JP2020133485A - Compressor - Google Patents

Abstract

To provide a compressor capable of preventing a gap between a vane and a fixed body face.SOLUTION: A compressor comprises: a rotating shaft 12; a rotating body 60 which is rotated along with rotation of the rotating shaft 12; fixed bodies 90 and 110 which are not rotated along with the rotation of the rotating shaft 12. The rotating body 60 has rotating body faces 71 and 72. The fixed bodies 90 and 110 have fixed body faces 100 and 120 opposite to the rotating body faces 71 and 72 in an axial direction Z. The compressor also has: a vane 131 which is inserted into a vane groove 130 formed on the rotating body 60; and compression chambers A4 and A5 which are partitioned with the rotating body faces 71 and 72 and the fixed body faces 100 and 120. The vane 131 has: a vane body 170 inserted into the vane groove 130; and tip seals 180 and 190 which are installed on the vane body 170 and deformable.SELECTED DRAWING: Figure 5

Description

The present invention relates to a compressor.

In Patent Document 1, a rotating shaft, a columnar rotor as a rotating body in which a plurality of slit grooves as vane grooves are formed, and a plurality of vanes oscillatingly fitted in the plurality of slit grooves are fixed. A side plate as a fixed body on which a cam surface as a body surface is formed and an axial vane type compressor provided with the side plate are 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.

Japanese Unexamined Patent Publication No. 2015-14250

Here, when the vane and the fixed body surface are separated from each other, the fluid may leak through the gap between the vane and the fixed body surface. In this case, the loss as a compressor becomes large and the efficiency decreases.
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 suppressing the formation of a gap between a vane and a fixed body surface.

A compressor that achieves the above object includes a rotating shaft, a rotating body that rotates with the rotation of the rotating shaft, and a rotating body having a rotating body surface that intersects the axial direction of the rotating shaft. 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 is inserted into a vane groove formed in the rotating body to rotate the rotating body. A vane that rotates while moving in the axial direction is partitioned by using the rotating body surface and the fixed body surface, and the vane rotates while moving in the axial direction to suck and compress the fluid. The vane is provided with a compression chamber, and the vane is a plate-shaped vane body inserted into the vane groove in a state where the thickness direction thereof coincides with the width direction of the vane groove, and the axial direction of the vane body. The deformable member is attached to the end surface of the body and is deformable so as to spread in the width direction, and the deformable member is a surface that is in contact with the fixed body surface and is curved so as to be convex toward the fixed body surface. It is characterized in that the sealing surface is widened in the width direction by deforming the deforming member so as to spread in the width direction.

According to this configuration, the vane rotates as the rotating body rotates. In this case, the vane moves in the axial direction along the fixed body surface when the sealing surface of the deforming member comes into contact with the fixed body surface. As a result, the vane rotates while moving in the axial direction, and the fluid is sucked and compressed in the compression chamber.

Further, according to this configuration, since the deformable member can be deformed so as to spread in the width direction of the vane groove, the seal surface can come into contact with the fixed body surface in a state where the deformable member is deformed so as to spread in the width direction. .. As a result, the sealing surface becomes wider in the width direction, and the sealing surface and the fixed body surface can easily come into contact with each other. Therefore, it is possible to suppress the formation of a gap between the vane and the fixed body surface.

In particular, in this configuration in which the vane rotates, centrifugal force is applied to the vane. Therefore, the vane body is preferably lightweight in order to reduce centrifugal force, and specifically, it is preferably thin. However, when the vane body is made thin, the width of the sealing surface tends to be narrowed, so that there is a concern that the sealing surface and the fixed body surface are less likely to come into local contact with each other.

In this respect, according to this configuration, the sealing surface becomes wider by deforming the deforming member so as to spread in the width direction of the vane groove (the thickness direction of the vane), so that the thickness of the vane body is thin. However, the sealing surface can be easily brought into contact with the fixed body surface.

Regarding the compressor, the vane body has a convex portion that protrudes from the axial end surface of the vane body toward the fixed body surface and has a width direction in the thickness direction of the vane body, and the deformable member is , A facing surface facing the axial end surface of the vane body in the axial direction, and a deformed groove formed so as to be recessed from the facing surface toward the fixed body surface and into which the convex portion is inserted. The convex portion has a tapered portion that gradually narrows in width from the axial end surface of the vane body toward the fixed body surface, and the deformed member has the deformed groove formed by the tapered portion. By being pushed out in the width direction, it may be deformed so as to spread in the width direction.

According to such a configuration, when the deforming member is pressed toward the fixed body surface by the vane body, the convex portion is deeply inserted into the deforming groove. As a result, the deformed groove is expanded in the width direction by the tapered portion, and as a result, the deformed member is deformed so as to expand in the width direction. Therefore, when the deformable member is pressed toward the fixed body surface by the vane body, the sealing surface becomes wider in the width direction, and the sealing surface and the fixed body surface are easily brought into contact with each other. As a result, it is possible to suppress the formation of a gap between the vane and the fixed body surface.

With respect to the compressor, the rotating body is provided on the rotating body cylinder portion having the outer peripheral surface of the tubular portion into which the rotating shaft is inserted and on the outer peripheral surface of the tubular portion so as to project radially outward of the rotating shaft. A first rotating body surface and a second rotating body surface as the rotating body surface, and a rotating body ring portion having the vane groove are provided, and the compressor serves as the fixed body on both sides of the rotating body ring portion in the axial direction. The first fixed body is provided with a first fixed body and a second fixed body provided in the above, and the first fixed body has a first fixed body surface facing the first rotating body surface in the axial direction as the fixed body surface. The second fixed body has a second fixed body surface that faces the second rotating body surface in the axial direction as the fixed body surface, and the rotating body is both fixed bodies formed on the both fixed bodies. It is supported by both fixed bodies by being inserted into the insertion holes, and the vane is inserted into the vane groove while being sandwiched between the surfaces of both fixed bodies, and the deformable member is not deformed. In the state, the facing surface and the axial end surface of the vane main body are held at positions separated from each other, and the deformable member is deformed so as to spread in the width direction, whereby the deformable member and the vane main body are formed. And should approach the axial direction.

According to such a configuration, a rotating body having both rotating body surfaces is supported by both fixed bodies having both fixed body surfaces. As a result, since both fixed bodies directly support the rotating body, the displacement of the rotating body with respect to both fixed bodies can be suppressed. Therefore, the misalignment between the first rotating body surface and the first fixed body surface and the misalignment between the second rotating body surface and the second fixed body surface can be suitably suppressed. Therefore, it is possible to suppress inconveniences such as the rotating body surface being caught on the fixed body surface due to the positional deviation of the rotating body surface with respect to the fixed body surface. In addition, the inclination of the rotating body is regulated by the support by both fixed bodies. As a result, it is possible to prevent the formation of a gap through which the fluid leaks due to the tilting of the rotating body.

Here, even if the rotating body is supported by both fixed bodies, there are places where the facing distance between the surfaces of both fixed bodies is short due to dimensional errors and assembly errors during manufacturing of the rotating body and both fixed bodies. It can occur locally. If the vane sandwiched between the surfaces of both fixed bodies tries to pass through such a locally narrow place, there is a concern that the vane may be caught.

On the other hand, according to this configuration, the deforming member is deformed so as to expand in the width direction of the vane groove, so that the deforming member moves in the axial direction Z so as to approach the vane body. As a result, the vane can smoothly rotate even in a portion where the facing distance is locally short. Therefore, the above inconvenience can be suppressed.

Regarding the compressor, the deformed groove has a groove opening wider than the width of the tip surface of the convex portion and a groove inclined so as to gradually become narrower from the groove opening toward the bottom surface of the deformed groove. It is said that the tapered portion has a side surface, the inclination angle of the tapered portion is larger than the inclination angle of the groove side surface, and the tapered portion has a wide portion formed wider than the width of the groove opening. Good.

According to such a configuration, the deformable member is held at a position where the facing surface and the axial end surface of the vane body are separated from each other by abutting the tapered portion and the groove side surface. From that state, the deformed groove is further expanded by the convex portion further entering the deformed groove, and the deformed member is deformed so as to expand in the width direction, and the deformed member and the vane body are brought closer to each other. As a result, the above-mentioned effect can be obtained with a relatively simple configuration.

Regarding the compressor, the fixed-point surface is provided on both sides of the fixed-point contact surface that comes into contact with the rotating body surface and the fixed-point contact surface in the circumferential direction of the rotating shaft. The vane groove includes the 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 vane groove is formed by the vane body regardless of the axial movement of the vane. The vane comes into contact with the fixed-point contact surface, including a first part groove to be inserted and a second part groove formed on the rotating body surface and wider than the first part groove. If so, the deformable member may be housed in the second part groove.

According to this configuration, when the vane is in contact with the fixed-point contact surface, the deformable member is housed in the second part groove. The second part groove is formed wider than the first part groove. As a result, it is possible to prevent the deforming member from being deformed so as to spread in the width direction by the vane groove, and the deformation member is caught in the vane groove, which hinders the axial movement of the vane. Can be suppressed. Further, since the vane body is held by the first part groove, rattling of the vane can be suppressed.

According to the present invention, it is possible to suppress the formation of a gap between the vane and the fixed body surface.

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. An exploded perspective view of the front cylinder, front valve, and front retainer. Enlarged cross section around the vane. Perspective view of rotating body and vane. An exploded perspective view of the vane. The cross-sectional view which shows typically the contact mode between a vane and a front fixed body surface in a state where a front tip seal is not deformed. The cross-sectional view which shows typically the contact mode between a vane and a front fixed body surface in a state where a front tip seal is deformed. 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. 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 side 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. By supplying the driving power from the inverter 14, the electric motor 13 rotates the rotating shaft 12 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. Let me.

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 inner and outer peripheral edges of both rotating body surfaces 71 and 72 are linear when viewed from the radial direction R, and the position in the axial direction Z is constant regardless of the circumferential direction.

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 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.

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 front fixed body inner peripheral surface 33 and a front fixed body outer peripheral surface 92 facing 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 front cylinder inner peripheral surface 33 and a rear fixed body outer peripheral surface 112 facing 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. 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 formed in the fixed bodies 90 and 110. There is.

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.

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. Further, similarly to the front curved surface 103, the rear curved surface 123 can be said to be a curved surface that is curved in a wavy shape. Therefore, focusing on this point, the rear fixed body surface 120 includes a portion that is curved in a wavy shape. It can be said to be a face.

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 fixed bodies 90 and 110 correspond to "fixed bodies", both fixed body surfaces 100 and 120 correspond to "fixed body surfaces", and 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”.

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 a front rotating body surface 71 and a front fixed body surface 100. In the present embodiment, the front rotating body surface 71, the front fixed body surface 100, the outer peripheral surface of the cylinder portion 62, and the inner circumference of the front cylinder are used. It is partitioned by a surface 33.

The rear compression chamber A5 is partitioned by using the rear rotating body surface 72 and the rear fixed body surface 120. In the present embodiment, the rear rotating body surface 72, the rear fixed body surface 120, the outer peripheral surface of the cylinder portion 62, and the inner circumference of the front cylinder are used. It is partitioned by a surface 33. 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 inserted into the vane groove 130 while being sandwiched between the fixed body surfaces 100 and 120. In the present embodiment, the thickness direction of the vane 131 coincides with the width direction of the vane groove 130, in other words, the direction orthogonal to both 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), and the vane 131 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. Both ends of the vane 131 in the axial direction Z are in contact with both the fixed body surfaces 100 and 120, and the vane 131 is sandwiched from the axial direction Z by both the 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 rotation direction M side of 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 that is in contact with the second front flat surface 102 are partitioned by the contact points between the front rotating body surface 71 and the second front flat surface 102, and are partitioned by the contact points. It is sealed. 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 is arranged by the three vanes 131 on the rotation direction M side of the first rear compression chamber A5a and the first rear compression chamber A5a. It is partitioned into a second rear compression chamber A5b and a third rear compression chamber A5c arranged between the first rear compression chamber A5a and the second rear compression chamber A5b in the circumferential direction. The first rear compression chamber A5a, the second rear compression chamber A5b, and the third rear compression chamber A5c are 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 141 and the rear intake port 142 are schematically shown in FIG.

As shown in FIGS. 2 to 4 and 6, the compressor 10 includes a front suction port 141 for sucking a suction fluid into the front compression chamber A4. The front suction port 141 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 141 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 141 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 141.

The front suction port 141 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 141.

Specifically, as shown in FIG. 6, the front suction port 141 has a front suction opening 141a opened at a position communicating with the first front compression chamber A4a. The front suction opening 141a extends in the rotation direction M from a position corresponding to the central portion of the second front flat surface 102 in the circumferential direction of the front cylinder inner peripheral surface 33. The extended length of the front suction opening 141a 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 141a is provided in the circumferential direction by substantially the same length as the circumferential interval of each vane 131 from the position corresponding to the central portion of the front cylinder inner peripheral surface 33 in the circumferential direction of the second front flat surface 102. May extend to.

Further, assuming that the angle position of the central portion of the second front flat surface 102 is 0 °, the front suction opening 141a 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, the compressor 10 includes a front discharge port 151 for discharging the compressed fluid compressed in the front compression chamber A4, a front valve 152 for opening and closing the front discharge port 151, and a front valve 152. It is provided with a front retainer 153 that adjusts the opening degree of the.

As shown in FIG. 6, the front discharge port 151 is, for example, outside the radial direction R of the front compression chamber A4 of the front cylinder side wall portion 32 and is on the rotation direction M side of the rotating body 60 with respect to the second front flat surface 102. Is provided at the opposite position.

Specifically, the curved front cylinder outer peripheral surface 34 is formed with a front seat surface 154 recessed from the front cylinder outer peripheral surface 34. The front seat surface 154 is formed on the outer peripheral surface 34 of the front cylinder between the front compression chamber A4 and the discharge chamber A1 and on the side opposite to the rotation direction M side from the second front flat surface 102. .. The front seat surface 154 is a flat surface orthogonal to the radial direction R.

As shown in FIG. 6, the front discharge port 151 is provided on the front seat surface 154. The front discharge port 151 communicates the second front compression chamber A4b with the discharge chamber A1 by penetrating the side wall portion 32 of the front cylinder.

In the present embodiment, a plurality of front discharge ports 151 are provided and are arranged in the circumferential direction. The plurality of front discharge ports 151 are each circular. However, the number and shape of the front discharge ports 151 are arbitrary. For example, the number of front discharge ports 151 may be one. Further, the front discharge port 151 may have an oval shape or the like. In a configuration in which a plurality of front discharge ports 151 are provided, the sizes of the front discharge ports 151 may be the same or different.

In the present embodiment, at least a part of the front discharge port 151 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 port 151.

The front suction port 141 and the front discharge port 151 are provided at positions separated from each other in the circumferential direction via the radial R outer portion of the second front flat surface 102 of the front cylinder side wall portion 32.

That is, the first front compression chamber A4a of the present embodiment is configured so as to communicate with the front suction port 141 but not with the front discharge port 151.
The second front compression chamber A4b communicates with the front discharge port 151. However, in the present embodiment, since the circumferential length of the second front compression chamber A4b is longer than the circumferential length of the second front flat surface 102, the second front compression chamber A4b is the front suction port 141 depending on the phase. It may be arranged so as to straddle both the inside of the radial R of the front discharge port 151 and the inside of the radial R of the front discharge port 151. In this respect, in the present embodiment, the front rotating body surface 71 and the second front flat surface are between the space inside the radial R of the front suction port 141 and the space inside the radial R of the front discharge port 151. There is a contact point with 102. As a result, both spaces are sealed by the contact points regardless of the angular positions of the plurality of vanes 131. Therefore, the communication between the front suction port 141 and the front discharge port 151 is restricted. That is, in the present embodiment, it can be said that the second front compression chamber A4b is further divided into a space where suction is performed and a space where compression is performed by the contact portion.

The third front compression chamber A4c of the present embodiment shifts from a state of not communicating with the front discharge port 151 to a state of communicating with the front discharge port 151 as the rotating body 60 rotates.

As shown in FIG. 8, the front valve 152 and the front retainer 153 are provided on the front seat surface 154. The front valve 152 and the front retainer 153 are screwed into the screw holes 154a formed in the front seat surface 154 in a state where the bolt B penetrates both the front valve 152 and the front retainer 153, so that the front seat surface 154 It is fixed to.

The front valve 152 normally blocks the front discharge port 151, and opens when the pressure in the front compression chamber A4 (specifically, the second front compression chamber A4b) exceeds the threshold value to block the front discharge port 151. To the state where the front discharge port 151 is 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 152 is regulated by the front retainer 153.

As shown in FIGS. 2 to 4 and 7, the compressor 10 includes a rear suction port 142 for sucking the suction fluid into the rear compression chamber A5. The rear suction port 142 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 rear suction port 142 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 142 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 142.

The rear suction port 142 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 142.

Specifically, as shown in FIG. 7, the rear suction port 142 has a rear suction opening 142a opened at a position communicating with the first rear compression chamber A5a. The rear suction opening 142a 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 142 and the rear suction opening 142a are the front discharge port 151, the front valve 152 and the front retainer 153 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.

However, the present invention is not limited to this, and the circumferential lengths of the rear suction port 142 and the rear suction opening 142a may be the same as the circumferential lengths of the front suction port 141 and the front suction opening 141a. In this case, the length of the front valve 152 or the like in the axial direction Z is shortened or the position of the front discharge port 151 is adjusted so that the rear suction port 142 and the rear suction opening 142a do not interfere with the front discharge port 151 or the like. It may be arranged in a staggered manner, or the angle range of the second front flat surface 102 may be narrowed.

By the way, in the present embodiment, two suction ports 141 and 142 are provided corresponding to the two compression chambers A4 and A5. The front suction port 141 and the rear suction port 142 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 141 and 142 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.

As shown in FIG. 7, the compressor 10 has a rear discharge port 161 for discharging the compressed fluid compressed in the rear compression chamber A5, a rear valve 162 for opening and closing the rear discharge port 161, and an opening degree of the rear valve 162. It is equipped with a rear retainer 163 that adjusts.

The rear discharge port 161 is provided, for example, at a position on the side wall portion 32 of the front cylinder, which is outside the radial direction R of the rear compression chamber A5 and is opposite to the second rear flat surface 122 in the rotation direction M side.

By the way, the rear discharge port 161 is positioned 180 ° in the circumferential direction with respect to the front discharge port 151 in response to the 180 ° deviation between the second front flat surface 102 and the second rear flat surface 122. It is formed. Further, the rear discharge port 161 is displaced in the axial direction Z with respect to the front discharge port 151 in correspondence with the front compression chamber A4 and the rear compression chamber A5 being displaced in the axial direction Z.

The specific configurations of the rear discharge port 161 and the rear valve 162 and the rear retainer 163 are basically the same as those of the front discharge port 151, the front valve 152, and the front retainer 153, except that the positions where they are provided are different. Therefore, a detailed description will be omitted. Further, "front" in the description of the front discharge port 151, the front valve 152 and the front retainer 153 described above may be read as "rear". The discharge ports 151 and 161 can be said to be discharge passages.

Next, the vane 131 and the vane groove 130 of the present embodiment will be described.
As shown in FIGS. 9 to 13, the vane 131 of the present embodiment is composed of a plurality of parts. Specifically, the vane 131 includes a vane body 170 inserted in the vane groove 130 and tip seals 180 and 190 as deformable members attached to both end faces 171 and 172 of the vane body 170 in the axial direction Z. Including. Both tip seals 180 and 190 form both ends of the vane 131 in the axial direction Z, and the tip seals 180 and 190 come into contact with the fixed body surfaces 100 and 120.

The vane body 170 is made of the same material as, for example, the rotating body 60 and both fixed bodies 90 and 110, and is made of metal as an example. The vane body 170 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 170 extends in the axial direction Z and the radial direction R. In the present embodiment, the vane main body 170 has a rectangular plate shape, but the present invention is not limited to this, and the vane main body 170 is arbitrary as long as it has a plate shape. Further, the vane body 170 of the present embodiment is inserted into the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z.

In the following description, the width direction of the vane groove 130 may be appropriately rephrased as the thickness direction of the vane body 170. Further, in the present embodiment, the vane body 170 has a rectangular plate shape, but the present invention is not limited to this, and the vane body 170 is arbitrary as long as it has a plate shape.

The vane main body 170 includes convex portions 173 and 174 protruding from both end surfaces 171 and 172 of the vane main body 170 in the axial direction Z toward the fixed body surfaces 100 and 120. The convex portions 173 and 174 are ridges extending in the radial direction R with the thickness direction of the vane body 170 as the width direction.

As shown in FIGS. 11 and 12, the convex portions 173 and 174 have tip surfaces 173a and 174a and convex side surfaces 173b and 174b. In the present embodiment, the convex portions 173 and 174 have a tapered shape that gradually narrows from the end faces 171 and 172 in the axial direction Z of the vane body 170 toward the fixed body surfaces 100 and 120. Therefore, the convex side surfaces 173b and 174b are inclined with respect to the axial direction Z. By the way, in the present embodiment, the entire convex portions 173 and 174 correspond to the tapered portions.

Next, the chip seals 180 and 190 will be described. In the present embodiment, since both the tip seals 180 and 190 have the same shape, the front tip seal 180 and the front convex portion 173 will be described in detail in the following description, and the description of the rear side configuration will be omitted. ..

The front tip seal 180 of the present embodiment is made of a material different from that of the vane body 170, and is made of, for example, a material that is more easily deformed than the vane body 170 (in other words, a soft material). As an example, the front tip seal 180 is made of resin. The front tip seal 180 is configured to be deformable in the width direction of the vane groove 130. The front tip seal 180 is configured to be deformed in the width direction of the vane groove 130 by being pressed from the vane body 170 toward the front fixed body surface 100. In this embodiment, the front tip seal 180 has the same shape.

As shown in FIGS. 9 to 11, the front tip seal 180 has a long shape extending in the radial direction R whose width direction is, for example, the width direction of the vane groove 130 (in other words, the thickness direction of the vane body 170). .. Here, assuming that the width of the front tip seal 180 is the seal width W1 and the thickness of the vane body 170 is the vane body thickness D1, the seal width W1 is the vane body thickness when the front tip seal 180 is not deformed. It is set to be the same as D1.

As shown in FIG. 9, the front tip seal 180 of the present embodiment is sandwiched from the axial direction Z by the end surface 171 of the vane main body 170 in the axial direction Z and the front fixed body surface 100. In other words, it can be said that the front tip seal 180 is interposed between the end surface 171 of the vane body 170 in the axial direction Z and the front fixed body surface 100.

As shown in FIGS. 11 and 12, the front tip seal 180 has, for example, an axial direction with respect to a seal surface 181 facing the front fixed body surface 100 in the axial direction Z and an end surface 171 of the vane body 170 in the axial direction Z. It has an facing surface 182 facing Z. The sealing surface 181 and the facing surface 182 extend in the radial direction R. In this embodiment, the seal surface 181 and the facing surface 182 are connected to each other.

The seal surface 181 is curved so as to be convex toward the front fixed body surface 100. In the present embodiment, the seal surface 181 comes into contact with the front fixed body surface 100.
Here, the radius of curvature of the front curved surface 103 of the present embodiment differs depending on the radial direction R. Specifically, the radius of curvature of the front curved surface 103 becomes smaller from the outer diameter side toward the inner diameter side.

On the other hand, since the seal surface 181 of the present embodiment is curved so as to be convex toward the front fixed body surface 100, even if the radius of curvature of the front curved surface 103 is different in the radial direction R. , The seal surface 181 is likely to come into contact with the front curved surface 103.

The degree of curvature of the seal surface 181 in this embodiment is looser than that in the case where the front tip seal 180 is formed in a semicircular shape. Specifically, the radius of curvature of the sealing surface 181 is set to be larger than 1/2 of the vane body thickness D1. However, the present invention is not limited to this, and the degree of curvature of the sealing surface 181 is arbitrary.

The front tip seal 180 is formed on the facing surface 182 and includes a deformation groove 183 into which the front convex portion 173 is inserted. The deformation groove 183 is formed so as to be recessed from the facing surface 182 toward the front fixed body surface 100, and extends in the radial direction R with the thickness direction of the vane 131 as the width direction. That is, the width direction of the deformed groove 183 and the width direction of the vane groove 130 coincide with each other. The deformation groove 183 is open both inside the radial direction R and outside the radial direction R. Further, the deformed groove 183 has a groove opening 183a that opens toward the vane body 170. The front tip seal 180 of the present embodiment is attached to the end surface 171 of the vane main body 170 in the axial direction Z by inserting the front convex portion 173 into the deformation groove 183.

As shown in FIG. 12, the deformed groove 183 has a groove bottom surface 183b facing the front tip surface 173a and the axial direction Z, and a groove side surface 183c rising from the groove bottom surface 183b.
The deformation groove 183 of the present embodiment is formed in a tapered shape so as to gradually become narrower as it gets deeper. Specifically, the groove side surface 183c is inclined with respect to the axial direction Z so as to gradually become narrower from the groove opening 183a toward the facing surface 182.

Here, the front tip seal 180 can be deformed so that the deformation groove 183 is expanded in the width direction of the vane groove 130 by the front convex portion 173 being expanded in the width direction of the vane groove 130.

More specifically, as shown in FIGS. 12 and 13, the groove opening 183a is formed wider than the front tip surface 173a. Specifically, the width of the groove opening 183a is wider than the width of the front tip surface 173a. The width of the groove opening 183a and the front tip surface 173a can be said to be the length of the vane groove 130 in the width direction.

Further, the inclination angle of the front convex side surface 173b with respect to the axial direction Z is larger than the inclination angle of the groove side surface 183c with respect to the axial direction Z, and a part of the front convex portion 173 is formed wider than the groove opening 183a. That is, the front convex portion 173 has a wide portion 173c wider than the width of the groove opening 183a.

Therefore, in the present embodiment, as shown in FIG. 12, when the front tip seal 180 is not deformed, the front tip seal 180 is located on the facing surface 182 of the front tip seal 180 and in the axial direction Z of the vane body 170. It is held at a position separated from the end face 171.

For convenience of explanation, in the following description, the relative positions of the front tip seal 180 and the front convex portion 173 in the undeformed state are set as the initial positions. At the initial position, a part of the front convex portion 173 has entered the deformation groove 183 and faces the deformation groove 183 in the circumferential direction.

According to such a configuration, when the front convex portion 173 is inserted deeper into the deformation groove 183 than the initial position, as shown in FIG. 13, the deformation groove 183 is expanded by the front convex portion 173. As a result, the front tip seal 180 is deformed so as to spread in the width direction. Therefore, when the front tip seal 180 is deformed, the seal width W1 is larger than the vane body thickness D1. Then, the seal surface 181 is deformed so that the front tip seal 180 is deformed so as to spread in the width direction of the vane groove 130, so that the front tip seal 180 is widened in the width direction of the vane groove 130. That is, the seal surface 181 is widely deformed. As a result, the sealing surface 181 and the front curved surface 103 are likely to come into contact with each other.

Further, by deforming the front tip seal 180 so as to expand in the width direction of the vane groove 130, the front tip seal 180 and the vane body 170 approach the axial direction Z. Specifically, the facing surface 182 and the end surface 171 of the vane body 170 come close to each other.

Incidentally, as an example, the length of the vane 131 in the axial direction Z in the state where the front tip seal 180 is not deformed may be set longer than the facing distance between the front fixed body surfaces 100. In this case, in the situation where the vane 131 is inserted into the vane groove 130 while being sandwiched between the front fixed body surfaces 100, the front tip seal 180 is always pressed from the vane body 170 toward the front fixed body surface 100. It is assumed that it is deformed so as to spread in the width direction.

The length of the vane 131 in the axial direction Z in the state where the front tip seal 180 is not deformed may be set to be equal to or less than the facing distance between the front fixed body surfaces 100. Even in this case, since the vane 131 moves in the axial direction Z along both front fixed body surfaces 100, the vane 131 has a pressing force toward the front fixed body surface 100 and a pressing toward the rear fixed body surface 120. At least one of the pressures is likely to be applied. Therefore, it is assumed that at least one of the front tip seals 180 is easily deformed.

Next, the vane groove 130 will be described.
As shown in FIGS. 10 and 12, the vane groove 130 of the present embodiment is formed from the first part groove 200 into which the vane body 170 is inserted and the first part groove 200 regardless of the movement of the vane 131 in the axial direction Z. Also has second part grooves 201 and 202 formed widely.

The first part groove 200 has a width equal to or slightly larger than the thickness of the vane body 170. The vane body 170 is sandwiched by both side surfaces of the first part groove 200.
The second part grooves 201 and 202 are provided on both sides in the axial direction Z with respect to the first part groove 200, and are specifically formed on the rotating body surfaces 71 and 72. The second part grooves 201 and 202 are configured to accommodate the deformed chip seals 180 and 190, and in detail, have a width equal to or larger than the deformed seal width W1 and the chip seal. It has a length in the axial direction Z that is equal to or greater than the height of 180 and 190.

Next, a series of operations of the compressor 10 will be described as the operation of the present embodiment with reference to FIGS. 14 and 15. 14 and 15 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. 14 and 15, for convenience of illustration, each port 141, 142, 151, 161 is schematically shown.

As shown in FIGS. 14 and 15, 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. 14 and 15, 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 second front flat surface 102 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 141. Will be done.

On the other hand, in the space on the side opposite to the rotation direction M side of the second front flat surface 102 in the second front compression chamber A4b and in the third front compression chamber A4c, the volume decreases as the rotating body 60 rotates. , 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 rotated in the rotation direction M more than the second front flat surface 102 in the second front compression chamber A4b. It is further compressed in the space opposite to the side.

Then, when the pressure in the space of the second front compression chamber A4b on the side opposite to the rotation direction M side of the second front flat surface 102 exceeds the threshold value, the front valve 152 is opened and the second front compression chamber A4b is opened. The compressed fluid compressed in (1) flows into the discharge chamber A1 via the front discharge port 151. 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 141a is formed over at least 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 the present embodiment, for convenience of explanation, each of the front compression chambers A4a to A4c shall be partitioned by a plurality of vanes 131, and the positional relationship between the front suction port 141 and the front discharge port 151 shall be defined and described. However, 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 second front flat surface 102, the first vane 131 communicates with the front suction port 141 on the side opposite to the rotation direction M side with respect to the first vane 131. A compression chamber is formed. As the vane 131 rotates, the compression chamber increases in volume while maintaining communication with the front suction port 141. As a result, inhalation is performed in the compression chamber.

After that, the second vane 131 moves toward the M side in the rotation direction with respect to the second front flat surface 102, 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 141a 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 141a on the rotation direction M side, the compression chamber does not communicate with the front suction port 141, and when the rotating body 60 further rotates. Communicates with the front discharge port 151. 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.

By the way, when the vane 131 is in contact with the second front flat surface 102 as the fixed-point contact surface, the front tip seal 180 is formed wider than the first part groove 200. It is housed in 201. As a result, it is possible to prevent the front tip seal 180 from being caught in the vane groove 130, thereby hindering the movement of the vane 131 in the axial direction Z. The same applies to the rear tip seal 190.

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 is formed on 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, and a rotating body 60. It is provided with a vane 131 that is inserted into the vane groove 130 and rotates while moving in the axial direction Z as the rotating body 60 rotates. The rotating body 60 has a front rotating body surface 71 that intersects the axial direction Z, and the front fixed body 90 has a front fixed body surface 100 that faces the front rotating body surface 71 and the axial direction Z. The compressor 10 is partitioned by using the front rotating body surface 71 and the front fixed body surface 100, and includes a front compression chamber A4 in which fluid is sucked and compressed by rotating the vane 131 while moving in the axial direction Z. ..

The vane 131 is attached to the vane body 170 inserted into the vane groove 130 in a plate-like shape and the thickness direction of the vane groove 130 coincides with the width direction of the vane groove 130, and the end surface 171 of the vane body 170 in the axial direction Z. It is provided with a front tip seal 180 as a deformable member. The front tip seal 180 has a seal surface 181 that is curved so as to be convex toward the front fixed body surface 100. The seal surface 181 comes into contact with the front fixed body surface 100.

The front tip seal 180 is deformable so as to expand in the width direction of the vane groove 130, and the seal surface 181 expands in the width direction by deforming the front tip seal 180 so as to expand in the width direction.

According to such a configuration, since the front tip seal 180 can be deformed so as to expand in the width direction of the vane groove 130, the seal surface 181 is deformed so as to expand in the width direction of the front fixed body surface 100. Can be in contact with. As a result, the seal surface 181 becomes wider in the width direction, and the seal surface 181 and the front fixed body surface 100 are likely to come into contact with each other. Therefore, it is possible to suppress the formation of a gap between the vane 131 and the front fixed body surface 100.

(2) The front fixed body surface 100 of the present embodiment is provided on both sides in the circumferential direction with respect to the second front flat surface 102 as the fixed body contact surface that contacts the front rotating body surface 71 and the second front flat surface 102. Includes a pair of front curved surfaces 103. The pair of front curved surfaces 103 are curved in the axial direction Z so as to be separated from the front rotating body surface 71 when they are separated from the second front flat surface 102 in the circumferential direction. Further, the seal surface 181 of the present embodiment is curved so as to be convex toward the front fixed body surface 100 so that it can easily come into contact with the front curved surface 103. However, even when the seal surface 181 is curved as described above, a portion where the seal surface 181 and the front curved surface 103 do not come into contact with each other may be locally generated depending on the front curved surface 103. For example, in the configuration in which the front curved surface 103 has an inflection point as in the present embodiment, the gradient on the inner diameter side in the vicinity of the inflection point tends to be large, and the sealing surface 181 and the front curved surface 103 are locally located. Easy to separate from.

On the other hand, paying attention to the point that the seal surface 181 and the front curved surface 103 are easily brought into contact with each other, for example, it is conceivable to increase the thickness of the vane body 170 to increase the seal width W1. However, if the vane body 170 is made thicker, the vane body 170 becomes heavier. Since centrifugal force is applied to the vane 131, if the vane body 170 becomes heavy, the load applied to the vane 131 increases and there is a concern that the power increases.

In this regard, according to the present embodiment, the front tip seal 180 is deformed so as to expand in the width direction, so that the seal surface 181 expands in the width direction. As a result, even when the thickness of the vane body 170 is thin, the seal surface 181 can be easily brought into contact with the front curved surface 103. Therefore, it is possible to suppress the formation of a gap between the front tip seal 180 and the front fixed body surface 100 without making the vane body 170 excessively thick.

(3) The vane main body 170 has a front convex portion 173 that protrudes from the end surface 171 of the vane main body 170 in the axial direction Z toward the front fixed body surface 100 and has the thickness direction of the vane main body 170 as the width direction. The front tip seal 180 is formed so as to be recessed from the facing surface 182 facing the end surface 171 in the axial direction Z and from the facing surface 182 toward the front fixed body surface 100, and the front convex portion 173 is inserted into the deformed groove. It is equipped with 183. The front convex portion 173 includes a tapered portion that gradually narrows from the axial end surface 171 of the vane body 170 toward the front fixed body surface 100. The front tip seal 180 is deformed so as to expand in the width direction by expanding the deformation groove 183 in the width direction by the front convex portion 173.

According to such a configuration, when the front tip seal 180 is pressed toward the front fixed body surface 100 by the vane body 170, the front convex portion 173 is deeply inserted into the deformation groove 183. As a result, the deformation groove 183 is expanded in the width direction by the front convex portion 173, and as a result, the front tip seal 180 is deformed so as to expand in the width direction. Therefore, when the front tip seal 180 is pressed toward the front fixed body surface 100 by the vane body 170, the seal surface 181 becomes wider in the width direction, and the seal surface 181 and the front fixed body surface 100 are likely to come into contact with each other. .. As a result, it is possible to suppress the formation of a gap between the vane 131 and the front fixed body surface 100.

(4) The vane groove 130 is formed in the first part groove 200 into which the vane body 170 is inserted and the front rotating body surface 71 regardless of the movement of the vane 131 in the axial direction Z, and is wider than the first part groove 200. Includes the second part groove 201, which is When the vane 131 is in contact with the second front flat surface 102, the front tip seal 180 is housed in the second part groove 201.

According to this configuration, when the vane 131 is in contact with the second front flat surface 102, the front tip seal 180 is housed in the second part groove 201. The second part groove 201 is formed wider than the first part groove 200. As a result, it is possible to prevent the front tip seal 180 from being deformed so as to spread in the width direction by the vane groove 130, and the shaft of the vane 131 due to the front tip seal 180 being caught in the vane groove 130. It is possible to suppress the hindrance to the movement in the direction Z. Further, since the vane body 170 is held by the first part groove 200, the rattling of the vane 131 can be suppressed.

(5) The rotating body 60 is provided with the rotating body 60 into which the rotating shaft 12 is inserted so as to protrude outward in the radial direction R from the rotating body tubular portion 61 having the outer peripheral surface 62 of the tubular portion and the outer peripheral surface 62 of the tubular portion. It is provided with a rotating body ring portion 70 having rotating body surfaces 71 and 72 and a vane groove 130. The rotating body 60 is supported by both fixed bodies 90 and 110 by inserting the rotating body cylinder portion 61 into the fixed body insertion holes 91 and 111 formed in both fixed bodies 90 and 110. The vane 131 is inserted into the vane groove 130 in a state of being sandwiched between the fixed body surfaces 100 and 120.

According to such a configuration, the rotating body 60 having the rotating body surfaces 71 and 72 is supported by the fixed bodies 90 and 110 having the fixed body surfaces 100 and 120. As a result, since the fixed bodies 90 and 110 directly support the rotating body 60, the displacement of the rotating body 60 with respect to the fixed bodies 90 and 110 can be suppressed. Therefore, the positional deviation between the rotating body surfaces 71 and 72 facing the axial direction Z and the fixed body surfaces 100 and 120 can be suitably suppressed. Therefore, due to the misalignment of the rotating body surfaces 71 and 72 with respect to the fixed body surfaces 100 and 120, the rotating body surfaces 71 and 72 are caught on the fixed body surfaces 100 and 120, or the vanes 131 sandwiched between the fixed body surfaces 100 and 120. Inconveniences such as hindrance to rotation can be suppressed.

Further, the inclination of the rotating body 60 is regulated by the support by the fixed bodies 90 and 110. As a result, it is possible to prevent the formation of a gap through which the fluid leaks due to the tilting of the rotating body 60.

(6) Here, even if the rotating body 60 is supported by both fixed bodies 90 and 110, due to dimensional errors and assembly errors during manufacturing of the rotating bodies 60 and both fixed bodies 90 and 110, etc. A portion where the facing distance between the fixed body surfaces 100 and 120 is short may occur locally. When the vane 131 tries to pass through such a locally narrow place, there is a concern that the vane 131 may be caught.

On the other hand, the tip seals 180 and 190 of the present embodiment move in the axial direction Z so as to approach the vane body 170 by deforming so as to expand in the width direction of the vane groove 130. As a result, the vane 131 can smoothly rotate even at a location where the facing distance is locally short. Therefore, the above inconvenience can be suppressed.

(7) The deformed groove 183 has a groove opening 183a wider than the width of the tip surface 173a of the front convex portion 173, and gradually narrows from the groove opening 183a toward the groove bottom surface 183b of the deformed groove 183. It has an inclined groove side surface 183c. The inclination angle of the front convex portion 173 is larger than the inclination angle of the groove side surface 183c, and the front convex portion 173 has a wide portion 173c formed wider than the width of the groove opening 183a.

According to such a configuration, the front tip seal 180 is held at a position where the groove bottom surface 183b and the axial Z end surface 171 of the vane body 170 are separated from each other by abutting the front convex portion 173 and the groove side surface 183c. .. From that state, the front convex portion 173 further enters the deformation groove 183, so that the deformation groove 183 is expanded, the front tip seal 180 is deformed so as to expand in the width direction, and the front tip seal 180 and the vane body 170 are formed. It will be approaching. As a result, the effect of (6) can be obtained with a relatively simple configuration.

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 front convex portion 173 and the front tip seal 180, the rear convex portion 174 and the rear chip seal 190 can be similarly changed.

The depth of the deformation groove 183 may be deeper than the protrusion dimension from the end surface 171 of the front convex portion 173. As a result, the front tip seal 180 is more easily deformed as compared with the configuration in which the depth of the deformation groove 183 is equal to or less than the protrusion dimension of the front convex portion 173.

Further, in this case, when the front convex portion 173 enters the deformation groove 183 from the initial position, the end surface 171 in the axial direction Z of the vane body 170 and the front tip seal before the front tip surface 173a abuts on the facing surface 182. The facing surface 182 of 180 is in contact with the surface, and the front convex portion 173 is regulated so as not to enter further. As a result, the front convex portion 173 is prevented from excessively entering the deformation groove 183.

○ The depth of the deformation groove 183 may be shallower than the protruding dimension of the front convex portion 173. As a result, the rigidity of the front tip seal 180 can be increased.
The front tip seal 180 may have a configuration having a facing surface 182, a curved tip surface, and a side surface connecting the facing surface 182 and the tip surface. The side surface of the front tip seal 180 may be orthogonal to the width direction of the vane groove 130 in a state where the front tip seal 180 is not deformed. In this case, the front convex portion 173 deforms the front tip seal 180 so as to expand in the width direction, so that the side surface also deforms so as to be inclined with respect to the axial direction Z. As a result, one sealing surface is formed by the front end surface and the side surface, and the sealing surface comes into contact with the front fixed body surface 100. That is, when the front tip seal 180 is not deformed, the tip surface functions as a sealing surface, and when the front tip seal 180 is deformed, the tip surface and the side surface function as a sealing surface. .. Therefore, even in this case, it can be said that the sealing surface is widened in the width direction.

○ A part of the front convex portion 173 may be tapered. In short, the front convex portion 173 may have a tapered portion, and at least a part of the front convex portion 173 may be tapered.

○ The second parts grooves 201 and 202 may be omitted. That is, the width of the vane groove 130 may be constant.
○ 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 compresses with the contact point between the second front flat surface 102 and the front rotating body surface 71 and the suction chamber where suction is performed by the vane 131. It is partitioned into a compression chamber.

○ Either one of both chip seals 180 and 190 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 170 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 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, and may be partitioned by using the front rotating body surface 71 and the front fixed body surface 100. 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 can be said to be a cylinder portion for accommodating the rotating body and the fixed body, and the inner peripheral surface of the rear housing 22 cooperates with the rotating body surface and the fixed body surface to partition the compression chamber. It can also be said to be the inner peripheral surface of the cylinder used. 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 configuration for introducing the suction fluid into the compression chambers A4 and A5 and the configuration for discharging the compressed fluid compressed in the compression chambers A4 and A5 are not limited to the configurations illustrated in the embodiment and are 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. 16, the rear fixed body 110, the rear compression chamber A5, the rear suction port 142, and the rear discharge port 161 may be omitted. In this case, the first front flat surface 101 may be omitted on the front fixed body surface 100. Although the vane 131 has the rear chip seal 190 in FIG. 16, the rear chip seal 190 may be omitted.

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, for example, two or four or more.
○ 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. The same applies to the rear curved surface 123.

○ 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, 90, 110 ... Fixed body, 91, 111 ... Fixed body insertion hole, 100, 120 ... Fixed body surface, 102, 122 ... Second flat surface (fixed body contact surface), 103, 123 ... Curved surface, 130 ... Vane groove, 131 ... Vane, 170 ... Vane body, 171, 172 ... Axial end face in vane body, 173, 174 ... Convex part, 173a, 174a ... Tip surface, 173b, 174b ... Convex side surface, 173c ... Wide part, 180, 190 ... Chip seal (deformable member) ), 181 ... Seal surface, 182 ... Facing surface, 183 ... Deformed groove, 183a ... Groove opening, 183b ... Groove bottom surface, 183c ... Groove side surface, 200 ... First part groove, 201, 202 ... Second part groove, A4 , A5 ... Compression chamber.

Claims (5)

The axis of rotation and
A rotating body that rotates with the rotation of the rotating shaft and has a rotating body surface that intersects the axial direction of the rotating shaft.
A fixed body that does not rotate with the rotation of the rotating shaft and has a fixed body surface that faces the rotating body surface and the axial 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 partitioned by the rotating body surface and the fixed body surface, in which the fluid is sucked and compressed by rotating the vane while moving in the axial direction.
With
The vane
A vane body inserted into the vane groove in a plate-like shape whose thickness direction coincides with the width direction of the vane groove.
A deformable member attached to the axial end face of the vane body and deformable so as to spread in the width direction.
With
The deformable member has a sealing surface that is a surface that comes into contact with the fixed body surface and is curved so as to be convex toward the fixed body surface.
A compressor characterized in that the sealing surface is widened in the width direction by deforming the deforming member so as to spread in the width direction. The vane body has a convex portion that protrudes from the axial end surface of the vane body toward the fixed body surface and has a width direction in the thickness direction of the vane body.
The deforming member is
An opposing surface of the vane body that faces the axial end surface in the axial direction,
A deformed groove formed so as to be recessed from the facing surface toward the fixed body surface and into which the convex portion is inserted.
With
The convex portion has a tapered portion that gradually narrows in width from the axial end surface of the vane body toward the fixed body surface.
The compressor according to claim 1, wherein the deforming member is deformed so as to expand in the width direction when the deformation groove is expanded in the width direction by the tapered portion. The rotating body
A rotating body cylinder portion into which the rotating shaft is inserted and having an outer peripheral surface of the cylinder portion,
A rotating body ring portion provided on the outer peripheral surface of the tubular portion so as to project outward in the radial direction of the rotating shaft, and having a first rotating body surface and a second rotating body surface as the rotating body surface, and the vane groove.
With
The compressor includes, as the fixed body, a first fixed body and a second fixed body provided on both sides of the rotating body ring portion in the axial direction.
The first fixed body has, as the fixed body surface, a first fixed body surface that faces the first rotating body surface in the axial direction.
The second fixed body has, as the fixed body surface, a second fixed body surface that faces the second rotating body surface in the axial direction.
The rotating body is supported by both fixed bodies by being inserted into both fixed body insertion holes formed in the both fixed bodies.
The vane is inserted into the vane groove while being sandwiched between the surfaces of both fixed bodies.
In the undeformed state, the deforming member is held at a position where the facing surface and the axial end surface of the vane body are separated from each other.
The compressor according to claim 2, wherein the deforming member and the vane body approach each other in the axial direction by deforming the deforming member so as to spread in the width direction. The deformation groove is
A groove opening wider than the width of the tip surface of the convex portion,
A groove side surface that is inclined so as to gradually narrow from the groove opening toward the bottom surface of the deformed groove, and
Have,
The inclination angle of the tapered portion is larger than the inclination angle of the groove side surface.
The compressor according to claim 3, wherein the tapered portion has a wide portion formed wider than the width of the groove opening. 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 vane groove is
With respect to the axial movement of the vane, the first part groove into which the vane body is inserted and
A second part groove formed on the rotating body surface and wider than the first part groove,
Including
The compressor according to any one of claims 1 to 4, wherein when the vane is in contact with the fixed-point contact surface, the deformable member is housed in the second part groove.