JP2020139462A - Compressor - Google Patents

Abstract

To provide a compressor which can discharge a compressed fluid preferably.SOLUTION: A compressor 10 includes: a rotary shaft 12; a rotating body 60 which rotates in conjunction with rotation of the rotary shaft 12; a front fixed body 90 which does not rotate in conjunction with the rotation of the rotary shaft 12; vanes 131 inserted into vane grooves 130 formed at the rotating body 60; a front compression chamber A4; and a discharge chamber A1. The compressor 10 includes: a front discharge port which penetrates through a front cylinder 30 to allow communication between the front compression chamber A4 and the discharge chamber A1; and front communication recessed parts 151 to 153 which allow communication between a fixed body overlapping area of the front discharge port and the front compression chamber A4.SELECTED DRAWING: Figure 1

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 as vane grooves are formed, and a plurality of vanes slidably fitted in the plurality of slit grooves are fixed. An axial vane type compressor equipped with a side plate on which a cam surface as a body surface is formed is described. In the axial vane type compressor described in Patent Document 1, a plurality of vanes rotate while moving in the axial direction of the rotating shaft as the rotating shaft and the rotor rotate, so that the axial end surface of the rotor and the cam as the rotating body surface The fluid is sucked and compressed in a compression chamber partitioned by a surface. Further, Patent Document 1 describes that a side plate as a fixed body is formed with a plurality of discharge refrigerant passages as a plurality of discharge ports penetrating in the axial direction of the rotation shaft. The plurality of discharged refrigerant passages are formed in a portion of the side plate corresponding to the top-side flat portion, which is the thickest portion.

Japanese Unexamined Patent Publication No. 2018-44483

Here, in a compressor that sucks and compresses a fluid using a rotating body, a fixed body, and a vane, there is still room for improvement in the configuration related to the discharge of the compressed fluid. For example, in a configuration in which a compressed fluid is discharged using a discharge port that penetrates the fixed body in the axial direction, the passage length of the discharge port that communicates the compression chamber and the discharge chamber tends to be long, so that the loss tends to be large. In particular, as shown in Patent Document 1, when the discharge port is provided in the thick portion of the fixed body, the passage length of the discharge port tends to be long, and the loss tends to be large.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a compressor capable of suitably discharging a compressed fluid.

A compressor that achieves the above object is a rotating shaft, a rotating body surface that rotates with the rotation of the rotating shaft, and a rotating body surface that intersects the axial direction of the rotating shaft, and a rotating shaft. A rotating body having an outer peripheral surface of a rotating body that intersects in the radial direction, a fixed body surface that does not rotate with the rotation of the rotating shaft, and which faces the rotating body surface in the axial direction, and the above. A fixed body having an outer peripheral surface of the fixed body intersecting in the radial direction, and the rotating body and the fixed body are accommodated, with respect to both the outer peripheral surface of the rotating body and the outer peripheral surface of the fixed body. A cylinder portion having a cylinder inner peripheral surface facing in the radial direction, a vane inserted into a vane groove formed in the rotating body, and a vane that rotates while moving in the axial direction with the rotation of the rotating body. A compression chamber is partitioned by a rotating body surface, a fixed body surface, and an inner peripheral surface of the cylinder, and fluid is sucked and compressed by rotating the vane while moving in the axial direction, via the cylinder portion. A discharge chamber arranged on the radial side of the rotation shaft with respect to the compression chamber and into which the compressed fluid compressed in the compression chamber is introduced, and the compression chamber and the discharge chamber by penetrating the cylinder portion. Is provided at a position facing the overlap region and a discharge port including an overlap region that overlaps with at least one of the fixed body and the rotating body. It is characterized in that it is provided with a communication portion for communicating with the compression chamber.

According to such a configuration, the discharge chamber is arranged radially outward with respect to the compression chamber via the cylinder portion, and the discharge port is formed in the cylinder portion instead of the fixed body. As a result, each discharge port only needs to penetrate the cylinder portion, and the passage length can be shortened. Therefore, the dead volume can be reduced.

Here, in the configuration in which the discharge port is provided in the cylinder portion as described above, a part of the discharge port may be blocked by the outer peripheral surface of the rotating body or the outer peripheral surface of the fixed body. Then, the opening area, which is the area where the discharge port is open with respect to the compression chamber, becomes small, the compressed fluid is not discharged smoothly, and there is a concern that overcompression may occur.

In this respect, according to this configuration, since the overlap region communicates with the compression chamber by the communication portion, the compressed fluid can flow into the overlap region. As a result, the opening area can be increased, and the compressed fluid can be smoothly introduced into the discharge chamber. Therefore, overcompression can be suppressed. From the above, the compressed fluid can be suitably discharged.

Regarding the compressor, the fixed body surface is provided on both sides of the fixed body contact surface that comes into contact with the rotating body surface and the fixed body contact surface in the circumferential direction of the rotating shaft, and the fixed body contact surface is provided. The compression chamber includes a pair of curved surfaces that are curved in the axial direction so as to be separated from the rotating body surface when separated from the circumferential direction, and the compression chamber is provided at a contact portion between the rotating body surface and the fixed body contact surface. On the other hand, a suction space provided on the rotation direction side of the rotating body and where fluid is sucked, and a compression space provided on the side opposite to the rotation direction side of the contact point and where fluid is compressed. The compression space becomes narrower in the axial direction as it approaches the contact point, and the discharge port is on the side opposite to the rotation direction side of the contact point in the cylinder portion. It is provided and communicates with the compression space, and it is preferable that the communication portion communicates the overlap region and the compression space.

According to this configuration, the fixed body surface is provided with the fixed body contact surface that contacts the rotating body surface, and the suction space and the compression space are arranged on both sides of the contact portion, so that the suction space and the compression space are arranged on both sides of the contact portion, so that the vane phase is not affected. It is possible to seal between the suction space and the compression space. As a result, it is possible to prevent the compressed fluid in the compressed space from leaking into the suction space.

Further, the discharge port is provided on the side opposite to the rotation direction side of the contact portion in the cylinder portion, and communicates with the compressed space. As a result, the compressed fluid compressed in the compression space is introduced into the discharge chamber through the discharge port.

Here, the compressed fluid located on the contact point side with respect to the discharge port in the compressed space is not discharged toward the discharge chamber, resulting in a loss. In order to reduce the loss, it is conceivable to arrange the discharge port near the contact point. However, the compressed space becomes narrower in the axial direction as it approaches the contact point. Therefore, if the discharge port is arranged near the contact portion, the overlap region becomes large, and the opening area of the discharge port cannot be increased.

In this regard, according to this configuration, since the communication portion for communicating the overlap region with the compression chamber is formed, the discharge port is a relatively narrow portion in the compression chamber in order to reduce the compressed fluid remaining in the compression space. Even when it is provided in, the opening area can be secured and overcompression can be suppressed.

Regarding the compressor, the discharge port is formed so as to straddle the fixed body edge which is the outer peripheral edge of the curved surface when viewed from the outside of the discharge port, and overlaps the fixed body as the overlap region. The fixed-point overlap region includes the communication portion, the communication portion includes a communication recess formed on the curved surface, and the communication recess is the fixed-point overlap region when viewed from the outside of the discharge port on the outer peripheral surface of the fixed body. It is preferable to have a communication opening formed at a position overlapping the above.

According to such a configuration, a part of the compressed fluid passes through the communication recess and flows into the fixed body overlapping region from the communication opening. As a result, the above-mentioned effect is obtained.
In particular, according to this configuration, the communication recess as the communication portion is formed not on the rotating body but on the curved surface of the fixed body. As a result, the fixed body does not rotate like the cylinder portion. Therefore, the relative position between the communication recess and the discharge port does not change with the rotation of the rotating body. Therefore, the state in which the communication recess and the discharge port are in communication can be maintained relatively easily.

Regarding the compressor, the communication recess may be formed in a tapered shape so that the cross-sectional area gradually decreases from the communication opening toward the inner peripheral side of the fixed body surface.
According to such a configuration, since the communication recess is formed in a tapered shape, the volume of the communication recess can be reduced. As a result, it is possible to reduce the inconvenience caused by forming the communication recess, and more specifically, the loss due to the remaining compressed fluid in the communication recess.

Regarding the compressor, a plurality of the discharge ports are provided in a state of being arranged in the circumferential direction, and a plurality of the communication recesses are provided corresponding to the plurality of discharge ports, and the plurality of discharge ports are provided. Includes a first discharge port and a second discharge port that is more distant from the contact point in the circumferential direction than the first discharge port, and the plurality of communication recesses are the said ones of the first discharge port. A first communication recess for communicating the first fixed-point overlap region, which is a fixed-point overlap region, and the compression chamber, and a second fixed-point overlap region, which is the fixed-point overlap region of the second discharge port. A position including a second communication recess for communicating with the compression chamber, the first communication recess overlapping the overlap region of the first fixed body when viewed from the outside of the first discharge port on the outer peripheral surface of the fixed body. It has a first communication opening as the communication opening formed in, and extends from the first communication opening toward the inner peripheral side of the fixed body surface, and the second communication recess is outside the fixed body. It has a second communication opening as the communication opening formed at a position overlapping the second fixed-point overlap region when viewed from the outside of the second discharge port on the peripheral surface, and from the second communication opening. It extends toward the inner peripheral side of the fixed-point surface, and the length of the first communication recess in the extension direction is preferably longer than the length of the second communication recess in the extension direction.

According to such a configuration, since a plurality of discharge ports are provided, a wider cross-sectional area of the flow path can be secured as compared with a configuration in which only one discharge port is provided. As a result, overcompression can be further suppressed.

Here, since the first discharge port is closer to the contact point than the second discharge port, the compression space of the first discharge port is formed at a position narrower in the axial direction than that of the second discharge port. Correspondingly, the length of the first communication recess corresponding to the first discharge port in the extension direction is longer than the length of the second communication recess corresponding to the second discharge port in the extension direction. This makes it easier to guide the compressed fluid to the first discharge port. Therefore, the compressed fluid can be suitably guided to the first discharge port where the compressed fluid is less likely to flow than the second discharge port.

With respect to the compressor, the discharge port is formed so as to straddle the edge of the rotating body, which is the outer peripheral edge of the rotating body surface, when viewed from the outside of the discharging port, and is formed as an overlapping region with the rotating body. It is preferable that the communicating portion includes an overlapping rotating body overlapping region, and the communicating portion includes a chamfered portion formed between the rotating body surface and the outer peripheral surface of the rotating body and extending in the circumferential direction of the rotating shaft.

According to such a configuration, the rotating body overlapping region communicates with the compression chamber through the gap created by the chamfered portion. As a result, the compressed fluid can flow into the rotating body overlapping region through the gap. Therefore, since the rotating body overlap region can contribute to the discharge of the compressed fluid, overcompression can be suppressed.

According to the present invention, the compressed fluid can be suitably discharged.

The schematic which shows the outline of a compressor. An exploded perspective view of the main configuration. An exploded perspective view of the main configuration seen from the side opposite to FIG. Sectional drawing of the main configuration in a compressor. Side view of the main configuration. FIG. 4 is a sectional view taken along line 6-6 of FIG. FIG. 4 is a sectional view taken along line 7-7 of FIG. Front view of the front discharge port. 9-9 cross-sectional view of FIG. An exploded perspective view of the front cylinder, front valve, and front retainer. A development view schematically showing a rotating body, both fixed bodies, and a vane. A development view schematically showing a rotating body, both fixed bodies, and vanes in a phase different from that of FIG. The exploded perspective view which shows the communication part of another example. The front view of the front discharge port for explaining the communication part of another example. FIG. 14 is a cross-sectional view taken along the line 15-15. The perspective view which shows the vane of another example. An exploded perspective view of another example vane. The cross-sectional view which shows typically the contact mode between the vane of another example and both fixed body surfaces. FIG. 5 is a cross-sectional view schematically showing another example compressor.

Hereinafter, an embodiment of the compressor will be described with reference to the drawings. The compressor of the present embodiment is for, for example, a vehicle, and is specifically mounted on a vehicle for use. The compressor is used in, for example, an air conditioner for vehicles, and the fluid to be compressed by the compressor is a refrigerant containing oil. For convenience of illustration, the rotating shaft 12, the rotating body 60, and both fixed bodies 90 and 110 are shown in a side view in FIG. Further, in FIGS. 6 and 7, a plurality of vanes 131 are schematically shown in a cross-sectional view.

As shown in FIG. 1, the compressor 10 includes a housing 11, a rotating shaft 12, an electric motor 13, an inverter 14, a front cylinder 30 as a cylinder portion, a rear plate 40, a rotating body 60, and a front. It includes a fixed body 90 and a rear fixed body 110.

The housing 11 is, for example, tubular as a whole, and has a suction port 11a for sucking an intake fluid from the outside and a discharge port 11b for discharging a compressed fluid. The rotating shaft 12, the electric motor 13, the inverter 14, the front cylinder 30, the rear plate 40, the rotating body 60, and both fixed bodies 90 and 110 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 on the bottom side of the side wall of the front housing 21 with respect to the open end. 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 that rises from the rear housing bottom portion 23 toward the front housing 21. The front housing 21 and the rear housing 22 are unitized so that the openings face each other. The discharge port 11b is provided on the side wall portion 24 of the rear housing. However, the position of the discharge port 11b is arbitrary.

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 abutted against the bottom 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 fixed bodies 90 and 110 and a rotating body 60. The front cylinder 30 has a bottomed cylinder shape formed smaller than the rear housing 22, and is open toward the bottom portion 23 of the rear housing.

The front cylinder 30 has a front cylinder bottom portion 31 and a front cylinder side wall portion 32 that stands up 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 stepped shape in the axial direction Z, and the rotation shaft 12 with respect to the first bottom portion 31a arranged on the center side and the first bottom portion 31a. It has a second bottom portion 31b which is outside the radial direction R and is arranged on the rear housing bottom portion 23 side with respect to the first bottom portion 31a. A front insertion hole 31c through 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 as an outer peripheral surface arranged on a 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 having the axial direction Z as the axial direction. The outer peripheral surface 34 of the front cylinder is in contact with the inner peripheral surface of the side wall portion 24 of the rear housing 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 outer peripheral surface 34 of the front cylinder in the axial direction Z, and is recessed inward in the radial direction R. The discharge chamber A1 in which the compressed fluid exists is partitioned by the discharge recess 35 and the side wall portion 24 of the rear housing. 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 protruding outward in the radial direction of the rotating shaft 12. The bulging portion 36 is provided at a position straddling both the base end side (front cylinder bottom portion 31 side) of the front cylinder bottom portion 31 and the front cylinder side wall portion 32. The bulging portion 36 bulges outward from the outer peripheral surface 34 of the front cylinder in the radial direction. The front housing 21 and the rear housing 22 are unitized with the bulging portion 36 sandwiched between them. Both housings 21 and 22 regulate the displacement of the front cylinder 30 in the axial direction Z.

As shown in FIG. 1, in the present embodiment, a motor chamber A2 partitioned by a front housing 21 and a front cylinder bottom 31 is provided in the housing 11, and the electric motor 13 is housed in the motor chamber A2. There is. The electric motor 13 is supplied with drive power from the inverter 14, so that the rotating shaft 12 is oriented in the direction indicated by the arrow M, in detail, in the clockwise direction when both fixed bodies 90 and 110 are viewed from the electric motor 13. , "Rotation direction M").

By the way, since the suction port 11a is provided in the front housing 21 that partitions 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 90, the rotating body 60, and the rear fixed body 110 are arranged in this order in the axial direction Z. However, the positions of these parts are arbitrary, and for example, the inverter 14 may be arranged outside the radial direction R of the rotating shaft 12 with respect to the electric motor 13.

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

The rear plate 40 is separate from the front cylinder bottom 31 of the front cylinder 30. The front cylinder 30 and the rear plate 40 are assembled so that the tip end portion of the front cylinder side wall portion 32 is abutted against the rear plate 40, and the opening portion of the front cylinder 30 is closed by the rear plate 40.

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

Incidentally, 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. As a result, the rear plate 40 is supported by the housing 11. If the rear plate 40 is supported by the housing 11, the specific support mode thereof 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 arranged 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 the plate recess 42 is formed.

In addition, in this specification, "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 within a technically consistent range, unless otherwise specified. 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 is in contact with each other and the other part is separated from each other.

As shown in FIG. 1, the compressor 10 includes shaft bearings 51 and 53 that rotatably support the rotating shaft 12.
The front shaft bearing 51 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 of the front housing 21. The front shaft bearing 51 is arranged inside the radial direction R of the rotating shaft 12 with respect to the boss portion 52, and is the front shaft end of both shaft end portions 12a and 12b which are both ends of the rotating shaft 12 in the axial direction Z. The portion 12a is rotatably supported.

A rear insertion hole 41 through which the rotating shaft 12 is inserted is formed in the central portion of the rear plate 40. The rear insertion hole 41 is formed to be the same as or larger than the rear shaft end portion 12b on the side opposite to the front shaft end portion 12a. The rear shaft end portion 12b is inserted into the rear insertion hole 41.

The rear shaft bearing 53 is provided on the inner wall surface of the rear insertion hole 41 and rotatably supports the rear shaft end portion 12b. The rear shaft bearing 53 is, for example, a coating bearing composed of a coating layer formed on the inner wall surface of the rear insertion hole 41.

The coating layer is arbitrary, and may include, for example, a thermosetting resin or a lubricant. Further, the rear shaft bearing 53 is not limited to the coated bearing formed from the coating layer, and may be arbitrary, for example, another sliding bearing or rolling bearing. For convenience of drawing, the rear shaft bearing 53 is shown thicker than it actually is in FIG. 1 and the like.

As described above, in the present embodiment, both shaft end portions 12a and 12b are rotatably supported by both shaft bearings 51 and 53. Here, considering that the front shaft bearing 51 is attached to the boss portion 52 of the front housing 21 and the rear plate 40 on which the rear shaft bearing 53 is formed is supported by the rear housing 22. It can be said that the rotating shaft 12 is rotatably supported with respect to the housing 11 by both shaft bearings 51 and 53. In this embodiment, the rotating shaft 12 is cylindrical.

As shown in FIG. 1, a housing recess 54 is formed at a position of the bottom 23 of the rear housing facing the rotating shaft 12 in the axial direction Z. The housing recess 54 is, for example, a circular recess formed to be one size larger than the rear shaft end portion 12b. A part of the rear shaft end portion 12b is inserted into the housing recess 54.

The compressor 10 is provided in the housing recess 54 and includes a ring plate 55 that regulates the displacement of the rotating shaft 12 in the axial direction Z. The ring plate 55 has, for example, a flat plate ring having the same outer diameter as the housing recess 54, and is fitted in the housing recess 54. The ring plate 55 is provided between the rear shaft end portion 12b and the bottom surface of the housing recess 54. The portion of the rotating shaft 12 excluding the front shaft end portion 12a is sandwiched in the axial direction Z by the front shaft bearing 51 and the ring plate 55. As a result, the movement of the rotating shaft 12 in the axial direction Z is restricted. However, a slight gap may be formed between the ring plate 55 and the rear shaft end portion 12b in order to deal with a dimensional error.

As shown in FIG. 1, a storage chamber A3 partitioned by a front cylinder 30 and a rear plate 40 is formed in the housing 11, and a rotating body 60 and both fixed bodies 90 and 110 are housed in the storage chamber A3. It is contained.

The motor chamber A2 and the accommodation chamber A3 are provided side by side in the axial direction Z in the housing 11. The motor chamber A2 and the accommodation chamber A3 are separated by a front cylinder bottom portion 31 so that the suction fluid in the motor chamber A2 does not flow into the accommodation chamber A3. That is, it can be said that the front cylinder bottom portion 31 is a partition wall portion that separates the motor chamber A2 and the accommodation chamber A3 so that the suction fluid in the motor chamber A2 does not easily flow into the accommodation chamber A3. The rotating shaft 12 is arranged so as to straddle both the motor chamber A2 and the accommodating chamber A3 by penetrating the front cylinder bottom portion 31 as a partition wall portion. Further, the rear plate 40 can be said to be a compartment used for partitioning the accommodation chamber A3.

Next, the rotating body 60 will be described in detail with reference to FIGS. 2 to 5. For convenience of illustration, the rotating body 60 shown in FIG. 5 is shown in a state of being arranged at a rotating position different from that of FIG. 4, that is, in a different phase.

The rotating body 60 rotates in the rotation direction M with the rotation of the rotating shaft 12. The rotating body 60 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 60 is arranged so as to be coaxial with the rotating shaft 12. Therefore, the compressor 10 has a structure of axial motion rather than eccentric motion.

The rotating body 60 includes a rotating body cylinder portion 61 through which the rotating body 12 is inserted, and a rotating body ring portion 70 projecting from the rotating body cylinder portion 61 toward the outer side in the radial direction R.
The rotating body cylinder portion 61 is attached to the rotating shaft 12 so as to rotate integrally with the rotating shaft 12. As a result, the rotating body 60 rotates with the rotation of the rotating shaft 12. The mounting mode of the rotating body cylinder 61 with respect to the rotating shaft 12 is arbitrary. For example, the rotating body cylinder 61 may be fixed to the rotating shaft 12 by press fitting, or straddles the rotating shaft 12 and the rotating body 61. The rotating body cylinder portion 61 may be fixed to the rotating shaft 12 by the fixing pin inserted in the rotating body. Further, the rotating body cylinder portion 61 and the rotating shaft 12 may be connected by a connecting member such as a key, or the rotating body cylinder portion 61 and the rotating shaft 12 are provided in the recess provided on one side and on the other side. It may be configured in which the convex portions are engaged.

The rotating body cylinder portion 61 has, for example, a cylindrical shape with the axial direction Z as the axial direction. The rotating body cylinder portion 61 has, for example, an inner diameter equal to or larger than that of the rotating shaft 12. The inner peripheral surface of the rotating body cylinder 61 and the outer peripheral surface of the rotating shaft 12 face each other in the radial direction R.

The rotating body tubular portion 61 has a tubular tubular portion outer peripheral surface 62 whose axial direction Z is the axial direction. The outer peripheral surface 62 of the tubular portion is curved so as to be convex outward in the radial direction R, and is a cylindrical surface in the present embodiment.

As shown in FIGS. 2 to 4, the rotating body ring portion 70 is at a predetermined position between both rotating body end portions 61a and 61b, which are both ends of the rotating body tubular portion 61 in the axial direction Z (central portion in the present embodiment). It is provided in the vicinity).

The rotating body ring portion 70 has an annular plate shape with the axial direction Z as the plate thickness direction, and has a front rotating body surface 71 and a rear rotating body surface 72 as both end faces in the axial direction Z. Both rotating body surfaces 71 and 72 have a ring shape. Both rotating body surfaces 71 and 72 intersect with respect to the axial direction Z, and in the present embodiment, are flat surfaces orthogonal to the axial direction Z. Therefore, the rotating body edges 71a and 72a, which are the outer peripheral edges of the rotating body surfaces 71 and 72, are linear when viewed from the outside of the radial direction R, and the position in the axial direction Z is constant regardless of the circumferential direction. In the present embodiment, the rotating body edges 71a and 72a are both ends of the ring outer peripheral surface 73 in the axial direction Z.

The ring outer peripheral surface 73, which is the outer peripheral surface of the rotating body ring portion 70, is a surface that intersects the radial direction R and faces the front cylinder inner peripheral surface 33 in the radial direction R. The ring outer peripheral surface 73 of the present embodiment is a cylindrical surface having a constant length in the axial direction Z regardless of the angular position. The outer peripheral surface 73 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 through a minute gap. In the present embodiment, the ring outer peripheral surface 73 corresponds to the “rotating body outer peripheral surface”.

As shown in FIG. 4, the compressor 10 includes thrust bearings 81 and 82 that support the rotating body 60 from the axial direction Z. Both thrust bearings 81 and 82 are arranged on both sides of the rotating body cylinder portion 61 in the axial direction Z, and sandwich the rotating body cylinder portion 61 from the axial direction Z.

Specifically, the front thrust bearing 81 is arranged in the space created by the front cylinder bottom portion 31 being formed in a stepped shape. The front thrust bearing 81 supports the rotating body cylinder portion 61 (specifically, the front rotating body end portion 61a) from the axial direction Z in a state of being supported by the front cylinder bottom portion 31.

The rear thrust bearing 82 is arranged in the thrust accommodating recess 83 formed in the rear plate 40. The thrust accommodating recess 83 is formed in a portion of the inner wall surface of the rear insertion hole 41 on the side of the first plate surface 43 with respect to the second plate surface 44 and a peripheral portion of the rear insertion hole 41 on the first plate surface 43. The rear thrust bearing 82 is arranged in the thrust accommodating recess 83, and supports the rotating body cylinder portion 61 (specifically, the rear rotating body end portion 61b) from the axial direction Z while being supported by the rear plate 40. ing.

Both thrust bearings 81 and 82 have a disk shape, and a rotating shaft 12 is inserted through both thrust bearings 81 and 82. In the present embodiment, the inner peripheral surfaces of both thrust bearings 81 and 82 and the outer peripheral surface of the rotating shaft 12 are in contact with each other. In this case, it can be said that both thrust bearings 81 and 82 support the rotating shaft 12 by abutting the rotating shaft 12 in the radial direction R. However, the present invention is not limited to this, and both thrust bearings 81 and 82 and the rotating shaft 12 may be separated from each other in the radial direction R.

Both fixed bodies 90 and 110 are arranged on both sides of the rotating body ring portion 70 in the axial direction Z. In other words, it can be said that the both fixed bodies 90 and 110 are arranged so as to face each other with the rotating body ring portions 70 separated from each other in the axial direction Z, and the rotating body ring portions 70 are between the both fixed bodies 90 and 110. It can be said that it is located in.

Both fixed bodies 90 and 110 are fixed to the front cylinder 30 (in other words, the housing 11) so as not to rotate with the rotation of the rotating shaft 12. For example, the fixed bodies 90 and 110 are fixed to the front cylinder 30 by fastening the fasteners (not shown) from the side of the fixed bodies 90 and 110 while penetrating the front cylinder side wall portion 32.

However, the present invention is not limited to this, and the fixing mode of both fixed bodies 90 and 110 to the front cylinder 30 is arbitrary, and may be fixed by, for example, press fitting or fitting. Further, one or a plurality of fastening portions for fastening the front fixed body 90 and the front cylinder bottom portion 31 may be provided, and one or a plurality of fastening portions for fastening the rear fixed body 110 and the rear plate 40 may be provided. It may have been.

The configurations of both fixed bodies 90 and 110 will be described in detail. In this embodiment, both fixed bodies 90 and 110 have the same shape.
As shown in FIGS. 1 to 4, of both the fixed bodies 90 and 110, the front fixed body 90 arranged on the front cylinder bottom 31 side (in other words, a position close to the motor chamber A2) has, for example, a ring shape (book). In the embodiment, it is an annular shape) and has a front fixed-point insertion hole 91 into which the rotating shaft 12 is inserted. In the present embodiment, the front fixed-point subring insertion hole 91 is a through hole penetrating in the axial direction Z. The front fixed body 90 is arranged in the front cylinder 30 with the rotating shaft 12 inserted into the front fixed body insertion hole 91.

The front fixed body 90 has a surface that intersects the radial direction R and has a front cylinder inner peripheral surface 33 and a front fixed body outer peripheral surface 92 that faces the radial direction R. In the present embodiment, the outer peripheral surface 92 of the front fixed body and the inner peripheral surface 33 of the front cylinder are in contact with each other. However, the present invention is not limited to this, and the inner peripheral surface 33 of the front cylinder and the outer peripheral surface 92 of the front fixed body may be separated from each other.

The front fixed body 90 includes a front rear surface 93 that faces the front cylinder bottom 31 and the axial direction Z. The front back surface 93 and the inner bottom surface 31d of the front cylinder bottom portion 31 may be separated from each other or may be in contact with each other.

As shown in FIGS. 1 to 4, the rear fixed body 110 arranged on the rear plate 40 side (in other words, the side away from the motor chamber A2) as a partition portion among the two fixed bodies 90 and 110 is Like the front fixed-point 90, it is ring-shaped (annular in this embodiment) and has a rear fixed-point insertion hole 111 into which the rotating shaft 12 is inserted. In the present embodiment, the rear fixed-point subring insertion hole 111 is a through hole penetrating in the axial direction Z. The rear fixed body 110 is arranged in the front cylinder 30 with the rotating shaft 12 inserted into the rear fixed body insertion hole 111. That is, in the present embodiment, the rotating shaft 12 penetrates both the fixed bodies 90 and 110 in the axial direction Z.

The rear fixed body 110 has a surface that intersects the radial direction R and has a front cylinder inner peripheral surface 33 and a rear fixed body outer peripheral surface 112 that faces the radial direction R. In the present embodiment, the outer peripheral surface 112 of the rear fixed body and the inner peripheral surface 33 of the front cylinder are in contact with each other. That is, the front cylinder inner peripheral surface 33 of the present embodiment faces the ring outer peripheral surface 73 and the outer peripheral surfaces 92 and 112 of both fixed bodies in the radial direction R. However, the present invention is not limited to this, and the inner peripheral surface 33 of the front cylinder and the outer peripheral surface 112 of the rear fixed body may be separated from each other.

The rear fixed body 110 includes a rear back surface 113 facing the first plate surface 43 of the rear plate 40 and the axial direction Z. The rear back surface 113 and the first plate surface 43 may be separated from each other or may be in contact with each other.

As shown in FIG. 4, the rotating body 60 is supported by the fixed bodies 90 and 110 by inserting the rotating body cylinder portion 61 into the fixed body insertion holes 91 and 111 of the fixed bodies 90 and 110.
Specifically, of the both rotating body end portions 61a and 61b which are both ends of the rotating body cylinder portion 61 in the axial direction Z, the front rotating body end portion 61a is inserted into the front fixed body insertion hole 91 and is fixed to the front. It penetrates the front fixed body 90 through the body insertion hole 91.

The front fixed body insertion hole 91 is formed so as to correspond to the rotating body cylinder portion 61 (specifically, the outer peripheral surface 62 of the cylinder portion), and in the present embodiment, the rotating body cylinder portion 61 corresponds to a cylindrical shape. It is formed in a circular shape when viewed from the axial direction Z. The diameter of the front fixed-point insertion hole 91 may be the same as or slightly larger than the diameter of the outer peripheral surface 62 of the tubular portion. The front rotating body end portion 61a is rotatably supported by the front fixed body 90 by the front rotating body bearing 94 formed on the inner wall surface of the front fixed body insertion hole 91.

Similarly, of the two rotating body end portions 61a and 61b, the rear rotating body end portion 61b on the side opposite to the front rotating body end portion 61a is inserted into the rear fixed-point body insertion hole 111, and the rear fixed-point body insertion hole 111. It penetrates the rear fixed body 110 through.

The rear fixed body insertion hole 111 is formed corresponding to the rotating body cylinder portion 61 (specifically, the outer peripheral surface 62 of the cylinder portion), and corresponds to the cylindrical shape of the rotating body cylinder portion 61 in the present embodiment. It is formed in a circular shape when viewed from the axial direction Z. The diameter of the rear fixed-point insertion hole 111 may be the same as or slightly larger than the diameter of the outer peripheral surface 62 of the tubular portion. The rear rotating body end portion 61b is rotatably supported by the rear fixed body 110 by the rear rotating body bearing 114 formed on the inner wall surface of the rear fixed body insertion hole 111.

That is, the end portions 61a and 61b of both rotating bodies are supported by both fixed bodies 90 and 110 via the bearings 94 and 114 of both rotating bodies. As a result, the rotating body 60 is supported with respect to both the fixed bodies 90 and 110, and the displacement of the rotating body 60 with respect to both the fixed bodies 90 and 110 can be suppressed.

Further, the end portions 61a and 61b of both rotating bodies constitute both ends of the rotating body 60 in the axial direction Z. Therefore, it can be said that both ends of the rotating body 60 are supported by the rotating body bearings 94 and 114. As a result, the rotating body 60 is stably held.

Further, since the fixed body insertion holes 91 and 111 are formed so as to correspond to the rotating body cylinder portion 61, there is a gap formed between the inner wall surface of the fixed body insertion holes 91 and 111 and the outer peripheral surface 62 of the cylinder portion. It is hard to occur or the gap is small.

Incidentally, the rotating body bearings 94 and 114 are, for example, coated bearings composed of a coating layer formed on the inner wall surface of the fixed body insertion holes 91 and 111. In this case, for convenience of drawing, the rotating body bearings 94 and 114 are shown thicker than they actually are in FIG. 4 and the like. The specific configurations of the rotating body bearings 94 and 114 are not limited to the coated bearings, and may be arbitrary, for example, other sliding bearings or rolling bearings.

The front fixed body 90 has a front fixed body surface 100 as a fixed body surface facing the front rotating body surface 71 in the axial direction Z. The front fixed body surface 100 is a plate surface on the side opposite to the front back surface 93. The front fixed body surface 100 has a ring shape, and in this embodiment, it is annular when viewed from the axial direction Z.

As shown in FIG. 3, the front fixed body surface 100 connects the first front flat surface 101 and the second front flat surface 102 that intersect the axial direction Z (orthogonal in the present embodiment) and both front flat surfaces 101 and 102. It includes a pair of front curved surfaces 103 as curved surfaces.

As shown in FIG. 4, both front flat surfaces 101 and 102 are displaced in the axial direction Z. Specifically, the second front flat surface 102 is arranged at a position closer to the front rotating body surface 71 than the first front flat surface 101, and is in contact with the front rotating body surface 71. The surfaces of the front fixed body surface 100 other than the second front flat surface 102 are separated from the front rotating body surface 71.

Both front flat surfaces 101 and 102 are arranged apart from each other in the circumferential direction of the front fixed body 90, for example, they are displaced by 180 °. In this embodiment, both front flat surfaces 101 and 102 are fan-shaped. In the following description, the circumferential positions of both fixed bodies 90 and 110 are also referred to as angular positions.

The pair of front curved surfaces 103 are each fan-shaped. As shown in FIG. 3, the pair of front curved surfaces 103 are arranged to face each other in the direction orthogonal to both the axial direction Z and the opposite directions of both front flat surfaces 101 and 102. Both front curved surfaces 103 have the same shape.

The pair of front curved surfaces 103 connect both front flat surfaces 101 and 102, respectively. Specifically, one of the pair of front curved surfaces 103 connects one ends of both front flat surfaces 101 and 102 in the circumferential direction, and the other end of both front flat surfaces 101 and 102 in the circumferential direction. The other ends on the opposite side of the part are connected to each other.

Here, for convenience of explanation, the angle position of the boundary portion between the front curved surface 103 and the first front flat surface 101 is set to the first angle position θ1, and the angle of the boundary portion between the front curved surface 103 and the second front flat surface 102. Let the position be the second angle position θ2. For convenience of illustration, the angular positions θ1 and θ2 are shown by broken lines in FIG. 3, but the boundary portions are actually smoothly continuous.

The front curved surface 103 is a curved surface displaced in the axial direction Z according to the circumferential direction (in other words, the angular position of the front fixed body 90). Specifically, the front curved surface 103 is curved in the axial direction Z so as to gradually approach the front rotating body surface 71 from the first angle position θ1 to the second angle position θ2. In other words, the pair of front curved surfaces 103 are provided on both sides in the circumferential direction with respect to the second front flat surface 102, and gradually separate from the front rotating body surface 71 as the distance from the second front flat surface 102 in the circumferential direction increases. It is curved in the axial direction Z.

In the present embodiment, the front curved surface 103 has a front concave surface 103a that is curved in the axial direction Z so as to be concave with respect to the front rotating body surface 71 and an axial direction that is convex toward the front rotating body surface 71. It has a front convex surface 103b that is curved in Z.

The front concave surface 103a is arranged closer to the first front flat surface 101 than the second front flat surface 102, and the front convex surface 103b is arranged closer to the second front flat surface 102 than the first front flat surface 101. There is. The front concave surface 103a and the front convex surface 103b are connected to each other. That is, the front curved surface 103 is a curved surface having an inflection point.

The angle range occupied by the front convex surface 103b and the angle range occupied by the front concave surface 103a may be the same or different. Moreover, the position of the inflection point is arbitrary. Further, since the front curved surface 103 can be said to be a curved surface that is curved in a wavy shape, focusing on this point, the front fixed body surface 100 can be said to be a front wave surface that includes a portion that is curved in a wavy shape.

Further, the thickness of the front fixed body 90 (in other words, the length in the axial direction Z) differs depending on the angular position in response to the wave shape of the front fixed body surface 100 as described above. There is. Specifically, the portion of the front fixed body 90 corresponding to the second front flat surface 102 is the thickest, and the portion corresponding to the first front flat surface 101 is the thinnest. The portion of the front fixed body 90 corresponding to the front curved surface 103 gradually becomes thinner from the second front flat surface 102 toward the first front flat surface 101.

Further, the front fixed body outer peripheral surface 92 has a shape in which the length in the axial direction Z differs depending on the angular position. Specifically, the front fixed body outer peripheral surface 92 has a cylindrical base surface 92a and a protruding surface 92b that protrudes from the base surface 92a toward the front rotating body surface 71 and has different protruding dimensions depending on the angle position. ing. The length of the base surface 92a in the axial direction Z is constant regardless of the angular position, and is the same as the minimum thickness of the front fixed body 90. The protruding surface 92b is formed so that the protruding dimension gradually becomes shorter from the portion corresponding to the second front flat surface 102 to the portion corresponding to the first front flat surface 101. The protruding surface 92b is not formed on the portion corresponding to the first front flat surface 101.

Here, the front fixed-point edge 104, which is the outer peripheral edge of the front curved surface 103, is displaced in the axial direction Z according to the circumferential direction. In the present embodiment, since the front curved surface 103 has a front concave surface 103a and a front convex surface 103b, the front fixed-point edge 104 has a sinusoidal shape when viewed from the radial R outside. The front fixed body edge 104 can be said to be a boundary between the front fixed body outer peripheral surface 92 and the front curved surface 103.

The rear fixed body 110 has a rear fixed body surface 120 as a fixed body surface facing the rear rotating body surface 72 in the axial direction Z. The rear fixed body surface 120 is a plate surface on the side opposite to the rear back surface 113. The rear fixed body surface 120 has a ring shape when viewed from the axial direction Z, and is annular in the present embodiment.

In the present embodiment, the rear fixed body surface 120 has the same shape as the front fixed body surface 100. As shown in FIG. 2, the rear fixed body surface 120 connects the first rear flat surface 121 and the second rear flat surface 122 which intersect with the axial direction Z (orthogonal in this embodiment) and both rear flat surfaces 121 and 122. It includes a pair of rear curved surfaces 123 as curved surfaces.

As shown in FIG. 4, both rear flat surfaces 121 and 122 are displaced in the axial direction Z. Specifically, the second rear flat surface 122 is arranged at a position closer to the rear rotating body surface 72 than the first rear flat surface 121, and is in contact with the rear rotating body surface 72. The surfaces of the rear fixed body surface 120 other than the second rear flat surface 122 are separated from the rear rotating body surface 72.

Both rear flat surfaces 121 and 122 are arranged apart from each other in the circumferential direction of the rear fixed body 110, for example, they are displaced by 180 °. In this embodiment, both rear flat surfaces 121 and 122 are fan-shaped.

The pair of rear curved surfaces 123 are each fan-shaped. The pair of rear curved surfaces 123 are arranged to face each other in the direction orthogonal to both the axial direction Z and the opposite directions of the two rear flat surfaces 121 and 122. One of the pair of rear curved surfaces 123 connects one end portions of both rear flat surfaces 121 and 122 in the circumferential direction, and the other is opposite to the one end portion of both rear flat surfaces 121 and 122 in the circumferential direction. The other ends on the side are connected to each other.

In other words, the pair of rear curved surfaces 123 are provided on both sides in the circumferential direction with respect to the second rear flat surface 122, and gradually separate from the rear rotating body surface 72 as the distance from the second rear flat surface 122 in the circumferential direction increases. It is curved in the axial direction Z.

Both fixed body surfaces 100 and 120 are opposed to each other via the rotating body ring portion 70 so as to be separated from each other in the axial direction Z with their angular positions shifted by 180 °.
The facing distance between the fixed body surfaces 100 and 120 is constant regardless of their angular position (in other words, the circumferential position). Specifically, as shown in FIG. 4, the first front flat surface 101 and the second rear flat surface 122 face each other in the axial direction Z, and the second front flat surface 102 and the first rear flat surface 121 It faces the axial direction Z. The amount of deviation in the axial direction Z between the two front flat surfaces 101 and 102 is the same as the amount of deviation between the two rear flat surfaces 121 and 122. Hereinafter, the amount of deviation in the axial direction Z between the front flat surfaces 101 and 102 and the amount of deviation between both rear flat surfaces 121 and 122 are simply referred to as "deviation amount Z1".

Further, the degree of curvature of the front curved surface 103 and the degree of curvature of the rear curved surface 123 are the same. That is, the front curved surface 103 and the rear curved surface 123 are curved in the same direction so that the facing distance does not fluctuate according to the angular position. As a result, the facing distance between the fixed body surfaces 100 and 120 is constant at any angle position.

The specific shapes of the first rear flat surface 121, the second rear flat surface 122, and the rear curved surface 123 are the same as those of the first front flat surface 101, the second front flat surface 102, and the front curved surface 103. Therefore, detailed description will be omitted. Similarly, the specific shapes of the rear fixed-point edge 124, which is the outer peripheral edge of the rear fixed-point outer peripheral surface 112 and the rear curved surface 123, are the same as those of the front fixed-point outer peripheral surface 92 and the front fixed-point edge 104. Explanation is omitted.

Here, the circumferential direction of both the fixed bodies 90 and 110 and the rotating body 60 and the circumferential direction of the rotating shaft 12 coincide with each other, and the radial direction of both the fixed bodies 90 and 110 and the rotating body 60 and the radial direction of the rotating shaft 12. It coincides with R, and the axial direction of both the fixed bodies 90 and 110 and the rotating body 60 and the axial direction Z of the rotating shaft 12 coincide with each other. Therefore, the circumferential direction, radial direction R, and axial direction Z of the rotating shaft 12 may be appropriately read as the circumferential direction, radial direction, and axial direction of the rotating body 60, and the circumferential direction and radial direction of both fixed bodies 90 and 110. And may be read as axial direction.

In the present embodiment, both rotating body surfaces 71 and 72 correspond to "rotating body surfaces", both fixed bodies 90 and 110 correspond to "fixed bodies", and both fixed body surfaces 100 and 120 correspond to "fixed body surfaces". Both rotating body surfaces 71 and 72 correspond to "rotating body surfaces". Further, in the present embodiment, the second front flat surface 102 and the second rear flat surface 122 correspond to the “fixed-point contact surface”. Both fixed-point outer peripheral surfaces 92 and 112 correspond to the "fixed-point outer peripheral surface", and both fixed-point edges 104 and 124 correspond to the "fixed-point edge".

In the following description, the contact portion between the front rotating body surface 71 and the second front flat surface 102 is also referred to as a front contact portion Pf. The front contact portion Pf has a fan shape like the second front flat surface 102. The contact point between the rear rotating body surface 72 and the second rear flat surface 122 is also referred to as a rear contact point Pr. The rear contact portion Pr is fan-shaped like the second rear flat surface 122.

As shown in FIG. 4, the compressor 10 includes compression chambers A4 and A5 in which fluid is sucked and compressed. Both compression chambers A4 and A5 are provided in the accommodation chamber A3, and are specifically arranged on both sides of the rotating body ring portion 70 in the axial direction Z.

The front compression chamber A4 is partitioned by using the front cylinder inner peripheral surface 33, the front rotating body surface 71, and the front fixed body surface 100, and in the present embodiment, these surfaces are partitioned by the cylinder portion outer peripheral surface 62. In the present embodiment, the front cylinder inner peripheral surface 33 corresponds to the “cylinder inner peripheral surface”.

The rear compression chamber A5 is partitioned by using the front cylinder inner peripheral surface 33, the rear rotating body surface 72, and the rear fixed body surface 120, and in the present embodiment, these surfaces are partitioned by the cylinder portion outer peripheral surface 62. .. In the present embodiment, the front compression chamber A4 and the rear compression chamber A5 have the same size.

Here, both 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 radial direction R of both compression chambers A4 and A5 via the front cylinder side wall portion 32.

By the way, in the present embodiment, the discharge chamber A1 faces the radial direction R with respect to a part of the front compression chamber A4, while it faces the radial direction R with respect to the entire rear compression chamber A5. , 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 to face at least a part of the rear compression chamber A5 in the radial direction R. ..

As shown in FIGS. 2 to 5, the compressor 10 includes a vane groove 130 formed in the rotating body 60 and a vane 131 inserted into the vane groove 130.
The vane groove 130 is formed in the rotating body ring portion 70 of the rotating body 60. The vane groove 130 penetrates the rotating body ring portion 70 in the axial direction Z and opens on both rotating body surfaces 71 and 72. The vane groove 130 of the present embodiment extends in the radial direction R with the direction orthogonal to both the axial direction Z and the radial direction R as the width direction, and opens toward the outside of the radial direction R. On the other hand, the vane groove 130 is not formed in the rotating body cylinder portion 61. The vane groove 130 has a pair of side surfaces arranged so as to be separated from each other in the circumferential direction.

As a reminder, in the present embodiment, the rotating body ring portion 70 is a portion outside the radial direction R with respect to the rotating body cylinder portion 61. Therefore, the rotating body cylinder portion 61 exists inside the radial direction R of the rotating body ring portion 70. That is, the rotating body ring portion 70 is a portion provided on the outer peripheral surface 62 of the tubular portion and projecting outward from the outer peripheral surface 62 of the tubular portion in the radial direction.

The vane 131 has a rectangular plate shape as a whole. The vane 131 is arranged between both fixed bodies 90 and 110 (in other words, both fixed body surfaces 100 and 120) in a state where the plate surfaces of the vane 131 intersect with respect to the circumferential direction of the rotation shaft 12. The vane 131 has a plate shape whose thickness direction is orthogonal to both the width direction of the vane groove 130, that is, the axial direction Z and the radial direction R.

Both plate surfaces of the vane 131 and both side surfaces of the vane groove 130 face each other in the circumferential direction (in other words, the width direction of the vane groove 130). The width of the vane groove 130 (in other words, the facing distance between both side surfaces of the vane groove 130) may be the same as or slightly wider than the plate thickness of the vane 131. The vane 131 inserted into the vane groove 130 is sandwiched by both side surfaces of the vane groove 130. The vane 131 is allowed to move axially Z along the vane groove 130. In the present embodiment, both ends of the vane 131, specifically, the vane 131 in the axial direction Z, are in contact with both fixed body surfaces 100 and 120.

The compressor 10 of the present embodiment includes a plurality of vane grooves 130 and vanes 131, and in detail, includes three. The plurality of vane grooves 130 are arranged at equal intervals in the circumferential direction, and in detail, they are arranged at positions shifted by 120 ° from each other. Correspondingly, a plurality of vanes 131 are arranged at equal intervals in the circumferential direction.

According to such a configuration, the vane 131 rotates in the rotation direction M as the rotating body 60 rotates. In this case, since both fixed body surfaces 100 and 120 are curved, the vane 131 moves in the axial direction Z along both fixed body surfaces 100 and 120 due to contact with both fixed body surfaces 100 and 120 (in other words,). Swing). That is, the vane 131 rotates while moving in the axial direction Z. As a result, the vane 131 enters the front compression chamber A4 and the rear compression chamber A5. That is, it can be said that the vane groove 130 rotates the vane 131 with the rotation of the rotating body 60 so that the vane 131 is arranged across both the compression chambers A4 and A5.

The moving distance (in other words, the swing distance) of the vane 131 is the amount of displacement in the axial direction Z between the two front flat surfaces 101 and 102 (or between the two rear flat surfaces 121 and 122), that is, the displacement amount Z1. Further, the vane 131 is continuously in contact with both fixed body surfaces 100 and 120 during the rotation of the rotating body 60, which may cause intermittent contact, in detail, periodical separation or contact. Hateful.

Here, as shown in FIG. 6, the front compression chamber A4 is divided into three parts chambers, that is, a first front compression chamber A4a, a second front compression chamber A4b, and a third front compression chamber A4c by three vanes 131. Has been done.

For convenience of explanation, the parts chamber arranged on the rotation direction M side with respect to the second front flat surface 102 among the three parts chambers is referred to as the first front compression chamber A4a.
Further, of the three parts chambers, the parts chamber arranged on the side opposite to the rotation direction M side with respect to the first front compression chamber A4a is referred to as the second front compression chamber A4b. 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 102.

Further, of the three parts chambers, the parts chamber arranged between the first front compression chamber A4a and the second front compression chamber A4b in the circumferential direction is referred to as the third front compression chamber A4c. 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.

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 an angle range of 120 °.

Strictly speaking, when one of the plurality of vanes 131 is in contact with the second front flat surface 102, the vanes 131 have not entered the front compression chamber A4. In this case, the spaces on both sides of the vane 131 in contact with the second front flat surface 102 are partitioned by the front contact portion Pf and sealed by the front contact portion Pf. Therefore, even when one of the plurality of vanes 131 is in contact with the second front flat surface 102, the front compression chamber A4 is divided into three parts chambers. In the present embodiment, for convenience of explanation, even when one of the plurality of vanes 131 is in contact with the second front flat surface 102, the front compression chamber A4 is provided by the three vanes 131 in each front compression chamber A4a. It is assumed that it is partitioned into ~ A4c.

As shown in FIG. 7, similarly to the front compression chamber A4, the rear compression chamber A5 has the first rear compression chamber A5a and the first rear compression chamber A5a on the rotation direction M side by the three vanes 131. It is partitioned into a second rear compression chamber A5b arranged on the opposite side and a third rear compression chamber A5c arranged on the rotation direction M side with respect to the first rear compression chamber A5a. The first rear compression chamber A5a, the second rear compression chamber A5b, and the third rear compression chamber A5c are the same as the first front compression chamber A4a, the second front compression chamber A4b, and the third front compression chamber A4c. The explanation is omitted.

Next, the configuration related to the suction of the suction fluid and the discharge of the compressed fluid into the compression chambers A4 and A5 will be described. For convenience of illustration, the front intake port 140 and the rear intake port 170 are schematically shown in FIG. Further, the configuration related to the suction of the suction fluid and the discharge of the compressed fluid into the front compression chamber A4 and the configuration related to the suction of the suction fluid and the discharge of the compressed fluid into the rear compression chamber A5 are basically the same.

As shown in FIGS. 2 to 4 and 6, the compressor 10 includes a front suction port 140 for sucking the suction fluid into the front compression chamber A4. The front suction port 140 is formed in, for example, the front cylinder 30, and specifically extends in the axial direction Z so as to straddle both the front cylinder bottom portion 31 and the front cylinder side wall portion 32.

Further, the front suction port 140 extends in the circumferential direction corresponding to the side wall portion 32 of the front cylinder, and is formed in an arc shape when viewed from the axial direction Z. At least a part of the front suction port 140 is arranged outside the radial direction R with respect to the first front compression chamber A4a. In other words, the first front compression chamber A4a includes a part or all of the space inside the radial R of the front suction port 140. The first front compression chamber A4a is configured so as to communicate with the front suction port 140 but not with the front discharge ports 141 to 143.

The front suction port 140 is open to the motor chamber A2 and is open to the front compression chamber A4. The motor chamber A2 and the front compression chamber A4 are communicated with each other by the front suction port 140.

Specifically, as shown in FIG. 6, the front suction port 140 has a front suction opening 140a opened at a position communicating with the first front compression chamber A4a. The front suction opening 140a extends in the rotation direction M from a position corresponding to the central portion in the circumferential direction of the front contact portion Pf (in other words, the second front flat surface 102) of the inner peripheral surface 33 of the front cylinder. There is. The extended length of the front suction opening 140a may be substantially the same as, for example, the extended length (length in the circumferential direction) of each of the front compression chambers A4a to A4c. That is, the front suction opening 140a is located in the circumferential direction of the inner peripheral surface 33 of the front cylinder by substantially the same length as the circumferential interval of each vane 131 from the position corresponding to the central portion of the front contact portion Pf in the circumferential direction. It may be extended.

Further, assuming that the angle position of the central portion of the second front flat surface 102 is 0 °, the front suction opening 140a is, for example, 120 ° in the rotation direction M from at least the end portion of the second front flat surface 102 on the rotation direction M side. It is preferable that it is formed over a range up to the angular position of.

As shown in FIGS. 6 and 8 to 10, the compressor 10 includes a plurality of front discharge ports 141 to 143 as discharge passages for discharging the compressed fluid compressed in the front compression chamber A4 toward the discharge chamber A1. ing.

As shown in FIG. 6, the plurality of front discharge ports 141 to 143 are located on the rotating body 60 rather than the front contact portion Pf (in other words, the second front flat surface 102) of the front cylinder side wall portions 32 of the front cylinder 30. It is provided at a position opposite to the rotation direction M side, and is arranged in the circumferential direction.

At least a part of the front discharge ports 141 to 143 is arranged outside the radial direction R with respect to the second front compression chamber A4b. In other words, the second front compression chamber A4b includes a part or all of the space inside the radial R of the front discharge ports 141 to 143. Further, the third front compression chamber A4c of the present embodiment shifts from a state in which it does not communicate with the front discharge ports 141 to 143 as the rotating body 60 rotates, to a state in which it communicates with the front discharge ports 141 to 143.

Here, focusing on the relationship between the suction / compression in the front compression chamber A4 and the front contact point Pf, the suction fluid is always sucked in the space on the rotation direction M side with respect to the front contact point Pf. On the other hand, the fluid is always compressed in the space opposite to the rotation direction M side with respect to the front contact portion Pf. That is, the front compression chamber A4 is provided on the rotation direction M side with respect to the front contact portion Pf, and the suction space Sf1 at which the suction fluid is sucked and the rotation direction M side with respect to the front contact portion Pf It includes a compression space Sf2 provided on the opposite side and where the fluid is compressed.

In the present embodiment, the suction space Sf1 is composed of the first front compression chamber A4a when the vane 131 is in contact with the second front flat surface 102, and the vane 131 is in contact with the second front flat surface 102. If not, it is composed of a space on the rotation direction M side of the front contact portion Pf in the second front compression chamber A4b. The volume of the suction space Sf1 increases with the rotation of the vane 131. The suction space Sf1 communicates with the front suction port 140, and the suction fluid is introduced into the suction space Sf1.

The compression space Sf2 is composed of a second front compression chamber A4b, and more specifically, is a space on the second front compression chamber A4b opposite to the front contact portion Pf in the rotation direction M side. In other words, the compression space Sf2 is a space surrounded by a vane 131 that separates the second front compression chamber A4b and the third front compression chamber A4c and the front contact portion Pf.

The compression space Sf2 gradually narrows in the axial direction Z toward the front contact portion Pf. Therefore, the volume of the compression space Sf2 decreases with the rotation of the vane 131. In the compressed space Sf2, there is a compressed fluid in which the suction fluid is compressed. Therefore, the pressure in the compression space Sf2 is higher than the pressure in the suction space Sf1. The plurality of front discharge ports 141 to 143 communicate with the compression space Sf2.

By the way, regardless of the position (phase) of the vane 131, the compression space Sf2 and the suction space Sf1 are sealed by the front contact portion Pf. As a result, the leakage of the compressed fluid from the compression space Sf2 to the suction space Sf1 is regulated, and the communication between the front suction port 140 and the front discharge ports 141 to 143 is regulated. That is, the front contact portion Pf functions as a sealing portion that regulates the movement of the fluid from the compression space Sf2 to the suction space Sf1.

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 102, the second front compression chamber A4b has the suction space Sf1 and the suction space Sf1 depending on the phase. Both of the compressed spaces Sf2 may be configured.

The same applies to the rear contact portion Pr. That is, as shown in FIG. 7, the rear compression chamber A5 is provided on the rotation direction M side with respect to the rear contact portion Pr, with respect to the suction space Sr1 in which the suction fluid is sucked and the rear contact portion Pr. The compression space Sr2, which is provided on the side opposite to the rotation direction M side and in which the fluid is compressed, is included.

The detailed configuration of the front discharge ports 141 to 143 will be described below.
As shown in FIG. 6 and the like, 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. The front seat surface 144 is the radial outside of the compression space Sf2, specifically, the rotation of the rotating body 60 between the front compression chamber A4 and the discharge chamber A1 of the outer peripheral surface 34 of the front cylinder, and the rotation of the rotating body 60 rather than the front contact portion Pf. It is formed on the portion opposite to the direction M side. The front seat surface 144 is a flat surface orthogonal to the radial direction R, and extends in the axial direction Z.

Here, the portion of the front 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 a front mounting seat portion 145 on which the front seat surface 144 is formed.

Since the front cylinder inner peripheral surface 33 is curved and the front seat surface 144 is a flat surface, the thickness of the front mounting seat portion 145 differs depending on the circumferential direction. Specifically, the thickness of the front mounting seat portion 145 is thinner on the central side than on both end sides of the front seat surface 144 when viewed from the axial direction Z.

As shown in FIGS. 6 and 8, a 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 so as to be separated from the front contact portion Pf in the order of the first front discharge port 141, the second front discharge port 142, and the third front discharge port 143. Therefore, the first front discharge port 141 is formed at a position closest to the front contact portion Pf 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 separated from the front contact portion Pf in the circumferential direction with respect to the first front discharge port 141.

The plurality of front discharge ports 141 to 143 communicate the front compression chamber A4 and the discharge chamber A1 by penetrating the front cylinder 30 (specifically, the front mounting seat portion 145). The penetration direction (in other words, the extension direction) of the plurality of front discharge ports 141 to 143 in the present embodiment is, for example, the thickness direction of the front mounting seat portion 145, and more specifically, the direction orthogonal to the front seat surface 144. is there.

As described above, since the thickness of the front mounting seat portion 145 differs depending on the circumferential direction, at least a part of the front discharge ports 141 to 143 is provided at positions where the thickness is relatively different. Therefore, in at least a part of the front discharge ports 141 to 143, the passage length is different 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 closer to the center than the first front discharge port 141. It is formed in a 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 the portion where the first front discharge port 141 is provided. Similarly, the first front discharge port 141 can be said to be a thick portion port provided in a portion of the front mounting seat portion 145 that is thicker than the portion where the second front discharge port 142 is provided.

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

As shown in FIG. 8, 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 path cross section of the first front discharge port 141 of the present 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 path cross section of the second front discharge port 142 and the third front discharge port 143 is larger than the flow path cross section 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 this 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. 8, the plurality of front discharge ports 141 to 143 correspond to the front fixed body edge 104 displaced in the axial direction Z according to the circumferential direction, and are axially oriented along the front fixed body edge 104. They are arranged in the circumferential direction while being displaced to Z.

Specifically, the line connecting the intermediate points between the front fixed-point edge 104 and the front rotating body edge 71a is defined as the intermediate line Ln2. The intermediate line Ln2 is displaced in the axial direction Z along the front fixed-point edge 104 according to the circumferential direction, and in detail, has a sinusoidal shape when viewed from the outside in the radial direction R.

In such a configuration, the line passing through the center of each front discharge port 141 to 143 is designated as the center line Ln1. In this case, the plurality of front discharge ports 141 to 143 are arranged so that the center line Ln1 is arranged closer to the intermediate line Ln2 than the front rotating body edge 71a and the front fixed body edge 104. Therefore, in the present embodiment, the plurality of front discharge ports 141 to 143 are arranged so as to be slightly displaced from each other in the axial direction Z. That is, the arrangement directions of the plurality of front discharge ports 141 to 143 are 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 to each other and are inclined.

In the present embodiment, the central line Ln1 and the intermediate line Ln2 substantially coincide with each other. The fact that the center line Ln1 is arranged closer to the intermediate line Ln2 than the front rotating body edge 71a and the front fixed body edge 104 includes the case where the center line Ln1 coincides with the intermediate line Ln2.

The size of the first front discharge port 141 is larger than, for example, the distance in the axial direction Z between the front rotating body edge 71a and the front fixed body edge 104 at the position where the first front discharge port 141 is provided. Focusing on the fact that the axial distance Z between the edges 71a and 104 can be said to be the axial length Z of the front compression chamber A4, the first front discharge port 141 is the axial Z of the front compression chamber A4. It can be said that it is formed larger than the length of.

Therefore, the first front discharge port 141 is formed so as to straddle both the front rotating body edge 71a and the front fixed body edge 104 when viewed from the outside of the first front discharge port 141. That is, the first front discharge port 141 overlaps both sides in the axial direction Z with respect to the front compression chamber A4, and overlaps with both the rotating body 60 and the front fixed body 90.

The first front discharge port 141 has a first fixed-point overlap region Ca1 that overlaps with the front fixed-point 90, and a first rotating body overlap region Cb1 that overlaps with the rotating body 60.

The first fixed-point overlapping region Ca1 is a region protruding from the front fixed-point edge 104 in a direction away from the rotating body 60. In other words, the first fixed-point overlapping region Ca1 is a region protruding from the front compression chamber A4 toward the outer peripheral surface 92 of the front fixed-point subring.

The first rotating body overlap region Cb1 is a region protruding from the front rotating body edge 71a in a direction away from the front fixed body 90. In other words, the first rotating body overlap region Cb1 is a region overhanging the ring outer peripheral surface 73 side from the front compression chamber A4.

The same applies to the second front discharge port 142 and the third front discharge port 143. That is, the second front discharge port 142 has a second fixed-point overlap region Ca2 that overlaps with the front fixed-point 90, and a second rotating body overlap region Cb2 that overlaps with the rotating body 60. The third front discharge port 143 has a third fixed-point overlap region Ca3 that overlaps with the front fixed-point 90, and a third rotating body overlap region Cb3 that overlaps with the rotating body 60.

In the present embodiment, the shapes of the fixed-point overlapping regions Ca1 to Ca3 are different, and the shapes of the rotating body overlapping regions Cb1 to Cb3 are also different.
As shown in FIGS. 8 and 9, the compressor 10 is provided at a position facing the fixed body overlapping regions Ca1 to Ca3, and the fixed body overlapping regions Ca1 to Ca3 and the front compression chamber A4 (specifically, It is provided with front communication recesses 151 to 153 as a communication portion for communicating with the compressed space Sf2).

The front communication recesses 151 to 153 are formed on the front curved surface 103. The front communication recesses 151 to 153 are arranged in the circumferential direction in correspondence with the plurality of front discharge ports 141 to 143 being arranged in the circumferential direction. Specifically, the first front communication recess 151, the second front communication recess 152, and the third front communication recess 153 are arranged in this order in the direction away from the front contact portion Pf. The first fixed-point overlap region Ca1 and the first front communication recess 151 face each other, the second fixed-point overlap region Ca2 and the second front communication recess 152 face each other, and the third fixed-point overlap The region Ca3 and the third front communication recess 153 face each other.

It can be said that the fixed-point overlap regions Ca1 to Ca3 and the front communication recesses 151 to 153 face each other in the radial direction R, and also face each other in the penetration direction of the front discharge ports 141 to 143.

The front communication recesses 151 to 153 have communication openings 151a to 153a formed on the outer peripheral surface 92 of the front fixed body. The communication openings 151a to 153a are formed at positions overlapping the fixed-point overlap regions Ca1 to Ca3 when viewed from the outside of the front discharge ports 141 to 143.

As a reminder, when viewed from the outside of the front discharge ports 141 to 143, the front discharge ports 141 to 143 are viewed from the outside in the penetration direction (in other words, the extension direction) of the front discharge ports 141 to 143. When you see it. Further, the case of viewing from the outside of the front discharge ports 141 to 143 can be said to be the case of viewing the front discharge ports 141 to 143 from the discharge chamber A1 side or the radial R outside.

The communication openings 151a to 153a may be formed so as to overlap the entire fixed-point overlap regions Ca1 to Ca3, for example. In the present embodiment, as shown in FIG. 8, the communication openings 151a to 153a are formed in the same shape as the fixed-point overlap regions Ca1 to Ca3.

The front communication recesses 151 to 153 extend from the communication openings 151a to 153a toward the inner peripheral side of the front fixed body surface 100. In the present embodiment, the front communication recesses 151 to 153 extend in the penetrating direction of the front discharge ports 141 to 143. That is, the extending direction of the front communication recesses 151 to 153 coincides with the penetrating direction of the front discharge ports 141 to 143.

The front communication recesses 151 to 153 of the present embodiment are formed in a tapered shape so that the cross section gradually decreases from the communication openings 151a to 153a toward the inner peripheral side of the front fixed body surface 100. In the present embodiment, the front communication recesses 151 to 153 extend in the penetrating direction of the front discharge ports 141 to 143 with the communication openings 151a to 153a as the base ends so as to gradually taper.

As shown in FIG. 6, the lengths L1 to L3 in the extending direction of the front communication recesses 151 to 153 are different. Specifically, the length L1 in the extension direction of the first front communication recess 151 communicating with the first fixed-point overlap region Ca1 is the extension of the second front communication recess 152 communicating with the second fixed-point overlap region Ca2. It is longer than the length L2 in the installation direction. Further, the length L2 of the second front communication recess 152 in the extension direction is longer than the length L3 of the third front communication recess 153 communicating with the third fixed-point overlap region Ca3 in the extension direction. That is, the front communication recesses 151 to 153 of the present embodiment are formed longer as they are closer to the front contact portion Pf.

Here, paying attention to the fact that the compression space Sf2 becomes narrower in the axial direction Z as it approaches the front contact portion Pf, the front communication recesses 151 to 153 are formed longer as the compression space Sf2 becomes narrower in the axial direction Z. It can be said that it has been done. However, in the present embodiment, the front communication recesses 151 to 153 are formed only on the outer peripheral side of the front curved surface 103 in the radial direction R from the center, and do not penetrate in the radial direction R.

As shown in FIGS. 9 and 10, the compressor 10 includes a front valve 161 that opens and closes the front discharge ports 141 to 143, and a front retainer 162 that adjusts the opening degree of the front valve 161.

The front valve 161 and the front retainer 162 are provided on the front seat surface 144. The front valve 161 and the front retainer 162 are screwed into the screw holes 144a formed in the front seat surface 144 in a state where the bolt B penetrates both the front valve 161 and the front retainer 162, whereby the front seat surface 144 It is fixed to.

The front valve 161 normally closes the front discharge ports 141 to 143, and opens when the pressure in the front compression chamber A4 (specifically, the compression space Sf2) exceeds the threshold value to close the front discharge ports 141 to 143. The state shifts from the state to the state in which the front discharge ports 141 to 143 are opened. As a result, the compressed fluid compressed in the front compression chamber A4 is discharged to the discharge chamber A1. In this case, the opening angle of the front valve 161 is regulated by the front retainer 162.

As shown in FIGS. 2 to 4, the compressor 10 includes a rear suction port 170 that sucks the suction fluid into the rear compression chamber A5. The rear suction port 170 is formed in, for example, the front cylinder 30, and specifically extends in the axial direction Z so as to straddle both the front cylinder bottom portion 31 and the front cylinder side wall portion 32.

Further, as shown in FIG. 7, the rear suction port 170 extends in the circumferential direction corresponding to the side wall portion 32 of the front cylinder, and is formed in an arc shape when viewed from the axial direction Z. At least a part of the rear suction port 170 is arranged outside the radial direction R with respect to the first rear compression chamber A5a. In other words, the first rear compression chamber A5a includes a part or all of the space inside the radial R of the rear suction port 170.

The rear suction port 170 is open to the motor chamber A2 and is open 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 170.

Specifically, as shown in FIG. 7, the rear suction port 170 has a rear suction opening 170a opened at a position communicating with the first rear compression chamber A5a. The rear suction opening 170a extends in the rotation direction M from a position corresponding to the central portion of the second rear flat surface 122 in the circumferential direction of the front cylinder inner peripheral surface 33.

By the way, in the present embodiment, the rear suction port 170 and the rear suction opening 170a are the front discharge ports 141 to 143, the front valve 161 and the front retainer from the positions corresponding to the central portion in the circumferential direction of the second rear flat surface 122. It extends in the rotation direction M within a range that does not interfere with 162.

However, the present invention is not limited to this, and the circumferential lengths of the rear suction port 170 and the rear suction opening 170a may be the same as the circumferential lengths of the front suction port 140 and the front suction opening 140a. In this case, the length of the front valve 161 or the like in the axial direction Z may be shortened or the front discharge port 141 to 141 to prevent the rear suction port 170 and the rear suction opening 170a from interfering with the front discharge ports 141 to 143 and the like. The positions of the 143s may be shifted, or the angle range of the second front flat surface 102 may be narrowed.

Incidentally, in the present embodiment, two suction ports 140 and 170 are provided corresponding to the two compression chambers A4 and A5. The front suction port 140 and the rear suction port 170 are arranged so as not to communicate with each other in the circumferential direction, and in detail, they are arranged at positions shifted by 180 °. As a result, both suction ports 140 and 170 communicate with each other, for example, the suction amount of the suction fluid in the other compression chamber is reduced due to the suction of the suction fluid in one of the compression chambers A4 and A5. It is possible to suppress the inconvenience caused by the above.

The compressor 10 includes a plurality of rear discharge ports 171 to 173 as discharge ports for discharging the compressed fluid compressed in the rear compression chamber A5 toward the discharge chamber A1, and rear communication recesses 174 to 176 as communication portions. , A rear valve 177 and a rear retainer 178. The specific configurations of the rear discharge ports 171 to 173, rear communication recesses 174 to 176, rear valves 177, and rear retainer 178 are the same as those of the front discharge ports 141 to 143, front communication recesses 151 to 153, rear valves 177, and rear retainer 178. Therefore, a detailed description will be omitted. In addition, "front" in the above-mentioned explanation may be read as "rear".

In the present embodiment, the first discharge ports 141, 171 and the first communication recesses 151, 174 correspond to the "first discharge port" and the "first communication recess", and the second discharge ports 142, 172 and the second It can be said that the communication recesses 152 and 175, or the third discharge ports 143 and 173 and the third communication recesses 153 and 176 correspond to the "second discharge port" and the "second communication recess". However, the present invention is not limited to this, and the second discharge ports 142, 172 and the second communication recesses 152, 175 correspond to the "first discharge port" and the "first communication recess", and the third discharge ports 143, 173 and the third It can be said that the communication recesses 153 and 176 correspond to the "second discharge port" and the "second communication recess".

Next, a series of operations of the compressor 10 will be described as the operation of the present embodiment with reference to FIGS. 11 and 12. 11 and 12 are development views schematically showing the rotating body 60, the fixed bodies 90, 110, and the vane 131, and both figures have different phases of the rotating body 60 and the vane 131. In FIGS. 11 and 12, for convenience of illustration, each port 140 to 143, 170 to 173 is schematically shown.

As shown in FIGS. 11 and 12, when the rotating shaft 12 is rotated by the electric motor 13, the rotating body 60 rotates accordingly. As a result, the plurality of vanes 131 rotate while moving in the axial direction Z along both the fixed body surfaces 100 and 120 while maintaining their circumferential positions. In FIGS. 11 and 12, the plurality of vanes 131 move downward while moving in the left-right direction of the paper surface. As a result, volume changes occur in the front compression chambers A4a to A4c and the rear compression chambers A5a to A5c, and the fluid is sucked, compressed, or expanded. That is, it can be said that the vane 131 rotates while moving in the axial direction Z to suck and compress the fluid in both the compression chambers A4 and A5.

Specifically, in the space on the rotation direction M side of the front contact portion Pf in the second front compression chamber A4b and the first front compression chamber A4a, the volume increases and the suction fluid is sucked from the front suction port 140. Will be.

On the other hand, in the compression space Sf2 and the third front compression chamber A4c, the volume decreases with the rotation of the rotating body 60, and the suction fluid is compressed. 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 further compressed in the compression space Sf2. Then, the compressed fluid compressed in the compression space Sf2 is discharged to the discharge chamber A1 via the front discharge ports 141 to 143. The same applies to the rear compression chamber A5.

As described above, as the rotating body 60 and the vane 131 rotate, in both the compression chambers A4 and A5, the suction and compression cycle operations with 480 ° as one cycle are repeatedly performed in the three parts chambers, respectively. Specifically, in both the compression chambers A4 and A5, the suction fluid is sucked or expanded in a phase of 0 ° to 240 °, and the suction fluid is compressed in a phase of 240 ° to 480 °.

For example, assuming that the angle position of the central portion of the second front flat surface 102 is 0 ° and the first vane 131 is arranged at the central portion, the first vane 131 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 131 until the angle position is reached.

In particular, since the front suction opening 140a is formed at least over a range from the end of the second front flat surface 102 on the rotation direction M side to an angular position of 120 ° in the rotation direction M, the first vane The suction fluid is sucked until the 131 reaches the 240 ° angular position. As a result, it is possible to prevent the fluid from expanding in the front compression chamber A4, and it is possible to improve the efficiency.

Then, until the second vane 131, which is on the side opposite to the rotation direction M side of the first vane 131, reaches the angle position of 360 ° from the angle position of 120 °, the second vane 131 with respect to the second vane 131. The suction fluid is compressed in the front compression chamber A4 on the rotation direction M side.

Here, for convenience of explanation, the front compression chambers A4a to A4c have been described separately, but the front compression chambers A4a to A4c can be said to be compression chambers having different phases. That is, the space partitioned by the front rotating body surface 71, the front fixed body surface 100, the outer peripheral surface of the cylinder portion 62, and the inner peripheral surface 33 of the front cylinder is partitioned by a plurality of vanes 131 into three compression chambers having different phases. It can be said that. In the present embodiment, the rotating body 60 rotates by 480 °, so that the fluid is sucked and compressed in each of the three compression chambers on the front side and the three compression chambers on the rear side.

In this embodiment, for convenience of explanation, the front compression chambers A4a to A4c are partitioned by a plurality of vanes 131, and are defined by the positional relationship between the front suction ports 140 and the front discharge ports 141 to 143. I explained, but it is not limited to this. For example, if one cycle of one compression chamber is focused on and explained, it is as follows.

By moving the first vane 131 to the rotation direction M side with respect to the front contact portion Pf, compression communicating with the front suction port 140 on the side opposite to the rotation direction M side with respect to the first vane 131. A chamber is formed. As the vane 131 rotates, the compression chamber increases in volume while maintaining communication with the front suction port 140. As a result, inhalation is performed in the compression chamber.

After that, the second vane 131 moves toward the front contact portion Pf in the rotation direction M, so that the compression chamber is partitioned by the first vane 131 and the second vane 131. Suction is performed in the compression chamber until the second vane 131 reaches the end of the front suction opening 140a on the M side in the rotation direction.

After that, when the second vane 131 moves to the rotation direction M side of the front suction opening 140a on the rotation direction M side, the compression chamber does not communicate with the front suction port 140, and the rotating body 60 further rotates. It communicates with the front discharge ports 141 to 143. Further, since the volume of the compression chamber decreases with the rotation of the rotating body 60 at this stage, compression is performed in the compression chamber. Then, when the second vane 131 reaches the position where it abuts on the second front flat surface 102, the volume of the compression chamber becomes "0", and one cycle of suction and compression of the compression chamber ends.

Further, in the present embodiment, since the front communication recesses 151 to 153 are formed, the fixed-point overlap regions Ca1 to Ca3 communicate with the front compression chamber A4 (specifically, the compression space Sf2). As a result, the area of the front discharge ports 141 to 143 that is open to the front compression chamber A4 (hereinafter, also simply referred to as “opening area”) is increased. In other words, the fixed-point overlap regions Ca1 to Ca3 function as portions for discharging the compressed fluid. The same applies to the rear communication recesses 174 to 176.

According to the present embodiment described in detail above, the following effects are obtained. In the following description, for convenience of explanation, the configuration on the front side is basically described, but the same effect can be obtained on the configuration on the rear side.

(1) The compressor 10 includes a rotating shaft 12, a rotating body 60 that rotates with the rotation of the rotating shaft 12, a front fixed body 90 that does not rotate with the rotation of the rotating shaft 12, a rotating body 60, and front fixing. It is provided with a front cylinder 30 as a cylinder portion for accommodating the body 90. The rotating body 60 has a front rotating body surface 71 that intersects the axial direction Z, and a ring outer peripheral surface 73 as the rotating body outer peripheral surface that intersects the radial direction R. The front fixed body 90 has a front fixed body surface 71 facing the front rotating body surface 71, a front fixed body surface 100 facing the axial direction Z, and a front fixed body outer peripheral surface 92 intersecting the radial direction R. The front cylinder side wall portion 32 of the front cylinder 30 has a front cylinder inner peripheral surface 33 facing the outer peripheral surface 73 of the ring and the outer peripheral surface 92 of the front fixed body in the radial direction R.

The compressor 10 includes a vane 131 inserted into a vane groove 130 formed in the rotating body 60, and a front compression chamber A4 partitioned by using a front rotating body surface 71, a front fixed body surface 100, and a front cylinder inner peripheral surface 33. The discharge chamber A1 is arranged on the outer side of the front compression chamber A4 in the radial direction via the front cylinder 30. In the front compression chamber A4, the vane 131 rotates while moving in the axial direction Z as the rotating body 60 rotates, so that the fluid is sucked and compressed.

The compressor 10 includes front discharge ports 141 to 143 that communicate the front compression chamber A4 and the discharge chamber A1 by penetrating the front cylinder 30. The compressed fluid compressed in the front compression chamber A4 by the front discharge ports 141 to 143 is introduced into the discharge chamber A1.

The front discharge ports 141 to 143 include overlapping regions Ca1 to Ca3 and Cb1 to Cb3 that overlap at least one of the front fixed body 90 and the rotating body 60 (both in the present embodiment). The compressor 10 is provided at a position facing the fixed body overlap regions Ca1 to Ca3, and is a front communication recess 151 to 153 as a communication portion for communicating the fixed body overlap regions Ca1 to Ca3 and the front compression chamber A4. It has.

According to this configuration, the discharge chamber A1 is arranged radially R outside with respect to the front compression chamber A4 via the front cylinder 30, and the front discharge ports 141 to 143 are not the front fixed body 90 but the front. It is formed on the cylinder 30. As a result, the front discharge ports 141 to 143 need only penetrate the front cylinder 30, and the passage length can be shortened. For example, in the present embodiment, the passage length of each front discharge port 141 to 143 can be made equal to or less than the thickness of the front cylinder side wall portion 32. Therefore, the dead volume can be reduced, and the loss caused by the compressed fluid in each of the front discharge ports 141 to 143 flowing back into the front compression chamber A4 can be reduced.

Here, in the configuration in which the front discharge ports 141 to 143 are provided on the front cylinder 30 as described above, a part of the front discharge ports 141 to 143 is a rotating body 60 or a front fixed body 90 (specifically, the ring outer peripheral surface 73 or the front). It may be blocked by the outer peripheral surface of the fixed body 92). Then, the opening area becomes small, the compressed fluid is not discharged smoothly, and there is a concern about the inconvenience of overcompression.

In this regard, according to the present embodiment, the fixed-point overlap regions Ca1 to Ca3 are communicated with the front compression chamber A4 by the front communication recesses 151 to 153. As a result, the compressed fluid can flow into the fixed body overlapping regions Ca1 to Ca3. Therefore, the opening area can be increased, and the compressed fluid can be smoothly introduced into the discharge chamber A1. That is, the fixed-point overlap regions Ca1 to Ca3 can function as contributing to the discharge of the compressed fluid. Therefore, overcompression can be suppressed. From the above, the compressed fluid can be suitably discharged.

(2) The front fixed body surface 100 is provided on both sides in the circumferential direction with respect to the front fixed body surface 100 that comes into contact with the front rotating body surface 71 and the front fixed body surface 100, and the front rotating body surface is separated from the front fixed body surface 100 in the circumferential direction. Includes a pair of front curved surfaces 103 curved in the axial direction Z away from 71. The front compressor chamber A4 is provided on the rotation direction M side with respect to the front contact portion Pf, which is the contact portion between the front rotating body surface 71 and the second front flat surface 102, and the suction space Sf1 at which fluid is sucked. A compression space Sf2 provided on the side opposite to the rotation direction M side with respect to the front contact portion Pf and in which the fluid is compressed is included.

According to this configuration, the front fixed body surface 100 is provided with the second front flat surface 102 that comes into contact with the front rotating body surface 71, and the suction space Sf1 and the compression space Sf2 are provided on both sides of the front contact point Pf that is the contact point. Is arranged so that the suction space Sf1 and the compression space Sf2 can be sealed regardless of the phase of the vane 131. As a result, it is possible to prevent the compressed fluid in the compressed space Sf2 from leaking into the suction space Sf1.

Further, the front discharge ports 141 to 143 are provided on the front cylinder 30 (specifically, the front cylinder side wall portion 32) on the side opposite to the rotation direction M side from the front contact portion Pf, and communicate with the compression space Sf2. are doing. As a result, the compressed fluid compressed in the compression space Sf2 is introduced into the discharge chamber A1 through the front discharge ports 141 to 143.

Here, in the compression space Sf2, the compressed fluid located on the front contact portion Pf side of the front discharge ports 141 to 143 is not discharged toward the discharge chamber A1, resulting in a loss. In order to reduce the loss, it is conceivable to arrange the front discharge ports 141 to 143 near the front contact portion Pf. However, since the compression space Sf2 gradually narrows in the axial direction Z toward the front contact portion Pf, when the front discharge ports 141 to 143 are arranged near the front contact portion Pf, the overlap region Ca1 to Ca3 and Cb1 to Cb3 become large, and the opening area of the front discharge ports 141 to 143 cannot be increased.

In this regard, according to the present embodiment, front communication recesses 151 to 153 are formed to communicate the fixed-point overlap regions Ca1 to Ca3 with the front compression chamber A4. As a result, the opening area can be secured even when the front discharge ports 141 to 143 are provided in a relatively narrow portion of the front compression chamber A4 in order to reduce the compressed fluid remaining in the compression space Sf2, and overcompression can be achieved. Can be suppressed.

(3) The front discharge ports 141 to 143 are formed so as to straddle the front fixed body edge 104 which is the outer peripheral edge of the front curved surface 103 when viewed from the outside of the front discharge ports 141 to 143, and are fixed to the front. It has fixed-point overlap regions Ca1 to Ca3 that overlap the body 90. The front communication recesses 151 to 153 are formed on the front curved surface 103. The front communication recesses 151 to 153 have communication openings 151a to 153a formed at positions overlapping the fixed body overlap regions Ca1 to Ca3 when viewed from the outside of the front discharge ports 141 to 143 on the outer peripheral surface 92 of the front fixed body. ing.

According to such a configuration, a part of the compressed fluid passes through the front communication recesses 151 to 153, flows into the fixed-point overlapping regions Ca1 to Ca3 from the communication openings 151a to 153a, and is discharged to the discharge chamber A1. To. As a result, the above-mentioned effect is obtained.

In particular, in the present embodiment, the front communication recesses 151 to 153 as the communication portion are formed not on the rotating body 60 but on the front curved surface 103 of the front fixed body 90. As a result, the front fixed body 90 does not rotate like the front cylinder 30. Therefore, the relative positions of the front communication recesses 151 to 153 and the front discharge ports 141 to 143 do not change with the rotation of the rotating body 60. Therefore, it is possible to easily maintain a state in which the front communication recesses 151 to 153 and the front discharge ports 141 to 143 are in communication with each other.

(4) The communication openings 151a to 153a are formed in the same shape as the fixed-point overlap regions Ca1 to Ca3.
According to such a configuration, the opening area can be increased while suppressing the increase in the volume of the front communication recesses 151 to 153.

(5) The front communication recesses 151 to 153 are formed in a tapered shape so that the cross section gradually decreases from the communication openings 151a to 153a toward the inner peripheral side of the front fixed body surface 100.

According to such a configuration, since the front communication recesses 151 to 153 are formed in a tapered shape, the volume of the front communication recesses 151 to 153 can be reduced. As a result, the loss caused by forming the front communication recesses 151 to 153 can be reduced.

More specifically, when the vane 131 passes over the front communication recesses 151 to 153, the compressed fluid remains in the front communication recesses 151 to 153. Since the remaining compressed fluid flows into the compressed space Sf2 before compression and expands, the compressed fluid remaining in the front communication recesses 151 to 153 becomes a loss.

In this regard, according to the present embodiment, since the front communication recesses 151 to 153 are tapered, the volume of the front communication recesses 151 to 153 can be reduced while ensuring a large area of the communication openings 151a to 153a. .. As a result, it is possible to reduce the compressed fluid remaining in the front communication recesses 151 to 153 while suppressing overcompression.

(6) The front communication recesses 151 to 153 extend in the penetrating direction of the front discharge ports 141 to 143.
According to such a configuration, the fluid introduced into the front communication recesses 151 to 153 is easily rectified along the penetrating direction of the front discharge ports 141 to 143 and then easily flows into the front discharge ports 141 to 143. As a result, it is possible to suppress the flow of the compressed fluid from being disturbed in the front discharge ports 141 to 143, and the compressed fluid can be introduced into the discharge chamber A1 more smoothly.

(7) A plurality of front discharge ports 141 to 143 are arranged in the circumferential direction. The plurality of front discharge ports 141 to 143 are provided at positions separated from the first front discharge port 141 having the first fixed-point overlap region Ca1 and the first front discharge port 141 in the circumferential direction from the front contact portion Pf. A second front discharge port 142 having a second fixed-point overlap region Ca2, and the like.

According to such a configuration, since a plurality of front discharge ports 141 to 143 are provided, a wider flow path cross section can be secured as compared with a configuration in which only one discharge port is provided. As a result, overcompression can be further suppressed.

Further, the compressor 10 is provided with a plurality of front communication recesses 151 to 153 corresponding to the plurality of front discharge ports 141 to 143. The plurality of front communication recesses 151 to 153 extend from the communication openings 151a to 153a toward the inner peripheral side of the front fixed body surface 100. The length L1 in the extending direction of the first front communication recess 151 that communicates the first fixed-point overlap region Ca1 and the front compression chamber A4 is such that the second fixed-point overlap region Ca2 and the front compression chamber A4 are connected to each other. The length of the second front communication recess 152 to be communicated is longer than the length L2 in the extending direction.

According to this configuration, the compression space Sf2 of the first front discharge port 141 is formed at a position narrower in the axial direction Z than that of the second front discharge port 142. Correspondingly, the length L1 of the first front communication recess 151 corresponding to the first front discharge port 141 becomes longer than the length L2 of the second front communication recess 152 corresponding to the second front discharge port 142. ing. This makes it easier to guide the compressed fluid to the first front discharge port 141. Therefore, the compressed fluid can be suitably guided to the first front discharge port 141, which is less likely to flow the compressed fluid than the second front discharge port 142.

(8) The plurality of front discharge ports 141 to 143 are displaced in the axial direction Z along the front fixed body edge 104 that is displaced in the axial direction Z according to the circumferential direction. As a result, the fixed-point overlap regions Ca1 to Ca3 can be reduced, so that the front communication recesses 151 to 153 can be reduced. Therefore, the volume of the front communication recesses 151 to 153 can be reduced.

(9) The line connecting the centers of the plurality of front discharge ports 141 to 143 is defined as the front center line Ln1. The front center line Ln1 is arranged closer to the front intermediate line Ln2 than the front rotating body edge 71a and the front fixed body edge 104.

According to this configuration, since the centers of the front discharge ports 141 to 143 are arranged near the front intermediate line Ln2, the overlap regions Ca1 to Ca3 and Cb1 to Cb3 can be reduced. As a result, the volume of the front communication recesses 151 to 153 can be reduced.

The above embodiment may be modified as follows. The above-described embodiment and the following alternative examples may be combined with each other within a technically consistent range. Further, with respect to another example regarding the configuration on the front side, the corresponding configuration on the rear side can be changed in the same manner. For example, with respect to another example regarding the front discharge ports 141 to 143 and the front communication recesses 151 to 153, the rear discharge ports 171 to 173 and the rear communication recesses 174 to 176 can be similarly changed.

○ As shown in FIGS. 13 to 15, the compressor 10 may include a front chamfered portion 201 formed between the ring outer peripheral surface 73 and the front rotating body surface 71 and extending in the circumferential direction as a communicating portion. .. The front chamfer portion 201 is formed over, for example, an angle range smaller than the angle range of the second front flat surface 102, and is arranged at a position on the rotation direction M side with respect to the vane groove 130 (in other words, vane 131). It is good to have. Further, the front chamfered portion 201 may be formed over an angle range larger than the angle range in which the plurality of front discharge ports 141 to 143 are formed. In this alternative example, a plurality of front chamfered portions 201 are provided apart from each other in the circumferential direction in correspondence with the case where a plurality of vane grooves 130 are provided apart from each other in the circumferential direction.

As shown in FIG. 14, the front chamfered portion 201 overlaps the rotating body overlap regions Cb1 to Cb3 when arranged inside the front discharge ports 141 to 143. That is, the front chamfered portion 201 prevents the ring outer peripheral surface 73 and the front discharge ports 141 to 143 from overlapping each other.

According to such a configuration, when the front chamfered portion 201 is arranged inside the front discharge ports 141 to 143, the rotating body overlapping regions Cb1 to Cb3 have a gap 202 (see FIG. 15) created by the front chamfered portion 201. Through, it communicates with the front compression chamber A4 (specifically, the compression space Sf2). As a result, the compressed fluid can flow into the rotating body overlapping regions Cb1 to Cb3 through the gap 202. Therefore, the rotating body overlap regions Cb1 to Cb3 can contribute to the discharge of the compressed fluid, and overcompression can be suppressed through it.

Further, in this alternative example, since the angle range in which the front chamfer portion 201 is formed is smaller than the angle range of the second front flat surface 102, the suction space Sf1 and the compression space Sf2 communicate with each other through the gap 202. Can be suppressed.

Further, in this alternative example, since the front chamfer portion 201 is arranged at a position on the rotation direction M side with respect to the vane groove 130 (in other words, vane 131), the timing of the latter half of the compression process in which the compression space Sf2 becomes narrower. The front chamfered portion 201 is arranged inside the radial direction R of the front discharge ports 141 to 143. As a result, the rotating body overlap regions Cb1 to Cb3 can be opened to the compression space Sf2 at an appropriate timing while suppressing the suction space Sf1 and the compression space Sf2 from communicating with each other through the gap 202.

The same applies to the rear side. That is, as shown in FIG. 13, the compressor 10 may include a rear chamfered portion 203 formed between the ring outer peripheral surface 73 and the rear rotating body surface 72 as a communicating portion and extending in the circumferential direction.

○ In the above alternative example, the specific shapes and positions of the chamfered portions 201 and 203 are arbitrary. For example, the front chamfered portion 201 may be formed over the entire circumference. Further, the front chamfered portion 201 may be formed over an angle range smaller than the angle range of the plurality of front discharge ports 141 to 143.

○ The compressor 10 may include both the front communication recesses 151 to 153 and the front chamfered portion 201, or may include only one of them.
○ The number of front discharge ports 141 to 143 is arbitrary and may be one. Further, the number of front communication recesses may be smaller than the number of front discharge ports. For example, in a configuration in which three front discharge ports 141 to 143 are provided, only the first front communication recess 151 may be provided, or the first front communication recess 151 and the second front communication recess 152 may be provided. ..

○ The shape of the front discharge ports 141 to 143 is arbitrary, and may be, for example, an oval shape or an arc shape extending in the circumferential direction. In this case, the front communication recesses 151 to 153 may also extend in the circumferential direction.

○ The shape of the front communication recesses 151 to 153 is arbitrary.
For example, the front communication recesses 151 to 153 may be formed in a semi-cylindrical shape having a constant cross section instead of being tapered. Further, the front communication recesses 151 to 153 may extend toward the inside of the radial direction R instead of the penetrating direction of the front discharge ports 141 to 143. The lengths L1 to L3 of the front communication recesses 151 to 153 in the extending direction may be the same, or may be set shorter as they are closer to the front contact portion Pf.

○ The penetration direction of each front discharge port 141 to 143 is arbitrary, and may be, for example, the radial direction R. In other words, each front discharge port 141 to 143 may penetrate the cylinder side wall portion 32 of the front cylinder 30 in the radial direction R. In this case, the outside of the front discharge ports 141 to 143 is the R outside in the radial direction. In such a configuration, the front communication recesses 151 to 153 may extend in the radial direction R or may extend in a direction orthogonal to the front seat surface 144.

That is, the extending direction of the front communication recesses 151 to 153 and the penetrating direction of the front discharge ports 141 to 143 may be the same or different.
○ The fixed-point overlap regions Ca1 to Ca3 and the front communication recesses 151 to 153 may face each other so that the compressed fluid can flow, and the opposite directions of the two are the radial direction R or the front discharge ports 141 to 141. It is not limited to the penetration direction of 143 and is arbitrary.

○ The shapes of the communication openings 151a to 153a are arbitrary, and may be formed smaller than or larger than the fixed-point overlap regions Ca1 to Ca3 when viewed from the outside of the front discharge ports 141 to 143, for example. You may.

○ The front discharge ports 141 to 143 may have a configuration having only one of the fixed body overlapping regions Ca1 to Ca3 and the rotating body overlapping regions Cb1 to Cb3. In short, the front discharge ports 141 to 143 may have at least one of both overlapping regions Ca1 to Ca3 and Cb1 to Cb3.

○ At least a part of the first front discharge port 141 may overlap with the front contact portion Pf. In this case, at least a part of the first front communication recess 151 may be formed on the second front flat surface 102. That is, the first front communication recess 151 may be formed so as to straddle both the second front flat surface 102 and the front curved surface 103. As a result, the compressed fluid remaining in the compressed space Sf2 can be further reduced.

○ As shown in FIGS. 16 to 18, the vane 131 may be composed of a plurality of parts. For example, the vane 131 has a vane body 240 inserted into the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z, and tip seals 250 and 260 provided on both sides of the vane body 240 in the axial direction Z. And may have. The vane 131 has a plate shape that is convex toward the fixed body surfaces 100 and 120 by combining the vane body 240 and both tip seals 250 and 260. In this case, both tip seals 250 and 260 form both ends of the vane 131 in the axial direction Z and come into contact with the fixed body surfaces 100 and 120.

The vane body 240 has a plate shape, and is inserted into the vane groove 130 in a state where the thickness direction thereof coincides with the width direction of the vane groove 130. The vane body 240 has both end faces 241,243 in the axial direction Z. The vane body 240 is made of metal, for example.

The chip seals 250 and 260 are made of resin, for example, and have seal body portions 251,261 that come into contact with the fixed body surfaces 100 and 120. The seal main bodies 251,261 are curved so as to be convex toward the fixed body surfaces 100 and 120.

The tip seals 250 and 260 have mounting protrusions 252 and 262 protruding from the seal body portions 251,261 toward the vane body 240, and are mounted on the axial Z end faces 241,243 of the vane body 240. Mounting grooves 242 and 244 into which the convex portions 252 and 262 can be inserted are formed. The tip seals 250 and 260 are attached to the vane body 240 in a state of being movable with respect to the vane body 240 by inserting the mounting protrusions 252 and 262 into the mounting grooves 242 and 244.

Further, as shown in FIG. 18, back pressure spaces 253 and 263 in which the fluid enters are formed between the tip seals 250 and 260 and the vane body 240. The tip seals 250 and 260 are pressed toward the fixed body surfaces 100 and 120 by the fluid in the back pressure spaces 253 and 263. As a result, the tip seals 250 and 260 come into contact with the fixed body surfaces 100 and 120. As a result, the vane 131 and the fixed body surfaces 100 and 120 can be sealed.

In the above alternative example, either one of both chip seals 250 and 260 may be omitted. That is, the chip seal may be provided only on either the front side or the rear side. In this case, it is preferable that the end portion of the vane body 240 on the side where the chip seal is not provided comes into contact with the fixed body surface. That is, the vane 131 may be composed of two parts.

○ The shape of the second front flat surface 102 is not limited to a fan shape and may be arbitrary, for example, a rectangular shape extending in the radial direction R with a constant width. That is, the shape of the front contact portion Pf is not limited to the fan shape and is arbitrary.

○ The rotating body surfaces 71 and 72 may be inclined with respect to the axial direction Z. In this case, both front flat surfaces 101, 102 and both rear flat surfaces 121, 122 may be flat surfaces orthogonal to the axial direction Z, or the rotating body surfaces 71, so as to make surface contact with the rotating body surfaces 71, 72. It may be tilted at the same tilt angle as 72.

○ A part of the rotating body cylinder portion 61 may be cut out or protruded. Further, the rotating body cylinder portion 61 has a cylindrical shape, but is not limited to this, and may have a non-cylindrical shape. The fixed body insertion holes 91 and 111 may be formed so as to correspond to the shape of the rotating body cylinder portion 61 so that the gap between the inner wall surface thereof and the rotating body cylinder portion 61 becomes small, and are not limited to the circular shape. .. When a part of the rotating body cylinder portion 61 is cut out, another member may be fitted in the cutout portion.

The rotating body may have a disk shape having no portion protruding from the rotating body surfaces 71 and 72 in the axial direction Z, and may not be supported by both the fixed bodies 90 and 110. In this case, the front compression chamber A4 may be partitioned by the outer peripheral surface of the rotating shaft 12. That is, the front compression chamber A4 is not limited to the configuration defined by the outer peripheral surface 62 of the tubular portion. The same applies to the rear compression chamber A5.

○ The number of shaft bearings 51 and 53 is not limited to two, and may be one. For example, the rear shaft bearing 53 may be omitted. Further, three or more shaft bearings may be provided.
○ In the present embodiment, the accommodation chamber A3 is partitioned by the front cylinder 30 and the rear plate 40, but the present invention is not limited to this, and the specific configuration for partitioning the accommodation chamber A3 is arbitrary.

For example, the compressor 10 may be configured to include a plate-shaped front plate instead of the front cylinder 30 and a bottomed tubular rear cylinder instead of the rear plate 40. In this case, the accommodation chamber A3 is partitioned by abutting the rear cylinder and the front plate.

Further, the compressor 10 may be provided with two cylindrical cylinders, and the storage chamber A3 may be partitioned by both cylinders. Further, the rear plate 40 may be omitted, and the accommodation chamber A3 may be partitioned by the front cylinder 30 and the rear housing bottom portion 23.

○ The compression chambers A4 and A5 may be partitioned by using the rotating body surfaces 71 and 72 and the fixed body surfaces 100 and 120, and the other surfaces used to partition the compression chambers A4 and A5 are arbitrary. For example, in a configuration in which the front cylinder 30 is omitted and the rear housing 22 (or housing 11) accommodates the rotating body 60 and both fixed bodies 90 and 110, the compression chambers A4 and A5 are replaced with the front cylinder inner peripheral surface 33. The inner peripheral surface of the rear housing 22 may be used for partitioning. In this case, the rear housing 22 or the housing 11 corresponds to the "cylinder portion", and the inner peripheral surface of the rear housing 22 corresponds to the "cylinder inner peripheral surface". Further, the compression chambers A4 and A5 may be partitioned by using the outer peripheral surface of the rotating shaft 12 instead of the outer peripheral surface 62 of the tubular portion.

○ The front fixed body 90 and the front cylinder 30 may be integrally formed, or the rear fixed body 110 and the rear plate 40 may be integrally formed.
○ The front cylinder bottom portion 31 and the front cylinder side wall portion 32 may be separate bodies. Further, the front cylinder bottom portion 31 may be omitted. In this case, the front cylinder side wall portion 32 corresponds to the “cylinder portion”.

○ The configuration for introducing the suction fluid into the suction spaces Sf1 and Sr1 is not limited to the configuration of the embodiment and is arbitrary. For example, at least one of the suction port and the discharge port may be provided on the fixed bodies 90 and 110.

○ Both fixed bodies 90 and 110 have the same shape, but the shape is not limited to this, and for example, the front fixed body 90 may have a larger diameter than the rear fixed body 110, or vice versa. In this case, the inner peripheral surface 33 of the front cylinder may have a stepped shape according to the shapes of both fixed bodies 90 and 110, and the front cylinder accommodating the front fixed body 90 and the rear accommodating the rear fixed body 110 may be formed. The cylinder may be provided separately. That is, the volumes of both compression chambers A4 and A5 may be the same or different.

○ The compressor 10 of the embodiment is 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 rear fixed body 110, the rear compression chamber A5, the rear suction port 170, and the rear discharge ports 171 to 173 may be omitted. In this case, the first front flat surface 101 may be omitted on the front fixed body surface 100.

In such a configuration, for example, it is preferable to provide an urging portion 300 for urging the vane 131 toward the front fixed body 90. The urging portion 300 may be supported by, for example, an urging support portion 301 provided on the rotating body cylinder portion 61 so that the urging portion 300 can rotate with the rotation of the rotating body 60. The urging support portion 301 is provided at, for example, the rear rotating body end portion 61b of the rotating body cylinder portion 61, and has a plate shape protruding outward in the radial direction R. As a result, the vane 131 rotates while moving in the axial direction Z while maintaining the state of being in contact with the front fixed body surface 100 as the rotating body 60 rotates. Instead of omitting the rear side configuration, the front side configuration may be omitted. In other words, there may be only one fixed body.

○ The fixed body insertion holes 91 and 111 do not have to be through holes as long as the rotating shaft 12 is inserted, and may be non-penetrating.
○ At least one of both thrust bearings 81 and 82 may be omitted. That is, the thrust bearings 81 and 82 are not essential.

○ At least one of both rotating body bearings 94 and 114 may be omitted.
○ The discharge chamber A1 does not have to have a tubular shape with the axial direction Z as the axial direction. For example, the discharge chamber A1 may have a C-shaped shape when viewed from the axial direction Z, or the two discharge chambers A1 may be arranged so as to face each other. In other words, the discharge chamber A1 may be formed in at least a part in the circumferential direction.

○ The number of vanes 131 is arbitrary, and may be one, two, or four or more. When there is only one vane 131, the front compression chamber A4 is divided into a suction chamber where suction is performed and a compression chamber where compression is performed by the front contact portion Pf and the vane 131.

○ Of the front fixed body surface 100, the contact surface (fixed body contact surface) with the front rotating body surface 71 does not have to be a flat surface like the second front flat surface 102. The same applies to the rear fixed body surface 120. However, from the viewpoint of sealing property, a flat surface is preferable.

The front curved surface 103 is curved so as to gradually move away from the front rotating body surface 71 as the distance from the second front flat surface 102 in the circumferential direction is increased, but the present invention is not limited to this. For example, the front curved surface 103 may have a portion where the distance from the front rotating body surface 71 is constant at an intermediate position thereof. That is, the front compression chamber A4 may be narrowed in the axial direction Z as a whole when approaching the front contact portion Pf, and may include a portion in which the length in the axial direction Z is constant. The same applies to the rear curved surface 123 and the rear compression chamber A5.

○ The fixed-point contact surface is not essential. For example, the second front flat surface 102 may be separated from the front rotating body surface 71 through a minute gap.
○ The specific shape of the housing 11 is arbitrary.

○ The specific shape of the rotating shaft 12 is arbitrary. For example, at least a part of the rotating shaft 12 may be formed in a hollow shape, or may be prismatic.
○ 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, for example, the rotating shaft 12 may be rotated by driving a belt or the like.

○ The compressor 10 may be used in addition to 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. That is, the fluid to be compressed by the compressor 10 is not limited to the refrigerant containing oil, and is arbitrary.

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

10 ... Compressor, 12 ... Rotating shaft, 60 ... Rotating body, 61 ... Rotating body cylinder, 62 ... Cylinder outer peripheral surface, 70 ... Rotating body ring, 71, 72 ... Rotating body surface, 71a, 72a ... Rotating body edge , 90, 110 ... Fixed body, 92, 112 ... Fixed body outer peripheral surface, 100, 120 ... Fixed body surface, 102, 122 ... Second flat surface (fixed body contact surface), 103, 123 ... Curved surface, 104, 124 ... Fixed body edge, 130 ... Vane groove, 131 ... Vane, 140 ... Front suction port, 141-143 ... Front discharge port, 151-153 ... Front communication recess, 151a-153a ... Communication opening, 171-173 ... Rear discharge Ports 174 to 176 ... Rear communication recesses, 201, 203 ... Chamfered parts, Ca1 to Ca3 ... Fixed-point overlap area, Cb1 to Cb3 ... Rotating body overlap area, L1 to L3 ... Length of communication recess in extending direction , Pf, Pr ... contact point, Sf1, Sr1 ... suction space, Sf2, Sr2 ... compression space, A1 ... discharge chamber, A4, A5 ... compression chamber.

Claims (6)

The axis of rotation and
A rotating body surface that rotates with the rotation of the rotating shaft and intersects the axial direction of the rotating shaft, and an outer peripheral surface of the rotating body that intersects the radial direction of the rotating shaft. With a rotating body,
A fixed body that does not rotate with the rotation of the rotating shaft and has a fixed body surface that faces the rotating body surface in the axial direction and a fixed body outer peripheral surface that intersects the radial direction.
A cylinder portion that accommodates the rotating body and the fixed body and has a cylinder inner peripheral surface that faces the outer peripheral surface of the rotating body and the outer peripheral surface of the fixed body in the radial direction.
A vane that is inserted into a vane groove formed in the rotating body and rotates while moving in the axial direction with the rotation of the rotating body.
A compression chamber that is partitioned by using the rotating body surface, the fixed body surface, and the inner peripheral surface of the cylinder, and in which the fluid is sucked and compressed by rotating the vane while moving in the axial direction.
A discharge chamber arranged on the radial side of the rotation shaft with respect to the compression chamber via the cylinder portion and into which the compressed fluid compressed in the compression chamber is introduced.
A discharge port that communicates the compression chamber and the discharge chamber by penetrating the cylinder portion and includes an overlapping region that overlaps with at least one of the fixed body and the rotating body.
A communicating portion provided at a position facing the overlapping region and communicating the overlapping region and the compression chamber,
A compressor characterized by being equipped with. The fixed body surface is
A fixed-point contact surface that comes into contact with the rotating body surface,
A pair of curvatures that are provided on both sides of the rotating shaft in the circumferential direction with respect to the fixed-point contact surface and are curved in the axial direction so as to be separated from the rotating body surface when the fixed-point contact surface is separated in the circumferential direction. Face and
Including
The compression chamber
A suction space provided on the rotation direction side of the rotating body with respect to the contact point between the rotating body surface and the fixed body contact surface and where fluid is sucked.
A compression space provided on the side opposite to the rotation direction side with respect to the contact point and where the fluid is compressed,
Including
The compressed space becomes narrower in the axial direction as it approaches the contact point.
The discharge port is provided on the side opposite to the rotation direction side of the contact portion in the cylinder portion, and communicates with the compression space.
The compressor according to claim 1, wherein the communicating portion communicates the overlapping region and the compressed space. The discharge port is formed so as to straddle the fixed body edge which is the outer peripheral edge of the curved surface when viewed from the outside of the discharge port, and the fixed body overlap region which overlaps with the fixed body as the overlap region. Including
The communication portion includes a communication recess formed on the curved surface.
The compressor according to claim 2, wherein the communicating recess has a communicating opening formed at a position overlapping the fixed overlap region when viewed from the outside of the discharge port on the outer peripheral surface of the fixed body. The compressor according to claim 3, wherein the communication recess is formed in a tapered shape so that the cross section gradually decreases from the communication opening toward the inner peripheral side of the fixed body surface. A plurality of the discharge ports are provided in a state of being arranged in the circumferential direction.
A plurality of the communication recesses are provided corresponding to the plurality of discharge ports.
The plurality of discharge ports
The first discharge port and
A second discharge port that is farther from the contact point in the circumferential direction than the first discharge port.
Including
The plurality of communication recesses
A first communication recess for communicating the first fixed body overlap region, which is the fixed body overlap region of the first discharge port, and the compression chamber,
A second communication recess for communicating the second fixed-point overlap region, which is the fixed-point overlap region of the second discharge port, and the compression chamber,
Including
The first communication recess is a first communication opening as the communication opening formed at a position overlapping the first fixed body overlap region when viewed from the outside of the first discharge port on the outer peripheral surface of the fixed body. It has and extends from the first communication opening toward the inner peripheral side of the fixed body surface.
The second communication recess is a second communication opening as the communication opening formed at a position overlapping the second fixed body overlap region when viewed from the outside of the second discharge port on the outer peripheral surface of the fixed body. It has and extends from the second communication opening toward the inner peripheral side of the fixed body surface.
The compressor according to claim 3 or 4, wherein the length of the first communication recess in the extension direction is longer than the length of the second communication recess in the extension direction. The discharge port is formed so as to straddle the edge of the rotating body which is the outer peripheral edge of the rotating body surface when viewed from the outside of the discharging port, and the rotating body overlaps as the overlapping region and overlaps with the rotating body. Including the area
The compressor according to any one of claims 1 to 5, wherein the communicating portion is formed between the rotating body surface and the rotating body outer peripheral surface, and includes a chamfered portion extending in the circumferential direction of the rotating body.