accordance with the shapes of both the fixed bodies 60 and 80, and the front cylinder for receiving the front fixed body 60 and the rear fixed body 80 are accommodated. The rear cylinder to be said may be formed separately. That is, the volumes of both compression chambers A4 and A5 may be the same or different.

○ The curvature of the contact surface 132 and the vane inner circumferential end face 124 is arbitrary, and may be, for example, the same as the curvature of the outer circumferential surface of the rotating shaft 12 or the curvature of the outer circumferential surface of the tube portion 101.

○ The contact member 130 and the concave tank 131 are omitted, and the outer peripheral surface of the cylinder portion 101 may be in contact with the vane 120.

○ Even if the vane inner circumferential end face 124 is curved to be convex toward the inside of the radial direction R, and the abutment surface 132 where the vane inner circumferential end face 124 abuts, bends so that it faces toward the inside of the radial direction R good.

○ The contact surface 132 and the outer peripheral surfaces of the rotating body bearings 111 and 112 do not have to be continuous.

○ The outer circumferential surfaces of the abutting surfaces 132 and the rotating body bearings 111 and 112 need not be uniform. For example, the abutment surface 132 is disposed inside the radial direction R than the outer circumferential surfaces of the rotating body bearings 111 and 112, and even if the vane inner circumferential end surface 124 abuts the abutting surface 132, good. In this case, the vane 120 may be slid in the axial direction Z while striking both of the abutment surface 132 and the outer peripheral surface of the cylinder 101, for example.

In such a configuration, the rotating body bearings 111 and 112 need only be formed at a position deviating from the moving range (in other words, the swinging range) of the vane 120. Accordingly, it is possible to suppress the vane 120 from interfering with the rotating body bearings 111 and 112.

The compressor 10 of the embodiment was a single stage two cylinder in which two compression chambers A4 and A5 were formed, but is not limited thereto.

For example, as shown in FIG. 19, the compressor 10 may be one cylinder. Specifically, while maintaining the configuration related to the front compression chamber A4, the rear fixture 80, the rear rotating body bearing 112, the rear compression chamber A5, the rear suction port 160, and the rear discharge port ( 161 to 163) may be omitted. In this case, the first front flat surface 71 may be omitted from the front fixed body surface 70.

In this configuration, for example, the vane 120 may be formed with an elastic pressing portion 300 that elastically presses the front fixing body 60. The elastic pressing portion 300 may be supported by, for example, an elastic pressing support portion 301 formed on the cylindrical portion 101 so as to rotate with rotation of the rotating body 100. The elastic pressing support portion 301 is, for example, formed at an end portion on the rear side of the cylindrical portion 101, and has a plate shape protruding outward in the radial direction R from the cylindrical portion 101. Accordingly, as the rotation body 100 rotates, the vane 120 rotates while moving in the axial direction Z while maintaining the state where the first vane end 121 and the front fixture surface 70 come into contact with each other. . In addition, in this separate example, as shown in FIG. 19, the abutting member 130 may be extended toward the rear thrust bearing 114 side.

In addition, for example, the front fixing body 60, the front rotating body bearing 111, and the front compression chamber A4 may be omitted while maintaining the configuration related to the rear compression chamber A5. That is, the number of fixed body and rotating body bearings may be one. In addition, the number of fixed body and rotating body bearings may be three or more.

○ The front fixing body 60 and the front cylinder 30 may be integrally formed, or the rear fixing body 80 and the rear plate 40 may be integrally formed.

○ The compressor 10 may be configured to perform two-stage compression. For example, the compressor 10 may be configured such that the compressed fluid compressed in the front compression chamber A4 is introduced into the rear compression chamber A5 and further compressed in the rear compression chamber A5.

○ The fixed body insertion holes 61 and 81 do not need to be through holes when the rotary shaft 12 is inserted, but may be non-perforated.

○ The specific configuration of the rotating body bearings 111 and 112 is arbitrary, and may be, for example, a coated bearing composed of a coating layer formed on the inner wall surfaces of the fixed body insertion holes 61 and 81. In this case, the rotating bearings 111 and 112, which are coated bearings, support the rotating body 100 against the inner wall surfaces of the fixed body insertion holes 61 and 81, thereby supporting the rotating body 100 to the fixed bodies 60 and 80. ).

Incidentally, when the rotating body bearings 111 and 112 are coated bearings, the compression chambers A4 and A5 are not partitioned by the outer circumferential surfaces of the rotating body bearings 111 and 112, but are provided on the outer circumferential surface of the cylindrical portion 101. Is partitioned by. Moreover, the rotating body bearings 111 and 112 may be formed on the entire inner wall surface of the fixed body insertion holes 61 and 81, or may be formed on a part of them.

In addition, the abutting member 130 may be formed to have the same length as the concave tank 131 and may be fitted into the concave tank 131. In this case, the vane 120 may move in the axial direction Z while the vane inner peripheral end face 124 and the abutting surface 132 slide.

○ The fixed body abutting surface which abuts on the front rotating body surface 103 on the front fixed body surface 70 is not limited to a flat surface, and may be a curved surface. In short, the front fixed body surface 70 only needs to have a fixed body abutting surface that abuts the front rotating body surface 103. The same is true for the rear fixture surface 90.

○ The rotating body 100 may be inclined with respect to the axial direction Z. In this case, both rotating body surfaces 103 and 104 may be orthogonal to the axial direction Z or may be inclined.

○ The position or shape of the suction port is arbitrary. In short, the configuration for inhaling the suction fluid in both compression chambers A4 and A5 is arbitrary.

○ At least one of the thrust bearings 113 and 114 may be omitted. That is, the thrust bearings 113 and 114 are not essential.

○ The first vane end portion 121 and the front fixture surface 70 are not limited to a configuration that abuts from the inner circumferential end to the outer circumferential end, but may be configured to abut over a portion of the radial direction R. Moreover, the 1st vane end part 121 and the front fixed body surface 70 are not limited to the structure which abuts over the whole circumference, and may be a structure which abuts over some angular range. The same is true for the second vane end 122 and the rear fixture surface 90.

○ The discharge chamber A1 need not have a cylindrical shape with the axial direction Z in the axial direction. For example, the discharge chamber A1 may be shaped like a C-shape when viewed from the axial direction Z. In other words, the discharge chamber A1 may be formed in at least part of the main direction.

○ The number of vanes 120 is arbitrary, for example, a plurality may be used. In addition, the main position of the vane 120 is arbitrary.

○ The shape of the vane 120 and the vane groove 125 is not limited to that of each embodiment, but is arbitrary as long as the vane 120 can rotate while moving in the axial direction Z. For example, the vane may have a fan shape. Further, the vane may be configured to rotate while moving in the axial direction Z like a pendulum with a predetermined location as the center.

○ The specific shape of the housing 11 is arbitrary.

○ The electric motor 13 and the inverter 14 may be omitted. That is, the electric motor 13 and the inverter 14 are not essential for the compressor 10. In this case, the rotating shaft 12 may be rotated by, for example, belt driving.

○ The compressor 10 may be used in addition to an air conditioning device. For example, the compressor 10 may be used to supply compressed air to a fuel cell mounted on a fuel cell vehicle.

○ The fluid to be compressed by the compressor 10 is not limited to a refrigerant containing oil, and is arbitrary.

○ The mounting target of the compressor 10 is not limited to a vehicle and is arbitrary.

Next, a suitable example that can be grasped from the above-described embodiment and a separate example is described below.

(a) The rotating body includes a cylinder through which the rotary shaft is inserted, and the compressor is a contact member formed on the outer circumferential surface of the cylinder and extending in the axial direction, and the abutting member fitted into the recess, The contact member may be provided with an abutting surface having an abutting surface that abuts on the inner circumferential end surface of the vane, and the abutting surface may be configured to constitute an inner circumferential end surface of the vane groove.

(b) the fixed body flat surface in contact with the rotating body surface is a second fixed body flat surface, and the fixed body surface is further, a first fixed body formed at a position spaced apart in the axial direction with respect to the rotating body surface A flat surface is provided, and the second fixed body flat surface is formed at a position shifted in a main direction with respect to the first fixed body flat surface, and the curved surface includes the first fixed body flat surface and the second fixed body. The flat surface is connected, and the curved surface may be configured to be curved in the axial direction so as to gradually approach the rotating body surface as the first fixed body flat surface is directed to the second fixed body flat surface. .

Claims (9)

The axis of rotation,
A rotating body rotating along with the rotation of the rotating shaft, the rotating body having a rotating body surface intersecting the axial direction of the rotating shaft,
A fixed body having a fixed body surface opposite to the axial direction on the rotating body surface, wherein the fixed body surface is a fixed body flat surface contacting the rotating body surface and a main body of the rotating shaft with respect to the fixed body flat surface. The fixed body includes a pair of curved surfaces formed on both sides, and the pair of curved surfaces are curved in the axial direction so as to gradually move away from the rotating body surface as they move away from the stationary flat surface in the main direction. Wow,
A cylinder portion accommodating the rotating body and the fixed body, the cylinder portion having an inner circumferential surface of the cylinder;
A vane that rotates while moving in the axial direction with rotation of the rotating body while being inserted into the vane groove formed in the rotating body,
The compression chamber, which is a chamber partitioned by the rotating body surface, the fixed body surface, and the inner circumferential surface of the cylinder, wherein the fluid is sucked and compressed by volume change of the compression chamber by the vanes. ,
A discharge chamber disposed in the radial direction outside of the rotating shaft with respect to the compression chamber through the cylinder portion, the discharge chamber in which compressed fluid compressed in the compression chamber is present;
A plurality of discharge ports communicating the compression chamber and the discharge chamber by penetrating the cylinder portion in the radial direction of the rotating shaft, in a position opposite to the rotational direction side of the rotating body than the flat surface of the fixed body among the cylinder portions. , The plurality of discharge ports arranged in the main direction,
And a valve blocking the plurality of discharge ports. According to claim 1,
The rotating body surface is a flat surface orthogonal to the axial direction,
The plurality of discharge ports,
A first discharge port,
A compressor including a second discharge port having a larger flow path cross-sectional area than the first discharge port as a second discharge port formed at a position farther away from the stationary flat surface than the first discharge port in the main direction. The method according to claim 1 or 2,
The cylinder portion is a cylindrical shape having a curved cylinder outer peripheral surface,
On the outer circumferential surface of the cylinder, a left surface of a flat surface that is pitted from the outer circumferential surface of the cylinder and orthogonal to the radial direction is formed.
The plurality of discharge ports and the valve are formed on the seat surface, the compressor. According to claim 3,
The cylinder portion has an attachment left portion that is a portion between the seat surface and the inner circumferential surface of the cylinder, and the thickness of the attachment left portion is different depending on the main direction,
The plurality of discharge ports include a thick portion port and a thin portion port, which are formed at positions having relatively different thicknesses among the attached left portions,
A compressor having a flow path cross-sectional area of the six-thickness port larger than that of the six-thickness port. The method according to claim 1 or 2,
The rotating body surface is a flat surface orthogonal to the axial direction,
The fixed edge, which is the outer periphery of the curved surface, is displaced in the axial direction along the main direction,
The plurality of discharge ports are arranged in the main direction while being displaced in the axial direction along the edge of the stationary body, viewed from the outside in the radial direction. The method of claim 5,
When viewed from the outside in the radial direction, a center line connecting the centers of the plurality of discharge ports is provided between the rotating body edge and the fixed body edge, respectively, than the rotating body edge and the fixed body edge, which are outer circumferences of the rotating body surface. Compressor, arranged on the middle line side. The method of claim 5,
The valve,
A base portion extending in an arrangement direction of the plurality of discharge ports,
A plurality of arm portions extending from the base portion in a direction perpendicular to both of the array direction and the radial direction, the plurality of arm portions covering the plurality of discharge ports,
The length of each arm portion in the extension installation direction is the same, the compressor. The method according to claim 1 or 2,
The rotating body has a cylindrical portion through which the rotating shaft is inserted,
The compressor,
A concave tank formed on the outer circumferential surface of the tube portion and extending in the axial direction
As the abutment member fitted to the concave tank, the abutment member having an abutment surface abutting the inner circumferential end face of the vane,
A compressor in which the abutting surface constitutes an inner circumferential end face of the vane groove. The method according to claim 1 or 2,
The flat surface of the fixed body contacting the surface of the rotating body is a flat surface of the second fixed body,
The fixed body surface further includes a first fixed body flat surface formed at a position spaced apart in the axial direction with respect to the rotating body surface,
The second fixture flat surface is formed at a position shifted in the main direction with respect to the first fixture flat surface,
The curved surface is to connect the first fixed body flat surface and the second fixed body flat surface, and the curved surface is directed to the second fixed body flat surface from the first fixed body flat surface, The compressor which curves in the said axial direction so that it may gradually approach the surface of the rotating body.

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