JP2020139431A - Compressor - Google Patents

Abstract

To provide a compressor which enables reduction of pressing force applied to vanes and acting to the radial outer side.SOLUTION: A compressor 10 includes: a rotary shaft 12; a rotating body 60 which rotates in conjunction with rotation of the rotary shaft 12; fixed bodies 90, 110 which do not rotate in conjunction with the rotation of the rotary shaft 12; vanes 131 inserted into vane grooves 130 formed at the rotating body 60; and compression chambers A4, A5 defined by using rotating body surfaces 71, 72 and fixed body surfaces 100, 120. The compressor 10 includes: a vane recessed part 190 which is formed on a vane outer peripheral end surface 183 and recessed from the vane outer peripheral end surface 183 to the radial R inner side; and a pressing space 192 which is formed by the vane recessed part 190 and a front cylinder inner peripheral surface 33 and into which a fluid is introduced.SELECTED DRAWING: Figure 1

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 rotates with the rotation of the rotating body, centrifugal force is applied to the vane. Therefore, the vane is pressed outward in the radial direction of the rotation shaft. In this case, there is a concern that the vane may be pressed excessively or a gap may be formed inside the vane in the radial direction.

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 reducing the pressing force applied to the vane in the radial direction.

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. It rotates while moving in the axial direction, and accommodates a vane having a vane outer peripheral end face which is a radial outer end face of the rotating shaft, and the rotating body and the fixed body. A cylinder portion having a cylinder inner peripheral surface facing the outer peripheral end surface of the vane in the radial direction of the rotating shaft, and the rotating body surface, the fixed body surface, and the cylinder inner peripheral surface are used to partition the vane. A compression chamber in which fluid is sucked and compressed by rotating while moving in the axial direction, a vane recess formed on the outer peripheral end face of the vane and recessed inward in the radial direction of the rotation shaft from the outer peripheral end face of the vane, and the above. The vane is provided with a pressing space formed by the vane recess and the inner peripheral surface of the cylinder into which a fluid is introduced, and the vane is pressed inward in the radial direction by the fluid in the pressing space. To do.

According to this configuration, the fluid in the pressing space presses the vane in the direction opposite to the centrifugal force. As a result, the pressing force applied to the vane in the radial direction can be reduced.
Regarding the compressor, the compression chambers are a first parts chamber arranged on the side opposite to the rotation direction side of the rotating body with respect to the vane, and a first parts chamber arranged on the rotation direction side with respect to the vane. The vane groove includes two parts chambers, and the vane groove is a pair of side surfaces arranged to face each other in the circumferential direction of the rotation axis, the first groove side surface which is a side surface opposite to the rotation direction side, and the rotation direction. It has a second groove side surface, which is a side surface, and the vane has a first plate surface facing the first groove side surface in the circumferential direction, and a rotation direction side of the first plate surface. It has a plate shape having a second plate surface facing the second groove side surface in the circumferential direction, and the vane recess has an opening formed in the second plate surface. It is good to have.

According to such a configuration, the fluid in the second part chamber is easily introduced into the pressing space through the opening. The pressure of the fluid in the second part chamber tends to be higher than the pressure of the fluid in the first part chamber. As a result, a high-pressure fluid is easily introduced into the pressing space, so that the pressing force of the fluid in the back pressure space can be increased. Therefore, the influence of the centrifugal force applied to the vane can be further reduced.

In particular, when the rotating body rotates, the side surface of the first groove and the surface of the first plate come into contact with each other, while a gap is likely to be formed between the side surface of the second groove and the surface of the second plate. As a result, the fluid in the second part chamber is easily introduced into the pressing space through the gap and the opening. Therefore, it is easy to fill the pressing space with the fluid in the second part chamber.

With respect to the compressor, the vane recess has a first position in which the entire opening faces the side surface of the second groove as the vane moves in the axial direction, and at least a part of the opening. May move between the second position exposed to the second parts chamber and the second position.

According to such a configuration, when the vane recess is arranged at the second position, the fluid in the second part chamber is likely to be introduced into the pressing space. As a result, the fluid in the second part chamber can be more preferably introduced into the pressing space.

Regarding the compressor, the vane outer peripheral end surface is provided on the side opposite to the rotation direction side with respect to the vane recess, and the leakage of the fluid in the pressing space is regulated by abutting with the cylinder inner peripheral surface. It is good to have a regulatory department.

When the opening is exposed to the second parts chamber as described above, there is a possibility that both parts chambers communicate with each other through the pressing space and fluid leaks. In this regard, according to this configuration, the fluid from the pressing space to the first parts chamber is brought into contact with the inner peripheral surface of the front cylinder by the regulation portion provided on the side opposite to the rotation direction side with respect to the vane recess. Movement is restricted. As a result, it is possible to prevent both parts chambers from communicating with each other via the pressing space.

For the compressor, the vane recess may penetrate in the circumferential direction.
According to such a configuration, since the pressing space is formed over the entire thickness of the vane, the area in which the fluid in the pressing space presses the vane can be increased. As a result, the pressing force of the fluid in the pressing space can be increased.

Regarding the compressor, it is preferable that the vane recess is arranged in the vane groove regardless of the axial movement of the vane.
As described above, when the vane recess penetrates in the circumferential direction, if the vane recess is interposed between the two parts chambers, there is a concern that the two parts chambers communicate with each other through the pressing space. In this regard, according to this configuration, since the vane recess is arranged in the vane groove regardless of the movement of the vane in the axial direction, the pressing space protrudes from the rotating body surface in the axial direction and is between the two parts chambers. There is no intervening situation. As a result, it is possible to prevent fluid from leaking between both parts chambers through the pressing space. Therefore, the above-mentioned inconvenience that may occur when the vane recess penetrates in the circumferential direction can be suppressed. Therefore, it is possible to increase the pressing force by the fluid in the pressing space while suppressing the above-mentioned inconvenience.

By the way, as already described, as the rotating body rotates, the side surface of the first groove and the surface of the first plate come into contact with each other, and a gap is likely to occur between the side surface of the second groove and the surface of the second plate. Therefore, even when the vane recess is always arranged in the vane groove, it is expected that the fluid in the second part chamber is introduced into the pressing space through the gap. Therefore, even when the vane recess is always arranged in the vane groove, the vane can be pressed inward in the radial direction by the fluid in the pressing space.

With respect to the compressor, the rotating body has 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, and the compressor has the rotating body as the fixed body. A first fixed body and a second fixed body provided on both sides of the body ring portion in the axial direction are provided, and the first fixed body faces 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 vane groove has the rotating body surface. The vane penetrates the body ring portion in the axial direction, and the vane is arranged between the first fixed body surface and the second fixed body surface in a state of being inserted into the vane groove, and the compressor. As the compression chamber, a first compression chamber partitioned by using the first rotating body surface, the first fixed body surface, and the inner peripheral surface of the cylinder, the second rotating body surface, the second fixed body surface, and the cylinder. It is provided with a second compression chamber partitioned by using an inner peripheral surface, and the axial length of the opening may be shorter than the axial length of the rotating body ring portion.

According to this configuration, the vane recess does not simultaneously communicate with both the first compression chamber and the second compression chamber regardless of the axial movement of the vane. As a result, it is possible to prevent both compression chambers from communicating with each other via the pressing space.

According to the present invention, the pressing force applied to the vane in the radial direction can be reduced.

The schematic diagram which shows the outline of the compressor of 1st Embodiment. 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. 9-9 cross-sectional view of FIG. Perspective view of Vane. A side view schematically showing a vane recess and its periphery when the vane recess is arranged at the first position. FIG. 5 is a side view schematically showing the vane recess and its periphery when the vane recess is arranged at the second position. A development view schematically showing a rotating body, both fixed bodies, and a vane. A development view schematically showing a rotating body, both fixed bodies, and vanes in a phase different from that of FIG. The side view which shows typically the vane recess and the periphery thereof in 2nd Embodiment. The side view which shows typically the vane recess of another example and the periphery thereof. The side view which shows typically the vane recess of another example and the periphery thereof. The side view which shows typically the vane recess of another example and the periphery thereof. The perspective view which shows the vane of another example. An exploded perspective view of another example vane. The cross-sectional view which shows typically the contact mode between the vane of another example and both fixed body surfaces. FIG. 5 is a cross-sectional view schematically showing another example compressor.

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

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

The housing 11 is, for example, tubular as a whole, and has a suction port 11a for sucking an intake fluid from the outside and a discharge port 11b for discharging a compressed fluid. The rotating shaft 12, the electric motor 13, the inverter 14, the front cylinder 30, the rear plate 40, the rotating body 60, and both fixed bodies 90 and 110 are housed in the housing 11.

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

The rear housing 22 has a bottomed tubular shape having a rear housing bottom portion 23 and a rear housing side wall portion 24 that rises from the rear housing bottom portion 23 toward the front housing 21. The front housing 21 and the rear housing 22 are unitized so that the openings face each other. The discharge port 11b is provided on the side wall portion 24 of the rear housing. However, the position of the discharge port 11b is arbitrary.

The inverter cover 25 is arranged on the side opposite to the rear housing 22 side with respect to the front housing 21. The inverter cover 25 is fixed to the front housing 21 in a state of being abutted against the bottom of the front housing 21. The inverter 14 is housed in the inverter cover 25. The inverter 14 drives the electric motor 13.

As shown in FIG. 1, the front cylinder 30 cooperates with the rear plate 40 to accommodate both fixed bodies 90 and 110 and a rotating body 60. The front cylinder 30 has a bottomed cylinder shape formed smaller than the rear housing 22, and is open toward the bottom portion 23 of the rear housing.

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

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

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

The front cylinder inner peripheral surface 33 and the front cylinder outer peripheral surface 34 are, for example, cylindrical surfaces having the axial direction Z as the axial direction. The outer peripheral surface 34 of the front cylinder is in contact with the inner peripheral surface of the side wall portion 24 of the rear housing in the radial direction R.

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

The front cylinder 30 is provided with a bulging portion 36 protruding outward in the radial direction of the rotating shaft 12. The bulging portion 36 is provided at a position straddling both the base end side (front cylinder bottom portion 31 side) of the front cylinder bottom portion 31 and the front cylinder side wall portion 32. The bulging portion 36 bulges outward from the outer peripheral surface 34 of the front cylinder in the radial direction. The front housing 21 and the rear housing 22 are unitized with the bulging portion 36 sandwiched between them. Both housings 21 and 22 regulate the displacement of the front cylinder 30 in the axial direction Z.

As shown in FIG. 1, in the present embodiment, a motor chamber A2 partitioned by a front housing 21 and a front cylinder bottom 31 is provided in the housing 11, and the electric motor 13 is housed in the motor chamber A2. There is. 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 of the fixed bodies 90 and 110.
Specifically, of the both rotating body end portions 61a and 61b which are both ends of the rotating body cylinder portion 61 in the axial direction Z, the front rotating body end portion 61a is inserted into the front fixed body insertion hole 91 and is fixed to the front. It penetrates the front fixed body 90 through the body insertion hole 91.

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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, for example, the front rotating body surface 71 corresponds to the "first rotating body surface", the front fixed body 90 corresponds to the "first fixed body", and the front fixed body surface 100 corresponds to the "first fixed body surface". .. Further, the rear rotating body surface 72 corresponds to the "second rotating body surface", the rear fixed body 110 corresponds to the "second fixed body", and the rear fixed body surface 120 corresponds to the "second fixed body surface". However, the present invention is not limited to this, and vice versa.

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

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

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

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

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

As shown in FIGS. 2 to 5, the compressor 10 includes a vane groove 130 formed in the rotating body 60 and a vane 131 inserted into the vane groove 130.
The vane groove 130 is formed in the rotating body ring portion 70 of the rotating body 60. The vane groove 130 penetrates the rotating body ring portion 70 in the axial direction Z and opens on both rotating body surfaces 71 and 72. The vane groove 130 of the present embodiment extends in the radial direction R with the direction orthogonal to both the axial direction Z and the radial direction R as the width direction.

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 plate shape as a whole, for example, a rectangular plate shape. The vane 131 is arranged between both fixed bodies 90 and 110 (in other words, both fixed body surfaces 100 and 120) in a state where the plate surfaces of the vane 131 intersect with respect to the circumferential direction of the rotation shaft 12. In the present embodiment, both ends of the vane 131, specifically, the vane 131 in the axial direction Z, are in contact with both fixed body surfaces 100 and 120. The vane 131 is allowed to move axially Z along the vane groove 130.

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

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

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

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

Further, of the three parts chambers, the parts chamber arranged between the first front compression chamber A4a and the second front compression chamber A4b in the circumferential direction is referred to as the third front compression chamber A4c. The third front compression chamber A4c is arranged on the rotation direction M side with respect to the first front compression chamber A4a and on the side opposite to the rotation direction M side with respect to the second front compression chamber A4b.

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

Strictly speaking, when one of the plurality of vanes 131 is in contact with the second front flat surface 102, the vanes 131 have not entered the front compression chamber A4. In this case, the spaces on both sides of the vane 131 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 has the first rear compression chamber A5a and the first rear compression chamber A5a on the rotation direction M side by the three vanes 131. It is partitioned into a second rear compression chamber A5b arranged on the opposite side and a third rear compression chamber A5c arranged on the rotation direction M side with respect to the first rear compression chamber A5a. The first rear compression chamber A5a, the second rear compression chamber A5b, and the third rear compression chamber A5c are the same as the first front compression chamber A4a, the second front compression chamber A4b, and the third front compression chamber A4c. The explanation is omitted.

Next, the configuration related to the suction of the suction fluid and the discharge of the compressed fluid into the compression chambers A4 and A5 will be described. For convenience of illustration, the front intake port 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 in detail with reference to FIGS. 9 to 12 and the like. In FIGS. 11 and 12, various members other than the vane 131 are hatched for convenience from the viewpoint of easy viewing.

Here, for convenience of explanation, in the following description, of the two parts chambers partitioned by the vane 131, the side opposite to the rotation direction M side is designated as the first parts chamber Ax, and the parts chamber on the rotation direction M side is the second. Let's call it the parts room Ay. Further, in the following description, the "rotation direction M side is the opposite side" can be said to be the "first parts chamber Ax side", and the "rotation direction M side" can be said to be the "second parts chamber Ay side".

In the vane 131 that partitions the first front compression chamber A4a and the third front compression chamber A4c, the first parts chamber Ax is the first front compression chamber A4a, and the second parts chamber Ay is the third front compression chamber A4c. In the vane 131 that partitions the third front compression chamber A4c and the second front compression chamber A4b, the first parts chamber Ax is the third front compression chamber A4c, and the second parts chamber Ay is the second front compression chamber A4b. In the vane 131 that partitions the second front compression chamber A4b and the first front compression chamber A4a, the first parts chamber Ax is the second front compression chamber A4b, and the second parts chamber Ay is the first front compression chamber A4a. The same applies to the rear compression chamber A5.

By the way, the pressures of the front compression chambers A4a to A4c tend to be higher as they are arranged on the rotation direction M side. Specifically, the first front compression chamber A4a, the third front compression chamber A4c, and the second front compression chamber A4b (particularly, the rotation direction M side of the contact point between the front rotating body surface 71 and the second front flat surface 102). It tends to increase in the order of the space on the opposite side). Therefore, the pressure of the second parts chamber Ay on the rotation direction M side with respect to the vane 131 tends to be higher than the pressure of the first parts chamber Ax on the side opposite to the rotation direction M side with respect to the vane 131. ..

As shown in FIG. 9, the vane groove 130 is open toward the outer side in the radial direction R. On the other hand, the vane groove 130 is not formed in the rotating body cylinder portion 61 and does not open inward in the radial direction R. Therefore, the vane groove 130 has a groove inner peripheral end surface 170 which is an end surface inside the radial direction R.

The groove inner peripheral end surface 170 is curved so as to be convex toward the outer side in the radial direction R, which is the same direction as the outer peripheral surface 62 of the tubular portion, for example. In the present embodiment, the curvature of the groove inner peripheral end surface 170 is the same as the curvature of the tubular portion outer peripheral surface 62. That is, the groove inner peripheral end surface 170 of the present embodiment is formed so as to be flush with the tubular portion outer peripheral surface 62, and is continuous with the tubular portion outer peripheral surface 62 in the axial direction Z.

In the present embodiment, the groove inner peripheral end surface 170 is provided on the rotating body 60 (specifically, the rotating body cylinder portion 61). However, the present invention is not limited to this, and any member having the groove inner peripheral end surface 170 is arbitrary. For example, in addition to the rotating body 60, an inner member having a groove inner peripheral end surface 170 may be separately provided, and the inner member may be attached to the rotating body 60.

As shown in FIG. 9, the vane groove 130 has a first groove side surface 171 and a second groove side surface 172 as a pair of side surfaces arranged to face each other in the circumferential direction. The first groove side surface 171 and the second groove side surface 172 stand up from the groove inner peripheral end surface 170. The first groove side surface 171 and the second groove side surface 172 intersect with each other in the circumferential direction, and extend in the axial direction Z and the radial direction R in the present embodiment. It can be said that the vane groove 130 extends in the axial direction Z and the radial direction R with the opposite directions of the side surfaces 171 and 172 of both grooves as the width direction.

The second groove side surface 172 is arranged on the rotation direction M side with respect to the first groove side surface 171. That is, the first groove side surface 171 is the side surface of the vane groove 130 opposite to the rotation direction M side, and the second groove side surface 172 is the side surface of the vane groove 130 on the rotation direction M side.

The vane 131 has a plate shape with the width direction of the vane groove 130 as the thickness direction, and in the present embodiment, the thickness direction of the vane 131 coincides with the direction orthogonal to both the axial direction Z and the radial direction R. There is. The vane 131 has a first plate surface 181 facing the first groove side surface 171 in the circumferential direction, and a second plate surface 182 facing the second groove side surface 172. Both plate surfaces 181, 182 intersect with each other in the circumferential direction, and extend in the axial direction Z and the radial direction R in the present embodiment. It can be said that the vane 131 extends in the axial direction Z and the radial direction R with the opposite directions of the plate surfaces 181, 182 as the thickness direction.

The second plate surface 182 is arranged on the rotation direction M side with respect to the first plate surface 181. That is, the first plate surface 181 is the side surface of the vane 131 opposite to the rotation direction M side, and the second plate surface 182 is the side surface of the vane 131 on the rotation direction M side.

The width W1 of the vane groove 130 is preferably equal to or greater than the thickness D1 of the vane 131, and in the present embodiment, the width W1 of the vane groove 130 is slightly wider than the thickness D1 of the vane 131. As a result, a gap S1 is formed between the first groove side surface 171 and the first plate surface 181 and at least one of the second groove side surface 172 and the second plate surface 182. Therefore, the vane 131 can be inserted into the vane groove 130, and the vane 131 can smoothly move in the axial direction Z.

The difference between the width W1 of the vane groove 130 and the thickness D1 of the vane 131 is arbitrary as long as the vane 131 can move in the axial direction Z, but if attention is paid to the viewpoint of suppressing the rattling of the vane 131 or the like. Smaller is preferable. Further, even if the width W1 of the vane groove 130 and the thickness D1 of the vane 131 are the same, a gap S1 may occur due to a slight inclination of the plane and an error.

The vane 131 includes vane outer peripheral end faces 183 and vane inner peripheral end faces 184 as both end faces in the radial direction R. The vane outer peripheral end surface 183 is the end surface on the outer peripheral side (specifically, the outer side of the radial direction R) of both end faces in the radial direction R of the vane 131, and the vane inner peripheral end surface 184 is both end faces of the vane 131 in the radial direction R. Of these, the end face on the inner peripheral side (specifically, inside R in the radial direction). The vane outer peripheral end surface 183 and the vane inner peripheral end surface 184 can be said to be both side surfaces of the plate-shaped vane 131.

The vane outer peripheral end surface 183 faces the front cylinder inner peripheral surface 33 regardless of the movement of the vane 131. In other words, it can be said that the front cylinder inner peripheral surface 33 extends in the axial direction Z longer than the moving range of the vane 131 so as to face the vane outer peripheral end surface 183 in the radial direction R regardless of the movement of the vane 131.

The inner peripheral surface 33 of the front cylinder and the outer peripheral end surface 183 of the vane are curved in the same direction. Specifically, the front cylinder inner peripheral surface 33 is curved so as to be convex toward the radial R outer side, and the vane outer peripheral end surface 183 is curved so as to be convex toward the radial R outer side. .. Therefore, when the vane outer peripheral end surface 183 is pressed toward the R outer side in the radial direction, the vane outer peripheral end surface 183 and the front cylinder inner peripheral surface 33 come into surface contact with each other. In the present embodiment, the curvature of the vane outer peripheral end surface 183 is set to be the same as the curvature of the front cylinder inner peripheral surface 33.

As shown in FIG. 9, the vane inner peripheral end surface 184 faces the groove inner peripheral end surface 170 in the radial direction R. In the present embodiment, the vane inner peripheral end surface 184 is curved in the same direction as the groove inner peripheral end surface 170, and in detail, is curved so as to be concave outward in the radial direction R. As a result, the vane inner peripheral end surface 184 and the groove inner peripheral end surface 170 are easily in surface contact with each other.

According to such a configuration, the vane 131 is sandwiched by both groove side surfaces 171 and 172 from the circumferential direction. As a result, when the rotating body 60 rotates, the first groove side surface 171 and the first plate surface 181 on the side opposite to the rotation direction M side (in other words, the first parts chamber Ax side) come into contact with each other in the circumferential direction. The vane 131 is pressed in the circumferential direction through the contact portion. As a result, the vane 131 rotates.

On the other hand, a gap S1 is formed between the second groove side surface 172 on the rotation direction M side and the second plate surface 182. The gap S1 communicates with the second parts chamber Ay. Therefore, the fluid in the second parts chamber Ay enters the gap S1.

As a reminder, when the rotating body 60 is stationary, the gap S1 is between the first groove side surface 171 and the first plate surface 181 and between the second groove side surface 172 and the second plate surface 182. It may be provided in any of the spaces between the two, and may be provided in both. Even in this case, as the rotating body 60 rotates, a gap S1 is naturally formed between the second groove side surface 172 and the second plate surface 182.

Further, the vane 131 is sandwiched from the radial direction R by the groove inner peripheral end surface 170 and the front cylinder inner peripheral surface 33. Therefore, the displacement of the vane 131 in the radial direction R is regulated. Further, it is possible to prevent the fluid in the gap S1 from leaking to the first parts chamber Ax side via the radial R inside or the radial R outside of the vane 131.

Here, since the vane 131 rotates with the rotation of the rotating body 60, a centrifugal force is applied to the vane 131. Therefore, the vane 131 is pressed toward the outer side in the radial direction, and the vane outer peripheral end surface 183 is pressed toward the front cylinder inner peripheral surface 33. In this case, there is a concern that the sliding of the vane outer peripheral end surface 183 and the front cylinder inner peripheral surface 33 may be hindered, or a gap may be formed between the vane inner peripheral end surface 184 and the groove inner peripheral end surface 170. In the stationary state where centrifugal force is not applied, the vane outer peripheral end surface 183 and the front cylinder inner peripheral surface 33 may be separated from each other.

On the other hand, the compressor 10 of the present embodiment has a configuration for reducing the pressing force applied to the vane 131 toward the outer side in the radial direction R. The configuration will be described in detail below.
As shown in FIGS. 9 and 10, the compressor 10 includes a vane recess 190 formed in the vane outer peripheral end surface 183, and a pressing space 192 formed by the vane recess 190 and the front cylinder inner peripheral surface 33. ing.

The vane recess 190 is recessed from the vane outer peripheral end surface 183 toward the inside of the radial direction R. The vane recess 190 of the present embodiment extends in the axial direction Z with the thickness direction of the vane 131 as the width direction.

The vane recess 190 of the present embodiment has an opening 191 formed in the second plate surface 182, and is open to both the outer side in the radial direction R and the side of the second parts chamber Ay. In other words, it can be said that the vane recess 190 is formed so as to straddle both the vane outer peripheral end surface 183 and the second plate surface 182. The vane recess 190 is not open in the axial direction Z and has both end faces in the axial direction Z.

As shown in FIGS. 11 and 12, the length Za of the opening 191 in the axial direction Z is set shorter than the ring thickness D2, which is the length of the rotating body ring portion 70 in the axial direction Z. In the present embodiment, the axial Z length Za of the opening 191 is the same as the axial Z length of the vane recess 190. That is, the vane recess 190 of the present embodiment is open to the rotation direction M side over the entire axial direction Z.

Further, the vane recess 190 of the present embodiment has a first position in which the entire opening 191 faces the second groove side surface 172 as the vane 131 moves in the axial direction Z, and at least one of the openings 191. The portion moves between the front compression chamber A4 and the second position exposed to the second parts chamber Ay. The first position can be said to be a position where the entire opening 191 is covered by the second groove side surface 172, and the second position is a position where at least a part of the opening 191 has entered the front compression chamber A4. It can be said that.

Incidentally, the opening 191 of the present embodiment is configured so as not to be exposed to the rear compression chamber A5. In detail, as shown in FIG. 11, when the vane 131 is most displaced toward the rear compression chamber A5, the opening 191 has the vane 131 with the second front flat surface 102 and the first rear flat surface 121. When it is arranged between the two, it is formed at a position facing the second groove side surface 172. It can be said that the case where the vane 131 is most displaced toward the rear compression chamber A5 is the case where the vane 131 protrudes most from the rear rotating body surface 72. Further, the position facing the second groove side surface 172 can be said to be a position closer to the front rotating body surface 71 than to the rear rotating body surface 72.

As a reminder, the opening 191 is formed at a position where at least a part of the opening 191 is exposed to the second parts chamber Ay of the front compression chamber A4, and the length of the opening 191 in the axial direction Z. If Za is shorter than the ring thickness D2, the opening 191 is not naturally exposed to the rear compression chamber A5.

As shown in FIGS. 9 to 12, the vane recess 190 is not open to the first plate surface 181. That is, the vane recess 190 of the present embodiment has a non-penetrating shape that does not penetrate the vane 131 in the circumferential direction. Therefore, the vane outer peripheral end surface 183 is arranged on the side opposite to the rotation direction M side with respect to the vane recess 190, and has a regulating portion 183a that comes into contact with the front cylinder inner peripheral surface 33. The regulation unit 183a regulates that the fluid in the pressing space 192 leaks to the side opposite to the rotation direction M (in other words, the first parts chamber Ax side) by contacting the inner peripheral surface 33 of the front cylinder. ..

As shown in FIG. 9, the vane recess 190 gradually narrows from the outside of the radial direction R to the inside of the radial direction R, for example. Further, the vane recess 190 is formed so as to gradually become shallower from the opening 191 toward the first plate surface 181 for example. As an example, the cross-sectional shape of the vane recess 190 in the present embodiment as viewed from the axial direction Z is triangular.

The pressing space 192 is a space partitioned by the vane recess 190 and the inner peripheral surface 33 of the front cylinder. The pressing space 192 opens to the rotation direction M side through the opening 191 and communicates with the gap S1. As a result, the fluid in the second parts chamber Ay in the gap S1 is introduced into the pressing space 192. The vane 131 is pressed by the fluid in the pressing space 192 toward the inside of the radial direction R, which is the direction opposite to the centrifugal force.

Further, since the vane recess 190 is formed so as to gradually become shallower from the opening 191 toward the first plate surface 181 the pressing space 192 gradually becomes shallower toward the first plate surface 181 from the opening 191. It is formed so that the cross section is small. For example, the pressing space 192 of the present embodiment has a triangular columnar shape extending in the axial direction Z.

Next, a series of operations of the compressor 10 will be described as the operation of the present embodiment with reference to FIGS. 13 and 14. 13 and 14 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. 13 and 14, for convenience of illustration, each port 141, 142, 151, 161 is schematically shown.

As shown in FIGS. 13 and 14, 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. 13 and 14, 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.

Incidentally, as shown in FIGS. 13 and 14, the vane recess 190 has an opening 191 of the front compression chamber A4 on the rotation direction M side (second parts chamber Ay) as the vane 131 moves in the axial direction Z. ), Or enter the vane groove 130. Therefore, the fluid in the second parts chamber Ay of the front compression chamber A4 is easily introduced into the vane recess 190.

On the other hand, since the vane recess 190 is formed at a position where it does not enter the rear compression chamber A5 regardless of the movement of the vane 131, the opening 191 is not exposed to the rear compression chamber A5.

According to the present embodiment described in detail above, the following effects are obtained.
(1-1) The compressor 10 includes a rotating shaft 12, a rotating body 60 that rotates with the rotation of the rotating shaft 12, fixed bodies 90 and 110 that do 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 a vane groove 130 formed in the above and rotates while moving in the axial direction Z as the rotating body 60 rotates. The rotating body 60 has rotating body surfaces 71 and 72 intersecting the axial direction Z, and the fixed bodies 90 and 110 have fixed body surfaces 100 and 120 facing the rotating body surfaces 71 and 72 in the axial direction Z. are doing. The vane 131 has a vane outer peripheral end surface 183 which is an end surface on the outer side in the radial direction. The compressor 10 has a front cylinder inner peripheral surface 33 in the radial direction R with respect to the vane outer peripheral end surface 183, and includes a front cylinder 30 that accommodates the rotating body 60 and the fixed bodies 90 and 110. The compressor 10 is partitioned by using the inner peripheral surface 33 of the front cylinder, the rotating body surfaces 71 and 72, and the fixed body surfaces 100 and 120, and the vane 131 rotates while moving in the axial direction Z to suck and compress the fluid. It is provided with compression chambers A4 and A5.

The compressor 10 is formed on the vane outer peripheral end surface 183 and is formed by a vane recess 190 recessed from the vane outer peripheral end surface 183 inward in the radial direction R, a vane recess 190, and a front cylinder inner peripheral surface 33 to introduce a fluid. It is provided with a pressing space 192 to be formed. The vane 131 is pressed inward in the radial direction by the fluid in the pressing space 192.

According to such a configuration, the vane 131 is pressed in the direction opposite to the centrifugal force by the fluid in the pressing space 192. As a result, the pressing force applied to the vane 131 toward the outer side in the radial direction R can be reduced.

(1-2) The compression chambers A4 and A5 are arranged on the first parts chamber Ax arranged on the side opposite to the rotation direction M side with respect to the vane 131 and on the rotation direction M side with respect to the vane 131, respectively. Includes the second parts room Ay.

The vane groove 130 has a first groove side surface 171 and a second groove side surface 172 as a pair of side surfaces arranged to face each other in the circumferential direction. The first groove side surface 171 is a side surface of the vane groove 130 opposite to the rotation direction M side, and the second groove side surface 172 is a side surface of the vane groove 130 on the rotation direction M side. The vane 131 is arranged on the first plate surface 181 facing the first groove side surface 171 in the circumferential direction and on the rotation direction M side of the first plate surface 181 in the circumferential direction with respect to the second groove side surface 172. It has a plate shape having a second plate surface 182 facing each other. The vane recess 190 includes an opening 191 formed in the second plate surface 182.

According to such a configuration, the fluid in the second parts chamber Ay is easily introduced into the pressing space 192 through the opening 191. The pressure of the fluid in the second parts chamber Ay tends to be higher than the pressure of the fluid in the first parts chamber Ax. As a result, a high-pressure fluid is easily introduced into the pressing space 192, so that the pressing force of the fluid in the pressing space 192 can be increased. Therefore, the influence of the centrifugal force applied to the vane 131 can be further reduced.

In particular, when the rotating body 60 rotates, the first groove side surface 171 and the first plate surface 181 come into contact with each other, while a gap S1 is likely to be formed between the second groove side surface 172 and the second plate surface 182. As a result, the fluid in the second parts chamber Ay is easily introduced into the pressing space 192 through the gap S1 and the opening 191. Therefore, the pressing space 192 can be easily filled with the fluid in the second parts chamber Ay.

(1-3) The vane recess 190 has a first position in which the entire opening 191 faces the second groove side surface 172 and at least a part of the opening 191 as the vane 131 moves in the axial direction Z. Moves between the second position exposed to the second parts chamber Ay.

According to such a configuration, when the vane recess 190 is arranged at the second position, the fluid in the second parts chamber Ay is likely to be introduced into the pressing space 192. Thereby, the fluid in the second parts chamber Ay can be more preferably introduced into the pressing space 192.

(1-4) The vane recess 190 has a non-penetrating shape in the circumferential direction (in other words, the thickness direction of the vane 131), and the vane is also on the side opposite to the rotation direction M with respect to the vane recess 190. An outer peripheral end face 183 is formed. That is, the vane outer peripheral end surface 183 includes a regulating portion 183a provided on the side opposite to the rotation direction M side with respect to the vane recess 190. The regulation unit 183a regulates the leakage of the fluid in the pressing space 192 by abutting with the inner peripheral surface 33 of the front cylinder.

When the opening 191 is exposed to the second parts chamber Ay as described above, there is a possibility that the two parts chambers Ax and Ay communicate with each other through the pressing space 192 and the fluid leaks. In this respect, in the present embodiment, the pressing space 192 to the first parts chamber is caused by the contact between the regulation portion 183a provided on the side opposite to the rotation direction M side with respect to the vane recess 190 and the front cylinder inner peripheral surface 33. The movement of fluid to Ax is restricted. As a result, it is possible to prevent the two parts chambers Ax and Ay from communicating with each other via the pressing space 192.

(1-5) The pressing space 192 is formed so that the cross section gradually decreases from the opening 191 toward the first plate surface 181.
According to such a configuration, it is possible to easily introduce the fluid in the second parts chamber Ay into the pressing space 192, and to suppress the loss that may occur by introducing the fluid in the second parts chamber Ay into the pressing space 192. ..

More specifically, it is preferable that the area of the opening 191 is large, paying attention to facilitating the introduction of the fluid in the second parts chamber Ay into the pressing space 192. On the other hand, since the fluid filled in the pressing space 192 becomes a loss, the larger the fluid filled in the pressing space 192, the larger the loss tends to be.

In this respect, according to the present embodiment, since the cross-sectional area of the pressing space 192 is gradually reduced from the opening 191 toward the first plate surface 181 while increasing the area of the opening 191. , The volume of the pressing space 192 can be reduced. As a result, the above-mentioned effect is obtained.

(1-6) The rotating body 60 includes a rotating body ring portion 70 having both rotating body surfaces 71 and 72 and a vane groove 130, and both fixed bodies 90 and 110 are in the axial direction Z of the rotating body ring portion 70. It is provided on both sides. The vane groove 130 penetrates the rotating body ring portion 70 in the axial direction Z, and the vane 131 is arranged between the fixed body surfaces 100 and 120 in a state of being inserted into the vane groove 130. The length Za of the opening 191 in the axial direction Z is shorter than the ring thickness D2, which is the length of the rotating body ring portion 70 in the axial direction Z.

According to this configuration, both compression chambers A4 and A5 are provided on both sides in the axial direction Z with respect to the rotating body ring portion 70, and the vane 131 rotates while moving in the axial direction Z to form both compression chambers A4 and A5. The fluid is sucked and compressed.

Here, since the length Za of the opening 191 in the axial direction Z is shorter than the ring thickness D2, the opening 191 is not arranged across both the compression chambers A4 and A5. As a result, the vane recess 190 does not communicate with both the compression chambers A4 and A5 at the same time. Therefore, it is possible to prevent the two compression chambers A4 and A5 from communicating with each other through the pressing space 192, and through this, it is possible to suppress the leakage of fluid between the two compression chambers A4 and A5.

(Second Embodiment)
As shown in FIG. 15, the vane recess 200 of the present embodiment is arranged in the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z. For example, the vane recess 200 is arranged in the vane groove 130 when the vane 131 is most displaced toward the front compression chamber A4, specifically when the vane 131 and the first front flat surface 101 are in contact with each other. There is. It can be said that the case where the vane 131 is most displaced to the front compression chamber A4 side is the case where the vane 131 protrudes most from the front rotating body surface 71. Further, it can be said that the vane recess 200 is arranged closer to the rear rotating body surface 72 than to the front rotating body surface 71 when the vane 131 is most displaced to the front compression chamber A4 side.

Similarly, the vane recess 200 of the present embodiment is arranged in the vane groove 130 when the vane 131 is most displaced toward the rear compression chamber A5. That is, the vane recess 200 of the present embodiment is formed at a position closer to the center by a distance longer than the deviation amount Z1 from both ends of the vane 131 in the axial direction Z.

Further, the vane recess 200 of the present embodiment penetrates in the circumferential direction (in other words, the thickness direction of the vane 131), and the first opening 201 formed on the first plate surface 181 and the second plate surface. It has a second opening 202 formed in 182. The openings 201 and 202 are arranged in the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z, and face the groove side surfaces 171 and 172.

Since the vane recess 200 is formed as described above, the pressing space 203 of the present embodiment is arranged in the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z. That is, both openings 201 and 202 are not exposed to both parts chambers Ax and Ay. Further, the pressing space 203 is formed over the entire thickness of the vane 131, and is open at both ends in the circumferential direction.

The specific shape of the bottom surface of the vane recess 200 in this embodiment is arbitrary. For example, the bottom surface of the vane recess 200 may be a flat surface orthogonal to the radial direction R, or may be convex toward the outer side of the radial direction R so as to be curved in the same direction as the inner peripheral surface 33 of the front cylinder. It may be curved to. On the contrary, the bottom surface of the vane recess 200 may be curved so as to be recessed inward in the radial direction R.

According to the present embodiment described in detail above, the following actions and effects are exhibited in place of the effects of (1-3) and (1-4).
(2-1) The vane recess 200 penetrates in the circumferential direction.

According to such a configuration, since the pressing space 203 is formed over the entire thickness of the vane 131, the pressing area by the fluid in the pressing space 203 can be increased. As a result, the pressing force of the fluid in the pressing space 203 toward the inside of the radial direction R can be increased.

(2-2) The vane recess 200 is arranged in the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z.
As described above, when the vane recess 200 penetrates in the circumferential direction, there is a concern that both parts chambers Ax and Ay communicate with each other through the pressing space 203.

In this respect, in the present embodiment, since the vane recess 200 is arranged in the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z, the pressing space 203 moves from the rotating body surfaces 71 and 72 to the axial direction Z. There is no situation in which it protrudes and intervenes between both parts chambers Ax and Ay. As a result, it is possible to prevent fluid from leaking between the two parts chambers Ax and Ay via the pressing space 203. Therefore, the above-mentioned inconvenience that may occur when the vane recess 200 penetrates in the circumferential direction can be suppressed. Therefore, while suppressing the above inconvenience, it is possible to increase the pressing force toward the inside of the radial direction R by the fluid in the pressing space 203.

By the way, as already described, as the rotating body 60 rotates, the first groove side surface 171 and the first plate surface 181 come into contact with each other, and the gap S1 between the second groove side surface 172 and the second plate surface 182. Is likely to occur. Therefore, even when the vane recess 200 is always arranged in the vane groove 130, it is expected that the fluid in the second parts chamber Ay is introduced into the pressing space 203 through the gap S1. To. Therefore, even when the vane recess 200 is always arranged in the vane groove 130, the vane 131 can be pressed inward in the radial direction by the fluid in the pressing space 203.

Each of the above embodiments may be modified as follows. In addition, each of the above-described embodiments and the following alternative examples may be combined with each other within a technically consistent range.
○ As shown in FIG. 16, in the second embodiment, the vane recess 210 may have a non-penetrating shape in the circumferential direction. That is, the vane recess 210 may be arranged in the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z, and the vane outer peripheral end surface 183 may have the regulation portion 183a. In this case, both parts chambers Ax, Ay pass through the gap S1, the pressing space 211 formed by the vane recess 210 and the front cylinder inner peripheral surface 33, and between the first groove side surface 171 and the first plate surface 181. It is possible to prevent fluid from leaking between them.

The vane recess may have an opening formed in the first plate surface 181 but not in the second plate surface 182. Even in this case, the fluid in the first parts chamber Ax may be introduced from a minute gap formed in a part between the first groove side surface 171 and the first plate surface 181.

○ The vane recess may be configured not to open on both plate surfaces 181, 182. Even in this case, the fluid can be introduced through a minute gap that can be formed between the vane 131 and the vane groove 130. However, paying attention to the fact that the fluid is easily introduced into the pressing space, it is preferable that the vane recess is open to at least one of both plate surfaces 181, 182.

○ In the first embodiment, the opening 191 is exposed to the second parts chamber Ay of the front compression chamber A4, but is not limited to this, and is exposed to the second parts chamber Ay of the rear compression chamber A5. It may be formed at a position to be used. That is, the second position may be a position where the opening 191 is exposed to the second parts chamber Ay of either one of the compression chambers A4 and A5.

○ The opening 191 faces the portion facing the second groove side surface 172 regardless of the movement of the vane 131 in the axial direction Z, and faces the second groove side surface 172 or with respect to the second parts chamber Ay depending on the phase. It may be configured to have a portion to be exposed. In this case, not all but a part of the opening 191 is exposed to the second parts chamber Ay.

○ The specific shape of the vane recess and the pressing space is arbitrary. For example, the pressing space may have a rectangular parallelepiped shape extending in the axial direction Z.
○ As shown in FIGS. 17 and 18, the length in the axial direction Z may be different between the vane recess 220 and the opening 221. For example, the length Za in the axial direction Z of the opening 221 may be shorter than the ring thickness D2, while the length Zb in the axial direction Z of the vane recess 220 may be set longer than the ring thickness D2. That is, the opening 221 may be formed narrower in the axial direction Z than the vane recess 220. In this case, the pressing space 222 formed by the vane recess 220 and the inner peripheral surface 33 of the front cylinder communicates with the gap S1 or the second parts chamber Ay only through the opening 221. On the other hand, the periphery of the pressing space 222 other than the opening 221 may be surrounded by a contact portion between the vane outer peripheral end surface 183 and the front cylinder inner peripheral surface 33 so that fluid does not leak.

According to such a configuration, the pressing space 222 is formed by lengthening the vane recess 220 while suppressing the communication between the two compression chambers A4 and A5 due to the opening 221 being arranged so as to straddle both the compression chambers A4 and A5. The pressing area by the fluid inside can be increased.

The length Za of the opening 191 in the axial direction Z may be a ring thickness D2 or more. In this case, the vane recess 190 may be provided unevenly on either end of the vane 131 in the axial direction Z so that the vane recess 190 does not communicate with both the compression chambers A4 and A5 at the same time.

-The specific shapes of the vane outer peripheral end face 183 and the vane inner peripheral end face 184 are arbitrary. For example, at least one of the vane outer peripheral end surface 183 and the vane inner peripheral end surface 184 may be a flat surface orthogonal to the radial direction R.

○ As shown in FIGS. 19 to 21, the vane 131 may be composed of a plurality of parts. For example, the vane 131 has a vane body 240 inserted into the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z, and tip seals 250 and 260 provided on both sides of the vane body 240 in the axial direction Z. And may have. The vane 131 has a plate shape that is convex toward the fixed body surfaces 100 and 120 by combining the vane body 240 and both tip seals 250 and 260. In this case, both tip seals 250 and 260 form both ends of the vane 131 in the axial direction Z and come into contact with the fixed body surfaces 100 and 120.

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

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

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

Further, as shown in FIG. 21, back pressure spaces 253 and 263 in which a fluid enters are formed between both tip seals 250 and 260 and the vane body 240. The tip seals 250 and 260 are pressed toward the fixed body surfaces 100 and 120 by the fluid in the back pressure spaces 253 and 263. As a result, the tip seals 250 and 260 come into contact with the fixed body surfaces 100 and 120. As a result, the vane 131 and the fixed body surfaces 100 and 120 can be sealed.

In this alternative example, as shown in FIG. 20, the vane outer peripheral end surface 183 is composed of the outer peripheral end surface 245 of the vane main body 240 and the outer peripheral end surfaces 254 and 264 of both tip seals 250 and 260. The outer peripheral end surface 245 of the vane body 240 is the radial R outer end surface of the vane body 240, and the outer peripheral end faces 254 and 264 of the chip seals 250 and 260 are the radial R outer end faces of the chip seals 250 and 260. .. In this alternative example, the vane recess 190 may be formed on, for example, the vane body 240, specifically, the outer peripheral end surface 245 of the vane body 240.

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

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

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

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

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

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

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

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

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

○ The configuration for introducing the suction fluid into the 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 first embodiment and are optional. is there. 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. 22, 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.

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

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

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

○ The number of vanes 131 is arbitrary, and may be one, two, or four or more. When there is only one vane 131, the front compression chamber A4 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.

○ 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.
Next, a suitable example that can be grasped from the above embodiment and another example will be described below.
(B) The vane recess has a first position where the entire opening faces the side surface of the second groove as the vane moves in the axial direction, and at least a part of the opening is a second parts chamber of the first compression chamber. Alternatively, it may move between the second position exposed to either one of the second parts chambers of the second compression chamber.

(B) 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 on both sides of the rotation axis in the circumferential direction with respect to the fixed-point contact surface, and rotates when separated from the fixed-point contact surface in the circumferential direction. It may include a pair of curved surfaces that are axially curved away from the body surface.

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, 100, 120 ... fixed body surface, 130 ... vane groove, 131 ... vane, 170 ... groove inner peripheral end surface, 171 ... first groove side surface, 172 ... second groove side surface, 181 ... first plate surface, 182 ... second plate surface , 183 ... vane outer peripheral end face, 183a ... regulation part, 184 ... vane inner peripheral end face, 190, 200, 210, 220 ... vane recess, 191, 202, 221 ... opening, 192, 203, 211, 222 ... pressing space, A4, A5 ... compression chamber, Ax ... first parts chamber, Ay ... second parts chamber, Za ... axial length of opening, D2 ... ring thickness, S1 ... gap.

Claims (7)

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.
It 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, and the vane outer peripheral end surface which is the radial outer end surface of the rotating body is With vanes to have
A cylinder portion that accommodates the rotating body and the fixed body and has a cylinder inner peripheral surface that faces the vane outer peripheral end surface in the radial direction of the rotating shaft.
A compression chamber that is partitioned by using the rotating body surface, the fixed body surface, and the inner peripheral surface of the cylinder, and in which the fluid is sucked and compressed by rotating the vane while moving in the axial direction.
A vane recess formed on the outer peripheral end surface of the vane and recessed inward in the radial direction of the rotation shaft from the outer peripheral end surface of the vane.
A pressing space formed by the vane recess and the inner peripheral surface of the cylinder into which a fluid is introduced,
With
The vane is a compressor characterized in that it is pressed inward in the radial direction by a fluid in the pressing space. The compression chamber
The first parts chamber arranged on the side opposite to the rotation direction side of the rotating body with respect to the vane,
A second parts chamber arranged on the rotation direction side with respect to the vane,
Including
The vane groove is formed as a pair of side surfaces arranged to face each other in the circumferential direction of the rotation axis.
The side surface of the first groove, which is the side surface opposite to the rotation direction side,
The side surface of the second groove, which is the side surface on the rotation direction side,
Have,
The vane
A first plate surface facing the first groove side surface in the circumferential direction,
A second plate surface that is arranged on the rotation direction side of the first plate surface and faces the circumferential direction with respect to the second groove side surface.
It is plate-shaped with
The compressor according to claim 1, wherein the vane recess has an opening formed on the second plate surface. The vane recess has a first position in which the entire opening faces the side surface of the second groove as the vane moves in the axial direction, and at least a part of the opening is the second part. The compressor according to claim 2, which moves between a second position exposed to the chamber. The vane outer peripheral end surface is provided on the side opposite to the rotation direction side with respect to the vane recess, and has a regulating portion that regulates leakage of fluid in the pressing space by abutting with the cylinder inner peripheral surface. The compressor according to claim 3. The compressor according to claim 2, wherein the vane recess penetrates in the circumferential direction. The compressor according to claim 5, wherein the vane recess is arranged in the vane groove regardless of the axial movement of the vane. The rotating body has 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.
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 vane groove penetrates the rotating body ring portion in the axial direction.
The vane is arranged between the first fixed body surface and the second fixed body surface in a state of being inserted into the vane groove.
The compressor serves as the compression chamber.
A first compression chamber partitioned by using the first rotating body surface, the first fixed body surface, and the inner peripheral surface of the cylinder.
A second compression chamber partitioned by using the second rotating body surface, the second fixed body surface, and the inner peripheral surface of the cylinder.
With
The compressor according to any one of claims 2 to 6, wherein the length of the opening in the axial direction is shorter than the length of the rotating body ring portion in the axial direction.