JP2020105983A - Compressor - Google Patents

Abstract

To provide a compressor capable of suppressing excessive compression and reducing a dead volume.SOLUTION: A compressor 10 includes a rotary shaft 12, a body of rotation 100 adapted to be rotated in association with the rotation of the rotary shaft 12, and having a front body-of-rotation surface 103 intersecting with the rotary shaft 12 in an axial direction Z, and a front fixed body 60 having a front fixed body surface 70 opposed to the front body-of-rotation surface 103 in the axial direction Z. Herein, the compressor 10 further includes a plurality of front discharge ports 141-143 passing through a front cylinder side wall part 32 in a radial direction R to communicate a front compression chamber A4 with a discharge chamber A1, and a front valve for blocking the plurality of front discharge ports 141-143.SELECTED DRAWING: Figure 4

Description

The present invention relates to a compressor.

For example, as shown in Patent Document 1, a rotating shaft, a rotor as a rotating body in which a plurality of slit grooves are formed, a plurality of vanes fitted in the slit grooves, and a plurality of vanes as the vanes are rotationally displaced. There is known a compressor including a side plate having a cam surface for displacing the vane in the axial direction, a compression chamber, and a discharge chamber. In Patent Document 1, the discharge chamber and the compression chamber are opposed to each other in the axial direction of the rotary shaft via a side plate as a fixed body, and the side plate has a plurality of discharge ports penetrating in the axial direction of the rotary shaft. It is described that a plurality of discharge refrigerant passages are formed. The plurality of discharge refrigerant passages are formed in a portion of the side plate that corresponds to the top-side flat surface portion that is the thickest portion. Further, Patent Document 1 describes that a discharge valve that opens and closes the openings of a plurality of discharge refrigerant passages is provided on the back side of the cam surface of the side plate.

JP, 2018-44483, A

As described above, in the configuration in which the compressed fluid is discharged using the discharge port that penetrates the fixed body in the axial direction, the passage length of the discharge port tends to be long. Therefore, there is a concern that the dead volume, which is a loss caused when the compressed fluid flows through the discharge port, becomes large. In particular, when the discharge port is provided in the thick portion of the fixed body as shown in Patent Document 1, the passage length of the discharge port tends to be long, and the above-mentioned inconvenience is likely to occur.

Further, generally, when the flow passage cross-sectional area of the discharge port is large, the dead volume tends to increase. However, if the flow passage cross-sectional area of the discharge port is excessively small, overcompression may occur in which the pressure inside the compression chamber becomes excessively high.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a compressor capable of suppressing overcompression and reducing dead volume.

A compressor that achieves the above object is a rotating shaft, which rotates with the rotation of the rotating shaft, and has a rotating body having a rotating body surface that intersects the axial direction of the rotating shaft, the rotating body surface, and the rotating body surface. A fixed body surface facing in the axial direction, the fixed body flat surface that abuts the rotary body surface, and the fixed body flat surface that is provided on both sides of the fixed body flat surface in the circumferential direction of the rotary shaft. A fixed body having the fixed body surface including a pair of curved surfaces curved in the axial direction so as to be gradually separated from the rotary body surface as the circumferential body moves away, and the rotary body and the fixed body are accommodated. A cylinder portion having a cylinder inner peripheral surface, a vane that rotates while moving in the axial direction with the rotation of the rotating body while being inserted into a vane groove formed in the rotating body, A chamber defined by a body surface, the fixed body surface and the cylinder inner peripheral surface, in which a volume change is caused by the vanes to suck and compress a fluid, and a compression chamber through the cylinder portion. On the other hand, the discharge chamber, which is arranged on the outer side in the radial direction of the rotary shaft, in which the compressed fluid compressed in the compression chamber exists, and the compression chamber and the compression chamber by penetrating the cylinder portion in the radial direction of the rotary shaft, A plurality of discharge ports arranged in the circumferential direction at a position of the cylinder portion opposite to the rotation direction side of the rotating body with respect to the flat surface of the fixed body; And a valve that closes the plurality of discharge ports.

According to this structure, the discharge chamber is arranged radially outside the compression chamber via the cylinder portion, and the plurality of discharge ports are formed in the cylinder portion, not in the fixed body. This tends to shorten the passage length of each discharge port. Therefore, it is possible to reduce the dead volume which is a loss due to the movement of the compressed fluid from the compression chamber to the discharge chamber.

In addition, since a plurality of discharge ports are provided, it is possible to secure a wider flow passage cross-sectional area as compared with a configuration in which only one discharge port is provided. As a result, it is possible to suppress overcompression in which the pressure in the compression chamber becomes excessively high due to the narrow flow passage cross-sectional area of the discharge port. From the above, it is possible to suppress overcompression and reduce dead volume.

In the compressor, the rotary body surface is a flat surface orthogonal to the axial direction, and the plurality of discharge ports are a first discharge port and the fixed body flat surface from the first discharge port. A second discharge port, which is provided at a position separated in the circumferential direction and has a larger flow passage cross-sectional area than the first discharge port, may be included.

According to such a configuration, the rotating body surface is a flat surface orthogonal to the axial direction of the rotating shaft, while the curved surface is curved in the axial direction so as to gradually separate from the rotating body surface as it moves away from the fixed body flat surface. Therefore, the compression chamber becomes wider in the axial direction as it goes away from the flat surface of the fixed body. For this reason, the second discharge port provided at a position farther from the flat surface of the fixed body than the first discharge port exists at a location where the compression chamber is wider than that of the first discharge port. Since the flow passage cross-sectional area of the second discharge port is larger than the flow passage cross-sectional area of the first discharge port, a large amount of compressed fluid can flow into the discharge chamber via the second discharge port. Therefore, it is possible to more appropriately suppress the overcompression.

In addition, since the first discharge port is provided on the flat surface side of the fixed body with respect to the second discharge port, the compressed fluid in the portion on the rotation direction side of the second discharge port in the compression chamber is discharged from the first discharge port. It is discharged to the discharge chamber via. Accordingly, it is possible to suppress the loss of the compressed fluid in the portion of the compression chamber on the rotation direction side of the second discharge port.

In particular, since the compression chamber becomes narrower in the axial direction toward the flat surface of the fixed body, the volume of the portion on the rotation direction side of the second discharge port in the entire volume of the compression chamber is relatively small. .. Therefore, even if the flow passage cross-sectional area of the first discharge port is smaller than the flow passage cross-sectional area of the second discharge port, overcompression can be suppressed.

In the compressor, the cylinder portion is a cylinder having a curved cylinder outer peripheral surface, and the cylinder outer peripheral surface has a flat seat surface recessed from the cylinder outer peripheral surface and orthogonal to the radial direction. Preferably, the plurality of discharge ports and the valves are provided on the seat surface.

With this configuration, it is not necessary to bend the valve along the outer peripheral surface of the cylinder. This can prevent the valve from becoming complicated in shape.
In the compressor, the cylinder portion has a mounting seat portion that is a portion between the seat surface and the cylinder inner peripheral surface, and the thickness of the mounting seat portion varies depending on the circumferential direction. The plurality of discharge ports include a thick part port and a thin part port provided at positions where the thickness is relatively different in the mounting seat part, and the flow passage cross-sectional area of the thin part port is It may be larger than the flow passage cross-sectional area of the thick portion port.

With such a configuration, since the flow passage cross-sectional area of the thin portion port is larger than the flow passage cross sectional area of the thick portion port, the flow rate of the compressed fluid discharged through the thin portion port can be increased, Compression can be suppressed. Further, since the thin portion port is provided in the thinner portion than the thick portion port, the passage length of the thin portion port is shorter than the passage length of the thick portion port. Therefore, even if the flow passage cross-sectional area of the thin portion port is increased, dead volume is unlikely to occur. Therefore, it is possible to suppress overcompression more preferably while suppressing the dead volume.

In the compressor, the rotor surface is a flat surface orthogonal to the axial direction, and the fixed body edge that is the outer peripheral edge of the curved surface is displaced in the axial direction according to the circumferential direction. The plurality of discharge ports may be arranged in the circumferential direction while being displaced in the axial direction along the fixed body edge when viewed from the outside in the radial direction.

According to this configuration, the plurality of discharge ports are axially displaced along the fixed body edge in correspondence with the axial displacement of the fixed body edge in the circumferential direction. As a result, it is possible to secure a wide area facing the compression chamber, which is an area that contributes to the discharge of the compressed fluid, in the plurality of discharge ports. Therefore, overcompression can be suppressed more preferably.

With respect to the compressor, as viewed from the outside in the radial direction, the center line connecting the centers of the plurality of discharge ports has a rotating body edge that is more than the rotating body edge and the fixed body edge that are the outer peripheral edges of the rotating body surface. It may be arranged near the intermediate line with the edge of the fixed body.

With this configuration, the centers of the plurality of discharge ports are arranged closer to the intermediate line, so that it is possible to secure a large area of the plurality of discharge ports facing the compression chamber.
In the compressor, the valve is provided with a base portion extending in an arrangement direction of the plurality of discharge ports, and extending from the base portion in a direction orthogonal to both the arrangement direction and the radial direction, and the plurality of discharges are provided. A plurality of arm portions covering the port may be provided, and the lengths of the respective arm portions in the extending direction may be the same.

According to this configuration, since the lengths of the respective arm portions in the extending direction are the same, it is possible to make the pressure for opening the plurality of discharge ports covered by the plurality of arm portions uniform. it can.

In particular, according to this configuration, the base portion extends in the arrangement direction of the plurality of discharge ports corresponding to the arrangement of the plurality of discharge ports in the circumferential direction while being displaced in the axial direction. As a result, the lengths of the arm portions in the extending direction can be made the same. That is, in a configuration in which the plurality of discharge ports are displaced in the axial direction, it is possible to make the pressure at which the plurality of discharge ports are opened uniform.

According to the present invention, it is possible to suppress overcompression and reduce dead volume.

Sectional drawing which shows the outline|summary of the compressor of 1st Embodiment. The exploded perspective view of main composition. FIG. 3 is an exploded perspective view of the main configuration viewed from the side opposite to FIG. 2. The elements on larger scale of FIG. The disassembled perspective view of a front cylinder, a front valve, and a front retainer. The side view of the front cylinder which shows a some front discharge port. The side view of the front cylinder which shows a front valve. FIG. 8 is a sectional view taken along line 8-8 of FIG. 7. 9 is a sectional view taken along line 9-9 of FIG. 7. The side view of the front cylinder which shows a rear valve. 11 is a sectional view taken along line 11-11 of FIG. FIG. 3 is a development view showing the states of both fixed bodies and vanes in a certain phase. FIG. 13 is a development view showing the states of both fixed bodies and vanes in a different phase from FIG. 12. The disassembled perspective view which shows the main structures of 2nd Embodiment. Sectional drawing which shows typically the relationship between a some vane and a front fixed body. Sectional drawing which shows typically the relationship between a some vane and a rear fixed body. The development view which shows both fixed bodies, a rotating body, and a vane typically. FIG. 18 is a development view schematically showing both fixed bodies, rotating bodies, and vanes in a different phase from FIG. 17. Sectional drawing which shows the compressor of another example typically.

(First embodiment)
Hereinafter, a first embodiment of the compressor will be described with reference to the drawings. The compressor of the present embodiment is for a vehicle, for example, and is mounted on a vehicle for use. 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.

For convenience of illustration, the rotary shaft 12 is shown in a side view in FIG. 1, the valves 150 and 170 and the retainers 155 and 175 are omitted in FIGS. 2 and 3, and one of the vanes 120 is shown in FIG. The part is shown broken away.

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

The housing 11 has, for example, a tubular shape as a whole, and has a suction port 11a through which a suction fluid from the outside is sucked and a discharge port 11b through which a compressed fluid is discharged. The rotary shaft 12, the electric motor 13, the inverter 14, the front cylinder 30, the rear plate 40, both fixed bodies 60 and 80, and the rotary body 100 are housed in the housing 11.

The housing 11 includes a front housing 21, a rear housing 22, and an inverter cover 25.
The front housing 21 has a bottomed tubular shape and opens toward the rear housing 22. The suction port 11a is provided, for example, at a position closer to the bottom than the opening end of the side wall of the front housing 21. However, the position of the suction port 11a is arbitrary.

The rear housing 22 has a bottomed tubular shape having a rear housing bottom portion 23 and a rear housing side wall portion 24 standing upright from the rear housing bottom portion 23 toward the front housing 21. The rear housing 22 opens toward the front housing 21. The discharge port 11b is provided in the rear housing side wall portion 24. However, the position of the ejection port 11b is arbitrary.

The front housing 21 and the rear housing 22 are unitized with their openings facing each other.
The inverter cover 25 is arranged on the side opposite to the rear housing 22 side with respect to the front housing 21. The inverter cover 25 is fixed to the front housing 21 in a state of being butted against the bottom portion of the front housing 21.

The inverter 14 is housed in the inverter cover 25. The inverter 14 drives the electric motor 13.
As shown in FIG. 1, the front cylinder 30 cooperates with the rear plate 40 to accommodate both the fixed bodies 60 and 80 and the rotating body 100. The front cylinder 30 has a bottomed cylindrical shape formed smaller than the rear housing 22, and opens toward the rear housing bottom portion 23.

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

As shown in FIGS. 1 and 2, the front cylinder bottom portion 31 has a step shape in the axial direction Z, and the first bottom portion 31a disposed on the center side and the rotary shaft 12 with respect to the first bottom portion 31a. And a second bottom portion 31b arranged outside the first bottom portion 31a in the radial direction R and closer to the rear housing bottom portion 23 than the first bottom portion 31a. A front insertion hole 31c into which the rotary shaft 12 can be inserted is formed in the first bottom portion 31a, and the rotary shaft 12 is inserted into the front insertion hole 31c.

As shown in FIG. 1, the front cylinder side wall portion 32 is inserted inside the rear housing 22. The front cylinder side wall portion 32 has a front cylinder inner peripheral surface 33 which is an inner peripheral surface, and a front cylinder outer peripheral surface 34 which is an outer peripheral surface arranged on the side opposite to the front cylinder inner peripheral 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 is in contact with the inner peripheral surface of the rear housing side wall portion 24 in the radial direction R.

In the present embodiment, a discharge recess 35 for partitioning the discharge chamber A1 is formed on the outer peripheral surface 34 of the front cylinder. The discharge recess 35 is formed between both ends of the front cylinder outer peripheral surface 34 in the axial direction Z, and is recessed toward the inner side in the radial direction R. The discharge chamber 35 in which the compressed fluid exists is defined by the discharge recess 35 and the rear housing side wall 24. The discharge chamber A1 in the present embodiment is formed in a cylindrical shape with the axial direction Z as 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.

The front cylinder 30 is provided with a bulging portion 36 that projects outward in the radial direction R of the rotating shaft 12. The bulging portion 36 is provided at a position extending over both the base cylinder side of the front cylinder bottom portion 31 and the front cylinder side wall portion 32 (the front cylinder bottom portion 31 side). The bulging portion 36 bulges outward from the outer peripheral surface 34 of the front cylinder in the radial direction R. The front housing 21 and the rear housing 22 are unitized with the bulging portion 36 interposed therebetween. The displacement of the front cylinder 30 in the axial direction Z is restricted by the housings 21 and 22.

As shown in FIG. 1, in the present embodiment, the motor chamber A2 is partitioned by the front housing 21 and the front cylinder bottom portion 31, and the electric motor 13 is housed in the motor chamber A2. The electric motor 13 is supplied with drive power from the inverter 14 to rotate the rotary shaft 12 in a direction indicated by an arrow M, specifically, in a clockwise direction when the two fixed bodies 60 and 80 are viewed from the electric motor 13. Let

Incidentally, since the suction port 11a is provided in the front housing 21 that defines the motor chamber A2, the suction fluid sucked from the suction port 11a is sucked into the motor chamber A2 in the housing 11. That is, the suction fluid exists in the motor chamber A2. In other words, the motor chamber A2 can be said to be a suction chamber into which the suction fluid is sucked.

In the compressor 10 of the present embodiment, the inverter 14, the electric motor 13, the front fixed body 60, the rotating body 100, and the rear fixed body 80 are arranged in order in the axial direction Z. However, the position of each of these components is arbitrary, and for example, the inverter 14 may be arranged outside the electric motor 13 in the radial direction R of the rotary shaft 12.

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

A rear plate insertion hole 41, through which the rotary shaft 12 is inserted, is formed in the center of the rear plate 40. In this embodiment, the rear plate insertion hole 41 is formed to have the same size as the rotary shaft 12. However, the invention is not limited to this, and the rear plate insertion hole 41 may be larger than the rotary shaft 12.

The front cylinder 30 and the rear plate 40 are assembled so that a front end portion of the front cylinder side wall portion 32 is brought into abutment with the rear plate 40, and the rear plate 40 closes an opening portion of the front cylinder 30.

More specifically, a recess 42 is formed in the rear plate 40 at a location facing the front end portion of the front cylinder side wall portion 32 in the axial direction Z. The recess 42 is formed over the entire circumference. The front cylinder 30 and the rear plate 40 are attached to each other with the front end of the front cylinder side wall portion 32 fitted in the recess 42.

By the way, the rear plate 40 is sandwiched between the front cylinder 30 supported by the housing 11 and the rear housing bottom portion 23 which is a part of the housing 11. Thereby, the rear plate 40 is supported by the housing 11. If the rear plate 40 is supported by the housing 11, its specific support mode is arbitrary.

The rear plate 40 has a first plate surface 43 and a second plate surface 44 as plate surfaces orthogonal to the axial direction Z. The first plate surface 43 is arranged 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 the present embodiment, the first plate surface 43 is smaller than the second plate surface 44 because of the formation of the depression 42.

In the present specification, the term “opposing” includes a mode in which they face each other through a gap and a mode in which they are in contact with each other, as long as there is no special explanation, within a technically consistent range. For example, the second plate surface 44 and the rear housing bottom portion 23 may be separated from each other or may be in contact with each other. Further, “opposing” includes a mode in which a part of the two surfaces are in contact with each other and the other parts are separated from each other.

As shown in FIG. 1, the compressor 10 includes two radial bearings 51 and 53 that rotatably support the rotary shaft 12 with respect to the housing 11.
The front radial bearing 51 of the radial bearings 51 and 53 is attached to a boss portion 52 provided at the bottom of the front housing 21. The boss portion 52 has a ring shape protruding from the bottom portion of the front housing 21. The front radial bearing 51 is arranged inside the radial direction R of the rotary shaft 12 with respect to the boss portion 52, and rotatably supports the first end, which is one of the both ends of the rotary shaft 12. ing.

Of the two radial bearings 51 and 53, the rear radial bearing 53 is attached to a radial housing recess 54 formed in the rear plate 40. The radial accommodating recesses 54 are formed in a portion of the inner wall surface of the rear plate insertion hole 41 closer to the second plate surface 44 than the first plate surface 43 and a peripheral edge portion of the rear plate insertion hole 41 in the second plate surface 44. There is. The radial accommodating recess 54 is open toward both the inner side in the radial direction R and the rear housing bottom 23 side. The rear radial bearing 53 is arranged in the radial accommodating recess 54, and rotatably supports a second end of the rotary shaft 12 opposite to the first end.

As shown in FIG. 1, a space is formed by the front cylinder 30 and the rear plate 40, and both fixed bodies 60 and 80 and the rotating body 100 are housed in the space. In detail, both fixed bodies 60 and 80 are spaced apart in the axial direction Z and face each other, and rotate between both fixed bodies 60 and 80 and between both fixed bodies 60 and 80 and the rotary shaft 12. The body 100 is placed.

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

Both fixed bodies 60 and 80 will be described.
As shown in FIGS. 1 to 3, the front fixing body 60 disposed on the electric motor 13 side of the two fixing bodies 60 and 80 is, for example, ring-shaped (in the present embodiment, annular), and includes the rotary shaft 12 Has a front fixed body insertion hole 61 in which is inserted. In the present embodiment, the front fixed body insertion hole 61 is a through hole that penetrates in the axial direction Z. The front fixed body 60 is arranged in the front cylinder 30 with the rotary shaft 12 inserted in the front fixed body insertion hole 61.

The front fixed body 60 has a front cylinder inner peripheral surface 33 and a front fixed body outer peripheral surface 62 that faces the radial direction R. In the present embodiment, the outer peripheral surface 62 of the front fixed body and the inner peripheral surface 33 of the front cylinder are in contact with each other, and the front fixed body 60 is supported by the front cylinder 30 by the contact. However, the invention is not limited to this, and the front cylinder inner peripheral surface 33 and the front fixed body outer peripheral surface 62 may be separated from each other.

The front fixed body 60 includes a front rear surface 63 that faces the front cylinder bottom portion 31 in the axial direction Z. The front back surface 63 and the front cylinder bottom portion 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 opposite to the front back surface 63. The front fixed body surface 70 has a ring shape, and has an annular shape in the present embodiment.

As shown in FIG. 3, the front fixed body surface 70 connects the first front flat surface 71 and the second front flat surface 72 intersecting the axial direction Z (orthogonal in the present embodiment) to the front flat surfaces 71 and 72. And a pair of front curved surfaces 73 as curved surfaces.

As shown in FIG. 4, both front flat surfaces 71, 72 are displaced in the axial direction Z. Specifically, the second front flat surface 72 is arranged closer to the rear fixed body 80 (in other words, the front rotary body surface 103) than the first front flat surface 71. The front rotator surface 103 will be described later.

Both front flat surfaces 71, 72 are arranged apart from each other in the circumferential direction of the front fixed body 60, and for example, both are offset by 180°. In the present embodiment, both front flat surfaces 71, 72 are fan-shaped. In the following description, the circumferential positions of both fixed bodies 60 and 80 are also referred to as angular positions.

Each of the pair of front curved surfaces 73 has a fan shape. As shown in FIG. 3, the pair of front curved surfaces 73 are arranged to face each other in a direction orthogonal to both the axial direction Z and the facing directions of the front flat surfaces 71 and 72. Both front curved surfaces 73 have the same shape.

The pair of front curved surfaces 73 connects the front flat surfaces 71 and 72, respectively. Specifically, one of the pair of front curved surfaces 73 connects one end of the front flat surfaces 71 and 72 in the circumferential direction, and the other one of the front flat surfaces 71 and 72 in the circumferential direction. The other end on the side opposite to the part is connected.

Here, for convenience of description, the angular position of the boundary portion between the front curved surface 73 and the first front flat surface 71 is referred to as a first angular position θ1, and the angle of the boundary portion between the front curved surface 73 and the second front flat surface 72 is set. The position is the second angular position θ2. For convenience of illustration, the angular positions θ1 and θ2 are shown by broken lines in FIG. 3, but in reality, the boundary portion is smoothly continuous.

The front curved surface 73 is a curved surface that is displaced in the axial direction Z according to the circumferential direction (in other words, the angular position of the front fixed body 60). More specifically, the front curved surface 73 is curved in the axial direction Z so as to gradually approach the rear fixed body 80 (in other words, the front rotary body surface 103) from the first angular position θ1 toward the second angular position θ2. ing.

That is, the pair of front curved surfaces 73 are provided on both sides in the circumferential direction with respect to the second front flat surface 72, and are gradually separated from the front rotary body surface 103 as they are separated from the second front flat surface 72 in the circumferential direction. Curved in the direction Z.

In the present embodiment, the front curved surface 73 has a front concave surface 73 a that is curved in the axial direction Z so as to be concave with respect to the front rotary body surface 103, and an axial direction that is convex toward the front rotary body surface 103. And a front convex surface 73b curved in the Z direction.

The front concave surface 73a is arranged closer to the first front flat surface 71 side than the second front flat surface 72, and the front convex surface 73b is arranged closer to the second front flat surface 72 side than the first front flat surface 71. There is. 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.

The angle range occupied by the front convex surface 73b and the front concave surface 73a may be the same or different. The position of the inflection point is arbitrary. Further, since the front curved surface 73 can be said to be a wavy curved surface, the front fixed body surface 70 can be said to be a wavy surface including a wavy curved portion.

Here, the front fixed body edge 73c, which is the outer peripheral edge of the front curved surface 73, is displaced in the axial direction Z in accordance with the circumferential direction. In the present embodiment, since the front curved surface 73 has the shape having the front concave surface 73a and the front convex surface 73b, the front fixed body edge 73c has a sinusoidal shape when viewed from the outside in the radial direction R.

As shown in FIGS. 2 to 4, the rear fixing body 80 arranged on the rear plate 40 side of the two fixing bodies 60 and 80 has a ring shape (in the present embodiment, an annular shape) like the front fixing body 60. ) And has a rear fixed body insertion hole 81 into which the rotary shaft 12 is inserted. In the present embodiment, the rear fixed body insertion hole 81 is a through hole that penetrates in the axial direction Z. The rear fixed body 80 is arranged in the front cylinder 30 with the rotary shaft 12 inserted in the rear fixed body insertion hole 81.

The rear fixed body 80 has a rear fixed body outer peripheral surface 82 that faces the front cylinder inner peripheral surface 33 in the radial direction R. In the present embodiment, the outer peripheral surface 82 of the rear fixed body and the inner peripheral surface 33 of the front cylinder are in contact with each other, and the rear fixed body 80 is supported by the front cylinder 30 by the contact. However, the present invention is not limited to this, and the front cylinder inner peripheral surface 33 and the rear fixed body outer peripheral surface 82 may be separated from each other.

The rear fixed body 80 includes a rear rear surface 83 that faces the first plate surface 43 of the rear plate 40 in the axial direction Z. 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 fixed body surface 90 has a ring shape, and has an annular shape in the present embodiment.

In the present 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 body surface 90 connects the first rear flat surface 91 and the second rear flat surface 92 intersecting the axial direction Z (orthogonal in the present embodiment) with the rear flat surfaces 91, 92. And a pair of rear curved surfaces 93 as curved surfaces.

As shown in FIG. 4, both rear flat surfaces 91 and 92 are displaced in the axial direction Z. Specifically, the second rear flat surface 92 is arranged closer to the front fixed body 60 (in other words, the rear rotary body surface 104) than the first rear flat surface 91. Further, the rear flat surfaces 91, 92 are arranged so as to be separated from each other in the circumferential direction of the rear fixed body 80, and for example, both are displaced by 180°. In this embodiment, both rear flat surfaces 91, 92 are fan-shaped.

Each of the pair of rear curved surfaces 93 has a fan shape. The pair of rear curved surfaces 93 are arranged to face each other in a direction orthogonal to both the axial direction Z and the facing directions of the two rear flat surfaces 91 and 92.
One of the pair of rear curved surfaces 93 connects one end of the rear flat surfaces 91 and 92 in the circumferential direction, and the other is opposite to the one end of the rear flat surfaces 91 and 92 in the circumferential direction. The other ends on the side are connected.

The fixed body surfaces 70 and 90 face each other with the angular position deviated from each other by 180° in the axial direction Z with the rotary body 100 interposed therebetween.
The facing distance between the two fixed body surfaces 70 and 90 is constant regardless of the angular position (in other words, the circumferential position). Specifically, as shown in FIG. 4, the first front flat surface 71 and the second rear flat surface 92 are opposed to each other in the axial direction Z, and the second front flat surface 72 and the first rear flat surface 91 are formed. It is opposed to the axial direction Z. The amount of deviation in the axial direction Z between the front flat surfaces 71 and 72 is the same as the amount of deviation between the rear flat surfaces 91 and 92. Hereinafter, the amount of deviation in the axial direction Z between the front flat surfaces 71 and 72 and the amount of deviation between the rear flat surfaces 91 and 92 will be simply referred to as “deviation amount Z1”.

Further, the bending degree of the front curved surface 73 and the bending degree of the rear curved surface 93 are the same. More specifically, the pair of rear curved surfaces 93 are provided on both sides in the circumferential direction with respect to the second rear flat surface 92, similarly to the front curved surface 73, and gradually become farther from the second rear flat surface 92 in the circumferential direction. Further, it is curved in the axial direction Z so as to be separated from the rear rotary body surface 104. That is, the front curved surface 73 and the rear curved surface 93 are curved in the same direction so that the facing distance does not vary depending on the angular position. As a result, the facing distance between the fixed body surfaces 70 and 90 is constant at any angular position.

The specific shapes of the first rear flat surface 91, the second rear flat surface 92, and the rear curved surface 93 are the same as those of the first front flat surface 71, the second front flat surface 72, and the front curved surface 73. Therefore, detailed description is omitted. Further, like the front curved surface 73, the rear curved surface 93 can be said to be a curved surface that is curved in a wavy shape. Therefore, focusing on this point, the rear fixed body surface 90 is a wave surface that includes a portion that is curved in a wavy shape. It can also be said.

Here, the rear fixed body edge 93c, which is the outer peripheral edge of the rear curved surface 93, is displaced in the axial direction Z according to the circumferential direction. In the present embodiment, the rear fixed body edge 93c has a sinusoidal shape when viewed from the outside in the radial direction R, similarly to the front fixed body edge 73c.

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

Here, the circumferential direction of both the fixed bodies 60 and 80 and the rotary body 100 and the circumferential direction of the rotary shaft 12 are the same, and the radial direction of both the fixed bodies 60 and 80 and the rotary body 100 and the radial direction of the rotary shaft 12 are the same. R is the same, and the axial directions of the fixed bodies 60, 80 and the rotating body 100 are the same as the axial direction Z of the rotary shaft 12. Therefore, the circumferential direction, the radial direction R, and the axial direction Z of the rotary shaft 12 may be appropriately read as the circumferential direction, the radial direction, and the axial direction of the rotating body 100, or the circumferential direction and the radial direction of both the fixed bodies 60 and 80. And may be read as the axial direction.

As shown in FIGS. 2 to 4, the rotating body 100 includes a tubular portion 101 through which the rotary shaft 12 is inserted, and a ring portion 102 that projects outward from the tubular portion 101 in the radial direction R. ..
The tubular portion 101 has, for example, a cylindrical shape whose axial direction is the axial direction Z, and has an inner diameter that is the same as or slightly larger than the rotating shaft 12 and an outer diameter that is smaller than both the fixed body insertion holes 61 and 81. doing.

The tubular portion 101 is attached to the rotary shaft 12 so as to rotate integrally with the rotary shaft 12. As a result, the rotating body 100 rotates as the rotating shaft 12 rotates. It should be noted that the manner in which the tubular portion 101 is attached to the rotary shaft 12 is arbitrary. For example, the tubular portion 101 may be fixed to the rotary shaft 12 by press fitting, or a fixing pin that is inserted across the rotary shaft 12 and the tubular portion 101. The tubular portion 101 may be fixed to the rotating shaft 12 by the. Alternatively, the cylinder 101 and the rotary shaft 12 may be connected by a connecting member such as a key, or the cylinder 101 and the rotary shaft 12 may have a concave portion provided on one side and a convex portion provided on the other side. It may be configured to be engaged.

The tubular portion 101 is arranged so as to straddle both the fixed bodies 60 and 80. Specifically, a first end of both ends of the tubular portion 101 in the axial direction Z is inserted into the front fixing body insertion hole 61, and a second end opposite to the first end is fixed to the rear. It has entered the body insertion hole 81.

The ring portion 102 is provided at a predetermined position (near the central portion in the present embodiment) between both end portions of the tubular portion 101 in the axial direction Z, and is arranged between the fixed bodies 60 and 80. In other words, the two fixed bodies 60 and 80 are arranged to face each other in the axial direction Z with the ring portion 102 interposed therebetween.

The ring portion 102 has an annular plate shape with the plate thickness direction in the axial direction Z, and has a ring-shaped front rotating body surface 103 and a rear rotating body surface 104 as both end surfaces in the axial direction Z. Both rotary body surfaces 103 and 104 are flat surfaces intersecting with the axial direction Z, and in the present embodiment, are flat surfaces orthogonal to the axial direction Z. Therefore, the two rotary body edges 103a and 104a, which are the outer peripheral edges of the two rotary body surfaces 103 and 104, are linear when viewed from the outside in the radial direction R, and the position in the axial direction Z is constant regardless of the circumferential direction. There is. The front rotary body surface 103 and the rear rotary body surface 104 can also be referred to as the first rotary body surface and the second rotary body surface.

As shown in FIG. 4, the front rotary body surface 103 faces the front fixed 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 the surfaces of the front fixed body surface 70 other than the second front flat surface 72 are separated from the front rotating body surface 103.

The rear rotary body surface 104 faces the rear fixed body surface 90 in the axial direction Z. In the present embodiment, the rear rotary body surface 104 and the second rear flat surface 92 are in contact with each other, and the surfaces of the rear fixed body surface 90 other than the second rear flat surface 92 are separated from the rear rotary body surface 104. ..

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

As shown in FIG. 4, the compressor 10 includes rotary body bearings 111 and 112 as radial bearings that rotatably support the tubular portion 101 with respect to both the fixed bodies 60 and 80.
The rotary body bearings 111 and 112 are arranged in the fixed body insertion holes 61 and 81. The rotary body bearings 111 and 112 are cylindrical and have the axial direction Z as the axial direction, and extend in the axial direction Z. The specific types of both rotary body bearings 111 and 112 are arbitrary.

The front rotary body bearing 111 is arranged between the tubular portion 101 and the inner wall surface of the front fixed body insertion hole 61, and is inserted into the front fixed body insertion hole 61 of the tubular portion 101 including the first end portion. The protruding part is rotatably supported.

The rear rotary body bearing 112 is arranged between the tubular portion 101 and the inner wall surface of the rear fixed body insertion hole 81, and enters the rear fixed body insertion hole 81 of the tubular portion 101 including the second end portion. The protruding part is rotatably supported.

In the present embodiment, the rotating body 100 is supported by the rotating body bearings 111 and 112 with respect to the fixed bodies 60 and 80 with the rotating body surfaces 103 and 104 and the fixed body surfaces 70 and 90 facing each other in the axial direction Z. Has been done. As a result, the posture of the rotating body 100 is maintained. In particular, in this embodiment, both ends of the rotating body 100 are supported by the rotating body bearings 111 and 112. Thereby, the rotating body 100 is stably held.

Incidentally, the outer peripheral surfaces of the rotary body bearings 111 and 112 are curved so as to be convex outward in the radial direction R. The outer peripheral surfaces of the rotary body bearings 111 and 112 are in contact with the inner wall surfaces of the fixed body insertion holes 61 and 81, and the corresponding curvatures of both are the same.

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

In detail, the front thrust bearing 113 is arranged in a space created by the front cylinder bottom 31 being formed in a stepped shape. The front thrust bearing 113 supports the first end surface of the tubular portion 101 in the axial direction Z while being supported by the front cylinder bottom portion 31.

The rear thrust bearing 114 is arranged in a thrust accommodating recess 115 formed in the rear plate 40. The thrust accommodating recess 115 is formed in a portion of the inner wall surface of the rear plate insertion hole 41 closer to the first plate surface 43 than the second plate surface 44 and a peripheral edge portion of the rear plate insertion hole 41 in the first plate surface 43. There is. In the present embodiment, the thrust accommodating recess 115 and the radial accommodating recess 54 are provided separately, and the rear plate 40 is interposed therebetween. The rear thrust bearing 114 is disposed in the thrust accommodating recess 115, and supports the second end surface of the tubular portion 101 in the axial direction Z while being supported by the rear plate 40.

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

As shown in FIG. 4, the compressor 10 includes compression chambers A4 and A5 for sucking and compressing a fluid. Both compression chambers A4 and A5 are arranged on both sides of the rotating body 100 in the axial direction Z.

The front compression chamber A4 is partitioned by the front fixed body surface 70, the front rotary body surface 103, the outer peripheral surface of the front rotary body bearing 111, and the front cylinder inner peripheral surface 33. The rear compression chamber A5 is partitioned by the rear fixed body surface 90, the rear rotary body surface 104, the outer peripheral surface of the rear rotary body bearing 112, and the front cylinder inner peripheral surface 33. In the present embodiment, the front compression chamber A4 and the rear compression chamber A5 have the same size.

Here, the compression chambers A4 and A5 and the discharge chamber A1 face each other in the radial direction R via the front cylinder side wall portion 32. That is, the discharge chamber A1 is arranged outside the compression chambers A4 and A5 in the radial direction R via the front cylinder side wall portion 32.

By the way, in the present embodiment, the discharge chamber A1 faces the part of the front compression chamber A4 in the radial direction R, while faces the entire rear compression chamber A5 in the radial direction R. , But not limited to this. In short, the discharge chamber A1 may extend in the axial direction Z so as to face at least a part of the front compression chamber A4 in the radial direction R and at least a portion of the rear compression chamber A5 in the radial direction R. ..

As shown in FIGS. 2 to 4, the compressor 10 includes a vane 120 that is inserted into a vane groove 125 formed in the rotating body 100.
The vane 120 has, for example, a rectangular plate shape. The vane 120 is disposed between the fixed bodies 60 and 80 (in other words, the fixed body surfaces 70 and 90 in other words) such that the plate surface of the vane 120 is orthogonal to the circumferential direction of the rotating shaft 12. That is, the vane 120 has a plate shape whose thickness direction is a direction orthogonal to both the axial direction Z and the radial direction R.

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 peripheral end face 123 and a vane inner peripheral end face 124 as both end faces in the radial direction R. ..

As shown in FIG. 4, the first vane end 121 is in contact with the front fixed body surface 70, and the second vane end 122 is in contact with the rear fixed body surface 90. That is, the vane 120 of this embodiment is in contact with both the fixed body surfaces 70 and 90. The specific shapes of the vane end portions 121 and 122 are arbitrary, but may be curved so as to be convex toward the fixed body surfaces 70 and 90, for example.

As shown in FIGS. 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 is open to both the rotary body surfaces 103 and 104. The vane groove 125 of this embodiment is open toward the outside in the radial direction R. On the other hand, the vane groove 125 does not open inside the radial direction R.

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 to the inside. However, the method of forming the vane groove 125 is not limited to this, and is arbitrary.

The vane groove 125 has both side surfaces facing each other in the circumferential 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 facing distance between both side surfaces of the vane groove 125) may be equal to or slightly wider than the plate thickness of the vane 120. The vane 120 inserted in the vane groove 125 is sandwiched by both side surfaces of the vane groove 125. The vane 120 is allowed to move in the axial direction Z along the vane groove 125.

With this configuration, the vane 120 rotates as the rotating body 100 rotates. In this case, since both the fixed body surfaces 70 and 90 are curved, the vane 120 moves (in other words, rocks) in the axial direction Z along the both fixed body surfaces 70 and 90. That is, the vane 120 rotates while moving in the axial direction Z. As a result, the first vane end 121 of the vane 120 enters the front compression chamber A4, and the second vane end 122 enters the rear compression chamber A5. That is, the vane groove 125 allows the vane 120 to be arranged across both compression chambers A4 and A5 while rotating the vane 120 as the rotary body 100 rotates.

Then, in each of the compression chambers A4 and A5, the vane 120 causes a periodic volume change with the rotation of the rotary shaft 12, so that the fluid is sucked and compressed. That is, it can be said that the vane 120 causes a volume change in both compression chambers A4 and A5. This point will be described later.

The moving distance of the vane 120 (in other words, the swing distance) is the amount of displacement in the axial direction Z between the front flat surfaces 71 and 72 (or between the rear flat surfaces 91 and 92), that is, the shift amount Z1. Further, the vane 120 maintains the state of being in contact with both the fixed body surfaces 70 and 90 during the rotation of the rotating body 100. That is, the vane 120 is continuously in contact with both the fixed body surfaces 70 and 90 during the rotation of the rotating body 100, and intermittent contact (specifically, regularly separating or contacting) is prevented. It does not happen.

Here, the vane outer peripheral end surface 123 is in contact with the front cylinder inner peripheral surface 33 regardless of the movement of the vane 120. In other words, it can be said that the front cylinder inner peripheral surface 33 extends in the axial direction Z longer than the length of the vane 120 in the axial direction Z so as to contact the vane outer peripheral end surface 123 regardless of the movement of the vane 120.

The shape of the vane outer peripheral end surface 123 is arbitrary, but for example, it is curved so as to be convex outward in the radial direction R so as to be continuous in the circumferential direction with the ring outer peripheral surface 105, and the curvature thereof is the front cylinder. The curvature may be the same as that of the inner peripheral surface 33.

The compressor 10 includes a contact member 130 that contacts the inner peripheral end surface 124 of the vane. In the present embodiment, the contact member 130 is a separate body from the rotating body 100 and is attached to the rotating body 100. The contact member 130 and the vane inner peripheral end surface 124 will be described below.

As shown in FIG. 4, on the outer peripheral surface of the tubular portion 101, a recessed strip 131 extending in the axial direction Z is formed. The groove 131 is opened toward the outside in the radial direction R and communicates with the vane groove 125.

The abutting member 130 has a rod shape (in other words, a columnar shape) extending in the axial direction Z, and its cross-sectional shape is formed so as to fit into the groove 131, according to the sectional shape of the groove 131. The contact member 130 is attached to the rotating body 100 by being fitted into the recess 131. The abutting member 130 is provided in a portion of the recess 131 that communicates with the vane groove 125. A part of the contact member 130 protrudes from the vane groove 125 to the outside in the radial direction R, and is sandwiched by the rotary body bearings 111 and 112 in the axial direction Z.

The contact member 130 includes a contact surface 132 that contacts the vane inner peripheral end surface 124 in the radial direction R. The abutment surface 132 is continuous with the outer peripheral surfaces of the two rotary body bearings 111 and 112. The contact surface 132 is curved so as to be convex outward in the radial direction R, for example, like the outer peripheral surfaces of the rotary body bearings 111 and 112, and is flush with the outer peripheral surfaces of both rotary body bearings 111 and 112. Has become. In detail, the curvature of the contact surface 132 is set to be the same as the curvature of the outer peripheral surfaces of the two rotary body bearings 111 and 112 (in other words, the curvature of the both inner wall surfaces 61a and 81a).

The vane inner peripheral end surface 124, which is the end surface on the inner side in the radial direction R of the vane 120, is formed so as to correspond to the contact surface 132 and the outer peripheral surfaces of both the rotary body bearings 111 and 112. It is curved so as to dent.

According to this configuration, the outer peripheral surfaces of the both rotary body bearings 111 and 112 and the contact surface 132 form one sliding surface on which the vane 120 slides, and when the vane 120 moves in the axial direction Z, The vane inner peripheral end surface 124 moves in the axial direction Z while sliding on the sliding surface. This makes it possible to smoothly move the vane 120 in the axial direction Z and suppress formation of a gap inside the vane 120 in the radial direction R.

Further, since the vane 120 is sandwiched between the inner peripheral surface 33 of the front cylinder and the contact surface 132 of the contact member 130 in the radial direction R, the displacement of the vane 120 in the radial direction R can be suppressed. Further, it is possible to suppress the fluid from leaking from the boundary portion between the vane 120 (vane outer peripheral end surface 123) and the front cylinder inner peripheral surface 33.

Next, with reference to FIGS. 2 to 11, a configuration relating to the suction of the suction fluid and the discharge of the compressed fluid to the front compression chamber A4 will be described. For convenience of illustration, the front retainer 155 is not shown in FIG. 7, while the front retainer 155 is shown in FIGS. 8 and 9. Further, in FIG. 8, the housing 11 is also illustrated.

As shown in FIGS. 2 to 4, the compressor 10 includes a front suction port 140 that sucks suction fluid into the front compression chamber A4. The front intake port 140 is formed in, for example, the front cylinder 30, and in detail, is formed over both the front cylinder bottom portion 31 and the front cylinder side wall portion 32. The front suction port 140 is open to the motor chamber A2, extends in the axial direction Z, and opens toward the front compression chamber A4. The front suction port 140 connects the motor chamber A2 and the front compression chamber A4.

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 increases, but does not communicate with the front compression chamber A4 in a phase where the volume of the front compression chamber A4 decreases. It is open to the position. For example, as shown in FIG. 8, the front intake port 140 is opened on the rotation direction M side with respect to the second front flat surface 72 of the portion defining the front compression chamber A4 in the front cylinder inner peripheral surface 33. ing. In the present embodiment, the front suction port 140 has an oval cross section, and the flow passage cross-sectional area of the front suction port 140 is larger than that of a circular shape.

As shown in FIGS. 3 to 6, the compressor 10 includes a plurality of front discharge ports 141 to 143 that discharge the compressed fluid compressed in the front compression chamber A4.
The plurality of front discharge ports 141 to 143 are provided at positions on the side of the front cylinder side wall portion 32 opposite to the rotation direction M side of the rotating body 100 with respect to the second front flat surface 72, and are arranged in the circumferential direction. ing.

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

Here, a portion of the front cylinder side wall portion 32 between the front seat surface 144 and the front cylinder inner peripheral surface 33 is referred to as a front mounting seat portion 145. That is, it can be said that the front cylinder side wall portion 32 includes the front mounting seat portion 145 having the front seat surface 144 formed therein.

As shown in FIG. 8, because the front cylinder inner peripheral surface 33 is curved and the front seat surface 144 is a flat surface, the front mounting seat portion 145 has a different thickness depending on the circumferential direction. ing. More specifically, the thickness of the front mounting seat portion 145 is thinner on the central side than on the both end sides of the front seating surface 144 when viewed in the axial direction Z.

As shown in FIGS. 5, 6 and 8, the plurality of front discharge ports 141 to 143 are provided on the front seat surface 144 of the front mounting seat portion 145. The plurality of front discharge ports 141 to 143 are arranged in the circumferential direction in the order of the first front discharge port 141→the second front discharge port 142→the third front discharge port 143 so as to be separated from the second front flat surface 72. Therefore, the first front discharge port 141 is formed at a position closest to the second front flat surface 72 as compared with the other front discharge ports 142 and 143. That is, the second front discharge port 142 and the third front discharge port 143 are circumferentially farther from the second front flat surface 72 than the first front discharge port 141. In the present embodiment, the second front discharge port 142 or the third front discharge port 143 corresponds to the “second discharge port”.

The plurality of front discharge ports 141 to 143 communicate the front compression chamber A4 and the discharge chamber A1 by penetrating the front mounting seat portion 145 in the radial direction R. As described above, since the thickness of the front mounting seat portion 145 differs depending on the circumferential direction, at least a part of each of the front discharge ports 141 to 143 is provided at a position where the thickness is relatively different. For this reason, in at least a part of each of the front discharge ports 141 to 143, the passage length (specifically, the length in the radial direction R) varies depending on the circumferential direction.

In the present embodiment, since the second front discharge port 142 is arranged closer to the center of the front seat surface 144 than the first front discharge port 141, the second front discharge port 142 is larger than the first front discharge port 141. It is formed in the thin part. Therefore, 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, it can be said that the second front discharge port 142 is a thin portion port provided in a portion of the front mounting seat portion 145 that is thinner than a portion where the first front discharge port 141 is provided. Similarly, it can be said that the first front discharge port 141 is a thick-walled portion port provided in a portion of the front mounting seat portion 145 that is thicker than a portion where the second front discharge port 142 is provided.

Incidentally, in this embodiment, the first front discharge port 141 and the second front discharge port 142 have different thicknesses depending on the position in the radial direction R. In this case, the maximum thickness of the second front discharge port 142 as the thin port is smaller than the minimum thickness of the first front discharge port 141 as the thick port. That is, in the present embodiment, the thin portion port is such that the maximum thickness of the thin portion port is smaller than the minimum thickness of the thick portion port.

However, the configuration is not limited to this, and in a configuration in which the thickness of the thin portion port or the thickness of the thick portion port varies depending on the position in the radial direction R, the thin portion port is the thickest portion of the thin portion port. May be thinner than the thickness of the thickest portion of the thick portion port. Further, the thin portion port may be configured such that the thickness of the thinnest portion of the thin portion port is smaller than the thickness of the thinnest portion of the thick portion port. Further, the thin portion port may be configured such that the average thickness of the thin portion port is smaller than the average thickness of the thick portion port.

As shown in FIGS. 5 and 6, the plurality of front discharge ports 141 to 143 have, for example, a circular shape. The diameter of the first front discharge port 141 is constant regardless of the radial direction R. That is, the flow passage cross-sectional area of the first front discharge port 141 of this embodiment is constant without changing according to the radial direction R. The same applies to the second front discharge port 142 and the third front discharge port 143.

The flow passage cross-sectional areas of the second front discharge port 142 and the third front discharge port 143 are larger than the flow passage cross-sectional area of the first front discharge port 141. Specifically, the diameters of the second front discharge port 142 and the third front discharge port 143 are larger than the diameter of the first front discharge port 141. In the present embodiment, the second front discharge port 142 and the third front discharge port 143 are formed to have the same size.

As shown in FIG. 6, the plurality of front discharge ports 141 to 143 correspond to the front fixed body edge 73c which is displaced in the axial direction Z in accordance with the circumferential direction, and are arranged in the axial direction along the front fixed body edge 73c. They are arranged in the circumferential direction while being displaced in the Z direction.

Specifically, a line connecting the midpoints of the front fixed body edge 73c and the front rotary body edge 103a is defined as a front midline La. The front middle line La is displaced along the front fixed body edge 73c in the axial direction Z in accordance with the circumferential direction, and more specifically has a sinusoidal shape when viewed from the outside in the radial direction R.

In such a configuration, a line passing through the centers of the front discharge ports 141 to 143 is defined as a front center line L1. In this case, the plurality of front discharge ports 141 to 143 are arranged such that the front center line L1 is arranged closer to the front intermediate line La than the front fixed body edge 73c and the front rotary body edge 103a when viewed from the outside in the radial direction R. Has been done. Therefore, in the present embodiment, the plurality of front discharge ports 141 to 143 are arranged while being slightly displaced 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 circumferential direction (in other words, the rotation direction M). In other words, the arrangement direction and the axial direction Z are not orthogonal and are inclined.

For convenience of explanation, in the following description, the arrangement direction of the plurality of front ejection ports 141 to 143 is simply referred to as “arrangement direction”. The arrangement direction is a curve passing through the centers of the front discharge ports 141 to 143 or an approximate straight line of the curve. In the present embodiment, since the front fixed body edge 73c around the second front flat surface 72 is the outer peripheral edge of the front convex surface 73b, it can be said that the front centerline L1 is along the outer peripheral edge of the front convex surface 73b.

Incidentally, in this embodiment, the front center line L1 and the front middle line La are substantially coincident with each other. The fact that the front center line L1 is arranged closer to the front middle line La than the front fixed body edge 73c and the front rotary body edge 103a includes the case where the front center line L1 coincides with the front middle line La.

The size of the first front discharge port 141 is, for example, larger than the distance in the axial direction Z between the front fixed body edge 73c and the front rotary body edge 103a at the position where the first front discharge port 141 is provided. Therefore, the first front discharge port 141 overlaps the front compression chamber A4 on both sides in the axial direction Z. In this case, a region of the first front discharge port 141 facing the front compression chamber A4, specifically, the front fixed body edge 73c and the front rotary body edge 103a of the first front discharge port 141 when viewed from the radial direction R. The region between the two greatly contributes to the discharge of the compressed fluid. The same applies to the second front discharge port 142 and the third front discharge port 143.

As shown in FIGS. 5 and 7 to 9, the compressor 10 includes a front valve 150 that closes 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 provided on the front seat surface 144. The front valve 150 is a thin plate that is elastically deformable. The front valve 150 is formed in a flat shape corresponding to the front seat surface 144 being a flat surface. More specifically, the front valve 150 is a flat plate formed along the front seat surface 144.

The front valve 150 includes a front base portion 151 extending in the arrangement direction of the front discharge ports 141 to 143, and a plurality of front portions extending from the front base portion 151 in a direction orthogonal to both the arrangement direction and the radial direction R. And arm portions 152 to 154.

The front base portion 151 is arranged on the side farther from the front fixed body 60 than the plurality of front discharge ports 141 to 143. The front base portion 151 has a rectangular shape whose longitudinal direction is the arrangement direction.

The front base portion 151 is provided with two front mounting holes 151 a for mounting the front valve 150 on the front seat surface 144. The two front mounting holes 151a are provided at both ends of the front base portion 151 in the extending direction, and penetrate the front valve 150 in the thickness direction.

As shown in FIGS. 5 and 6, the front seat surface 144 has a front bolt hole 144a communicating with the front mounting hole 151a. The front valve 150 is fixed to the front seat surface 144 by being screwed into the front bolt hole 144a with the bolt B inserted in the front mounting hole 151a.

Here, as described above, the arrangement direction of the plurality of front discharge ports 141 to 143 is inclined with respect to the circumferential direction. Therefore, as shown in FIG. 7, the front base portion 151 is inclined with respect to the circumferential direction.

As shown in FIGS. 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 arrangement direction with a gap in between.

The first front arm portion 152 extends toward the first front discharge port 141 from the end portion on the second front flat surface 72 side of the longitudinal end portions of the front base portion 151, and the first front discharge port 141. Has a first front end portion 152a that covers the. In the present embodiment, the first front end portion 152a has a semicircular shape and is arranged so that the center of the semicircle coincides with the center of the first front discharge port 141.

The second front arm portion 153 extends from the vicinity of the longitudinal center of the front base portion 151 toward the second front discharge port 142, and has a second front tip portion 153 a that covers the second front discharge port 142. ing. In the present embodiment, the second front end portion 153a has a circular shape and is arranged so that the center thereof coincides with the center of the second front discharge port 142.

The third front arm portion 154 extends toward the third front discharge port 143 from the end portion on the opposite side to the second front flat surface 72 side of the longitudinal end portions of the front base portion 151. It has a third front tip 154a that covers the front discharge port 143. In the present embodiment, the third front end portion 154a has a circular shape and is arranged so that the center thereof coincides with the center of the third front discharge port 143.

As shown in FIG. 7, the lengths of the front arm portions 152 to 154 in the present embodiment in the extending direction are the same. Specifically, the distance from the front base 151 to the center of the semicircle of the first front tip 152a is the first arm length X1, and the distance from the front base 151 to the center point of the second front tip 153a is the second. The arm length is X2, and the distance from the front base portion 151 to the center point of the third front tip portion 154a is the third arm length X3. In this case, the arm lengths X1 to X3 are set to be the same.

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 an inclined state with respect to the circumferential direction so that the arm lengths X1 to X3 are the same. Can be said.

As shown in FIGS. 5 and 9, the front retainer 155 has a plate shape thicker than the front valve 150, and is fixed to the front seat surface 144 by the bolt B while sandwiching the front valve 150. The front retainer 155 has the same shape as the front valve 150 and overlaps with the front valve 150 when viewed from a direction orthogonal to the front seat surface 144. The portion of the front retainer 155 that overlaps the front base portion 151 receives the tightening force of the bolt B and presses the front valve 150 toward the front seat surface 144 side. On the other hand, the portions of the front retainer 155 that overlap the front arm portions 152 to 154 are warped so that the portions that overlap the front tip portions 152a to 154a are separated from the front tip portions 152a to 154a. Therefore, each of the front end portions 152a to 154a can swing between the front seat surface 144 and the front retainer 155.

With this configuration, when the pressure in the front compression chamber A4 exceeds the threshold value, the compressed fluid in the front compression chamber A4 is pushed out of the front tip portions 152a to 154a and discharged from the front discharge ports 141 to 143. As a result, the compressed fluid is discharged into 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 angles of the front end portions 152a to 154a are restricted by the front retainer 155. On the other hand, the movement (that is, backflow) of the compressed fluid from the discharge chamber A1 to the front compression chamber A4 is suppressed by the front valve 150.

Here, in the present embodiment, since the arm lengths X1 to X3 are set to be the same, the threshold values that trigger the opening of the front end portions 152a to 154a are 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 relating to suction of the suction fluid into the rear compression chamber A5 and discharge of the compression fluid will be described. For convenience of illustration, the rear retainer 175 is omitted in FIG. 10, while the rear retainer 175 is illustrated in FIG. 11. Further, in FIG. 11, the housing 11 is also illustrated.

As shown in FIGS. 2 to 4, the compressor 10 includes a rear suction port 160 that sucks suction fluid into the rear compression chamber A5.
The rear suction port 160 is formed in, for example, the front cylinder 30, and in detail, is formed over both the front cylinder bottom portion 31 and the front cylinder side wall portion 32. The front suction port 140 is open to the motor chamber A2, extends in the axial direction Z to a position radially outside the rear compression chamber A5, and opens to the rear compression chamber A5. The motor chamber A2 and the rear compression chamber A5 are communicated 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 where the volume of the rear compression chamber A5 increases, but does not communicate with the rear compression chamber A5 in a phase where the volume of the rear compression chamber A5 decreases. It is open to the position. For example, as shown in FIG. 11, the rear suction port 160 is opened on the rotation direction M side with respect to the second rear flat surface 92 in the portion of the front cylinder inner peripheral surface 33 that defines the rear compression chamber A5. ing. In the present embodiment, the rear suction port 160 has an oval cross section, and the flow passage cross-sectional area of the rear suction port 160 is larger than that of a circular shape.

The compressor 10 includes a plurality of rear discharge ports 161 to 163 that discharge the 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 are located on the side of the front cylinder side wall portion 32 opposite to the second rear flat surface 92 on the rotation direction M side of the rotating body 100. They are provided and arranged in the circumferential direction.

In detail, the curved front cylinder outer peripheral surface 34 is formed with a rear seat surface 164 recessed from the front cylinder outer peripheral surface 34. The rear seat surface 164 is located between the rear compression chamber A5 and the discharge chamber A1 of the outer peripheral surface 34 of the front cylinder, and is a portion on the opposite side of the second rear flat surface 92 from the rotation direction M side of the rotating body 100. Is formed in. The rear seat surface 164 is a flat surface orthogonal to the radial direction R and extends in the axial direction Z.

Here, a portion of the front cylinder side wall portion 32 between the rear seat surface 164 and the front cylinder inner peripheral surface 33 is referred to as a rear mounting seat portion 165. In other words, it can be said that the front cylinder side wall portion 32 includes the rear mounting seat portion 165 having the rear seat surface 164.

As shown in FIG. 11, the rear mounting seat portion 165 has a different thickness depending on the circumferential direction, and more specifically, the thickness of the rear mounting seat portion 165 is the rear seat surface 164 when viewed from the axial direction Z. The center side is thinner than both ends.

The plurality of rear discharge ports 161 to 163 are provided on the rear seat surface 164 of the rear mounting seat portion 165. The plurality of rear discharge ports 161 to 163 are arranged in the circumferential direction in the order of the first rear discharge port 161, the second rear discharge port 162, and the third rear discharge port 163 so as to be separated from the second rear flat surface 92. That is, the second rear discharge port 162 and the third rear discharge port 163 are circumferentially separated from the first rear discharge port 161 and from the second rear flat surface 92. In the present embodiment, the second rear discharge port 162 or the third rear discharge port 163 corresponds to the “second discharge port”.

The plurality of rear discharge ports 161 to 163 communicate the rear compression chamber A5 and the discharge chamber A1 by penetrating the rear mounting seat portion 165 in the radial direction R. As described above, since the thickness of the rear mounting seat portion 165 differs depending on the circumferential direction, at least a part of each of the rear discharge ports 161 to 163 is provided at a position where the thickness is relatively different.

In the present embodiment, the second rear discharge port 162 is arranged closer to the center of the rear seat surface 164 than the first rear discharge port 161, so that the second rear discharge port 162 is more than the first rear discharge port 161. It is formed in the thin part. Therefore, 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 shape of the plurality of rear discharge ports 161 to 163 is the same as that of the plurality of front discharge ports 141 to 143. Therefore, detailed description of the shapes of the plurality of rear discharge ports 161 to 163 will be omitted.

The plurality of rear discharge ports 161 to 163 correspond to the rear fixed body edge 93c which is displaced in the axial direction Z according to the circumferential direction, and are displaced in the axial direction Z along the rear fixed body edge 93c while being circumferentially displaced. Are arranged in. Specifically, a line connecting the intermediate points of the rear fixed body edge 93c and the rear rotary body edge 104a is referred to as a rear intermediate line Lb, and a line passing through the centers of the plurality of rear discharge ports 161 to 163 is referred to as a rear center line L2. .. In this case, the plurality of rear discharge ports 161 to 163 are arranged so that the rear center line L2 is arranged closer to the rear intermediate line Lb than the rear fixed body edge 93c and the rear rotary body edge 104a. In the present embodiment, the rear center line L2 and the rear middle line Lb substantially coincide with each other.

As shown in FIGS. 10 and 11, the compressor 10 includes a rear valve 170 that closes the plurality of rear discharge ports 161-163, and a rear retainer 175 that adjusts the opening of the rear valve 170.

The rear valve 170 is a thin plate that is elastically deformable, and is provided on the rear seat surface 164. The rear valve 170 is provided with a rear base portion 171 extending in the arrangement direction of the plurality of rear discharge ports 161-163, and extending from the rear base portion 171 in a direction orthogonal to both the arrangement direction and the radial direction R and the rear tip portion 172a-. And a plurality of rear arm portions 172 to 174 having 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 with the rear valve 170.

The specific configurations of the rear valve 170 and the rear retainer 175 are the same as those of the front valve 150 and the front retainer 155. In detail, the rear base part 171 and the rear arm parts 172-174 are the same as the front base part 151 and the front arm parts 152-154. Therefore, 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 value, the compressed fluid in the rear compression chamber A5 is pushed out of the rear tip portions 172a to 174a and is discharged from the rear discharge ports 161 to 163. As a result, the compressed fluid is discharged into the discharge chamber A1. That is, the rear valve 170 opens and closes the rear discharge ports 161 to 163.

By the way, in response to the second front flat surface 72 and the second rear flat surface 92 being displaced by 180°, the front seating surface 144 and the rear seating surface 164 are displaced by 180° and a plurality of front surfaces are arranged. The discharge ports 141 to 143 and the plurality of rear discharge ports 161 to 163 are offset by 180°. Further, the two seating surfaces 144, 164 are displaced in the axial direction Z, and the front discharge ports 141-143 and the rear discharge ports 161-163 are displaced in the axial direction Z. Therefore, the front valve 150 and the rear valve 170 are arranged so as to be offset from each other in the axial direction Z.

Next, the positional relationship between the ports 140 to 143, 160 to 164 and the volume change caused by the vane 120 in the compression chambers A4 and A5 in the present embodiment will be described in detail with reference to FIGS. 12 and 13.

12 and 13 are developed views showing the states of the fixed bodies 60 and 80, the rotating body 100, and the vanes 120, and the phases of the two are different. 12 and 13, the ports 140 to 143 and 160 to 164 are schematically shown.

As shown in FIG. 12, the vane 120 is arranged across 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. As a result, the front compression chamber A4 is divided into two parts with the vane 120 as a boundary. 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 partitioned by the vane 120 and the contact portion between the second front flat surface 72 and the front rotor surface 103, and are adjacent to each other in the circumferential direction. ..

The first front compression chamber A4a communicates with the front suction port 140, but does not communicate with the plurality of front discharge ports 141-143. 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 port 140.

That is, the vane 120 includes the first front compression chamber A4a communicating with the front suction port 140 and the plurality of front discharge ports 141 to 141 so that the front suction port 140 does not communicate with the plurality of front discharge ports 141 to 143. It can also be said that it partitions the second front compression chamber A4b communicating with 143.

Here, as described above, the front curved surface 73 is curved in the axial direction Z so as to gradually separate from the front rotary body surface 103 as it separates from the second front flat surface 72. Therefore, as the distance from the second front flat surface 72 increases, the distance between the front curved surface 73 and the front rotary member surface 103 becomes wider. That is, the second front compression chamber A4b (in other words, the front compression chamber A4) becomes wider in the axial direction Z as it moves away from the second front flat surface 72. Therefore, it can be said that the plurality of front discharge ports 141 to 143 are sequentially arranged from the narrow position to the wide position of the front compression chamber A4.

Similarly, since a 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 parts with the vane 120 as a boundary. 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 partitioned by the vane 120 and the contact portion between the second rear flat surface 92 and the rear rotor surface 104, and are adjacent to each other in the circumferential direction. ..

The first rear compression chamber A5a communicates with the rear suction port 160, but does not communicate with the plurality of rear discharge ports 161 to 163. The second rear compression chamber A5b communicates with the plurality of rear discharge ports 161-163, but does not communicate with the rear suction port 160.

That is, in the vane 120, the first rear compression chamber A5a communicating with the rear suction port 160 and the plurality of rear discharge ports 161 to 161 to prevent the rear suction port 160 from communicating with the plurality of rear discharge ports 161 to 163. It can also be said that it partitions the second rear compression chamber A5b that is in communication with 163.

Here, as already described, the rear curved surface 93 is curved in the axial direction Z so as to gradually separate from the rear rotary body surface 104 as it separates from the second rear flat surface 92. Therefore, as the distance from the second rear flat surface 92 increases, the distance between the rear curved surface 93 and the rear rotary body surface 104 becomes wider. That is, the second rear compression chamber A5b (in other words, the rear compression chamber A5) becomes wider in the axial direction Z as the distance from the second rear flat surface 92 increases. Therefore, it can be said that the plurality of rear discharge ports 161 to 163 are sequentially arranged from the narrow position to the wide position of the rear compression chamber A5.

After that, when the rotating shaft 12 is rotated by the electric motor 13, the rotating body 100 and the vanes 120 are rotated accordingly. Note that, in FIG. 12, the rotating body 100 and the vane 120 move downward in the drawing.

As a result, as shown in FIG. 13, the vane 120 moves in the axial direction Z (left and right direction on the paper surface), and the volume changes in both compression chambers A4 and A5.
Specifically, in the first front compression chamber A4a, the volume increases and the suction fluid is sucked from the front suction port 140, while in the second front compression chamber A4b, the volume decreases and the suction fluid is compressed. .. Then, when the pressure in the second front compression chamber A4b exceeds the threshold value, the front valve 150 opens and the compressed fluid compressed in the second front compression chamber A4b passes through the plurality of front discharge ports 141-143. Flow into the discharge chamber A1.

Similarly, in the first rear compression chamber A5a, the volume increases and the suction fluid is sucked from the rear suction port 160, while in the second rear compression chamber A5b, the volume decreases and the fluid is compressed. When the pressure in the second rear compression chamber A5b exceeds the threshold value, the rear valve 170 opens and the compressed fluid compressed in the second rear compression chamber A5b passes through the plurality of rear discharge ports 161 to 163. Flow into the discharge chamber A1.

As described above, by rotating the rotating body 100 and the vane 120, the suction and compression cycle operations with 720° (two rotations of the rotating body 100) as one cycle are repeatedly performed in both compression chambers A4 and A5. ..

Here, for the sake of convenience of description, the two front compression chambers A4a and A4b are distinguished from each other. However, if the front compression chamber A4 is cycled with 720° as one cycle, the first front compression chamber A4a will be described. Can be said to be the front compression chamber A4 having a phase of 0° to 360°, and the second front compression chamber A4b can be said to be a front compression chamber A4 having a phase of 360° to 720°. That is, the space defined by the front fixed body surface 70, the front rotary body surface 103, the outer peripheral surface of the front rotary body bearing 111, and the front cylinder inner peripheral surface 33 is divided by the vane 120 into a front compression chamber A4 having a phase of 0° to 360°. It can also be said that it is partitioned into the front compression chamber A4 having a phase of 360° to 720°. In other words, the vane 120 divides the above space into a first chamber into which the fluid is sucked and a second chamber into which the fluid is compressed, and the vane 120 is rotated by the rotating body 100 and the vane 120 to rotate the first chamber. It can be said that a change in volume of the chamber and the second chamber (specifically, the volume of the first chamber increases and the volume of the second chamber decreases). The same applies to the first rear compression chamber A5a and the second rear compression chamber A5b.

According to this embodiment described in detail above, the following operational effects are obtained. Note that, for convenience of explanation, only the front side will be described below, but the same operational effects can be obtained on the rear side.
(1-1) The compressor 10 rotates with the rotating shaft 12, and the rotating body 100 that rotates with the rotation of the rotating shaft 12 and has the front rotating body surface 103 that intersects the axial direction Z of the rotating shaft 12. , A front fixed body 60 having a front fixed body surface 70 facing the front rotary body surface 103 in the axial direction Z. The front fixed body surface 70 is a second front flat surface 72 as a fixed body flat surface that abuts the front rotary body surface 103, and front curved surfaces provided on both sides of the second front flat surface 72 in the circumferential direction of the rotary shaft 12. And a surface 73. The front curved surface 73 is curved in the axial direction Z such that the front curved surface 73 is gradually separated from the front rotary body surface 103 as it is separated from the second front flat surface 72 in the circumferential direction.

The compressor 10 accommodates the rotating body 100 and the front fixed body 60, and is inserted into the front cylinder side wall portion 32 having the front cylinder inner peripheral surface 33 and the vane groove 125 formed in the rotating body 100. The vane 120, the front compression chamber A4, and the discharge chamber A1 are provided. The vane 120 rotates while moving in the axial direction Z as the rotating body 100 rotates. The front compression chamber A4 is partitioned by the front rotating body surface 103, the front fixed body surface 70, and the front cylinder inner peripheral surface 33. In the front compression chamber A4, the vane 120 causes a change in volume to suck and compress the fluid. The discharge chamber A1 is arranged radially outside the front compression chamber A4 via the front cylinder side wall portion 32.

In such a configuration, the compressor 10 includes a plurality of front discharge ports 141 to 143 that communicate the front compression chamber A4 and the discharge chamber A1 by penetrating the front cylinder side wall portion 32 in the radial direction R. The plurality of front discharge ports 141 to 143 are circumferentially arranged at positions on the side of the front cylinder side wall portion 32 opposite to the second front flat surface 72 on the rotation direction M side of the rotating body 100. The compressor 10 includes a front valve 150 that closes the plurality of front discharge ports 141 to 143.

According to such a configuration, the discharge chamber A1 is arranged radially outside the front compression chamber A4 via the front cylinder side wall portion 32, and the plurality of front discharge ports 141 to 143 are connected to the front fixed body 60. Instead, it is formed on the front cylinder side wall portion 32. As a result, the passage length of each of the front discharge ports 141 to 143 tends to be short. Therefore, it is possible to reduce the loss (hereinafter, referred to as "dead volume") due to the movement of the compressed fluid from the front compression chamber A4 to the discharge chamber A1.

More specifically, in order to discharge the compressed fluid in the front compression chamber A4 partitioned by the front rotary body surface 103, the front fixed body surface 70, and the front cylinder inner peripheral surface 33, for example, the front fixed body 60 is axially moved. It is conceivable to form the discharge port so as to penetrate Z. In this case, the length of the discharge port tends to be long. In particular, since the second front flat surface 72 or the periphery thereof corresponds to a thick portion in the front fixed body 60, the length of the discharge port is likely to be long and the passage length is likely to be long.

In this respect, in the present embodiment, the plurality of front discharge ports 141 to 143 are arranged in the circumferential direction and are formed in the front cylinder side wall portion 32, and penetrate the front cylinder side wall portion 32 in the radial direction R. Accordingly, the passage length of each of the front discharge ports 141 to 143 can be set to be about the thickness of the front cylinder side wall portion 32, so that the passage length can be shortened. Therefore, the dead volume can be reduced.

Further, since a plurality of front discharge ports 141 to 143 are provided, it is possible to secure a wider flow passage cross-sectional area, as compared with a configuration in which only one discharge port is provided. As a result, it is possible to suppress overcompression in which the pressure in the front compression chamber A4 becomes excessively high due to the narrow passage cross-sectional area of the discharge port.

From the above, it is possible to suppress overcompression and reduce dead volume.
In particular, in the present embodiment, the plurality of front discharge ports 141 to 143 are arranged in the circumferential direction having a length longer than the radial direction R of the front fixed body 60. The spacing and size can be adjusted relatively freely. Thereby, the plurality of front discharge ports 141 to 143 can be set to appropriate positions and sizes in consideration of overcompression and dead volume.

(1-2) The front rotary 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 discharge port 143 provided at a position distant from the second front flat surface 72 in the circumferential direction with respect to the first front discharge port 141. , Are provided. The flow passage cross-sectional area of the third front discharge port 143 is larger than the flow passage cross-sectional area of the first front discharge port 141.

The front rotary body surface 103 is a flat surface orthogonal to the axial direction Z, while the front curved surface 73 is gradually curved away from the front rotary body surface 103 in the axial direction Z as the front curved surface 73 moves away from the second front flat surface 72. Therefore, the front compression chamber A4 becomes wider in the axial direction Z as it moves away from the second front flat surface 72. Therefore, the third front discharge port 143, which is provided at a position farther from the second front flat surface 72 than the first front discharge port 141, has a larger front compression chamber A4 than the first front discharge port 141. Will exist. Since the flow passage cross-sectional area of the third front discharge port 143 is larger than the flow passage cross-sectional area of the first front discharge port 141, a large amount of compressed fluid is discharged through the third front discharge port 143 into the discharge chamber A1. Can be flushed to. Therefore, it is possible to suppress overcompression.

Further, since the first front discharge port 141 is provided closer to the second front flat surface 72 side than the third front discharge port 143, a portion of the front compression chamber A4 that is closer to the rotation direction M than the third front discharge port 143 is. The compressed fluid in (hereinafter, referred to as “discharge end portion”) is discharged into the discharge chamber A1 via the first front discharge port 141. As a result, it is possible to suppress the loss of the compressed fluid at the discharge end portion.

In particular, since the front compression chamber A4 becomes narrower in the axial direction Z toward the second front flat surface 72, the ratio of the volume of the discharge end portion to the entire volume of the front compression chamber A4 is relatively small. Therefore, even if the flow passage cross-sectional area of the first front discharge port 141 is smaller than the flow passage cross-sectional area of the third front discharge port 143, overcompression can be suppressed. Note that, for convenience of description, the relationship between the first front discharge port 141 and the third front discharge port 143 has been described, but the same applies to the relationship between the first front discharge port 141 and the second front discharge port 142.

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

With this configuration, it is not necessary to bend the front valve 150 along the outer peripheral surface 34 of the front cylinder. This can prevent the shape of the front valve 150 from becoming complicated.
(1-4) The front cylinder side wall portion 32 includes a front mounting seat portion 145 which is a portion between the front seat surface 144 and the front cylinder inner peripheral surface 33. Since the front seat surface 144 is a flat surface, the thickness of the front mounting seat portion 145 varies depending on the circumferential direction.

In this configuration, the plurality of front discharge ports 141 to 143 serve as the first front discharge port 141 and the thin part port, which are the thick part ports provided at the positions of the front mounting seat portion 145 having relatively different thicknesses. The second front discharge port 142 of FIG. The flow passage cross-sectional area of the second front discharge port 142 is larger than the flow passage cross-sectional area of the first front discharge port 141.

According to this configuration, since the flow passage cross-sectional area of the second front discharge port 142 is larger than the flow passage cross-sectional area of the first front discharge port 141, the flow rate of the compressed fluid discharged through the second front discharge port 142. Can be increased, and overcompression can be suppressed. Further, since the second front discharge port 142 is provided in a thinner portion than the first front discharge port 141, the passage length of the second front discharge port 142 is shorter than the passage length of the first front discharge port 141. Has become. Therefore, even if the flow passage cross-sectional area of the second front discharge port 142 is increased, dead volume is unlikely to occur. Therefore, it is possible to suppress overcompression more preferably while suppressing the dead volume.

(1-5) Since the front rotary body surface 103 is a flat surface orthogonal to the axial direction Z, the front rotary body edge 103a which is the outer peripheral edge of the front rotary body surface 103 is not displaced in the axial direction Z regardless of the circumferential direction. .. On the other hand, the front fixed body edge 73c, which is the outer peripheral edge of the front curved surface 73, is displaced in the axial direction Z according to the circumferential direction. The plurality of front discharge ports 141 to 143 are arranged in the circumferential direction while being displaced in the axial direction Z along the front fixed body edge 73c.

It is difficult for the compressed fluid to flow in the portions of the plurality of front discharge ports 141 to 143 facing the front fixed body outer peripheral surface 62 and the ring outer peripheral surface 105. Therefore, the region of the plurality of front discharge ports 141 to 143 facing the front compression chamber A4 contributes to discharge of the compressed fluid. The area facing the front compression chamber A4 is an area between the front fixed body edge 73c of the plurality of front discharge ports 141 to 143 and the outer peripheral edge of the front rotary body surface 103 (front rotary body edge 103a). is there.

In this respect, in the present embodiment, the plurality of front discharge ports 141 to 143 are arranged along the front fixed body edge 73c in response to the displacement of the front fixed body edge 73c in the axial direction Z according to the circumferential direction. It is displaced in the axial direction Z. As a result, it is possible to secure a wide area in the plurality of front discharge ports 141 to 143 that contributes to the discharge of the compressed fluid, in other words, a region facing the front compression chamber A4. Therefore, overcompression can be suppressed.

Here, from the viewpoint of suppressing overcompression, it is possible to enlarge the plurality of front discharge ports 141 to 143 without displacing the plurality of front discharge ports 141 to 143 in the axial direction Z, for example. However, in this case, the dead volume becomes large.

In this respect, according to the present embodiment, by arranging the plurality of front discharge ports 141 to 143 while displacing them in the axial direction Z, it is possible to increase the region that contributes to the discharge of the compressed fluid, and through that, the plurality of fronts Overcompression can be suppressed without making the discharge ports 141 to 143 excessively large.

(1-6) A line connecting the centers of the plurality of front discharge ports 141 to 143 is defined as a front center line L1. The front center line L1 is arranged closer to the front intermediate line La between the front fixed body edge 73c and the front rotary body edge 103a than the front fixed body edge 73c and the front rotary body edge 103a when viewed from the outside in the radial direction R. There is.

With this configuration, the center of each of the front discharge ports 141 to 143 is arranged closer to the front intermediate line La, so that a large area of the plurality of front discharge ports 141 to 143 facing the front compression chamber A4 can be secured. ..

(1-7) The front valve 150 extends from the front base portion 151 extending in the arrangement direction of the plurality of front discharge ports 141 to 143, and extends from the front base portion 151 in a direction orthogonal to both the arrangement direction and the radial direction R. And a plurality of front arm portions 152 to 154 that cover the plurality of front discharge ports 141 to 143. The arm lengths X1 to X3, which are the lengths of the front arm portions 152 to 154 in the extending direction, are the same.

According to this configuration, since the arm lengths X1 to X3 are the same, the pressures for opening the plurality of front discharge ports 141 to 143 covered by the plurality of front arm portions 152 to 154 are made uniform. Can be planned.

In particular, in the present embodiment, the front base portion 151 corresponds to the plurality of front discharge ports 141 to 143 arranged in the circumferential direction while being displaced in the axial direction Z. It extends in the arrangement direction. As a result, the lengths of the front arm portions 152 to 154 in the extending direction can be made the same. That is, in the configuration in which the plurality of front discharge ports 141 to 143 are displaced in the axial direction Z, the pressure at which the plurality of front discharge ports 141 to 143 are opened can be made uniform.

(Second embodiment)
In this embodiment, the number of vanes 120 is different from that in the first embodiment. This point will be described.

As shown in FIGS. 14 to 16, the compressor 10 of the present embodiment includes a plurality of vanes 120 and a plurality of vane grooves 125, specifically three. The plurality of vane grooves 125 are arranged at equal intervals in the circumferential direction, and more specifically, they are arranged at positions displaced from each other by 120°. Corresponding to this, a plurality of vanes 120 are arranged at equal intervals in the circumferential direction.

Further, a plurality of contact members 190 and a plurality of recessed strips 191 are also provided corresponding to the plurality of vanes 120 and vane grooves 125 provided. The abutting member 190 and the recessed portion 191 are provided inside the plurality of vanes 120 in the radial direction R, and are arranged at equal intervals in the circumferential direction. The contact member 190 and the recess 191 of the present embodiment are provided only in the portion corresponding to the ring portion 102, and do not extend in the axial direction Z from both the rotating body surfaces 103 and 104.

According to this configuration, as shown in FIG. 15, the front compression chamber A4 has three chambers by the three vanes 120, that is, the first front compression chamber A4a, the second front compression chamber A4b, and the third front compression chamber A4c. It is divided into

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

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

The second front compression chamber A4b is arranged on the rotation direction M side of the first front compression chamber A4a. At least a part of the second front compression chamber A4b is arranged on the side opposite to the rotation direction M side with respect to the second front flat surface 72, and of the space inside the front discharge ports 141 to 143 in the radial direction R. Including some or all.

The third front compression chamber A4c is arranged between the first front compression chamber A4a and the second front compression chamber A4b in the circumferential direction. The third front compression chamber A4c is arranged on the rotation direction M side with respect to the first front compression chamber A4a and on the side opposite to the rotation direction M side with respect to the second front compression chamber A4b.

The front intake port 201 of the present embodiment extends in the circumferential direction corresponding to the front cylinder side wall portion 32, and is formed in an arc shape when viewed in the axial direction Z. The front intake port 201 has a front intake opening 201a that opens to the front compression chamber A4. The front intake opening 201a extends in the rotation direction M from a position corresponding to the central portion of the second front flat surface 72 in a portion of the front cylinder inner peripheral surface 33 that defines the front compression chamber A4.

In this embodiment, the circumferential length of the front suction port 201 (in other words, the angular range) and the circumferential length of the front suction opening 201a are set to be the same. The circumferential lengths of the front suction port 201 and the front suction opening 201a may be substantially the same as the extension lengths (circumferential lengths) of the front compression chambers A4a to A4c, for example. That is, the front intake opening 201a extends in the circumferential direction from the position corresponding to the circumferential central portion of the second front flat surface 72 of the front cylinder inner circumferential surface 33 by substantially the same length as the interval between the vanes 120. May be.

Further, assuming that the angular position of the central portion of the second front flat surface 72 is 0°, the front suction opening portion 201a of the present embodiment has the rotation direction M from at least the end portion on the rotation direction M side of the second front flat surface 72. It can be said that it is formed over the range up to the angular position of 120°.

When one of the vanes 120 is in contact with the second front flat surface 72, the vane 120 does not enter the front compression chamber A4. In this case, the spaces on both sides of the vanes 120 that are in contact with the second front flat surface 72 are partitioned by the contact points between the front rotary body surface 103 and the second front flat surfaces 72, and the contact points cause the spaces. It is sealed.

The front intake port 201 and the front discharge ports 141 to 143 are provided at positions circumferentially separated from each other through the portion of the front cylinder side wall portion 32 outside the second front flat surface 72 in the radial direction R. Thus, in the circumferential direction, between the space inside the radial direction R of the front suction port 201 and the space inside the radial direction R of the front discharge ports 141 to 143, the front rotor surface 103 and the second front flat surface are provided. There is a contact point with the surface 72. Thereby, regardless of the positions of the plurality of vanes 120, the both spaces are sealed by the contact points.

That is, the first front compression chamber A4a is configured to communicate with the front intake port 201, but not to communicate with the front discharge ports 141 to 143.
The second front compression chamber A4b is a chamber that communicates with the front discharge ports 141 to 143. However, in the present embodiment, since the circumferential length of the second front compression chamber A4b is longer than the circumferential length of the second front flat surface 72, the second front compression chamber A4b may move the front suction port 201 depending on the phase. There is a case where it is arranged so as to straddle both the inside in the radial direction R and the inside in the radial direction R of the front discharge ports 141 to 143. Even in this case, since the front rotating body surface 103 and the second front flat surface 72 are sealed by the contact portion, the front suction port 201 and the front discharge ports 141 to 143 are restricted from communicating with each other. There is.

The third front compression chamber A4c is a chamber configured so as not to communicate with the front suction port 201, and changes from a state in which the third front compression chamber A4c does not communicate with the front discharge ports 141 to 143 as the rotor 100 rotates to a front discharge port 141 to 143. Move to the state of communication.

As shown in FIG. 16, similarly to the front compression chamber A4, the rear compression chamber A5 is disposed by the three vanes 120 on the first rear compression chamber A5a and on the rotation direction M side of the first rear compression chamber A5a. It is divided into a second rear compression chamber A5b and a third rear compression chamber A5c arranged between the first rear compression chamber A5a and the second rear compression chamber A5b in the circumferential direction. The first rear compression chamber A5a, the second rear compression chamber A5b, and the third rear compression chamber A5c are similar to the first front compression chamber A4a, the second front compression chamber A4b, and the third front compression chamber A4c. The description is omitted.

Further, the rear intake port 202 of the present embodiment is formed in an arc shape extending in the circumferential direction similarly to the front intake port 201, and is arranged to face the front intake port 201. The rear intake port 202 has a rear intake opening 202a that opens to the rear compression chamber A5. The rear suction opening 202a is formed in a portion of the inner peripheral surface 33 of the front cylinder that defines the rear compression chamber A5.

As shown in FIG. 16, in the present embodiment, the rear suction port 202 and the rear suction opening 202a are located from the position corresponding to the center portion of the second rear flat surface 92 in the circumferential direction from the front discharge ports 141 to 143 and the front. It is preferable to extend in the rotation direction M within a range that does not interfere with the valve 150 and the front retainer 155.

However, the present invention is not limited to this, and the circumferential lengths of the rear suction port 202 and the rear suction opening 202a may be the same as the circumferential lengths of the front suction port 201 and the front suction opening 201a. In this case, the length of the front valve 150 and the like in the axial direction Z is shortened, and the front discharge port 141 to 143 and the like so that the rear suction port 202 and the rear suction opening 202a do not interfere with the front discharge ports 141 to 143 and the like. It is preferable to displace the position of 143 or to narrow the angular range of the second front flat surface 72.

Next, the compression operation of the compressor 10 of this embodiment will be described.
As shown in FIGS. 17 and 18, when the rotating shaft 12 is rotated by the electric motor 13, the rotating body 100 is rotated accordingly. As a result, the plurality of vanes 120 rotate while moving in the axial direction Z (left and right direction on the paper surface) along the fixed body surfaces 70 and 90 while maintaining their relative positions. As a result, a volume change occurs in each of the front compression chambers A4a to A4c and each of the rear compression chambers A5a to A5c, and suction, compression or expansion of fluid is performed.

Specifically, in the first front compression chamber A4a, the volume is increased and the suction fluid is sucked from the front suction port 201. In this case, since the front intake opening 201a extends in the rotation direction M from the position corresponding to the center of the second front flat surface 72, the front intake opening 201a opens toward the first front compression chamber A4a. The area (hereinafter, also simply referred to as “opening area”) gradually increases. As a result, the amount of suction sucked from the front suction port 201 into the first front compression chamber A4a increases as the volume of the first front compression chamber A4a increases.

On the other hand, the second front compression chamber A4b, more specifically, the portion of the second front compression chamber A4b on the side opposite to the rotation direction M side with respect to the second front flat surface 72, and the third front compression chamber A4c have different volumes. It is a decreasing room. Therefore, the suction fluid is compressed in the portions of the third front compression chamber A4c and the second front compression chamber A4b on the side opposite to the rotation direction M side with respect to the second front flat surface 72. 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 rotated in the rotation direction M more than the second front flat surface 72 in the second front compression chamber A4b. It is further compressed at the portion opposite to the side.

Then, when the pressure in the portion of the second front compression chamber A4b on the side opposite to the rotation direction M side of the second front flat surface 72 exceeds the threshold value, the front valve 150 opens and the second front compression chamber A4b. The compressed fluid that has been compressed in the above flows into the discharge chamber A1 through the plurality of front discharge ports 141 to 143. The same applies to the rear compression chamber A5.

As described above, the rotating body 100 and the vane 120 rotate, so that the suction and compression cycle operations with 480° as one cycle are repeatedly performed in both compression chambers A4 and A5. In detail, in both compression chambers A4 and A5, the suction fluid is sucked or expanded over a phase of 0° to 240°, and the suction fluid is compressed over a phase of 240° to 480°.

For example, assuming that the angular position of the central portion of the second front flat surface 72 is 0° and the first vane 120 is arranged in the central portion, the first vane 120 is 240° from the angular position of 0°. The suction fluid is sucked in the front compression chamber A4 on the side opposite to the rotation direction M side with respect to the first vane 120 until the angle position is reached.

In particular, since the front intake opening 201a is formed at least over the range from the end of the second front flat surface 72 on the rotational direction M side to the angular position of 120° in the rotational direction M, the first vane is formed. Inhalation fluid is inhaled until 120 reaches an angular position of 240°. As a result, the expansion of the fluid in the front compression chamber A4 can be avoided, and the efficiency can be improved.

Then, until the second vane 120 located on the side opposite to the rotation direction M side of the first vane 120 reaches the angular position of 360° from the angular position of 120°, the second vane 120 is The suction fluid is compressed in the front compression chamber A4 on the rotational direction M side.

Here, for convenience of description, the front compression chambers A4a to A4c are described separately, but the front compression chambers A4a to A4c can be said to be front compression chambers A4 having different phases. That is, it can be said that the space partitioned by the front fixed body surface 70 and the front rotary body surface 103 is partitioned by the plurality of vanes 120 into the front compression chambers A4 having different phases.

According to this embodiment described in detail above, the following operational effects are obtained.
(2-1) Three vanes 120 and vane grooves 125 are provided at equal intervals in the circumferential direction. The compression chambers A4, A5 are composed of a plurality of vanes 120, and first compression chambers A4a, A5a communicating with the suction ports 201, 202 and second compression chambers A4b, A5b communicating with the discharge ports 141-143, 161-163. , And is divided into third compression chambers A4c, A5c arranged between the first compression chambers A4a, A5a and the second compression chambers A4b, A5b in the circumferential direction. The suction fluid is sucked into the first compression chambers A4a and A5a as the rotating body 100 rotates. On the other hand, in the third compression chambers A4c and A5c, the suction fluid is compressed as the rotor 100 rotates, and in the second compression chambers A4b and A5b, the fluid compressed in the third compression chambers A4c and A5c is compressed. Compression is done.

According to such a configuration, the fluid is sucked and compressed in a state where it is partitioned into three chambers by the plurality of vanes 120. As a result, the volume per chamber can be reduced, while the volume can be tripled, so that the overall volume of the compressor 10 can be improved.

Further, as compared with the case where the number of the vanes 120 is one, it is possible to reduce the loss caused by the blowback from the discharge ports 141 to 143, 161 to 163 communicating with the second compression chambers A4b and A5b.

More specifically, in the second compression chambers A4b and A5b, when the next compression is started after the previous compression is completed, the compressed fluid generated by the previous compression is discharged via the discharge ports 141 to 143, 161 to 163. Is blown back to the second compression chambers A4b and A5b at the initial stage. This causes a loss. The loss tends to increase as the pressure difference between the initial stage and the final stage in the second compression chambers A4b and A5b increases.

Here, if the third compression chambers A4c and A5c are not provided as in the first embodiment, the pressure of the second compression chambers A4b and A5b at the initial stage is almost the same as the pressure of the suction fluid. , The pressure change in the second compression chambers A4b and A5b is large. Therefore, the loss tends to increase. Further, the inflow destination of the compressed fluid blown back from the discharge ports 141 to 143, 161 to 163 is a space where the suction fluid is present and is open, so that the circulating flow rate decreases and loss occurs.

In this respect, according to the present embodiment, since the third compression chambers A4c and A5c for performing compression are provided, the pressure of the second compression chambers A4b and A5b in the initial stage is not the pressure of the suction fluid, The pressure of the fluid compressed in the three compression chambers A4c and A5c is obtained. As a result, 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. Further, the inflow destination of the compressed fluid blown back from the discharge ports 141 to 143, 161 to 163 is the third compression chambers A4c and A5c which are not in communication with the suction ports 201 and 202, so that the circulating flow rate is reduced. The resulting loss can be suppressed.

The above embodiments may be modified as follows. Note that the above-described embodiments and the following examples may be combined with each other within a technically consistent range. For convenience of description, the front side (for example, the plurality of front discharge ports 141 to 143) will be described below, but the rear side (for example, the plurality of rear discharge ports 161 to 163) can be similarly changed. ..

In the present embodiment, the accommodation chambers for both the fixed bodies 60, 80 and the rotating body 100 are partitioned by the front cylinder 30 and the rear plate 40, but the present invention is not limited to this, and a specific configuration for partitioning the accommodation chambers. Is optional.

For example, the compressor 10 may include a plate-shaped front plate in place of the front cylinder 30, and a bottomed tubular rear cylinder in place of the rear plate 40. In this case, the accommodation chambers for both the fixed bodies 60 and 80 and the rotating body 100 are defined by the butting of the rear cylinder and the front plate. In this another 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”.

Further, the compressor 10 may be configured to include two cylindrical cylinders, and the two accommodating chambers for the fixed bodies 60 and 80 and the rotating body 100 may be defined by the two cylinders. In this case, the side wall portions of both cylinders correspond to the “cylinder portion”, and the inner peripheral surfaces of both cylinders correspond to the “cylinder inner peripheral surface”. That is, the “cylinder portion” and the “cylinder inner peripheral surface” may be configured by one member or may be configured by a plurality of members. Further, the rear plate 40 may be omitted, and the accommodation chamber may be partitioned by the front cylinder 30 and the rear housing bottom portion 23.

The compression chambers A4, A5 need only be partitioned by at least the rotating body surfaces 103, 104, the fixed body surfaces 70, 90 and the front cylinder inner peripheral surface 33, and other surfaces used to partition the compression chambers A4, A5. Is optional. For example, the compression chambers A4 and A5 may be partitioned by the outer peripheral surface of the tubular portion 101 instead of the outer peripheral surfaces of the rotating body bearings 111 and 112.

The number of front discharge ports is arbitrary as long as it is plural, and may be, for example, two or four or more.
The size of the plurality of front discharge ports 141 to 143 is arbitrary.

For example, the diameter of the first front discharge port 141 may be equal to or less than the distance between the front fixed body edge 73c and the front rotary body edge 103a where the first front discharge port 141 is provided. That is, the discharge port does not need to overlap the front compression chamber A4 in the axial direction Z.

For example, of the plurality of front discharge ports 141 to 143, the third front discharge port 143 located farthest from the second front flat surface 72 has a flow passage cross-sectional area that is closest to the second front flat surface 72. It may be larger than the flow passage cross-sectional area of the discharge port 141. That is, in a configuration in which a plurality of front discharge ports are provided, the first front discharge port is located farther from the second front flat surface 72 than the first front discharge port, and the flow passage cross-sectional area is the second. And a second front discharge port larger than the one front discharge port.

For example, the size of the second front discharge port 142 formed in the thin portion of the front mounting seat portion 145 may be smaller than the size of the first front discharge port 141 formed in the thick portion, or may be the same. Good.

For example, the sizes of the plurality of front discharge ports 141 to 143 may be the same.
The shapes of the plurality of front discharge ports 141 to 143 are not limited to circular shapes and may be arbitrary. For example, the plurality of front discharge ports 141 to 143 may have an oval shape or another shape. Further, the plurality of front discharge ports 141 to 143 may have different shapes. For example, the first front discharge port 141 may have an oval shape having the circumferential direction as the longitudinal direction, and the third front discharge port 143 may have a circular shape.

The plurality of front discharge ports 141 to 143 may have a shape in which the diameter gradually increases from the inner side in the radial direction R toward the outer side in the radial direction R, or vice versa. In this case, the flow path cross-sectional area changes according to the radial direction R.

In such a configuration, the minimum flow passage cross-sectional area of the second front discharge port 142 may be larger than the minimum flow passage cross-sectional area of the first front discharge port 141. Similarly, the minimum flow passage cross-sectional area of the third front discharge port 143 may be larger than the minimum flow passage 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, considering that the front valve 150 can be prevented from being complicated in shape, it is preferable to provide the front seat surface 144.

The plurality of front discharge ports 141 to 143 may be arranged in the circumferential direction without shifting in the axial direction Z.
The arm lengths X1 to X3 may be different. In this case, the front valve 150 may be attached along the circumferential direction so that the extending direction of the front base portion 151 coincides with the circumferential direction.

In this another example, the front retainer 155 may be configured to press the front base portion 151 and a part of each front arm portion 152 to 154. In this case, the front retainer 155 adjusts the pressing area for each front arm portion 152-154 so that the lengths of the swinging portions that cannot be pressed by the front retainer 155 are the same in each front arm portion 152-154. You may. Accordingly, even when the arm lengths X1 to X3 are different, the opening pressures of the front discharge ports 141 to 143 can be made uniform.

When the front base portion 151 extends in the circumferential direction, the width (length in the lateral direction) of the front base portion 151 is adjusted in the circumferential direction so that the front arm portions 152 to 154 have the same length. You may make it different.

The both fixed bodies 60, 80 have the same shape, but the present invention is not limited to this. For example, the front fixed body 60 may have a larger diameter than the rear fixed body 80, or vice versa. In this case, the inner peripheral surface 33 of the front cylinder may have a stepped shape in accordance with the shapes of both the fixed bodies 60 and 80, or the front cylinder that houses the front fixed body 60 and the rear cylinder that houses the rear fixed body 80. The cylinder and the cylinder may be provided separately. That is, the volumes of the compression chambers A4 and A5 may be the same or different.

The curvatures of the contact surface 132 and the vane inner peripheral end surface 124 are arbitrary, and may be the same as the outer peripheral surface of the rotating shaft 12 or the outer peripheral surface of the tubular portion 101, for example.
The contact member 130 and the concave strip 131 may be omitted, and the outer peripheral surface of the tubular portion 101 and the vane 120 may contact.

The vane inner peripheral end surface 124 may be curved so as to be convex inward in the radial direction R, and the abutment surface 132 with which the vane inner peripheral end surface 124 is abutted may be curved so as to be recessed inward in the radial direction R. ..
The contact surface 132 and the outer peripheral surfaces of the rotor bearings 111 and 112 do not have to be continuous.

The contact surface 132 and the outer peripheral surfaces of the rotor bearings 111 and 112 may not be flush with each other. For example, the contact surface 132 may be arranged on the inner side in the radial direction R with respect to the outer peripheral surfaces of the rotary body bearings 111 and 112, and the vane inner peripheral end surface 124 may contact the contact surface 132. In this case, the vane 120 may slide in the axial direction Z while straddling both the contact surface 132 and the outer peripheral surface of the tubular portion 101, for example.

In such a configuration, the rotor bearings 111 and 112 are preferably provided at positions outside the moving range of the vanes 120 (in other words, the swinging range). This can prevent the vane 120 from interfering with the rotor bearings 111 and 112.

The compressor 10 of the embodiment is a single-stage two-cylinder provided with two compression chambers A4 and A5, but the present invention is not limited to this.
For example, as shown in FIG. 19, the compressor 10 may have one cylinder. In detail, the rear fixed body 80, the rear rotary body bearing 112, the rear compression chamber A5, the rear suction port 160, and the rear discharge ports 161-163 may be omitted. In this case, the first front flat surface 71 may be omitted from the front fixed body surface 70.

In such a configuration, for example, a biasing portion 300 that biases the vane 120 toward the front fixed body 60 may be provided. The urging portion 300 may be supported by, for example, an urging support portion 301 provided on the tubular portion 101 so that the urging portion 300 can rotate with the rotation of the rotating body 100. The urging support portion 301 is provided, for example, at the rear end of the tubular portion 101, and has a plate shape protruding outward in the radial direction R. As a result, as the rotating 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 fixed body surface 70 are in contact with each other. In addition, in this another example, as shown in FIG. 19, the contact member 130 may be extended to the rear thrust bearing 114 side.

Further, for example, the front fixed body 60, the front rotary body bearing 111, and the front compression chamber A4 may be omitted. That is, the number of fixed body and rotating body bearings may be one. Further, the number of fixed bodies and rotating body bearings may be three or more.

The front fixed body 60 and the front cylinder 30 may be integrally formed, or the rear fixed 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 need not be through holes as long as the rotary shaft 12 is inserted, and may be non-through holes.
The specific configuration of the rotating body bearings 111 and 112 is arbitrary, and may be, for example, a coated bearing formed of a coating layer formed on the inner wall surfaces of the fixed body insertion holes 61 and 81. In this case, the rotating body bearings 111 and 112 which are coating bearings may support the rotating body 100 on the fixed bodies 60 and 80 by supporting the tubular portion 101 on the inner wall surfaces of the fixed body insertion holes 61 and 81.

Incidentally, when the rotary body bearings 111 and 112 are coating bearings, the compression chambers A4 and A5 are defined by the outer peripheral surface of the cylindrical portion 101, not the outer peripheral surface of the rotary body bearings 111 and 112. The rotary 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 thereof.

Further, the contact member 130 may be formed to have the same length as the recessed strip 131 and fit into the recessed strip 131. In this case, the vane 120 may be configured to move in the axial direction Z while the vane inner peripheral end surface 124 and the contact surface 132 slide.

The fixed body contact surface of the front fixed body surface 70 that contacts the front rotary body surface 103 is not limited to a flat surface, and may be a curved surface. In short, the front fixed body surface 70 may have a fixed body contact surface that contacts the front rotary body surface 103. The same applies to the rear fixed body surface 90.

The rotating body 100 may be inclined with respect to the axial direction Z. In this case, both rotary body surfaces 103 and 104 may be orthogonal to the axial direction Z or may be inclined.
○ The position and shape of the suction port are arbitrary. In short, the structure for sucking the suction fluid into 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 fixed body surface 70 are not limited to the configuration in which they contact all over the inner peripheral end to the outer peripheral end, but may also contact in some radial range R. Further, the first vane end portion 121 and the front fixed body surface 70 are not limited to contact with each other over the entire circumference, but may contact with each other over a partial angular range. The same applies to the second vane end 122 and the rear fixed body surface 90.

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

The number of vanes 120 is arbitrary, and may be plural, for example. Further, the position of the vane 120 in the circumferential direction is arbitrary.
The shapes of the vane 120 and the vane groove 125 are not limited to those of the respective embodiments as long as the vane 120 can rotate while moving in the axial direction Z, and are arbitrary. For example, the vanes may be fan-shaped. Further, the vane may be configured to rotate while moving in the axial direction Z like a pendulum around a predetermined position.

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 in the compressor 10. In this case, the rotating shaft 12 may be rotated by, for example, driving the belt.

The compressor 10 may be used for other than the air conditioner. 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, but may be any fluid.

The compressor 10 may be mounted on any object, not limited to the vehicle.
Next, a suitable example that can be understood from the above-described embodiment and another example will be described below.
(A) A recessed line formed on the outer peripheral surface of the cylindrical portion and extending in the axial direction, and a contact member fitted to the recessed line and having a contact surface for contacting the inner peripheral end surface of the vane. It is preferable that the contact surface forms an inner peripheral end surface of the vane groove.

(B) The fixed body surface is located at a position offset from the first fixed body flat surface in the circumferential direction with respect to the first fixed body flat surface provided at a position separated from the rotating body surface in the axial direction. A second fixed body flat surface that is provided as the fixed body flat surface and is in contact with the rotary body surface, and the curved surface is the first fixed body flat surface and the second fixed body flat surface. It is preferable that the first fixed body is curved in the axial direction so as to gradually approach the rotary body surface from the first fixed body flat surface toward the second fixed body flat surface.

10... Compressor, 11... Housing, 12... Rotating shaft, 30... Front cylinder, 32... Front cylinder side wall part (cylinder part), 33... Front cylinder inner peripheral surface (cylinder inner peripheral surface), 60, 80... Fixed body , 61, 81... Fixed body insertion hole, 62, 82... Fixed body outer peripheral surface, 70, 90... Fixed body surface, 72... Second front flat surface (fixed body flat surface), 73c, 93c... Fixed body edge, 92... Second rear flat surface (fixed body flat surface), 100... Rotating body, 101... Cylindrical portion, 102... Ring portion, 103, 104... Rotating body surface, 103a, 104a... Rotating body edge, 120... Vanes, 121, 122... Vane end portion, 125... vane groove, 141-143, 161-163... plural discharge ports, 144, 164... seat surface, 145, 165... mounting seat portion, 150, 170... valve, 151, 171... base portion, 152-154, 172-174... Arm part, 155, 175... Retainer, La, Lb... Intermediate line, L1, L2... Center line, A1... Discharge chamber, A4, A5... Compression chamber.

Claims (7)

A rotation axis,
A rotating body that rotates with the rotation of the rotating shaft, and has a rotating body surface that intersects the axial direction of the rotating shaft;
A fixed body surface facing the rotating body surface in the axial direction, the fixed body flat surface contacting with the rotating body surface, and provided on both sides in the circumferential direction of the rotating shaft with respect to the fixed body flat surface, and A fixed body having the fixed body surface including a pair of curved surfaces curved in the axial direction so as to gradually separate from the rotary body surface as it moves away from the fixed body flat surface in the circumferential direction;
A cylinder portion for accommodating the rotating body and the fixed body, and having a cylinder inner peripheral surface;
A vane that rotates while moving in the axial direction with the rotation of the rotating body while being inserted into a vane groove formed in the rotating body,
A chamber defined by the rotating body surface, the fixed body surface, and the cylinder inner peripheral surface, in which a volume change is caused by the vanes to suck and compress a fluid,
A discharge chamber, which is arranged radially outside the rotary shaft with respect to the compression chamber via the cylinder portion, and in which a compressed fluid compressed in the compression chamber exists,
Comprising the compression chamber and the discharge chamber to communicate with each other by penetrating the cylinder portion in the radial direction of the rotating shaft, wherein the rotation direction side of the rotating body is more than the flat surface of the fixed body in the cylinder portion. And a plurality of discharge ports arranged in the circumferential direction at a position on the opposite side,
A valve that closes the plurality of discharge ports,
A compressor characterized by being equipped with. The rotating body surface is a flat surface orthogonal to the axial direction,
The plurality of discharge ports,
A first discharge port,
A second discharge port which is provided at a position farther from the flat surface of the fixed body than the first discharge port in the circumferential direction, and has a larger flow passage cross-sectional area than the first discharge port;
The compressor according to claim 1, comprising: The cylinder portion has a cylindrical shape having a curved cylinder outer peripheral surface,
On the cylinder outer peripheral surface, a flat seat surface is formed which is recessed from the cylinder outer peripheral surface and is orthogonal to the radial direction,
The compressor according to claim 1, wherein the plurality of discharge ports and the valve are provided on the seat surface. The cylinder portion has a mounting seat portion that is a portion between the seat surface and the cylinder inner peripheral surface, the thickness of the mounting seat portion is different according to the circumferential direction,
The plurality of discharge ports include a thick-walled portion port and a thin-walled portion port that are provided at positions where the thickness is relatively different in the mounting seat portion,
The compressor according to claim 3, wherein a flow passage cross-sectional area of the thin portion port is larger than a flow passage cross sectional area of the thick portion port. The rotating body surface is a flat surface orthogonal to the axial direction,
The fixed body edge that is the outer peripheral edge of the curved surface is displaced in the axial direction according to the circumferential direction,
The plurality of discharge ports are arranged in the circumferential direction while being displaced in the axial direction along the fixed body edge when viewed from the outside in the radial direction. Compressor. When viewed from the outside in the radial direction, the center line connecting the centers of the plurality of discharge ports has the rotating body edge and the fixed body edge more than the rotating body edge and the fixed body edge which are the outer peripheral edges of the rotating body surface. The compressor according to claim 5, wherein the compressor is arranged closer to the intermediate line. The valve is
A base portion extending in the arrangement direction of the plurality of discharge ports,
A plurality of arm portions extending from the base portion in a direction orthogonal to both the arrangement direction and the radial direction and covering the plurality of discharge ports;
Equipped with
The compressor according to claim 5 or 6, wherein the lengths of the respective arm portions in the extending direction are the same.