COMPRESSOR

Abstract

A compressor includes a rotary shaft, a rotating body, a fixed body, a vane, and a compression chamber. The vane has a vane end that contacts the surface of fixed body. The fixed body surface includes two curved surfaces. The curved surface includes a convex surface and a concave surface. The convex surface has a convex surface inner end and a convex surface outer end. The curvature of the convex surface inner end is greater than the curvature of the convex surface outer end. The concave surface has a concave surface inner end and a concave surface outer end. The curvature of the concave surface inner end is greater than the curvature of the concave surface outer end.

Description

BACKGROUND

1. Field

The present disclosure relates to a compressor.

2. Description of Related Art

Japanese Laid-Open Patent Publication No. 2015-14250 describes an axial vane compressor that includes a rotary shaft, a columnar rotor, which has slit grooves, vanes fitted in the slit grooves to be allowed to swing, and side plates having cam surfaces. Each cam surface serves as a fixed body surface provided in the side plate, which serves as a fixed body. Rotation of the rotary shaft and the rotor of this axial vane compressor causes the vanes to rotate while moving in the axial direction of the rotary shaft. This results in suction and compression of the fluid in the compression chambers defined by the axial end faces of the rotor and the cam surfaces.

SUMMARY

The present inventors discovered that when the vanes and the fixed body surface contact each other, each vane tends to swing in the circumferential direction of the rotary shaft of the vanes on a pivot, which is the contact area between the vane and the fixed body surface.

It is an objective of the present disclosure to provide a compressor that restricts swinging motion of vanes in the circumferential direction.

This Summary is provided to introduce a selection of concepts in a simplified form that are further described below in the Detailed Description. This Summary is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to be used as an aid in determining the scope of the claimed subject matter.

In one general aspect, a compressor is provided that includes a rotary shaft, a rotating body, a fixed body, a vane, and a compression chamber. The rotating body is configured to rotate together with the rotary shaft and includes a rotating body surface, which intersects with an axial direction of the rotary shaft, and a vane groove. The fixed body is configured not to rotate together with the rotary shaft and includes a fixed body surface, which faces the rotating body surface in the axial direction. The vane is inserted in the vane groove and configured to rotate together with the rotating body while moving in the axial direction. The compression chamber is defined by the rotating body surface and the fixed body surface and in which suction and compression of fluid is performed when the vane rotates while moving in the axial direction. The vane has a vane end at an end in the axial direction. The vane end contacts the fixed body surface. The vane end is curved to be convex toward the fixed body surface and extends in a direction orthogonal to the axial direction. The fixed body surface includes a fixed body contact surface and two curved surfaces. The fixed body contact surface contacts the rotating body surface. The curved surfaces are respectively provided on opposite sides of the fixed body contact surface in a circumferential direction of the rotary shaft. Each curved surface is curved such that a distance to the rotating body surface increases as a distance to the fixed body contact surface increases. Each curved surface includes a convex surface and a concave surface. The convex surface is continuous with the fixed body contact surface and is curved to be convex toward the rotating body surface. The concave surface is continuous with the convex surface and is curved to be concave with respect to the rotating body surface. The convex surface includes a convex surface inner end and a convex surface outer end at opposite ends in a radial direction of the rotary shaft. A curvature in the axial direction of the convex surface inner end is greater than a curvature in the axial direction of the convex surface outer end. The concave surface includes a concave surface inner end and a concave surface outer end at opposite ends in the radial direction. A curvature in the axial direction of the concave surface inner end is greater than a curvature in the axial direction of the concave surface outer end.

In another general aspect, a compressor is provided that includes a rotary shaft, a rotating body, a fixed body, a vane, and a compression chamber. The rotating body is configured to rotate together with the rotary shaft and includes a rotating body surface, which intersects with an axial direction of the rotary shaft, and a vane groove. The fixed body is configured not to rotate together with the rotary shaft and includes a fixed body surface, which faces the rotating body surface in the axial direction, and a fixed body insertion hole. The vane is inserted in the vane groove and configured to rotate together with the rotating body while moving in the axial direction. The compression chamber is defined by the rotating body surface and the fixed body surface and in which suction and compression of fluid is performed when the vane rotates while moving in the axial direction. The rotating body includes a rotating body tube and a rotating body ring portion. The rotary shaft is inserted in the rotating body tube. The rotating body tube has a tube outer circumferential surface. The rotating body ring portion is provided on the tube outer circumferential surface to protrude outward in a radial direction of the rotary shaft. The rotating body ring portion includes the rotating body surface and the vane groove. The rotating body tube is inserted in the fixed body insertion hole so that the rotating body is supported by the fixed body. A boundary between the tube outer circumferential surface and the rotating body surface is curved. A chamfered portion that avoids interference with the boundary is provided at a corner portion of the fixed body surface and an inner wall surface of the fixed body insertion hole.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram of a compressor according to a first embodiment.

FIG. 2 is an exploded perspective view of the main components of the compressor of FIG. 1.

FIG. 3 is an exploded perspective view of the main components as viewed in the opposite direction from FIG. 2.

FIG. 4 is a cross-sectional view of the main components of the compressor of FIG. 1.

FIG. 5 is a side view of the main components of the compressor of FIG. 1.

FIG. 6 is a cross-sectional view taken along line 6-6 in FIG. 4.

FIG. 7 is a cross-sectional view taken along line 7-7 in FIG. 4.

FIG. 8 is an exploded perspective view of a front cylinder, a front valve, and a front retainer of the compressor of FIG. 1.

FIG. 9 is an enlarged cross-sectional view illustrating the front boundary and its surroundings in the compressor of FIG. 1.

FIG. 10 is an enlarged cross-sectional view illustrating the rear boundary and its surroundings in the compressor of FIG. 1.

FIG. 11 is a cross-sectional view schematically showing the manner in which a vane and curved surfaces contact each other in the compressor of FIG. 1.

FIG. 12 is a graph showing displacement in the axial direction of the fixed body surface in relation to changes in the angle in the compressor of FIG. 1.

FIG. 13 is a cross-sectional view taken at the point of inflection, schematically showing the rotating body, the fixed bodies, and a vane of the compressor of FIG. 1.

FIG. 14 is a schematic diagram illustrating the front contact line in the compressor of FIG. 1 when viewed in the axial direction.

FIG. 15 is a cross-sectional view taken along line 15-15 of FIG. 4.

FIG. 16 is a partially enlarged view of FIG. 15.

FIG. 17 is a developed view schematically showing the rotating body, the fixed bodies, and the vanes in the compressor of FIG. 1.

FIG. 18 is a developed view schematically showing the rotating body, the two fixed bodies, and the vanes at a phase different from that in FIG. 17.

FIG. 19 is a cross-sectional view of a vane outer end face and a vane inner end face according to a second embodiment.

FIG. 20 is a partial cross-sectional view showing a vane outer end face according to a first modification.

FIG. 21 is a partial cross-sectional view showing a vane inner end face according to a second modification.

FIG. 22 is a perspective view showing vanes according to a second modification.

FIG. 23 is an exploded perspective view of the vane of FIG. 22.

FIG. 24 is a cross-sectional view schematically showing the manner in which the vane of FIG. 22 and fixed body surfaces contact each other.

FIG. 25 is a cross-sectional view schematically showing a compressor according to a fourth modification.

Throughout the drawings and the detailed description, the same reference numerals refer to the same elements. The drawings may not be to scale, and the relative size, proportions, and depiction of elements in the drawings may be exaggerated for clarity, illustration, and convenience.

DETAILED DESCRIPTION

This description provides a comprehensive understanding of the methods, apparatuses, and/or systems described. Modifications and equivalents of the methods, apparatuses, and/or systems described are apparent to one of ordinary skill in the art. Sequences of operations are exemplary, and may be changed as apparent to one of ordinary skill in the art, with the exception of operations necessarily occurring in a certain order. Descriptions of functions and constructions that are well known to one of ordinary skill in the art may be omitted.

Exemplary embodiments may have different forms, and are not limited to the examples described. However, the examples described are thorough and complete, and convey the full scope of the disclosure to one of ordinary skill in the art.

First Embodiment

Referring to the drawings, a first embodiment of a compressor will now be described. The compressor of the present embodiment may be used for a vehicle. Specifically, the compressor may be mounted on a vehicle. The compressor may be used for a vehicle air conditioner, and the fluid compressed by the compressor may be a refrigerant containing oil. For convenience of illustration, FIG. 1 shows a rotary shaft 12, a rotating body 60, and two fixed bodies 90 and 110 in side views. In addition, FIGS. 6 and 7 schematically show vanes 131 in cross-sectional views.

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

The housing 11 may be cylindrical as a whole and includes a suction port 11a, through which fluid is drawn from outside, and a discharge port 11b, through which the compressed fluid is discharged. The housing 11 accommodates the rotary shaft 12, the electric motor 13, the inverter 14, the front cylinder 30, the rear plate 40, the rotating body 60, and the two fixed bodies 90 and 110.

The housing 11 includes a front housing member 21, a rear housing member 22, and an inverter cover 25.

The front housing member 21 has a circumferential wall, an end wall located at one end in the axial direction of the circumferential wall, and an open end opening toward the rear housing member 22. The suction port 11a may be provided in the circumferential wall of the front housing member 21 at a position closer to the end wall than to the open end. However, the suction port 11a may be provided at any position.

The cylindrical rear housing member 22 includes a rear housing end wall 23 and a rear housing circumferential wall 24 extending from the rear housing end wall 23 toward the front housing member 21. The front housing member 21 and the rear housing member 22 are combined as one unit with their open ends facing each other. The discharge port 11b is provided in the rear housing circumferential wall 24. However, the discharge port 11b may be provided at any position.

The inverter cover 25 and the rear housing member 22 are located on the opposite sides of the front housing member 21. The inverter cover 25 is butted against and fixed to the end wall of the front housing member 21. The inverter cover 25 accommodates the inverter 14, which actuates the electric motor 13.

As shown in FIG. 1, the front cylinder 30 cooperates with the rear plate 40 and accommodates the two fixed bodies 90 and 110 and the rotating body 60. The front cylinder 30 is cylindrical and smaller in diameter than the circumferential wall 24 of the rear housing member 22. The front cylinder 30 opens toward the rear housing end wall 23.

The front cylinder 30 includes a front cylinder end wall 31 and a front cylinder circumferential wall 32 extending from the front cylinder end wall 31 toward the rear housing end wall 23.

As shown in FIGS. 1 and 2, the front cylinder end wall 31 has steps arranged in the axial direction Z of the rotary shaft 12, and includes a first end wall 31a, which is closer to the center, and a second end wall 31b, which is located on the outer side of the first end wall 31a in the radial direction R of the rotary shaft 12. The second end wall 31b is displaced from the first end wall 31a toward the rear housing end wall 23. The first end wall 31a has a front insertion hole 31c, which receives the rotary shaft 12.

As shown in FIG. 1, the front cylinder circumferential wall 32 is positioned inside the rear housing member 22. The front cylinder circumferential wall 32 has a front cylinder inner circumferential surface 33 and a front cylinder outer circumferential surface 34, which is on the opposite side from the front cylinder inner circumferential surface 33.

The front cylinder inner and outer circumferential surfaces 33 and 34 may be cylindrical surfaces having an axis extending in the axial direction Z of the rotary shaft 12. The front cylinder outer circumferential surface 34 is in contact with the inner circumferential surface of the rear housing circumferential wall 24 in the radial direction R.

The front cylinder outer circumferential surface 34 includes a discharge recess 35 defining a discharge chamber A1. The discharge recess 35 is provided between the two axial ends of the front cylinder outer circumferential surface 34 and is recessed radially inward. The discharge recess 35 and the rear housing circumferential wall 24 define the discharge chamber A1 containing the compressed fluid. The discharge chamber A1 is cylindrical and has an axis extending in the axial direction Z of the rotary shaft 12. The discharge chamber A1 is continuous with the discharge port 11b. The compressed fluid in the discharge chamber A1 is discharged through the discharge port 11b.

The front cylinder 30 has a bulging section 36 projecting outward in the radial direction. The bulging section 36 connects the front cylinder end wall 31 to the front cylinder circumferential wall 32. The bulging section 36 projects radially outward from the front cylinder outer circumferential surface 34. The front housing member 21 and the rear housing member 22 are coupled to each other with the bulging section 36 sandwiched between them. The housing members 21 and 22 limit displacement of the front cylinder 30 in the axial direction Z.

As shown in FIG. 1, the front housing member 21 and the front cylinder end wall 31 define a motor chamber A2 in the housing 11. The motor chamber A2 accommodates the electric motor 13. When the electric power is supplied from the inverter 14, the electric motor 13 rotates the rotary shaft 12 in the direction indicated by arrow M, specifically, in the clockwise direction as viewed in the direction from the electric motor 13 to the two fixed bodies 90 and 110.

Since the suction port 11a is provided in the front housing member 21, which defines the motor chamber A2, the fluid entering through the suction port 11a is drawn into the motor chamber A2 in the housing 11. That is, the motor chamber A2 contains the fluid drawn through the suction port 11a. The motor chamber A2 is a suction chamber into which the fluid is drawn.

In the compressor 10 of this 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 components may be changed, and the inverter 14 may be located radially outward from the electric motor 13, for example.

The rear plate 40 is planar (has the shape of a circular plate in the present embodiment) and accommodated in the rear housing member 22 such that its thickness direction coincides with the axial direction Z. The outer diameter of the rear plate 40 may be the same as the diameter of the front cylinder outer circumferential surface 34 (or the inner circumferential surface of the rear housing circumferential wall 24). The rear plate 40 is fitted into and supported by the rear housing member 22.

The rear plate 40 is separate from the front cylinder end wall 31. The front cylinder 30 and the rear plate 40 are assembled such that the distal end (open end) of the front cylinder circumferential wall 32 is butted against the rear plate 40. The rear plate 40 closes the opening of the front cylinder 30.

Specifically, the rear plate 40 has a plate recess 42 in the position facing the distal end of the front cylinder circumferential wall 32 in the axial direction Z. The plate recess 42 extends over the entire circumference. The front cylinder 30 is coupled to the rear plate 40 with the distal end of the front cylinder circumferential wall 32 fitted into the plate recess 42.

The housing 11 supports the rear plate 40. Specifically, the rear plate 40 is held between the front cylinder 30, which is supported by the housing 11, and the rear housing end wall 23, which is a part of the housing 11. This may be changed as long as the housing 11 supports the rear plate 40.

The rear plate 40 has a first plate surface 43 and a second plate surface 44 extending orthogonal to the axial direction Z. The first plate surface 43 faces away from the rear housing end wall 23. The second plate surface 44 faces the rear housing end wall 23 in the axial direction Z. Since the present embodiment has the plate recess 42, the first plate surface 43 is smaller than the second plate surface 44.

As used herein, the term “face” refers to a state where two members face each other with a gap created between them, and also a state where the two members are in contact with each other. For example, the second plate surface 44 and the rear housing end wall 23 may be spaced apart from each other or in contact with each other. The term “face” also refers to a state where two surfaces face each other with parts of the surfaces are in contact with each other and other parts are spaced apart from each other.

As shown in FIG. 1, the compressor 10 includes shaft bearings 51 and 53, which support the rotary shaft 12 in a rotatable manner.

The front shaft bearing 51 is attached to a boss 52 provided on the end wall of the front housing member 21. The boss 52 is ring-shaped and protrudes from the end wall of the front housing member 21. The front shaft bearing 51 is located radially inward from the boss 52 and supports a front shaft end 12a in a rotatable manner. The front shaft end 12a is one of the two axial shaft ends 12a and 12b of the rotary shaft 12.

The central section of the rear plate 40 has a rear insertion hole 41, which receives the rotary shaft 12. The diameter of the rear insertion hole 41 is greater than or equal to the diameter of the rear shaft end 12b. The rear shaft end 12b is inserted in the rear insertion hole 41.

The inner wall surface defining the rear insertion hole 41 includes a rear shaft bearing 53, which supports the rear shaft end 12b in a rotatable manner. The rear shaft bearing 53 may be a coating bearing formed by a coating layer on the inner wall surface defining the rear insertion hole 41.

The coating layer may be changed and include a thermosetting resin or a lubricant. Further, the rear shaft bearing 53 does not have to be the coating bearing formed by the coating layer, and may be other sliding bearings or rolling bearings. FIG. 1 shows the rear shaft bearing 53 thicker than the actual size.

In the present embodiment, the two shaft bearings 51 and 53 support the shaft ends 12a and 12b in a rotatable manner. The front shaft bearing 51 is attached to the boss 52 of the front housing member 21, and the rear housing member 22 supports the rear plate 40 including the rear shaft bearing 53. As such, the rotary shaft 12 may be considered as being supported by the housing 11 with the shaft bearings 51 and 53 so as to be rotatable relative to the housing 11. In the present embodiment, the rotary shaft 12 is columnar.

As shown in FIG. 1, the rear housing end wall 23 includes a housing recess 54 in the position facing the rotary shaft 12 in the axial direction Z. The housing recess 54 is circular and slightly larger than the rear shaft end 12b, for example. A part of the rear shaft end 12b is located in the housing recess 54.

The compressor 10 includes a ring plate 55 placed in the housing recess 54, and the ring plate 55 limits displacement of the rotary shaft 12 in the axial direction Z. The ring plate 55 may be a flat ring fitted into the housing recess 54. The outer diameter of the ring plate 55 may be equal to the inner diameter of the housing recess 54. The ring plate 55 is arranged between the rear shaft end 12b and the bottom surface of the housing recess 54. The section of the rotary shaft 12 other than the front shaft end 12a is located between the front shaft bearing 51 and the ring plate 55 in the axial direction Z. This limits movement of the rotary shaft 12 in the axial direction Z. However, to accommodate dimensional errors, a small clearance may be provided between the ring plate 55 and the rear shaft end 12b.

As shown in FIG. 1, in the housing 11, the front cylinder 30 and the rear plate 40 define an accommodation chamber A3, which accommodates the rotating body 60 and the two fixed bodies 90 and 110.

The motor chamber A2 and the accommodation chamber A3 are arranged in the axial direction Z in the housing 11. The front cylinder end wall 31 separates the motor chamber A2 from the accommodation chamber A3 so that the fluid in the motor chamber A2 does not flow into the accommodation chamber A3. The front cylinder end wall 31 serves as a partition wall that separates the motor chamber A2 from the accommodation chamber A3 and limits migration of the fluid from the motor chamber A2 to the accommodation chamber A3. The rotary shaft 12, which extends through the front cylinder end wall 31 serving as the partition wall, is located in both of the motor chamber A2 and the accommodation chamber A3. The rear plate 40 serves as a defining portion used to define the accommodation chamber A3.

Referring to FIGS. 2 to 5, the details of the rotating body 60 will now be described. For the convenience of illustration, FIG. 5 shows the rotating body 60 in a different rotational position, that is, at a different phase, from that in FIG. 4.

As the rotary shaft 12 rotates, the rotating body 60 rotates in a rotation direction M. The rotational axis of the rotating body 60 placed in the housing 11 coincides with the center axis of the rotary shaft 12. That is, the rotating body 60 is coaxial with the rotary shaft 12. Accordingly, the compressor 10 performs concentric motion instead of eccentric motion.

The rotating body 60 includes a rotating body tube 61, which receives the rotary shaft 12, and a rotating body ring 70, which extends radially outward from the rotating body tube 61.

The rotating body tube 61 is coupled to the rotary shaft 12 so as to rotate together with the rotary shaft 12. Rotation of the rotary shaft 12 thus rotates the rotating body 60. The rotating body tube 61 may be coupled to the rotary shaft 12 in any manner. For example, the rotating body tube 61 may be fixed to the rotary shaft 12 by press-fitting, or a fixing pin may extend through the rotary shaft 12 and the rotating body tube 61 to fix the rotating body tube 61 to the rotary shaft 12. The rotating body tube 61 may be coupled to the rotary shaft 12 by a coupling member, such as a key. Further, the rotating body tube 61 may be connected to the rotary shaft 12 by the engagement between a recess provided in one of them and a projection provided in the other.

The rotating body tube 61 is a cylindrical member having an axis extending in the axial direction Z, for example. The rotating body tube 61 may have an inner diameter that is greater than or equal to the diameter of the rotary shaft 12. The inner circumferential surface of the rotating body tube 61 faces the outer circumferential surface of the rotary shaft 12 in the radial direction R.

The rotating body tube 61 has a tube outer circumferential surface 62 having an axis extending in the axial direction Z. The tube outer circumferential surface 62 curves to be convex radially outward and is a tubular surface in this embodiment.

As shown in FIGS. 2 to 4, the rotating body ring 70 may be located at an arbitrary position (in the central section in the present embodiment) between opposite rotating body ends 61a and 61b, which the ends in the axial direction Z of the rotating body tube 61.

The rotating body ring 70 is an annular plate having a plate thickness in the axial direction Z. The rotating body ring 70 includes two axial end faces, a front rotating body surface 71 and a rear rotating body surface 72. These rotating body surfaces 71 and 72 are ring-shaped. The two rotating body surfaces 71 and 72 intersect with the axial direction Z. In the present embodiment, the rotating body surfaces 71 and 72 are flat surfaces extending orthogonal to the axial direction Z. Thus, the inner and outer edges of the rotating body surfaces 71 and 72 extend linearly as viewed in the radial direction R, and the entire circumference of each edge is located in the same position in the axial direction Z.

The rotating body ring 70 has a ring outer circumferential surface 73, which intersects with the radial direction R. The ring outer circumferential surface 73 faces the front cylinder inner circumferential surface 33 in the radial direction R. The ring outer circumferential surface 73 and the front cylinder inner circumferential surface 33 may be in contact with each other, or may be spaced apart from each other by a small gap.

As shown in FIG. 4, the compressor 10 includes thrust bearings 81 and 82, which support the rotating body 60 in the axial direction Z. The thrust bearings 81 and 82 are located on the opposite axial ends of the rotating body tube 61 and sandwich the rotating body tube 61 in the axial direction Z.

Specifically, the front thrust bearing 81 is located in a space created by the steps in the front cylinder end wall 31. The front thrust bearing 81, which is supported by the front cylinder end wall 31, supports the rotating body tube 61 (specifically, the front rotating body end 61a) in the axial direction Z.

The rear thrust bearing 82 is located in a thrust accommodation recess 83 provided in the rear plate 40. The thrust accommodation recess 83 is provided in a section of the inner wall surface defining the rear insertion hole 41 that is adjacent to the first plate surface 43. The rear thrust bearing 82, which is supported by the rear plate 40, supports the rotating body tube 61 (specifically, the rear rotating body end 61b) in the axial direction Z.

The two thrust bearings 81 and 82 are shaped as circular plates and receive the rotary shaft 12. In the present embodiment, the inner circumference surfaces of the thrust bearings 81 and 82 are in contact with the outer circumference surface of the rotary shaft 12. The thrust bearings 81 and 82 are in contact with the rotary shaft 12 in the radial direction R and thus support the rotary shaft 12. However, the thrust bearings 81 and 82 may be spaced apart from the rotary shaft 12 in the radial direction R.

The fixed bodies 90 and 110 are arranged on the opposite sides of the rotating body ring 70 in the axial direction. That is, the fixed bodies 90 and 110 are spaced apart from each other in the axial direction Z with the rotating body ring 70 located between them. In other words, the rotating body ring 70 is positioned between the two fixed bodies 90 and 110.

The fixed bodies 90 and 110 are fixed to the front cylinder 30 (i.e., the housing 11) so as not to rotate together with the rotary shaft 12. For example, the fixed bodies 90 and 110 are fastened to the front cylinder circumferential wall 32 using fasteners (not shown) extending through the front cylinder circumferential wall 32. The fixed bodies 90 and 110 are thus fixed to the front cylinder 30.

However, the two fixed bodies 90 and 110 may be fixed to the front cylinder 30 by any method, such as press-fitting and mating. One or more fastening sections may be provided to fasten the front fixed body 90 to the front cylinder end wall 31, and one or more fastening sections may be provided to fasten the rear fixed body 110 to the rear plate 40.

The structure of the two fixed bodies 90 and 110 will now be described in detail. In this embodiment, the fixed bodies 90 and 110 have the same shape.

As shown in FIGS. 1 to 4, the front fixed body 90 is located close to the front cylinder end wall 31, in other words, close to the motor chamber A2. The front fixed body 90 is ring-shaped (annular in this embodiment) and has a front fixed body insertion hole 91, which receives the rotary shaft 12. In the present embodiment, the front fixed body insertion hole 91 is a through hole extending through the front fixed body 90 in the axial direction Z. The front fixed body 90 is located in the front cylinder 30 with the rotary shaft 12 inserted in the front fixed body insertion hole 91.

The front fixed body 90 has a front fixed body outer circumferential surface 92 facing the front cylinder inner circumferential surface 33 in the radial direction R. In the present embodiment, the front fixed body outer circumferential surface 92 is in contact with the front cylinder inner circumferential surface 33. However, the present disclosure is not limited to this, and the front cylinder inner circumferential surface 33 may be spaced apart from the front fixed body outer circumferential surface 92.

The front fixed body 90 includes a front back surface 93 facing the front cylinder end wall 31 in the axial direction Z. The front back surface 93 and the inner bottom surface 31d of the front cylinder end wall 31 may be spaced apart from each other or in contact with each other.

As shown in FIGS. 1 to 4, in the same manner as the front fixed body 90, the rear fixed body 110 is located close to the rear plate 40 serving as the defining portion, in other words, located far from the motor chamber A2, is ring-shaped (annular in this embodiment) and has a rear fixed body insertion hole 111, which receives the rotary shaft 12. In the present embodiment, the rear fixed body insertion hole 111 is a through hole extending through the rear fixed body 110 in the axial direction Z. The rear fixed body 110 is located in the front cylinder 30 with the rotary shaft 12 inserted in the rear fixed body insertion hole 111. That is, in this embodiment, the rotary shaft 12 extends through the two fixed bodies 90 and 110 in the axial direction Z.

The rear fixed body 110 has a rear fixed body outer circumferential surface 112 facing the front cylinder inner circumferential surface 33 in the radial direction R. In the present embodiment, the rear fixed body outer circumferential surface 112 is in contact with the front cylinder inner circumferential surface 33. However, the present disclosure is not limited to this, and the rear fixed body outer circumferential surface 112 may be spaced apart from the front cylinder inner circumferential surface 33.

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

As shown in FIG. 4, the rotating body tube 61 is inserted in the fixed body insertion holes 91 and 111 so that the fixed bodies 90 and 110 support the rotating body 60.

Specifically, the front rotating body end 61a of the rotating body tube 61 is inserted in the front fixed body insertion hole 91 and extends through the front fixed body 90.

The front fixed body insertion hole 91 is shaped and sized corresponding to the rotating body tube 61 (specifically, the tube outer circumferential surface 62). In the present embodiment, the front fixed body insertion hole 91 is circular as viewed in the axial direction Z corresponding to the circular rotating body tube 61. The front fixed body insertion hole 91 is equal to or slightly larger than the tube outer circumferential surface 62 in diameter. The front rotating body end 61a is supported by a front rotating body bearing 94, which is provided in the inner wall surface defining the front fixed body insertion hole 91, so as to be rotatable relative to the front fixed body 90.

Likewise, the rear rotating body end 61b is inserted in the rear fixed body insertion hole 111 and extends through the rear fixed body 110.

The rear fixed body insertion hole 111 is shaped and sized corresponding to the rotating body tube 61 (specifically, the tube outer circumferential surface 62). In the present embodiment, the rear fixed body insertion hole 111 is circular as viewed in the axial direction Z corresponding to the circular rotating body tube 61. The rear fixed body insertion hole 111 is equal to or slightly larger than the tube outer circumferential surface 62 in diameter. The rear rotating body end 61b is supported by a rear rotating body bearing 114, which is provided in the inner wall surface defining the rear fixed body insertion hole 111, so as to be rotatable relative to the rear fixed body 110.

The two fixed bodies 90 and 110 support the rotating body ends 61a and 61b through the two rotating body bearings 94 and 114. The fixed bodies 90 and 110 thus support the rotating body 60 and limit displacement of the rotating body 60 relative to the two fixed bodies 90 and 110.

Further, the two rotating body ends 61a and 61b are the axial ends of the rotating body 60, so that the rotating body bearings 94 and 114 support the axial ends of the rotating body 60. The rotating body 60 is thus supported in a stable manner.

Further, the fixed body insertion holes 91 and 111 provided corresponding to the rotating body tube 61 reduce or eliminate a gap provided between the tube outer circumferential surface 62 and the inner wall surfaces defining the fixed body insertion holes 91 and 111.

Each rotating body bearing 94, 114 may be a coating bearing formed by a coating layer on the inner wall surface defining the fixed body insertion hole 91, 111. FIG. 4 shows the rotating body bearing 94, 114 thicker than the actual size. The rotating body bearing 94, 114 does not have to be a coating bearing, and may be other sliding bearings or rolling bearings.

The front fixed body 90 has a front fixed body surface 100, which is 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 opposite to the front back surface 93. The front fixed body surface 100 is ring-shaped, and annular as viewed in the axial direction Z in the present embodiment.

As shown in FIG. 3, the front fixed body surface 100 includes a first front flat surface 101, a second front flat surface 102, and two front curved surfaces 103. The first and second front flat surfaces 101 and 102 intersect with the axial direction Z (at right angles in the present embodiment). The front curved surfaces 103 connect the two front flat surfaces 101 and 102. The first front flat surface 101 and the second front flat surface 102 each have the shape of a sector in the present embodiment.

As shown in FIG. 4, the two front flat surfaces 101 and 102 are displaced from each other in the axial direction Z. Specifically, the second front flat surface 102, which serves as a fixed body contact surface, is 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 section of the front fixed body surface 100 other than the second front flat surface 102 is spaced apart from the front rotating body surface 71.

The two front flat surfaces 101 and 102 are spaced apart in the circumferential direction of the front fixed body 90, and are displaced from each other by 180°, for example. In the present embodiment, each front flat surface 101, 102 has the shape of a sector. In the following descriptions, the circumferential positions in the fixed bodies 90 and 110 are also referred to as angular positions.

Each of the two front curved surfaces 103 has the shape of a sector. As shown in FIG. 3, the two front curved surfaces 103 are aligned in the radial direction as viewed in the axial direction Z. The two front curved surfaces 103 have the same shape.

Each front curved surface 103 connects the two front flat surfaces 101 and 102. Specifically, one of the front curved surfaces 103 connects the first ends in the circumferential direction of the front flat surfaces 101 and 102, and the other front curved surface 103 connects the second ends in the circumferential direction of the front flat surfaces 101 and 102.

The angular positions of the borders between the first front flat surface 101 and the front curved surfaces 103 are defined as first angular positions θ1, and the angular positions of the borders between the second front flat surface 102 and the front curved surfaces 103 are defined as second angular positions θ2. Although the angular positions θ1 and θ2 are indicated by broken lines in FIG. 3, the front curved surfaces 103 and the front flat surfaces 101 and 102 are actually connected smoothly at the borders.

The position in the axial direction Z of each front curved surface 103 varies with circumferential position, in other words, the angular position in the front fixed body 90. Specifically, each front curved surface 103 is curved in the axial direction Z such that the distance to the front rotating body surface 71 gradually decreases from the first angular position θ1 to the second angular position θ2. In other words, the two front curved surfaces 103 are located on the opposite sides of the second front flat surface 102 in the circumferential direction and curved in the axial direction Z such that the distance to the front rotating body surface 71 gradually increases as the front curved surfaces 103 extend away from the second front flat surface 102 in the circumferential direction.

The rear fixed body 110 has a rear fixed body surface 120, which is 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 opposite to the rear back surface 113. The rear fixed body surface 120 is ring-shaped, and annular as viewed in the axial direction Z 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 includes a first rear flat surface 121, a second rear flat surface 122, and two rear curved surfaces 123. The first and second rear flat surfaces 121 and 122 intersect with the axial direction Z (at right angles in the present embodiment). The rear curved surfaces 123 connect the two rear flat surfaces 121 and 122.

As shown in FIG. 4, the two rear flat surfaces 121 and 122 are displaced from each other in the axial direction Z. Specifically, the second rear flat surface 122, which serves as a fixed body contact surface, is 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 section of the rear fixed body surface 120 other than the second rear flat surface 122 is spaced apart from the rear rotating body surface 72.

The two rear flat surfaces 121 and 122 are spaced apart from each other in the circumferential direction of the rear fixed body 110, and are displaced from each other by 180°, for example. In the present embodiment, each rear flat surface 121, 122 has the shape of a sector.

Each of the two rear curved surfaces 123 has the shape of a sector. The two rear curved surfaces 123 face each other in the radial direction as viewed in the axial direction Z. One of the rear curved surfaces 123 connects the first ends in the circumferential direction of the rear flat surfaces 121 and 122, and the other rear curved surface 123 connects the second ends in the circumferential direction of the rear flat surfaces 121 and 122.

The two rear curved surfaces 123 are arranged on the opposite sides of the second rear flat surface 122 in the circumferential direction and curved in the axial direction Z such that the distance to the rear rotating body surface 72 gradually increases as the curved surfaces 123 extend away from the second rear flat surface 122 in the circumferential direction.

The two fixed body surfaces 100 and 120 face toward each other in the axial direction Z with the rotating body ring 70 placed between them. In addition, the two fixed body surfaces 100 and 120 are arranged in angular positions that are different from each other by 180°.

The distance between the two fixed body surfaces 100 and 120 in the axial direction Z is uniform at any angular positions (i.e., the circumferential positions). 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 face each other in the axial direction Z. The displacement in the axial direction Z between the two front flat surfaces 101 and 102 is equal to the displacement between the two rear flat surfaces 121 and 122. Hereinafter, the displacement in the axial direction Z between the two front flat surfaces 101 and 102 and the displacement between the two rear flat surfaces 121 and 122 are simply referred to as displacement Z1.

Further, the front curved surfaces 103 and the rear curved surfaces 123 have the same curvatures. That is, the front curved surfaces 103 and the rear curved surfaces 123 are curved in the same manner so that the distance in the axial direction Z does not vary with the angular position. The distance between the two fixed body surfaces 100 and 120 in the axial direction Z is therefore uniform at any angular positions.

The shapes of the first rear flat surface 121, the second rear flat surface 122, and the two rear curved surfaces 123 are the same as those of the first front flat surface 101, the second front flat surface 102, and the two front curved surfaces 103 and thus not described in detail. As with the front curved surface 103, since the rear curved surface 123 is curved in a wave shape, the rear fixed body surface 120 may be considered as a rear wavy surface including sections that are curved in a wave shape.

The circumferential direction of the two fixed bodies 90 and 110 and the rotating body 60 is the same as the circumferential direction of the rotary shaft 12. The radial direction of the two fixed bodies 90 and 110 and the rotating body 60 is the same as the radial direction R of the rotary shaft 12. The axial direction of the fixed bodies 90 and 110 and the rotating body 60 is the same as the axial direction Z of the rotary shaft 12. As such, the circumferential direction, the radial direction R, and the axial direction Z of the rotary shaft 12 are interchangeable with those of the rotating body 60 and the fixed bodies 90 and 110.

As shown in FIG. 4, the compressor 10 includes compression chambers A4 and A5, in which suction and compression of the fluid are performed. The compression chambers A4 and A5 are provided in the accommodation chamber A3, specifically, on the opposite sides of the rotating body ring 70 in the axial direction Z.

The front compression chamber A4 is defined by the front rotating body surface 71 and the front fixed body surface 100, more specifically, by the front rotating body surface 71, the front fixed body surface 100, the tube outer circumferential surface 62, and the front cylinder inner circumferential surface 33.

The rear compression chamber A5 is defined by the rear rotating body surface 72 and the rear fixed body surface 120, more specifically, by the rear rotating body surface 72, the rear fixed body surface 120, the tube outer circumferential surface 62, and the front cylinder inner circumferential surface 33. In the present embodiment, the front compression chamber A4 and the rear compression chamber A5 are equal in size.

The front cylinder inner circumferential surface 33 can be regarded as cooperating with the rotating body surfaces 71 and 72 and the fixed body surfaces 100 and 120 to define the compression chambers A4 and A5.

The compression chambers A4 and A5 face the discharge chamber Al in the radial direction R with the front cylinder circumferential wall 32 located between them. That is, the discharge chamber A1 is located on the outer side of the compression chambers A4 and A5 in the radial direction R.

In the present embodiment, the discharge chamber A1 faces a part of the front compression chamber A4 in the radial direction R, and faces the entire rear compression chamber A5 in the radial direction R. However, the present disclosure is not limited to this configuration. Any configuration may be used as long as the discharge chamber A1 extends in the axial direction Z so as to face at least a part of the front compression chamber A4 and 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 multiple (three) vane grooves 130 provided in the rotating body 60 and multiple (three) vanes 131 inserted in the respective vane grooves 130.

The vane grooves 130 are provided in the rotating body ring 70. The vane grooves 130 extend through the rotating body ring 70 in the axial direction Z and open at the two rotating body surfaces 71 and 72. Each vane groove 130 extends in the radial direction R, has a width in a direction orthogonal to both of the axial direction Z and the radial direction R, and opens radially outward. The rotating body tube 61 does not have a vane groove 130. Each vane groove 130 has two side surfaces that face each other and are spaced apart from each other in the circumferential direction.

The rotating body ring 70 is a section positioned radially outward from the rotating body tube 61. As such, the rotating body tube 61 is located radially inward from the rotating body ring 70. That is, the rotating body ring 70 is a section that is positioned on the tube outer circumferential surface 62 and protrudes radially outward from the tube outer circumferential surface 62.

Each vane 131 is generally a rectangular plate having plate surfaces that intersect with (extend orthogonal to) the circumferential direction of the rotary shaft 12. The vane 131 is located between the two fixed bodies 90 and 110 (i.e., the two fixed body surfaces 100 and 120). The vane 131 is a plate having a thickness in the width direction of the vane groove 130, in other words, in a direction orthogonal to both of the axial direction Z and the radial direction R.

The vane 131 is inserted in the vane groove 130 and has a thickness in the width direction of the vane groove 130, in other words, in a direction orthogonal to both of the axial direction Z and the radial direction R. The plate surfaces of the vane 131 and the side surfaces of the vane groove 130 face each other. The width of the vane groove 130 (in other words, the distance between the side surfaces of the vane groove 130) is equal to or slightly greater than the thickness of the vane 131 (hereinafter, referred to as the vane thickness D). The vane 131 is held between the side surfaces of the vane groove 130. The vane 131 is allowed to move in the axial direction Z along the vane groove 130.

The vane 131 has opposite ends in the axial direction, which are a front vane end 132 and a rear vane end 133. The vane ends 132 and 133 extend in a direction orthogonal to the axial direction Z, for example, in the radial direction R. The vane ends 132 and 133 are respectively in contact with the fixed body surfaces 100 and 120.

The vane 131 is a plate-shaped body that has a thickness in a direction that is orthogonal to both of the axial direction Z and the extending direction of the vane ends 132 and 133.

The vane grooves 130 are arranged at regular intervals in the circumferential direction, specifically, at intervals of 120°. The vanes 131 are arranged accordingly at regular intervals in the circumferential direction.

Rotation of the rotating body 60 rotates the vanes 131 in the rotation direction M. At the same time, the vanes 131, which are in contact with the fixed body surfaces 100 and 120, move (swing) in the axial direction Z along the curved fixed body surfaces 100 and 120. That is, the vanes 131 rotate while moving in the axial direction Z. As a result, the vanes 131 move into the front compression chamber A4 and the rear compression chamber A5. That is, the vane grooves 130 rotate and place the vanes 131 in the compression chambers A4 and A5 as the rotating body 60 rotates.

The moving distance (in other words, the swinging distance) of the vanes 131 in the axial direction Z is the difference between the positions of the front flat surfaces 101 and 102 (or between the rear flat surfaces 121 and 122) in the axial direction Z, that is, the displacement Z1. The vanes 131 are continuously in contact with the two fixed body surfaces 100 and 120 while the rotating body 60 rotates. The vanes 131 are thus unlikely to intermittently come into contact, or more specifically, come into and out of contact repeatedly, with the fixed body surfaces 100 and 120.

As shown in FIG. 6, the three vanes 131 partition the front compression chamber A4 into three part chambers, a first front compression chamber A4a, a second front compression chamber A4b, and a third front compression chamber A4c.

For convenience of description, of the three part chambers, the part chamber located on the leading side of the second front flat surface 102 in the rotation direction M is referred to as the first front compression chamber A4a.

Of the three part chambers, the part chamber located on the trailing side of the first front compression chamber A4a in the rotation direction M is referred to as the second front compression chamber A4b. At least a part of the second front compression chamber A4b is located on the trailing side of the second front flat surface 102 in the rotation direction M.

Of the three part chambers, the part chamber located 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. In the rotation direction M, the third front compression chamber A4c is located on the leading side of the first front compression chamber A4a and located on the trailing side of the second front compression chamber A4b.

In the following description, the leading side in the rotation direction M and the trailing side in the rotation direction M may simply be referred to as the leading side and the trailing side, respectively.

Each of the front compression chambers A4a to A4c spans over an angular range of 120°. That is, each of the front compression chambers A4a to A4c extends in the circumferential direction, and the length of each chamber in the circumferential direction corresponds to an angular range of 120°.

Specifically, when one of the vanes 131 is in contact with the second front flat surface 102, this vane 131 is not positioned within the front compression chamber A4. At this time, the spaces at opposite sides in the circumferential direction of the vane 131 that is in contact with the second front flat surface 102 are separated from each other by the section where the front rotating body surface 71 is in contact with the second front flat surface 102. The spaces are not continuous with each other. Thus, even when one of the vanes 131 is in contact with the second front flat surface 102, the front compression chamber A4 is partitioned into three part chambers. In the present embodiment, for convenience of description, even when one of the vanes 131 is in contact with the second front flat surface 102, the front compression chamber A4 is considered to be partitioned by the three vanes 131 into the front compression chambers A4a to A4c.

As shown in FIG. 7, in the same manner as the front compression chamber A4, the three vanes 131 partition the rear compression chamber A5 into a first rear compression chamber A5a, a second rear compression chamber A5b, which is on the trailing side of the first rear compression chamber A5a, and a third rear compression chamber A5c located on the leading side of the first rear compression chamber A5a. The first to third rear compression chambers A5a, A5b and A5c are the same as the first to third front compression chambers A4a, A4b and A4c and thus not described in detail.

The configuration relating to the suction of fluid into the compression chambers A4 and A5 and the discharging of compressed fluid will now be described. FIG. 4 schematically shows a front suction port 141 and a rear suction port 142.

As shown in FIGS. 2 to 4 and 6, the compressor 10 includes a front suction port 141 through which fluid is drawn into the front compression chamber A4. The front suction port 141 may be provided in the front cylinder 30. Specifically, the front suction port 141 extends in the front cylinder end wall 31 and the front cylinder circumferential wall 32 in the axial direction Z.

In addition, the front suction port 141 extends in the circumferential direction along the front cylinder circumferential wall 32 and is formed in an arc shape as viewed in the axial direction Z. At least a part of the front suction port 141 is located radially outward from the first front compression chamber A4a. In other words, the first front compression chamber A4a includes a part of or the entire cavity located radially inward from the front suction port 141.

The front suction port 141 opens to the motor chamber A2 and also to the front compression chamber A4. The front suction port 141 thus connects the motor chamber A2 and the front compression chamber A4 to each other.

Specifically, as shown in FIG. 6, the front suction port 141 has a front suction opening 141a, which is positioned to be continuous with the first front compression chamber A4a. The front suction opening 141a extends in the front cylinder inner circumferential surface 33 in the rotation direction M from a position corresponding to the circumferential center of the second front flat surface 102. The extending length of the front suction opening 141a may be substantially the same as the circumferential length of each of the front compression chambers A4a to A4c, for example. That is, the front suction opening 141a may extend in the front cylinder inner circumferential surface 33 in the circumferential direction from a position corresponding to the circumferential center of the second front flat surface 102 by substantially the same length as the circumferential interval between the vanes 131.

When the angular position of the circumferential center of the second front flat surface 102 is defined as 0° and the angle increases from this 0° angular position in the rotation direction M, the front suction opening 141a preferably extends at least from the leading edge in the rotation direction M of the second front flat surface 102 to the 120° angular position.

As shown in FIGS. 6 and 8, the compressor 10 includes front discharge ports 151, which discharge the fluid compressed in the front compression chamber A4, a front valve 152, which opens and closes the front discharge ports 151, and a front retainer 153, which adjusts the opening degree of the front valve 152.

As shown in FIG. 6, the front discharge ports 151 may be placed in a position of the front cylinder circumferential wall 32 that is radially outward from the front compression chamber A4 and on the trailing side of the second front flat surface 102.

Specifically, the curved front cylinder outer circumferential surface 34 has a front seat surface 154, which is a recessed surface in the front cylinder outer circumferential surface 34. The front seat surface 154 is provided in a section of the front cylinder outer circumferential surface 34 that is located between the front compression chamber A4 and the discharge chamber A1 and on the trailing side of the second front flat surface 102. The front seat surface 154 is a flat surface extending orthogonal to the radial direction R.

As shown in FIG. 6, the front discharge ports 151 are provided in the front seat surface 154. The front discharge ports 151 extend through the front cylinder circumferential wall 32 in the radial direction R, thereby connecting the second front compression chamber A4b and the discharge chamber A1 to each other.

The front discharge ports 151 are arranged in the circumferential direction. Each front discharge port 151 is circular. However, the number and shape of the front discharge ports 151 may be changed. For example, the front seat surface 154 may include only one front discharge port 151. The front discharge port 151 may be oval. When front discharge ports 151 are provided, the sizes of the front discharge ports 151 may be the same or different from one another.

At least a part of each front discharge port 151 is located radially outward from the second front compression chamber A4b. In other words, the second front compression chamber A4b includes a part of or the entire cavity located radially inward from the front discharge ports 151.

The front suction port 141 and the front discharge ports 151 are spaced apart from each other in the circumferential direction. A section of the front cylinder circumferential wall 32 that is located radially outward from the second front flat surface 102 is present between these ports 141 and 151.

The second front compression chamber A4b is continuous with the front discharge ports 151. However, since the second front compression chamber A4b has a longer circumferential length than the second front flat surface 102, depending on the angular position of the vanes 131, the second front compression chamber A4b may be located radially inward from the front suction port 141 and radially inward from the front discharge ports 151 simultaneously. Nevertheless, in the present embodiment, the area of contact between the front rotating body surface 71 and the second front flat surface 102 is present between the space radially inward from the front suction port 141 and the space radially inward from the front discharge ports 151. As such, regardless of the angular position of the vanes 131, this contact area disconnects these two spaces from each other. Thus, the front suction port 141 is not continuous with the front discharge ports 151. That is, the contact area partitions the second front compression chamber A4b further into a space for suction and a space for compression.

As the rotating body 60 rotates, the third front compression chamber A4c moves from a position where the chamber A4c is not continuous with the front discharge ports 151 to a position where it is continuous with the front discharge ports

As shown in FIG. 8, the front valve 152 and the front retainer 153 are provided on the front seat surface 154. The front seat surface 154 has screw holes 154a. The front valve 152 and the front retainer 153 are fixed to the front seat surface 154 by bolts B, which extend through the front retainer 153 and the front valve 152 and engage the screw holes 154a.

The front valve 152 normally closes the front discharge ports 151. When the pressure in the front compression chamber A4 (specifically, the second front compression chamber A4b) exceeds the threshold, the front valve 152 moves from a position that closes the front discharge ports 151 to a position that opens the front discharge ports 151. The fluid compressed in the front compression chamber A4 is thus discharged into the discharge chamber A1. The front retainer 153 limits the opening angle of the front valve 152.

As shown in FIGS. 2 to 4 and 7, the compressor 10 includes a rear suction port 142 through which the fluid is drawn into the rear compression chamber A5. The rear suction port 142 may be formed in the front cylinder 30. Specifically, the rear suction port 142 extends in the front cylinder end wall 31 and the front cylinder circumferential wall 32 in the axial direction Z.

In addition, the rear suction port 142 extends in the circumferential direction along the front cylinder circumferential wall 32 and is formed in an arc shape as viewed in the axial direction Z. At least a part of the rear suction port 142 is located radially outward from the first rear compression chamber A5a. In other words, the first rear compression chamber A5a includes a part of or the entire cavity located radially inward from the rear suction port 142.

The rear suction port 142 opens to the motor chamber A2 and also to the rear compression chamber A5. The rear suction port 142 thus connects the motor chamber A2 and the rear compression chamber A5 to each other.

Specifically, as shown in FIG. 7, the rear suction port 142 has a rear suction opening 142a, which is positioned to be continuous with the first rear compression chamber A5a. The rear suction opening 142a extends in the front cylinder inner circumferential surface 33 in the rotation direction M from a position corresponding to the circumferential center of the second rear flat surface 122.

The rear suction port 142 and the rear suction opening 142a extend in the rotation direction M from the position corresponding to the circumferential center of the second rear flat surface 122 to an extent that does not interferes with the front discharge ports 151, the front valve 152, or the front retainer 153.

However, the present disclosure is not limited to this, and the rear suction port 142 and the rear suction opening 142a may have the same circumferential length as the front suction port 141 and the front suction opening 141a. In this case, to prevent the rear suction port 142 and the rear suction opening 142a from interfering with the front discharge ports 151 or other parts, the axial length of the front valve 152 may be shortened, the front discharge ports 151 may be displaced, or the angular range of the second front flat surface 102 may be reduced.

The present embodiment has two suction ports 141 and 142 corresponding to the two compression chambers A4 and A5. The front suction port 141 and the rear suction port 142 are displaced from each other in the circumferential direction so as not to be continuous with each other. Specifically, these ports 141 and 142 are displaced from each other by 180°. As a result, the suction of fluid into one of the compression chambers A4 and A5 is less likely to reduce the amount of the fluid drawn into the other compression chamber, which would otherwise occur if the two suction ports 141 and 142 are continuous with each other.

As shown in FIG. 7, the compressor 10 includes rear discharge ports 161, which discharge the fluid compressed in the rear compression chamber A5, a rear valve 162, which opens and closes the rear discharge ports 161, and a rear retainer 163, which adjusts the opening degree of the rear valve 162.

The rear discharge ports 161 may be placed in a position of the front cylinder circumferential wall 32 that is radially outward from the rear compression chamber A5 and on the trailing side of the second rear flat surface 122.

In accordance with the second front flat surface 102 and the second rear flat surface 122, which are displaced from each other by 180°, the rear discharge ports 161 are displaced from the front discharge ports 151 by 180° in the circumferential direction. Further, in accordance with the front compression chamber A4 and the rear compression chamber A5, which are displaced from each other in the axial direction Z, the rear discharge ports 161 are displaced from the front discharge ports 151 in the axial direction Z.

The specific configurations of the rear discharge ports 161, the rear valve 162, and the rear retainer 163 are substantially the same as those of the front discharge ports 151, the front valve 152, and the front retainer 153 except for their positions, and thus not described in detail. The term “front” in the description of the front discharge ports 151, the front valve 152, and the front retainer 153 may be replaced with “rear.” The discharge ports 151 and 161 may be considered as discharge passages.

As shown in FIGS. 9 and 10, the shape of the boundary portion between the rotating body tube 61 and the rotating body ring portion 70 is not a right angle but is curved, for example. Specifically, a front boundary 171, which is the boundary portion between the tube outer circumferential surface 62 and the front rotating body surface 71, is not a right angle but is curved, for example, curved as shown in FIG. 9. In the present embodiment, the front boundary 171 is curved to have an arcuate cross section. The front boundary 171 extends over the entire circumference.

In correspondence with the shape of the front boundary 171, the corner portion of the front fixed body surface 100 and the inner wall surface of the front fixed body insertion hole 91 is chamfered. Specifically, a front chamfered portion 172 is provided at the corner portion of the front fixed body surface 100 and the inner wall surface of the front fixed body insertion hole 91. The front chamfered portion 172 faces the front boundary 171. As shown in FIG. 6, the front chamfered portion 172 extends over the entire circumference and has an annular shape when viewed in the axial direction Z. The front chamfered portion 172 prevents the front boundary 171 and the front fixed body 90 from interfering with each other. That is, the front chamfered portion 172 serves as an escape portion that prevents interference with the front boundary 171.

Likewise, a rear boundary 173, which is the boundary portion between the tube outer circumferential surface 62 and the rear rotating body surface 72, is curved to have an arcuate shape. The rear fixed body 110 has a rear chamfered portion 174 at the position that faces the rear boundary 173. The rear chamfered portion 174 prevents the rear boundary 173 and the rear fixed body 110 from interfering with each other.

The relationship between the fixed body surfaces 100 and 120 and the vane ends 132 and 133 will now be described. The specific structure of the front vane end 132 and the front fixed body surface 100 and the manner in which these contact each other are the same as those of the rear vane end 133 and the rear fixed body surface 120. Accordingly, for convenience of description, only the front vane end 132 and the front fixed body surface 100 will be described below, and the rear vane end 133 and the rear fixed body surface 120 are not described in detail. FIGS. 11 to 14 schematically show changes in curvature and the curved degree of a contact line.

FIG. 12 is a graph showing the displacement in the axial direction Z of the front fixed body surface 100 in relation to changes in the angle. The solid line in FIG. 12 represents the displacement in the axial direction Z of the inner end of the front fixed body surface 100. The long dashed short dashed line in FIG. 12 represents the displacement in the axial direction Z of the outer end of the front fixed body surface 100. The vertical axis of the graph of FIG. 12 represents the amount of displacement in the axial direction Z with reference to the first front flat surface 101. FIG. 12 indicates that the farther from zero the displacement in the axial direction Z, the closer to the front rotating body surface 71 the front fixed body surface 100 becomes. Also, for the illustrative purposes, the central angular position on the second front flat surface 102 is defined as 0° in FIG. 12 and the following description. The angular position can be referred to as the phase, and changes in the angle may be considered as changes in the phase.

As shown in FIG. 11, the front vane end 132 is curved to have a convex shape toward the front fixed body surface 100. The front vane end 132 extends in a direction orthogonal to the axial direction Z (in the radial direction R in the present embodiment). The position in the axial direction Z of the front vane end 132 is not displaced regardless of the position in the radial direction R.

The front flat surfaces 101 and 102 are orthogonal to the axial direction Z. Thus, the inner ends and the outer ends of the front flat surfaces 101 and 102 are not displaced regardless of the phase. In FIG. 12, the region including 0° corresponds to the second front flat surface 102, and the region including 180° corresponds to the first front flat surface 101.

As shown in FIGS. 6 and 12, the front curved surface 103 includes front concave surfaces 181 and front convex surfaces 182. The front concave surfaces 181 are curved in the axial direction Z to be concave with respect to the front rotating body surface 71. The front convex surfaces 182 are curved in the axial direction Z to be convex toward the front rotating body surface 71.

The front concave surfaces 181 are located closer to the first front flat surface 101 than to the second front flat surface 102 and are continuous with the first front flat surface 101. The front convex surface 182 are located closer to the second front flat surface 102 than to the first front flat surface 101 and are continuous with both of the front concave surfaces 181 and the second front flat surface 102. That is, the front curved surface 103 is a curved surface having points of inflection θm.

The angular range occupied by the front convex surfaces 182 may be the same as or different from the angular range occupied by the front concave surfaces 181. The points of inflection Om can be set at any positions. The front curved surface 103 is a wavy surface. The front fixed body surface 100 is a front wavy surface having wavy portions.

As shown in FIG. 6, the front concave surface 181 has a front concave surface inner end 181a and a front concave surface outer end 181b at the opposite ends in the radial direction R. Likewise, the front convex surface 182 has a front convex surface inner end 182a and a front convex surface outer end 182b at the opposite ends in the radial direction R. The inner ends 181a and 182a and the outer ends 181b and 182b are all arcuate.

The inner ends 181a and 182a constitute the inner end of the front curved surface 103. In the present embodiment, the inner ends 181a and 182a are located radially outward from the tube outer circumferential surface 62 by the amount removed by the front chamfered portion 172. The inner ends 181a and 182a are continuous with each other. The front concave surface inner ends 181a are continuous with the inner end of the first front flat surface 101, and the front convex surface inner ends 182a are continuous with the inner end of the second front flat surface 102. As represented by the solid line of FIG. 12, the curve of displacement in the axial direction Z of the inner ends 181a and 182a in relation to changes in the angle is a sine wave.

The outer ends 181b and 182b constitute the outer end of the front curved surface 103. The outer ends 181b and 182b are continuous with each other. The front concave surface outer ends 181b are continuous with the outer end of the first front flat surface 101, and the front convex surface outer ends 182b are continuous with the outer end of the second front flat surface 102. As represented by the long dashed short dashed line of FIG. 12, the curve of displacement in the axial direction Z of the outer ends 181b and 182b in relation to changes in the angle is a sine wave.

The inner end 181a, 182a and the outer end 181b, 182b are different in the radius of curvature or in the curvature, which indicate the extent of displacement in the axial direction Z. The radius of curvature and the curvature of the inner end 181a, 182a and the outer end 181b, 182b as used in the present description are parameters indicating displacement with respect to the axial direction Z, but do not refer to the radius of curvature or the curvature of the inner end 181a, 182a and the outer end 181b, 182b in a plane orthogonal to the axial direction Z.

Specifically, the curvature in the axial direction Z of the front concave surface inner end 181a is greater than the curvature in the axial direction Z of the front concave surface outer end 181b. In the present embodiment, the curvature of the front concave surface 181 gradually increases from the front concave surface outer end 181b toward the front concave surface inner end 181a.

Likewise, the curvature in the axial direction Z of the front convex surface inner end 182a is greater than the curvature in the axial direction Z of the front convex surface outer end 182b. In the present embodiment, the curvature of the front convex surface 182 gradually increases from the front convex surface outer end 182b toward the front convex surface inner end 182a.

In other words, the radius of curvature in the axial direction Z of the front concave surface inner end 181a is smaller than the radius of curvature in the axial direction Z of the front concave surface outer end 181b, and the radius of curvature in the axial direction Z of the front convex surface inner end 182a is smaller than the radius of curvature in the axial direction Z of the front convex surface outer end 182b.

As shown in FIG. 12, the curvature of the displacement curve in the axial direction Z of the front convex surface inner end 182a in relation to changes in the angle is greater than the curvature of the displacement curve in the axial direction Z of the front convex surface outer end 182b in relation to changes in the angle. Accordingly, in the front convex surface 182, the difference between the front convex surface outer end 182b and the front convex surface inner end 182a gradually increases from the second front flat surface 102 toward the point of inflection θm.

Further, as shown in FIG. 12, the curvature of the displacement curve in the axial direction Z of the front concave surface inner end 181a in relation to changes in the angle is greater than the curvature of the displacement curve in the axial direction Z of the front concave surface outer end 181b in relation to changes in the angle. Accordingly, in the front concave surface 181, the difference between the front concave surface outer end 181b and the front concave surface inner end 181a gradually decreases from the the point of inflection Om toward the first front flat surface 101.

Thus, the front curved surface 103 is gradually tilted with respect to the axial direction Z such that the inner end is more separated from the front rotating body surface 71 than the outer end from the second front flat surface 102 toward the point of inflection θm. Accordingly, the inner end and the outer end approach the same position in the axial direction Z from the point of inflection θm toward the first front flat surface 101.

Thus, as shown in FIG. 13, the front curved surface 103 is tilted with respect to the axial direction Z such that the inner end is more separated from the front rotating body surface 71 than the outer end at least at the point of inflection θm. In other words, the front curved surface 103 is gradually recessed from the outer end toward the inner end at least at the point of inflection θm and is curved such that the recess from the outer end toward the inner end decreases from the point of inflection θm toward either angular position θ1, θ2.

In the present embodiment, the vane thickness D, which is the thickness of the vane 131, is set such that the front vane end 132 contacts the front curved surface 103 in a range from the inner end to the outer end regardless of the angular position on the front curved surface 103. Specifically, the vane thickness D is set such that the front vane end 132 contacts the inner end of the front curved surface 103 when the vane 131 is located at the angular position corresponding to the point of inflection θm. The vane thickness D is the measurement of the vane 131 in the width direction of the vane groove 130. In other words, the vane thickness D is the measurement of the vane 131 in a direction orthogonal to both of the axial direction Z and the extending direction of the front vane end 132.

The manner in which the front curved surface 103 and the front vane end 132, which have the above-described configuration, contact each other will now be described.

As shown in FIG. 14, the front vane end 132 is in contact with the front curved surface 103, which is curved in the axial direction Z, in a linear manner. That is, the front vane end 132 and the front curved surface 103 are in linear contact with each other. The contact line of the front curved surface 103 and the front vane end 132 will be referred to as a front contact line P1. The front contact line P1 is the contact line of the front vane end 132 and the front curved surface 103.

As described above, the front vane end 132 extends in a direction orthogonal to the axial direction Z such that the front vane end 132 is not displaced in the axial direction Z in correspondence with the position in the radial direction R. On the other hand, the inner and the outer end of the front curved surface 103 are different in the curvature of the displacement curve in the axial direction Z in relation to changes in the angle. At least at the point of inflection θm, the inner end and the outer end are displaced from each other in the axial direction Z. Thus, the angular position on the front curved surface 103 that contacts the front vane end 132 differs between the inner end and the outer end of the front curved surface 103. For example, when the vane 131 slides on the front curved surface 103 from the first front flat surface 101 toward the second front flat surface 102, the contact area at the inner end of the front curved surface 103 is displaced from the contact area at the outer end toward the second front flat surface 102. Accordingly, the front contact line P1 is not a straight line extending in the radial direction R, but is a curve that is gradually displaced in the circumferential direction (in other words, in the width direction of the vane groove 130) from the outer end toward the inner end.

The curvature of the front vane end 132, which is convex toward the front fixed body surface 100, can be any value. For example, the curvature can be appropriately set based on the vane thickness D or the diameter of the front fixed body surface 100.

The same applies to the rear side. That is, a rear contact line P2, which is a contact line of the rear vane end 133 and the rear fixed body surface 120 is curved with respect to the radial direction R such that the rear contact line P2 is gradually displaced in the circumferential direction from the outer end toward the inner end.

In a case in which the front curved surface 103 is curved in the axial direction Z so as to approach the front rotating body surface 71 from the first angular position 01 toward the second angular position 02, the rear curved surface 123, which faces the front curved surface 103, is curved to be separated from the rear rotating body surface 72 such that the separation distance to the front curved surface 103 is constant. That is, when one of the curved surfaces 103 and 123 is inclined upward, the other is inclined downward. Therefore, the front contact line P1 and the rear contact line P2 are curved in the opposite directions when viewed in the axial direction Z.

The graph of FIG. 12 represents the displacement in the axial direction Z of the rear fixed body surface 120. In this case, the solid line of FIG. 12 represents displacement in the axial direction Z of the inner end of the rear fixed body surface 120, and the long dashed short dashed line of FIG. 12 represents displacement in the axial direction Z of the outer end of the rear fixed body surface 120. The vertical axis of FIG. 12 represents the amount of displacement in the axial direction Z in reference to the first rear flat surface 121. As the displacement in the axial direction Z is separated away from 0, the rear fixed body surface 120 approaches the rear rotating body surface 72.

As shown in FIG. 15, the vane 131 includes opposite end faces in the radial direction R, which are a vane outer end face 201 and a vane inner end face 202. The vane outer end face 201 is one of the opposite end faces in the radial direction R of the vane 131 and is located on the outer side (specifically, on the outer side in the radial direction R). The vane inner end face 202 is one of the opposite end faces in the radial direction R of the vane 131 and is located on the inner side (specifically, on the inner side in the radial direction R).

The vane outer end face 201 is in contact with the front cylinder inner circumferential surface 33 regardless of the movement of the vane 131. That is, the front cylinder inner circumferential surface 33 can be considered to be longer in the axial direction Z than the moving range of the vane 131 so as to maintain the contact with the vane outer end face 201 regardless of the movement of the vane 131.

The front cylinder inner circumferential surface 33 and the vane outer end face 201 are curved in the same direction. Specifically, the front cylinder inner circumferential surface 33 is curved to be convex radially outward, and the vane outer end face 201 is curved to be convex radially outward. In the present embodiment, the curvature of the vane outer end face 201 is set to be the same as the curvature of the front cylinder inner circumferential surface 33.

As shown in FIGS. 15 and 16, the vane inner end face 202 contacts a groove inner end face 130a, which is the end face of the vane groove 130 on the radially inner side. In the present embodiment, the groove inner end face 130a is curved to be convex radially outward with the same curvature as the tube outer circumferential surface 62. The vane inner end face 202 is curved in the same direction as the groove inner end face 130a to be concave radially outward.

As shown in FIG. 16, the curvature of the vane inner end face 202 of the present embodiment is smaller than the curvature of the groove inner end face 130a. That is, the vane inner end face 202 is concave radially outward and curved more gently than the tube outer circumferential surface 62. This creates inner clearances S1 between the vane inner end face 202 and the groove inner end face 130a. Fluid flows into the inner clearances S1.

The vane inner end face 202 and the groove inner end face 130a are in contact with each other. This restricts movement of fluid between the chambers on the opposite sides of the vane 131 through between the vane inner end face 202 and the groove inner end face 130a. Further, the inner clearances S1 are located on the opposite sides in the circumferential direction of the contact area between the vane inner end face 202 and the groove inner end face 130a.

The curvature of the groove inner end face 130a is the same as the curvature of the tube outer circumferential surface 62. Thus, the curvature of the vane inner end face 202 may be considered to be smaller than the curvature of the tube outer circumferential surface 62.

In the present embodiment, the groove inner end face 130a is provided on the rotating body 60. However, the configuration is not limited to this, and the groove inner end face 130a may be provided in any member. For example, an inner member that includes a groove inner end face 130a may be provided in addition to the rotating body 60, and the inner member may be attached to the rotating body 60.

Referring to FIGS. 17 and 18, the sequence of operations of the compressor 10 will now be described. FIGS. 17 and 18 are developed views schematically showing the rotating body 60, the fixed bodies 90 and 110, and the vanes 131. FIGS. 17 and 18 show the rotating body 60 and the vanes 131 at different phases. The ports 141, 142, 151 and 161 are shown schematically in FIGS. 17 and 18.

As shown in FIGS. 17 and 18, when the electric motor 13 rotates the rotary shaft 12, the rotating body 60 rotates accordingly. The vanes 131 thus rotate while moving in the axial direction Z along the fixed body surfaces 100 and 120 and maintaining the positional relationship between one another in the circumferential direction. As viewed in FIGS. 17 and 18, the vanes 131 move downward while moving in the left-right direction. This changes the volumes of the front compression chambers A4a to A4c and the rear compression chambers A5a to A5c, allowing for suction, compression and expansion of the fluid. That is, the rotation and movement in the axial direction Z of the vanes 131 perform the suction and compression of fluid in the compression chambers A4 and A5.

Specifically, the first front compression chamber A4a and the space in the second front compression chamber A4b that is located on the leading side of the second front flat surface 102 increase in volume and perform suction of fluid through the front suction port 141.

In contrast, the third front compression chamber A4c and the space in the second front compression chamber A4b that is located on the trailing side of the second front flat surface 102 (the trailing space) decrease in volume as the rotating body 60 rotates and perform compression of the fluid. Specifically, the fluid is compressed in the third front compression chamber A4c, and the fluid compressed in the third front compression chamber A4c is further compressed in the trailing space of the second front compression chamber A4b.

When the pressure in the trailing space of the second front compression chamber A4b exceeds the threshold, the front valve 152 opens allowing the fluid compressed in the second front compression chamber A4b to be discharged into the discharge chamber A1 through the front discharge ports 151. The same applies to the rear compression chamber A5.

As described above, the rotation of the rotating body 60 and the vanes 131 results in one cycle of suction and compression, which corresponds to 480°, repeated in the three part chambers in each of the compression chambers A4 and A5. Specifically, in each compression chamber A4, A5, the fluid is drawn and expanded in the phase between 0° and 240°, and the fluid is compressed in the phase between 240° and 480°.

For example, it is assumed that the angular position of the circumferential center of the second front flat surface 102 is 0°, and the first vane 131 is located at this circumferential center. Additionally, it is assumed that the angle increases in the rotation direction M from this 0° angular position. In this case, while the first vane 131 moves from the 0° angular position to the 240° angular position, the fluid is drawn into the part chamber located on the trailing side of the first vane 131.

In particular, since the front suction opening 141a extends at least from the leading edge of the second front flat surface 102 to the 120° angular position, the suction of the fluid continues until the first vane 131 reaches the 240° angular position. This limits expansion of the fluid in this part chamber, thereby improving the efficiency.

While the second vane 131, which is on the trailing side of the first vane 131, moves from the 120° angular position to the 360° angular position, the fluid is compressed in the part chamber on the leading side of the second vane 131.

The three front compression chambers A4a to A4c are at different phases. That is, the space defined by the front rotating body surface 71, the front fixed body surface 100, the tube outer circumferential surface 62, and the front cylinder inner circumferential surface 33 is partitioned by the vanes 131 into three compression chambers at different phases. In the present embodiment, while the rotating body 60 rotates 480°, the suction and compression of fluid take place in each of the three front compression chambers and the three rear compression chambers.

In the above description, the three front compression chambers A4a to A4c separated by the vanes 131 are defined in terms of the positional relationship with the front suction port 141 and the front discharge ports 151. However, the front compression chambers A4a to A4c may be described from another viewpoint. For example, the following description focuses on one cycle in one compression chamber.

As the first vane 131 moves to the leading side of the second front flat surface 102, a compression chamber continuous with the front suction port 141 is provided on the trailing side of the first vane 131. This compression chamber increases in volume as the vane 131 rotates, while maintained to be continuous with the front suction port 141. The fluid is thus drawn into this compression chamber.

Then, the second vane 131 moves to the leading side of the second front flat surface 102, so that the compression chamber is defined by the first and second vanes 131. The fluid is drawn into this compression chamber until the second vane 131 reaches the leading end of the front suction opening 141a.

The second vane 131 continues to move beyond the leading end of the front suction opening 141a to the leading side, so that the compression chamber is no longer continuous with the front suction port 141. As the rotating body 60 rotates further, the compression chamber becomes continuous with the front discharge ports 151. In this stage, the volume of the compression chamber decreases as the rotating body 60 rotates, thereby compressing the fluid in the compression chamber. Then, when the second vane 131 reaches a position where it comes into contact with the second front flat surface 102, the volume of the compression chamber becomes 0, and one cycle of suction and compression in the compression chamber is completed.

The present embodiment has the following advantages. Although only the structure on the front side will be discussed in the following description for the illustrative purposes, the structure on the rear side has the same advantages.

(1-1) The compressor 10 includes the rotary shaft 12, the rotating body 60, which rotates together with the rotary shaft 12, the front fixed body 90, which does not rotate together with the rotating body 60, and the vanes 131, which are inserted in the vane grooves 130 of the rotating body 60. As the rotating body 60 rotates, the vanes 131 rotate while moving in the axial direction Z. The rotating body 60 includes the front rotating body surface 71, which intersects with the axial direction Z. The front fixed body 90 includes the front fixed body surface 100, which faces the front rotating body surface 71 in the axial direction Z. The compressor 10 includes the front compression chamber A4, which is defined by the front rotating body surface 71 and the front fixed body surface 100. Suction and compression of fluid performed in the front compression chamber A4 when the vanes 131 rotate while moving in the axial direction Z.

The vane 131 has the front vane end 132, which is the end in the axial direction Z and is in contact with the front fixed body surface 100. The front vane end 132 is curved to be convex toward the front fixed body surface 100 and extends in a direction orthogonal to the axial direction Z. The front fixed body surface 100 has the second front flat surface 102 and the two front curved surfaces 103. The second front flat surface 102 is a fixed body contact surface, which is in contact with the front rotating body surface 71. The front curved surface 103 are located on the opposite sides of the second front flat surface 102 in the circumferential direction. The two front curved surfaces 103 are curved in the axial direction Z such that the distance to the front rotating body surface 71 increases as the distance to the second front flat surface 102 increases in the circumferential direction.

The front curved surface 103 includes the front convex surface 182 and the front concave surface 181. The front convex surface 182 is curved to convex toward the front rotating body surface 71 and is continuous with the second front flat surface 102. The front concave surface 181 is curved to be concave with respect to the front rotating body surface 71 and is continuous with the front convex surface 182.

The front convex surface 182 has the front convex surface inner end 182a and the front convex surface outer end 182b at the opposite ends in the radial direction R. The curvature in the axial direction Z of the front convex surface inner end 182a is greater than the curvature in the axial direction Z of the front convex surface outer end 182b.

Likewise, the front concave surface 181 has a front concave surface inner end 181a and a front concave surface outer end 181b at the opposite ends in the radial direction R. The curvature in the axial direction Z of the front concave surface inner end 181a is greater than the curvature in the axial direction Z of the front concave surface outer end 181b.

With this configuration, the front contact line P1, which is the area of contact between the vane 131 and the front fixed body surface 100, is a curved line. As compared to a case in which the front contact line P1 is a straight line, swinging motion of the vane 131 on the front contact line P1 as the pivot is suppressed. This restricts swinging motion of the vane 131 in the circumferential direction.

Specifically, when the front vane end 132 of the vane 131, which rotates together with the rotating body 60, is in contact with the front fixed body surface 100, which does not rotate together with the rotating body 60, the vane 131 swings on the front contact line P1 as the pivot.

In this regard, the present inventors discovered that the orientation of the vane 131 is more stabilized and less likely to swing when the front contact line P1 is a curved line than when the front contact line P1 is a straight line. In view of this finding, the curvature in the axial direction Z is differentiated between the front convex surface inner end 182a and the front convex surface outer end 182b such that the front contact line P1 is a curved line, and the curvature in the axial direction Z is differentiated between the front concave surface inner end 181a and the front concave surface outer end 181b. The front contact line P1 is thus a curved line to suppress swinging motion of the vane 131. Therefore, disadvantages caused by swinging motion of the vane 131, for example, noise, vibration, and fluid leakage due to swinging motion of the vane 131 are suppressed.

Fluid leakage due to swinging motion of the vane 131, for example, refers to fluid leakage through between the vane 131 and the front fixed body surface 100. Specifically, at the vane 131 that divides the second front compression chamber A4b and the third front compression chamber A4c, fluid may leak from the second front compression chamber A4b to the third front compression chamber A4c.

(1-2) The vane 131 is inserted in the vane groove 130. The vane 131 contacts the vane groove 130 (specifically, the side surfaces of the vane groove 130), so as to rotate together with the rotating body 60.

Since the vane 131 needs to be inserted in the vane groove 130 to be movable in the axial direction Z, a slight clearance is provided between the vane 131 and the vane groove 130 in some cases so as to allow the vane 131 to move smoothly in the axial direction Z. In this case, the vane 131 can swing in the vane groove 130.

In this regard, since the front contact line P1 is a curved line in the present embodiment, swinging motion of the vane 131 in the vane groove 130 is suppressed. While allowing smooth movement of the vane 131 in the axial direction Z, swinging motion of the vane 131 in the vane groove 130 caused by the sliding motion is suppressed.

(1-3) The vane 131 is a plate of which the thickness direction is a direction orthogonal to both of the axial direction Z and the extending direction of the front vane end 132. The vane thickness D is set such that the front vane end 132 contacts the front curved surface 103 in a range from the inner end to the outer end regardless of the angular position on the front curved surface 103.

In this configuration, the vane thickness D is set in the above-described manner, so that the front vane end 132 is maintained in contact with the front curved surface 103 in a range from the inner end to the outer end regardless of the angular position on the front curved surface 103. This configuration prevents the front vane end 132 and the front curved surface 103 from being locally separated from each other while allowing the front contact line P1 to be curved line. Accordingly, fluid is prevented from leaking through between the front vane end 132 and the front curved surface 103.

As has been described, the inner end of the front curved surface 103 is concave with respect to the outer end by the greatest amount at the point of inflection θm. Thus, the vane thickness D is preferably set such that the front vane end 132 contacts the inner end of the front curved surface 103 in a state in which the vane 131 is located at the angular position corresponding to the point of inflection θm. This configuration allows the front vane end 132 to readily contact the front curved surface 103 in a range from the inner end to the outer end regardless of the angular position of the rotating body 60.

(1-4) The rotating body 60 includes the rotating body tube 61 and the rotating body ring portion 70. The rotating body tube 61 has the tube outer circumferential surface 62 and receives the rotary shaft 12. The rotating body ring portion 70 extends radially outward from the tube outer circumferential surface 62 and has the front rotating body surface 71 and the vane grooves 130. The rotating body 60 is supported by the front fixed body 90 by inserting the rotating body tube 61 into the front fixed body insertion hole 91 provided in the front fixed body 90.

In the above-described configuration, the rotating body 60, which includes the front rotating body surface 71, is supported by the front fixed body 90, which includes the front fixed body surface 100. Since the front fixed body 90 directly supports the rotating body 60, the rotating body 60 is prevented from being displaced with respect to the front fixed body 90. Thus, the front rotating body surface 71 and the front fixed body surface 100, which face each other in the axial direction Z, are prevented from being displaced from each other. This prevents trouble caused by displacement of the front rotating body surface 71 with respect to the front fixed body surface 100, for example, the front rotating body surface 71 being caught on the front fixed body surface 100.

Particularly, in the present embodiment, the second front flat surface 102, which is part of the front fixed body surface 100, is in contact with the front rotating body surface 71. Thus, when displacement of the front rotating body surface 71 with respect to the front fixed body surface 100 increases, the frictional force due to sliding of the second front flat surface 102 and the front rotating body surface 71 increases, accordingly. This may increase the power required to drive the compressor 10.

In this regard, since the rotating body 60 is supported by the front fixed body 90, the position of the rotating body 60 is determined with respect to the front fixed body 90. This prevents the front rotating body surface 71 from being displaced with respect to the front fixed body surface 100, thereby suppressing increase in the required power due to such displacement.

Being supported by the front fixed body 90, the rotating body 60 is prevented from tilting. This prevents gaps through which fluid leaks from being formed by tilting of the rotating body 60.

(1-5) Particularly, the compressor 10 includes the fixed bodies 90 and 110, which are arranged on the opposite sides in the axial direction of the rotating body ring portion 70, and the compression chambers A4 and A5, which are arranged on the opposite sides in the axial direction of the rotating body ring portion 70. The front compression chamber A4 is defined by the front rotating body surface 71 and the front fixed body surface 100, and the rear compression chamber A5 is defined by the rear rotating body surface 72 and the rear fixed body surface 120. The rotating body ends 61a and 61b, which are the opposite ends in the axial direction of the rotating body tube 61, are respectively inserted in the fixed body insertion holes 91 and 111 to be supported by the fixed bodies 90 and 110.

In this configuration, the rotating body 60 is supported by the fixed bodies 90 and 110, which are arranged on the opposite sides in the axial direction of the rotating body ring portion 70, which has the rotating body surfaces 71 and 72. This stably maintains the orientation of the rotating body ring portion 70, thereby reliably preventing displacement between the rotating body surfaces 71 and 72 and the fixed body surfaces 100 and 120.

(1-6) The front boundary 171, which is the boundary between the tube outer circumferential surface 62 and the front rotating body surface 71, is curved. The front chamfered portion 172, which avoids interference with the front boundary 171, is provided at the corner portion of the front fixed body surface 100 and the inner wall surface of the front fixed body insertion hole 91.

When the rotating body 60 includes the rotating body tube 61 and the rotating body ring portion 70 as described above, stress may be concentrated on the front boundary 171, which corresponds to the boundary between the rotating body tube 61 and the rotating body ring portion 70.

In this regard, since the front boundary 171 is curved, stress can be dispersed in the front boundary 171 as compared to a case in which the front boundary 171 is a right angle. This prevents stress from being concentrated locally in the rotating body 60.

Further, the front chamfered portion 172 prevents the front boundary 171 and the front fixed body 90 from interfering with each other. This prevents rotation of the rotating body 60 from being hindered by contact between the boundary 171 and the front fixed body 90. Also, the required power is not increased by contact between the front boundary 171 and the front fixed body 90.

(1-7) The compressor 10 includes the front cylinder 30, which accommodates the rotating body 60 and the front fixed body 90. The front cylinder 30 includes the front cylinder inner circumferential surface 33, which cooperates with the front rotating body surface 71 and the front fixed body surface 100 to define the front compression chamber A4. The vane 131 has the vane outer end face 201, which is the radially outer end face, and the vane inner end face 202, which is the radially inner end face. The vane outer and inner end faces 201 and 202 are the opposite end faces in the radial direction. The vane outer end face 201 contacts the front cylinder inner circumferential surface 33. The vane inner end face 202 contacts the groove inner end face 130a, which is the radially inner end face of the vane groove 130. The vane inner end face 202 and the groove inner end face 130a are curved in the same direction, and the curvature of the vane inner end face 202 is smaller than the curvature of the groove inner end face 130a.

This configuration prevents the curvature of the vane inner end face 202 from being greater than the curvature of the groove inner end face 130a, for example, due to manufacturing errors. Accordingly, disadvantages caused by the curvature of the vane inner end face 202 being greater than the curvature of the groove inner end face 130a are eliminated.

Specifically, if the curvature of the vane inner end face 202 is set to be equal to the curvature of the groove inner end face 130a, manufacturing errors and the like may cause the curvature of the vane inner end face 202 to be greater than the curvature of the groove inner end face 130a. In this case, the opposite ends of the vane inner end face 202 may be caught on the groove inner end face 130a, hindering movement of the vane 131 in the axial direction Z or wearing the opposite ends of the vane inner end face 202.

In this respect, since the curvature of the groove inner end face 130a is positively set to be smaller than the curvature of the groove inner end face 130a, the curvature of the vane inner end face 202 will not be greater than the curvature of the groove inner end face 130a even if manufacturing errors are caused. Accordingly, disadvantages caused by the curvature of the vane inner end face 202 being greater than the curvature of the groove inner end face 130a are eliminated.

Since the vane inner end face 202 is curved more gently than the groove inner end face 130a, the inner clearances 51 are created between the vane inner end face 202 and the groove inner end face 130a, and fluid flows into the inner clearances S1. The vane 131 is pushed radially outward by the fluid in the inner clearances S1. This provides sealing between the vane outer end face 201 and the front cylinder inner circumferential surface 33.

Second Embodiment

As shown in FIG. 19, the curvature of a vane outer end face 211 of the present embodiment is greater than the curvature of the front cylinder inner circumferential surface 33. That is, the vane outer end face 211 is convex radially outward and is curved more sharply than the front cylinder inner circumferential surface 33. This creates outer clearances S2, into which fluid flows, between the vane outer end face 211 and the front cylinder inner circumferential surface 33.

However, since the vane outer end face 211 and the front cylinder inner circumferential surface 33 contact each other, movement of fluid between the chambers on the opposite sides of the vane 131 through between the vane outer end face 211 and the front cylinder inner circumferential surface 33 is restricted.

The curvature of a vane inner end face 212 of the present embodiment is set to be equal to the curvature of the groove inner end face 130a.

The present embodiment, which has been described above, has the following operational advantages in addition to the advantage (1-7).

(2-1) The vane outer end face 211 is curved in the same direction as the front cylinder inner circumferential surface 33, and the curvature of the vane outer end face 211 is greater than the curvature of the front cylinder inner circumferential surface 33.

This configuration prevents the curvature of the vane outer end face 211 from being smaller than the curvature of the front cylinder inner circumferential surface 33, for example, due to manufacturing errors.

Specifically, if the curvature of the vane outer end face 211 is set to be equal to the curvature of the front cylinder inner circumferential surface 33, manufacturing errors and the like may cause the curvature of the vane outer end face 211 to be smaller than the curvature of the front cylinder inner circumferential surface 33. In this case, the opposite ends of the vane outer end face 211 may be caught on the front cylinder inner circumferential surface 33. This may hinder movement of the vane 131 in the axial direction Z or wear the opposite ends of the vane outer end face 211.

In this regard, since the curvature of the vane outer end face 211 is positively set to be greater than the curvature of the front cylinder inner circumferential surface 33, the curvature of the vane outer end face 211 will not be smaller than the curvature of the front cylinder inner circumferential surface 33 even if there are manufacturing errors and the like. Accordingly, disadvantages caused by the curvature of the vane outer end face 211 being smaller than the curvature of the front cylinder inner circumferential surface 33 are eliminated.

(2-2) Since the vane outer end face 211 is curved more sharply than the front cylinder inner circumferential surface 33, the outer clearances S2, into which fluid flows, are created between the vane outer end face 211 and the front cylinder inner circumferential surface 33. The vane 131 is pushed radially inward, which is the direction opposite to the centrifugal force, by the fluid in the outer clearances S2. This configuration prevents the vane outer end face 211 from being excessively pressed against the front cylinder inner circumferential surface 33 due to the centrifugal force acting on the vane 131.

Specifically, since the vane 131 rotates together with the rotating body 60, centrifugal force acts on the vane 131. The vane 131 is thus likely to be pushed radially outward. If the vane outer end face 211 is excessively pressed against the front cylinder inner circumferential surface 33, some drawbacks may be caused. For example, sliding of the vane outer end face 211 and the front cylinder inner circumferential surface 33 may be hindered. Also, the vane outer end face 211 may be worn excessively.

In this respect, the fluid in the outer clearances S2 applies to the vane 131 pushing force acting in the direction cancelling the centrifugal force. This reduces the radially outward pushing force due to the centrifugal force, thereby eliminating the above-described disadvantages.

The above described embodiments may be modified as follows. The above-described embodiments and the following modifications can be combined as long as the combined modifications remain technically consistent with each other.

The vane 131 may have a vane inner end face 202 having a curvature smaller than the curvature of the groove inner end face 130a and a vane outer end face 211 having a curvature greater than the curvature of the front cylinder inner circumferential surface 33.

FIG. 20 shows a vane outer end face 230 of a first modification, which is configured such that a part on the leading side in the rotation direction M and a part on the trailing side in the rotation direction M have different curvatures. For example, the vane outer end face 230 may include a first part outer end face 231, which has a curvature greater than that of the front cylinder inner circumferential surface 33, and a second part outer end face 232, which is located on the leading side of the first part outer end face 231 in the rotation direction M and has a curvature greater than that of the first part outer end face 231. The first part outer end face 231 is a surface on the trailing side in the rotation direction M of the vane outer end face 230, and the second part outer end face 232 is a surface on the leading side in the rotation direction M in the vane outer end face 230. This improves the sealing performance between the vane outer end face 230 and the front cylinder inner circumferential surface 33.

Specifically, the pressure of the respective front compression chambers A4a to A4c tends to be higher if the chamber is located on the leading side in the rotation direction M. More specifically, the pressure tends to be higher in order of the first front compression chamber A4a, the third front compression chamber A4c, and the second front compression chamber A4b. Particularly, the space on the trailing side in the rotation direction M of the contact area between the front rotating body surface 71 and the second front flat surface 102 tends to have a higher pressure. Thus, the pressure in the chamber on the leading side of the vane 131 in the rotation direction M is likely to be higher than the pressure in the chamber on the trailing side in the rotation direction M of the vane 131. For example, in the case of the vane 131 that divides the second front compression chamber A4b and the third front compression chamber A4c from each other, the third front compression chamber A4c is located on the trailing side in the rotation direction M of the vane 131, and the second front compression chamber A4b is located on the leading side of the vane 131 in the rotation direction M. The pressure of the second front compression chamber A4b is likely to be higher than the pressure of the third front compression chamber A4c.

In this regard, according to the first modification, the curvature of the first part outer end face 231 is closer to the curvature of the front cylinder inner circumferential surface 33 than the second part outer end face 232. Thus, the contact area between the first part outer end face 231 and the front cylinder inner circumferential surface 33 is likely to extend in the circumferential direction, increasing the contact area between the first part outer end face 231 and the front cylinder inner circumferential surface 33. This improves the sealing performance between the vane outer end face 230 and the front cylinder inner circumferential surface 33.

On the other hand, the second part outer end face 232, which is located on the leading side of the first part outer end face 231 in the rotation direction M, is curved more sharply than the first part outer end face 231. Thus, the outer clearance S2 on the leading side in the rotation direction M is greater than the outer clearance S2 on the trailing side in the rotation direction M. Accordingly, the ratio of the fluid of higher pressure is likely to be higher in the fluid flowing into the outer clearances S2. This prevents the pushing force of the fluid in the outer clearances S2 from being reduced due to the first part outer end face 231. This configuration improves the sealing performance between the vane outer end face 230 and the front cylinder inner circumferential surface 33, while preventing the pushing force of the fluid in the outer clearances S2 from being reduced.

FIG. 21 shows a vane inner end face 233 of a second modification, which has a first part inner end face 234 and a second part inner end face 235. The first part inner end face 234 has a curvature smaller than the curvature of the groove inner end face 130a. The second part inner end face 235 is located on the leading side of the first part inner end face 234 in the rotation direction M and has a curvature smaller than the curvature of the first part inner end face 234. The first part inner end face 234 is a surface on the trailing side in the rotation direction M of the vane inner end face 233, and the second part inner end face 235 is a surface on the leading side of the vane inner end face 233 in the rotation direction M. This improves the sealing performance between the vane inner end face 233 and the groove inner end face 130a.

Specifically, the curvature of the first part inner end face 234 is closer to the curvature of the groove inner end face 130a than the curvature of the second part inner end face 235. Thus, the contact area between the first part inner end face 234 and the groove inner end face 130a is likely to extend in the circumferential direction, increasing the contact area between the first part inner end face 234 and the groove inner end face 130a. This improves the sealing performance between the vane inner end face 233 and the groove inner end face 130a.

On the other hand, the second part inner end face 235, which is located on the leading side of the first part inner end face 234 in the rotation direction M, is curved less sharply than the first part inner end face 234. Thus, the inner clearance S1 on the leading side in the rotation direction M is greater than the inner clearance S1 on the trailing side in the rotation direction M. Accordingly, the ratio of the fluid of higher pressure is likely to be higher in the fluid flowing into the inner clearances S1. This prevents the pushing force of the fluid in the inner clearances S1 from being reduced due to the first part inner end face 234. This configuration improves the sealing performance between the vane inner end face 233 and the groove inner end face 130a, while preventing the pushing force of the fluid in the inner clearances S1 from being reduced.

FIGS. 22 to 24 show a vane 131 according to a third modification, which is composed of multiple components. For example, the vane 131 may include a vane body 240 and tip seals 250 and 260. The vane body 240 is inserted in the vane groove 130 regardless of movement of the vane 131 in the axial direction Z. The tip seals 250 and 260 are provided on the opposite sides of the vane body 240 in the axial direction Z. The plate-shaped vane 131 is a combination of the vane body 240 and the tip seals 250 and 260, which is convex toward the fixed body surfaces 100, 120. In this case, the tip seals 250 and 260 located at the opposite ends of the vane 131 in the axial direction and contact the fixed body surfaces 100 and 120. That is, the tip seals 250 and 260 correspond to vane ends.

The plate-shaped vane body 240 is inserted in the vane groove 130 such that the thickness direction matches the width direction of the vane groove 130. The vane body 240 has opposite end faces 241 and 243 in the axial direction.

The tip seals 250 and 260, for example, respectively include seal bodies 251 and 261, which respectively contact the fixed body surfaces 100 and 120. The seal bodies 251 and 261 are respectively curved to be convex toward the fixed body surfaces 100 and 120.

The tip seals 250 and 260 respectively have attachment protrusions 252 and 262, which protrude toward the vane body 240 from the seal bodies 251 and 261. The vane body 240 has attachment grooves 242 and 244 at the end faces 241 and 243 in the axial direction. The attachment protrusions 252, 262 are inserted into the attachment grooves 242 and 244. When the attachment protrusions 252, 262 are inserted into the attachment grooves 242 and 244, the tip seals 250 and 260 are attached to the vane body 240 while being movable relative to the vane body 240. In this case, the attachment protrusions 252 and 262 respectively face the attachment grooves 242 and 244 in the circumferential direction.

As shown in FIG. 24, back pressure spaces 253 and 263 are respectively defied between the tip seals 250 and 260 and the vane body 240. Fluid flows into the back pressure spaces 253 and 263. The tip seals 250 and 260 are respectively pushed toward the fixed body surfaces 100 and 120 by the fluid in the back pressure spaces 253 and 263.

With the above-described configuration, when the tip seals 250 and 260 are respectively pushed toward the fixed body surfaces 100 and 120 by the fluid in the back pressure spaces 253 and 263, the tip seals 250 and 260 are brought into contact with the fixed body surfaces 100 and 120. This provides sealing between the vane 131 and the fixed body surfaces 100 and 120.

In the third modification, either one of the tip seals 250 and 260 may be omitted. That is, a tip seal may be provided either on the front side or the rear side. In this case, the end of the vane body 240 at which no tip seal is provided is preferably brought into contact with the fixed body surface. That is, the vane 131 may be composed of two components.

The front vane end 132 and the front fixed body surface 100 do not necessarily need to contact each other in a range from the inner end to the outer end, but may contact each other partly in the radial direction R. The front vane end 132 and the front fixed body surface 100 do not necessarily need to contact each other over the entire circumference, but may partly contact each other in a certain angular range. The same applies to the rear vane end 133 and the rear fixed body surface 120.

The vane thickness D may be any value. Specifically, the vane thickness D may have such a value that the front vane end 132 and the inner end of the front curved surface 103 do not contact each other at the point of inflection θm.

One of the contact lines P1 and P2 may be a straight line and the other may be a curved line. In short, the fixed body surfaces 100 and 120 only needs to be configured such that at least one of the contact lines P1 and P2 is a curved line.

The boundaries 171 and 173 may be right angles. In this case, the chamfered portions 172 and 174 may be omitted. Since no gap due to the chamfered portions 172 and 174 is created, leakage of fluid is prevented. Further, the boundaries 171 and 173 may be concave portions that are concave with respect to the tube outer circumferential surface 62 and the front rotating body surface 71. In this case, the chamfered portions 172 and 174 may be provided or omitted.

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

The rotating body tube 61 may include a cutout section or a protrusion. In the embodiments described above, the rotating body tube 61 is cylindrical, that is, has a circular cross-section, but may have a non-circular cross section. As long as each fixed body insertion hole 91, 111 is shaped corresponding to the shape of the rotating body tube 61 so as to reduce a gap between the inner wall surface defining the fixed body insertion hole 91, 111 and the rotating body tube 61, the fixed body insertion hole 91, 111 does not have to be circular. In addition, when the rotating body tube 61 has a cutout section, an additional member may be fitted into the cutout section.

The rotating body may be a circular plate that does not have any projection extending from the rotating body surfaces 71 and 72 in the axial direction Z. The rotating body does not have to be supported by the two fixed bodies 90 and 110. In this case, the front compression chamber A4 may be defined by the outer circumferential surface of the rotary shaft 12. That is, the front compression chamber A4 does not have to be defined by the tube outer circumferential surface 62 and may have any configuration as long as it is defined by the front rotating body surface 71 and the front fixed body surface 100. The same applies to the rear compression chamber A5.

The number of the shaft bearings 51 and 53 is not limited to two and may be one. For example, the rear shaft bearing 53 may be omitted. Three or more shaft bearings may be provided.

In the present embodiment, the front cylinder 30 and the rear plate 40 define the accommodation chamber A3. However, the accommodation chamber A3 may be defined in any manner.

For example, the compressor 10 may include a front plate instead of the front cylinder 30. Further, instead of the rear plate 40, the compressor 10 may include a rear cylinder having a circumferential wall and an end wall. In this case, the rear cylinder is butted against the front plate to define the accommodation chamber A3.

Alternatively, the compressor 10 may include two cylinders that define the accommodation chamber A3. Further, the rear plate 40 may be omitted, and the accommodation chamber A3 may be defined by the front cylinder 30 and the rear housing end wall 23.

As long as each compression chamber A4, A5 is defined by the rotating body surface 71, 72 and the fixed body surface 100, 120, the other surfaces defining the compression chamber A4, A5 may be changed. For example, in a configuration in which the front cylinder 30 is omitted and the rear housing member 22 (or the housing 11) accommodates the rotating body 60 and the fixed bodies 90 and 110, the compression chambers A4 and A5 may be defined by the inner circumference surface of the rear housing member 22, instead of the front cylinder inner circumferential surface 33. In this case, the rear housing member 22 or the housing 11 is the cylinder portion, and the inner circumferential surface of the rear housing member 22 is the cylinder inner circumferential surface. Further, the compression chambers A4 and A5 may be defined by the outer circumferential surface of the rotary shaft 12 instead of the tube outer circumferential surface 62.

The front fixed body 90 and the front cylinder 30 may be formed integrally, and the rear fixed body 110 and the rear plate 40 may be formed integrally.

The front cylinder end wall 31 and the front cylinder circumferential wall 32 may be separate components. The front cylinder end wall 31 may be omitted. In this case, the front cylinder circumferential wall 32 is the cylinder portion.

The configuration for introducing the fluid into the compression chambers A4 and A5 and the configuration for discharging the fluid compressed in the compression chambers A4 and A5 are not limited to the configurations described in the first embodiment. For example, at least one of the suction port and the discharge port may be provided in the fixed bodies 90 and 110.

The two fixed bodies 90 and 110 have the same shape. However, the present disclosure is not limited to this. 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 front cylinder inner circumferential surface 33 may have steps corresponding to the shapes of the fixed bodies 90 and 110, or a front cylinder accommodating the front fixed body 90 may be provided separately from a rear cylinder accommodating the rear fixed body 110. That is, the volumes of the two compression chambers A4 and A5 may be the same or different.

The compressor 10 of the embodiments has the two compression chambers A4 and A5, but the present disclosure is not limited to this.

For example, as in a fourth modification shown in FIG. 25, the rear fixed body 110, the rear compression chamber A5, the rear suction port 142, and the rear discharge ports 161 may be omitted. In this case, the front fixed body surface 100 does not have to include the first front flat surface 101.

In this case, an urging portion 300 may be provided that urges the vane 131 toward the front fixed body 90. The urging portion 300 may be supported by an urging support section 301 provided in the rotating body tube 61 so as to be rotatable together with the rotating body 60. The urging support section 301 may be plate-shaped and protrude radially outward from the rear rotating body end 61b of the rotating body tube 61. As such, the vane 131 remains in contact with the front fixed body surface 100 while rotating and moving in the axial direction Z along with the rotation of the rotating body 60. Instead of omitting the rear side configuration, the front side configuration may be omitted. In other words, the compressor 10 may include only one fixed body.

The fixed body insertion holes 91 and 111 do not have to be through holes and may have closed ends, as long as they receive the rotary shaft 12.

At least one of the thrust bearings 81 and 82 may be omitted. That is, the compressor 10 does not have to include the thrust bearings 81 and 82.

At least one of the two rotating body bearings 94 and 114 may be omitted.

The discharge chamber A1 is not required to have the shape of a cylinder with the axis extending in the axial direction Z. For example, the discharge chamber A1 may be C-shaped as viewed in the axial direction Z, or two discharge chambers A1 may be arranged to face each other. In other words, the discharge chamber A1 may be configured to extend at least partially in the circumferential direction.

The number of the vanes 131 is arbitrary, and may be one, two, or four or more. When only one vane 131 is provided, the front compression chamber A4 is partitioned into a chamber for suction and a chamber for compression by the vane 131 and the area of contact between the second front flat surface 102 and the front rotating body surface 71.

The area of the front fixed body surface 100 that is in contact with the front rotating body surface 71 (the fixed body contact surface) 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. Nevertheless, a flat surface is desirable in view of the sealing performance.

In the above-described embodiments, the front curved surface 103 is curved such that the distance to the front rotating body surface 71 increases as the distance to the second front flat surface 102 increases in the circumferential direction. However, the present disclosure is not limited to this. For example, the front curved surface 103 may have a section in the middle in which the distance to the front rotating body surface 71 is constant. The same applies to the rear curved surface 123.

The housing 11 may have an arbitrary shape.

The rotary shaft 12 may have an arbitrary shape. For example, at least a part of the rotary shaft 12 may be hollow or has the shape of a prism.

The electric motor 13 and the inverter 14 may be omitted. That is, the compressor 10 does not have to include the electric motor 13 or the inverter 14. In this case, the rotary shaft 12 may be driven and rotated by a belt, for example.

The compressor 10 may be used for other than an 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 compressed by the compressor 10 is not limited to a refrigerant containing oil.

The compressor 10 may be mounted on an object other than a vehicle.

The specific shapes of the fixed body surfaces 100 and 120 may be changed.

Various changes in form and details may be made to the examples above without departing from the spirit and scope of the claims and their equivalents. The examples are for the sake of description only, and not for purposes of limitation. Descriptions of features in each example are to be considered as being applicable to similar features or aspects in other examples. Suitable results may be achieved if sequences are performed in a different order, and/or if components in a described system, architecture, device, or circuit are combined differently, and/or replaced or supplemented by other components or their equivalents. The scope of the disclosure is not defined by the detailed description, but by the claims and their equivalents. All variations within the scope of the claims and their equivalents are included in the disclosure.

Claims

1. A compressor comprising:

a rotary shaft;

a rotating body that is configured to rotate together with the rotary shaft and includes a rotating body surface, which intersects with an axial direction of the rotary shaft, and a vane groove and;

a fixed body that is configured not to rotate together with the rotary shaft and includes a fixed body surface, which faces the rotating body surface in the axial direction;

a vane that is inserted in the vane groove and configured to rotate together with the rotating body while moving in the axial direction; and

a compression chamber that is defined by the rotating body surface and the fixed body surface and in which suction and compression of fluid is performed when the vane rotates while moving in the axial direction, wherein

the vane has a vane end at an end in the axial direction, the vane end contacting the fixed body surface,

the vane end is curved to be convex toward the fixed body surface and extends in a direction orthogonal to the axial direction,

the fixed body surface includes a fixed body contact surface that contacts the rotating body surface, and two curved surfaces respectively provided on opposite sides of the fixed body contact surface in a circumferential direction of the rotary shaft, each curved surface being curved such that a distance to the rotating body surface increases as a distance to the fixed body contact surface increases, and

each curved surface includes a convex surface continuous with the fixed body contact surface, the convex surface being curved to be convex toward the rotating body surface, and a concave surface continuous with the convex surface, the concave surface being curved to be concave with respect to the rotating body surface, wherein

the convex surface includes a convex surface inner end and a convex surface outer end at opposite ends in a radial direction of the rotary shaft,

a curvature in the axial direction of the convex surface inner end is greater than a curvature in the axial direction of the convex surface outer end,

the concave surface includes a concave surface inner end and a concave surface outer end at opposite ends in the radial direction, and

a curvature in the axial direction of the concave surface inner end is greater than a curvature in the axial direction of the concave surface outer end.

2. The compressor according to claim 1, wherein

the vane is plate-shaped and has a thickness in a direction that is orthogonal to both of the axial direction and an extending direction of the vane end, and

the thickness of the vane is set such that the vane end contacts the curved surface in a range from an inner end to an outer end of the curved surface regardless of an angular position on the curved surface.

3. The compressor according to claim 1, wherein

the rotating body includes a rotating body tube in which the rotary shaft is inserted, the rotating body tube having a tube outer circumferential surface, and a rotating body ring portion that extends radially outward from the tube outer circumferential surface, the rotating body ring portion including the rotating body surface and the vane groove,

the fixed body includes a fixed body insertion hole,

the rotating body tube is inserted in the fixed body insertion hole so that the rotating body is supported by the fixed body,

a boundary between the tube outer circumferential surface and the rotating body surface is curved, and

a chamfered portion that avoids interference with the boundary is provided at a corner portion of the fixed body surface and an inner wall surface of the fixed body insertion hole.

4. The compressor according to claim 1 further comprising a cylinder portion, wherein

the cylinder portion includes a cylinder inner circumferential surface that cooperates with the rotating body surface and the fixed body surface to define the compression chamber, and accommodates the rotating body and the fixed body,

the vane includes a vane outer end face that is an outer end face in the radial direction of the rotary shaft and contacts the cylinder inner circumferential surface, and a vane inner end face that is an inner end face in the radial direction of the rotary shaft and contacts a groove inner end face that is an inner end face of the vane groove in the radial direction,

the vane inner end face and the groove inner end face are curved in the same direction, and

a curvature of the vane inner end face is smaller than a curvature of the groove inner end face.

5. The compressor according to claim 4, wherein

the vane inner end face includes a first part inner end face that has a curvature smaller than that of the groove inner end face, and a second part inner end face located on a leading side of the first part inner end face in a rotation direction of the rotating body, the second part inner end face having a curvature smaller than that of the first part inner end face.

6. The compressor according to claim 1 further comprising a cylinder portion, wherein

the cylinder portion

includes a cylinder inner circumferential surface that cooperates with the rotating body surface and the fixed body surface to define the compression chamber, and

accommodates the rotating body and the fixed body,

the vane includes a vane outer end face that is an outer end face in the radial direction of the rotary shaft,

the vane outer end face contacts the cylinder inner circumferential surface,

the vane outer end face is curved in the same direction as the cylinder inner circumferential surface, and

a curvature of the vane outer end face is greater than a curvature of the cylinder inner circumferential surface.

7. The compressor according to claim 6, wherein

the vane outer end face includes

a first part outer end face having a curvature greater than that of the cylinder inner circumferential surface, and

a second part outer end face located on a leading side of the first part outer end face in a rotation direction of the rotating body, the second part outer end face having a curvature greater than that of the first part outer end face.

8. The compressor according to claim 1, wherein

the convex surface is configured such that a curvature of a displacement curve in the axial direction of the convex surface inner end in relation to changes in an angle is greater than a curvature of a displacement curve in the axial direction of the convex surface outer end in relation to changes in an angle, and

the concave surface is configured such that a curvature of a displacement curve in the axial direction of the concave surface inner end in relation to changes in an angle is smaller than a curvature of a displacement curve in the axial direction of the concave surface outer end in relation to changes in an angle.

9. A compressor comprising:

a rotary shaft;

a rotating body that is configured to rotate together with the rotary shaft and includes a rotating body surface, which intersects with an axial direction of the rotary shaft, and a vane groove;

a fixed body that is configured not to rotate together with the rotary shaft and includes a fixed body surface, which faces the rotating body surface in the axial direction, and a fixed body insertion hole;

a vane that is inserted in the vane groove and configured to rotate together with the rotating body while moving in the axial direction; and

a compression chamber that is defined by the rotating body surface and the fixed body surface and in which suction and compression of fluid is performed when the vane rotates while moving in the axial direction, wherein

the rotating body includes a rotating body tube in which the rotary shaft is inserted, the rotating body tube having a tube outer circumferential surface, and a rotating body ring portion that is provided on the tube outer circumferential surface to protrude outward in a radial direction of the rotary shaft, the rotating body ring portion including the rotating body surface and the vane groove,

the rotating body tube is inserted in the fixed body insertion hole so that the rotating body is supported by the fixed body,

a boundary between the tube outer circumferential surface and the rotating body surface is curved, and

a chamfered portion that avoids interference with the boundary is provided at a corner portion of the fixed body surface and an inner wall surface of the fixed body insertion hole.