COMPRESSOR

Abstract

A compressor includes a rotary shaft, a rotating body, which rotates together with the rotary shaft, and a fixed body, which does not rotate together with the rotary shaft. The rotating body has a rotating body surface, and the fixed body has a fixed body surface facing the rotating body surface in the axial direction. The compressor includes a vane, which is inserted in a vane groove provided in the rotating body, and a compression chamber, which is defined by the rotating body surface and the fixed body surface. The vane includes a vane body, which is inserted in the vane groove, and a tip seal, which is movable in the axial direction relative to the vane body.

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.

If the vanes are spaced apart from the fixed body surfaces, the fluid may leak through the gap between the vanes and the fixed body surfaces. This increases the loss of the compressor and thus lowers the efficiency.

SUMMARY

It is an objective of the present disclosure to provide a compressor that reduces the likelihood of a gap created between the vanes and the fixed body surfaces.

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 includes a vane body inserted in the vane groove and a sealing member attached to an end face in the axial direction of the vane body so as to be movable in the axial direction relative to the vane body. A back pressure space is located between the sealing member and the vane body. The sealing member is configured to be pressed by the back pressure space toward the fixed body surface so as to be in contact with the fixed body surface.

Other features and aspects will be apparent from the following detailed description, the drawings, and the claims.

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 of the configuration around a vane in the compressor of FIG. 1.

FIG. 10 is a perspective view of a rotating body and vanes of the compressor of FIG. 1.

FIG. 11 is an exploded perspective view of a vane of FIG. 10.

FIG. 12 is a cross-sectional view schematically showing how a vane is in contact with two fixed body surfaces in the compressor of FIG. 1.

FIG. 13 is a cross-sectional view taken along line 13-13 in FIG. 9.

FIG. 14 is a developed view schematically showing the rotating body, the two fixed bodies, and the vanes of the compressor of FIG. 1.

FIG. 15 is a developed view schematically showing the rotating body, the two fixed bodies, and the vanes at a phase different from that in FIG. 14.

FIG. 16 is a cross-sectional view schematically showing how a vane is in contact with two fixed body surfaces according to a second embodiment.

FIG. 17 is a cross-sectional view schematically showing how a vane is in contact with two fixed body surfaces according to a third embodiment.

FIG. 18 is a cross-sectional view schematically showing how a vane is in contact with two fixed body surfaces according to a fourth embodiment.

FIG. 19 is a cross-sectional view schematically showing tip seals of a modification.

FIG. 20 is a cross-sectional view schematically showing a compressor of another 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 side 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 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 are axial ends 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, which is one of the fixed bodies 90 and 110 that is located closer to the front cylinder end wall 31, in other words, closer to the motor chamber A2, 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, which is one of the fixed bodies 90 and 110 that is located closer to the rear plate 40 serving as the defining portion, in other words, located farther 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.

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.

Each front curved surface 103 includes a front concave surface 103a, which is curved in the axial direction Z away from the front rotating body surface 71, and a front convex surface 103b, which is curved in the axial direction Z toward the front rotating body surface 71.

The front concave surface 103a is closer to the first front flat surface 101 than to the second front flat surface 102, and the front convex surface 103b is closer to the second front flat surface 102 than to the first front flat surface 101. The front concave surface 103a is continuous with the front convex surface 103b. That is, the front curved surface 103 has an inflection point.

The angular range of the front convex surface 103b and the angular range of the front concave surface 103a may be the same or different. Further, the position of the inflection point is arbitrary. Since the front curved surface 103 is curved in a wave shape, the front fixed body surface 100 may be considered as a front wavy surface including sections that are curved in a wave shape.

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 compression chambers A4 and A5 face the discharge chamber A1 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 two plate surfaces of the vane 131 face the respective side surfaces of the vane groove 130 in the circumferential direction (i.e., the width direction of the vane groove 130). The width of the vane groove 130 (i.e., the distance between the two side surfaces of the vane groove 130) is the same as or slightly wider than the plate thickness of the vane 131. The vane 131 inserted in the vane groove 130 is sandwiched between the two side surfaces of the vane groove 130. The vane 131 can move in the axial direction Z along the vane groove 130. In the present embodiment, the vane 131, specifically, the two axial ends of the vane 131, is in contact with the fixed body surfaces 100 and 120.

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 between the first rear compression chamber A5a and the second rear compression chamber A5b in the circumferential direction. 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.

That is, the first front compression chamber A4a is configured to be continuous with the front suction port 141 but not with the front discharge ports 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 151.

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.

The vanes 131 will now be described. In the following description, of the two part chambers separated by a vane 131, the part chamber on the trailing side of the vane 131 is referred to as a first part chamber Ax, and the part chamber located on the leading side of the vane 131 is referred to as a second part chamber Ay. For the vane 131 separating the first front compression chamber A4a from the third front compression chamber A4c, the first part chamber Ax is the first front compression chamber A4a, and the second part chamber Ay is the third front compression chamber A4c. For the vane 131 separating the third front compression chamber A4c from the second front compression chamber A4b, the first part chamber Ax is the third front compression chamber A4c, and the second part chamber Ay is the second front compression chamber A4b. For the vane 131 separating the second front compression chamber A4b from the first front compression chamber A4a, the first part chamber Ax is the second front compression chamber A4b, and the second part chamber Ay is the first front compression chamber A4a. The same applies to the rear compression chamber A5.

The pressure in each of the front compression chambers A4a to A4c tends to be higher if the chamber is located on the leading side in the rotation direction M. Specifically, the pressure tends to be the highest in the second front compression chamber A4b (in particular, the space on the trailing side of the area of contact between the front rotating body surface 71 and the second front flat surface 102), followed by the third front compression chamber A4c and the first front compression chamber A4a. For this reason, the pressure of the second part chamber Ay on the leading side of a vane 131 tends to be higher than the pressure of the first part chamber Ax on the trailing side of the vane 131.

As shown in FIGS. 9 to 13, each vane 131 consists of multiple parts. Specifically, the vane 131 includes a vane body 170, which is inserted in a vane groove 130, and two tip seals 180 and 190, which are arranged on the opposite end faces 171, 172 in the axial direction Z of the vane body 170. The tip seals 180 and 190 form the axial ends of the vane 131 and are in contact with the fixed body surfaces 100 and 120, respectively.

The vane body 170 is made of the same material as the rotating body 60 and the fixed bodies 90 and 110. In one example, the vane body 170 is made of metal. The vane body 170 is planar and inserted in a vane groove 130 with its thickness direction extending in the width direction of the vane groove 130. The vane body 170 extends in the axial direction Z and the radial direction R. The vane body 170 is a rectangular plate in the present embodiment, but the vane body 170 may be a plate of any shape. The vane body 170 is received in the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z.

The vane body 170 has two end faces 171 and 172 including body attachment grooves 173 and 174, respectively, which serve as body attachment sections. The body attachment grooves 173 and 174 have a width in the thickness direction of the vane 131, extend in the radial direction R, and open to the inner and outer sides in the radial direction R.

Each body attachment groove 173, 174 has a body groove bottom surface 173a, 174a and a first body groove side surface 173b, 174b and a second body groove side surface 173c, 174c, which extend from the body groove bottom surface 173a, 174a. The first body groove side surface 173b, 174b and the second body groove side surface 173c, 174c intersect with the circumferential direction (in other words, a direction orthogonal to both of the axial direction Z and the radial direction R). These two surfaces face each other and spaced apart from each other in the circumferential direction. The second body groove side surface 173c, 174c is on the leading side of the first body groove side surface 173b, 174b in the rotation direction M. That is, the first body groove side surface 173b, 174b is the side surface on the trailing side of the body attachment groove 173, 174, and the second body groove side surface 173c, 174c is the side surface on the leading side of the body attachment groove 173, 174.

The tip seals 180 and 190 are made of a material that differs from the material of the vane body 170, such as a material that is easier to deform (i.e., softer) than the vane body 170. For example, the tip seals 180 and 190 are made from resin. Each tip seal 180, 190 is in contact with the fixed body surface 100, 120, so that the two part chambers Ax and Ay on the opposite sides in the circumferential direction of the vane 131 are not continuous with each other. In this embodiment, the two tip seals 180 and 190 have the same shape. The areas of contact between the tip seals 180 and 190 and the fixed body surfaces 100 and 120 are referred to as distal end contact areas Pa1 and Pa2, respectively.

As shown in FIGS. 9 to 11, the tip seal 180, 190 may be elongated and extend in the radial direction R. Each tip seal 180, 190 may include a seal body 181, 191, which is in contact with the fixed body surface 100, 120, and a seal attachment protrusion 182, 192, which serves as a seal attachment section attached to the vane body 170.

As shown in FIG. 12, each seal body 181, 191 has a width that is substantially the same as the thickness of the vane body 170 and is sandwiched by the end face 171, 172 of the vane body 170 and the fixed body surface 100, 120 in the axial direction Z. In other words, the seal body 181, 191 is located between the end face 171, 172 of the vane body 170 and the fixed body surface 100, 120.

As shown in FIGS. 11 and 12, each seal body 181, 191 includes a seal surface 181a, 191a, which is a convex surface curved toward the fixed body surface 100, 120, and a seal body bottom surface 181b, 191b, which faces the end face 171, 172 of the vane body 170 in the axial direction Z.

The seal surface 181a, 191a faces the fixed body surface 100, 120 in the axial direction Z. The seal surface 181a, 191a is in contact with the fixed body surface 100, 120. The curvature of the seal surface 181a, 191a is flatter than that of a configuration in which the seal body 181, 191 is semicircular. Specifically, the curvature radius of the seal surface 181a, 191a is greater than half the thickness of the vane 131. However, the present disclosure is not limited to this, and the seal surface 181a, 191a may have any curvature.

The seal surface 181a, 191a extends in the radial direction R and is in contact with the fixed body surface 100, 120 along its entire length in the radial direction R. However, the present disclosure is not limited to this, and the seal body 181, 191 may be in contact with the fixed body surface 100, 120 only partially along its length in the radial direction R.

Each seal attachment protrusion 182, 192 is a ridge that protrudes from the seal body 181, 191 toward the vane body 170, has a width in the thickness direction of the vane 131, and extends in the radial direction R. The seal attachment protrusion 182, 192 includes an attachment distal end face 182a, 192a, a first seal protrusion side surface 182b, 192b, and a second seal protrusion side surface 182c, 192c located on the leading side of the first seal protrusion side surface 182b, 192b. The first seal protrusion side surface 182b, 192b and the second seal protrusion side surface 182c, 192c intersect with the circumferential direction. The first seal protrusion side surface 182b, 192b is the side surface on the trailing side of the seal attachment protrusion 182, 192, and the second seal protrusion side surface 182c, 192c is the side surface on the leading side of the seal attachment protrusion 182, 192.

The seal attachment protrusion 182, 192 is inserted in the body attachment groove 173, 174 so that the tip seal 180, 190 is attached to the vane body 170. The body attachment groove 173, 174, which is a body attachment section, and the seal attachment protrusion 182, 192 face each other in the circumferential direction (i.e., the width direction of the vane groove 130). Specifically, the first body groove side surface 173b, 174b and the first seal protrusion side surface 182b, 192b face each other in the circumferential direction, and the second body groove side surface 173c, 174c and the second seal protrusion side surface 182c, 192c face each other in the circumferential direction. The tip seals 180 and 190 can move toward and away from the vane body 170 in the axial direction Z. That is, the tip seals 180 and 190 are attached to the vane body 170 so as to be movable in the axial direction Z relative to the vane body 170.

The tip seals 180 and 190 are movable in the axial direction Z relative to the vane body 170, and the vane 131 includes the vane body 170 and the tip seals 180 and 190. As such, the vane 131 may be considered as extendable in the axial direction Z.

As shown in FIGS. 11 and 12, a back pressure space 183, 193, which is provided between the vane body 170 and the tip seal 180, 190, pushes the tip seal 180, 190 toward the fixed body surface 100, 120.

The front back pressure space 183 is defined by the front attachment distal end face 182a, the front body groove bottom surface 173a, the front first body groove side surface 173b, and the front second body groove side surface 173c. The width of the front seal attachment protrusion 182 is the same as or slightly smaller than the width of the front body attachment groove 173. Thus, the gap between the front seal attachment protrusion 182 and the front body attachment groove 173 allows the fluid to enter the front back pressure space 183. The same applies to the rear back pressure space 193.

As shown in FIGS. 11 and 12, the compressor 10 has introduction grooves 184 and 194 that introduce the fluid into the back pressure spaces 183 and 193 from the second part chamber Ay.

Each tip seal 180, 190 has introduction grooves 184, 194. The tip seal 180, 190 includes multiple (two in this embodiment) introduction grooves 184, 194, which are spaced apart from each other in the radial direction R. However, the number of the introduction grooves 184, 194 is arbitrary, and may be one or three or more.

As shown in FIG. 12, the introduction grooves 184, 194 extend along the seal body 181, 191 and the seal attachment protrusion 182, 192. Specifically, each introduction groove 184, 194 extends along the second seal protrusion side surface 182c, 192c and a section of the seal body bottom surface 181b, 191b located on the leading side of the seal attachment protrusion 182, 192.

Each front introduction groove 184 is provided on the leading side of the front tip seal 180 and opens to the second part chamber Ay, which is located on the leading side. Likewise, each rear introduction groove 194 is provided on the leading side of the rear tip seal 190 and opens to the second part chamber Ay. This allows the fluid in the second part chamber Ay to flow easily into the back pressure spaces 183 and 193 through the introduction grooves 184 and 194.

In this configuration, the fluid in each back pressure space 183, 193 pushes the tip seal 180, 190 toward the fixed body surface 100, 120, reducing the likelihood of a gap created between the tip seal 180, 190 and the fixed body surface 100, 120.

Specifically, even in a configuration in which the rotating body 60 is supported by the two fixed bodies 90 and 110 with the rotating body tube 61, dimensional or assembly errors in the manufacturing of the rotating body 60 and the fixed bodies 90 and 110 can result in a gap created between a vane 131 and at least one of the two fixed body surfaces 100 and 120. Such a gap can be created over the entire angular range in which the vane 131 rotates, or only in a specific angular range.

In the present embodiment, as shown in FIG. 12, when the vane bodies 170 rotate together with the rotating body 60, the vane bodies 170 push the tip seals 180 and 190 in the rotation direction M. This brings each first seal protrusion side surface 182b, 192b, which is the side surface on the trailing side of the seal attachment protrusion 182, 192, into contact with the first body groove side surface 173b, 174b, which is the side surface on the trailing side of the body attachment groove 173, 174, in the circumferential direction. This area of contact (hereinafter referred to as a “side surface contact area Pb1, Pb2”) provides sealing, thereby reducing the possibility that the fluid moves through between each tip seal 180, 190 and the vane body 170 and thus between the two part chambers Ax and Ay.

In particular, each side surface contact area Pb1, Pb2 of the present embodiment extends in the axial direction Z. This helps to maintain the contact between the first seal protrusion side surface 182b, 192b and the first body groove side surface 173b, 174b even when the tip seal 180, 190 moves in the axial direction Z relative to the vane body 170.

Since the body attachment groove 173, 174 forms the body attachment section, the side surface contact area Pb1, Pb2 may be considered as an area of contact between the body attachment section and the seal attachment protrusion 182, 192.

On the other hand, a clearance is provided on the leading side in the rotation direction M. Specifically, a clearance is provided between each second seal protrusion side surface 182c, 192c and the second body groove side surface 173c, 174c. As indicated by the long dashed double-short dashed lines in FIG. 12, the clearance introduces the fluid into the back pressure space 183, 193 from the second part chamber Ay. In particular, in the present embodiment, the introduction grooves 184, 194 facilitate the flow of fluid from the second part chamber Ay into the back pressure space 183, 193.

The fluid flowing into the back pressure space 183, 193 pushes the tip seal 180, 190 toward the fixed body surface 100, 120. This maintains the contact and thus the sealing between the tip seal 180, 190 (specifically, the seal surface 181a, 191a) and the fixed body surface 100, 120. A gap is therefore unlikely to be created between the tip seal 180, 190 and the fixed body surface 100, 120.

The depth of the body attachment groove 173, 174 may be greater than the protruding amount of the seal attachment protrusion 182, 192. This maintains the back pressure space 183, 193 even when the seal body bottom surface 181b, 191b is in contact with the end face 171, 172, aspaceing the problem that the back pressure space 183, 193 disappears. However, the depth of the body attachment groove 173, 174 is not limited to this, and may be less than or equal to the protruding amount of the seal attachment protrusion 182, 192.

As shown in FIGS. 9 and 13, each vane 131 includes a vane outer end face 201 and a vane inner end face 202, which are the two end faces in the radial direction R. Of the two end faces in the radial direction R, the vane outer end face 201 is on the outer side in the radial direction R (located radially outward), and the vane inner end face 202 is on the inner side in the radial direction R (located radially inward).

The vane outer end face 201 includes the outer end face of the vane body 170 and the outer end faces of the two tip seals 180 and 190. The outer end face of the vane body 170 and the outer end faces of the two tip seals 180 and 190 are continuous in the axial direction Z and flush with one another. The vane outer end face 201 is thus a single plane.

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 is 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.

As shown in FIG. 13, the vane outer end face 201 may be a convex surface curved radially outward so as to be continuous with the ring outer circumferential surface 73 in the circumferential direction. The curvature of the vane outer end face 201 is preferably the same as that of the front cylinder inner circumferential surface 33. That is, the vane outer end face 201 is preferably in planar contact with the front cylinder inner circumferential surface 33. However, the vane outer end face 201 may have other shapes.

In the same manner as the vane outer end face 201, each vane inner end face 202 includes the inner end face of the vane body 170 and the inner end faces of the two tip seals 180 and 190. The inner end face of the vane body 170 and the inner end faces of the two tip seals 180 and 190 are continuous in the axial direction Z and flush with one another. The vane inner end face 202 is thus a single plane.

As shown in FIG. 13, the vane inner end face 202 is a concave surface curved radially outward. The curvature of the vane inner end face 202 is preferably the same as that of the tube outer circumferential surface 62. That is, the vane inner end face 202 is preferably in planar contact with the tube outer circumferential surface 62. However, the vane inner end face 202 may have other shapes.

Referring to FIGS. 14 and 15, the sequence of operations of the compressor 10 will now be described. FIGS. 14 and 15 are developed views schematically showing the rotating body 60, the fixed bodies 90 and 110, and the vanes 131. FIGS. 14 and 15 show the rotating body 60 and the vanes 131 at different phases. The ports 141, 142, 151 and 161 are shown schematically in FIGS. 14 and 15.

As shown in FIGS. 14 and 15, 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. 14 and 15, 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.

(1-1) The compressor 10 includes the rotary shaft 12, the rotating body 60, which rotates together with the rotary shaft 12, the fixed bodies 90 and 110, which do not rotate together with the rotary shaft 12, and the vanes 131, which are inserted in the vane grooves 130 provided in the rotating body 60 and rotate while moving in the axial direction Z as the rotating body 60 rotates. The rotating body 60 has the rotating body surfaces 71 and 72 intersecting with the axial direction Z. The fixed bodies 90 and 110 have the fixed body surfaces 100 and 120, which face the respective rotating body surfaces 71 and 72 in the axial direction Z. The compressor 10 includes the compression chambers A4 and A5 defined by the rotating body surfaces 71 and 72 and the fixed body surfaces 100 and 120. The vanes 131 rotate while moving in the axial direction Z, causing the suction and compression of fluid in the compression chambers A4 and A5.

Each vane 131 includes the vane body 170, which is inserted in a vane groove 130, and the tip seals (sealing members) 180 and 190, which are attached to the respective end faces 171, 172 of the vane body 170 in the axial direction Z so as to be movable in the axial direction Z relative to the vane body 170. The fluid (pressure) in each back pressure space 183, 193, which is provided between the vane body 170 and the tip seal 180, 190, pushes the tip seal 180, 190 toward the fixed body surface 100, 120 so that the tip seal 180, 190 is in contact with the fixed body surface 100, 120.

The tip seal 180, 190, which is pressed by the fluid (pressure) in the back pressure space 183, 193 and thus in contact with the fixed body surface 100, 120, ensures the sealing between the vane 131 and the fixed body surface 100, 120. A gap is therefore unlikely to be created between the vane 131 and each fixed body surface 100, 120.

(1-2) The front compression chamber A4 includes the first part chamber Ax and the second part chamber Ay located on the opposite sides of each vane 131 in the circumferential direction. The first part chamber Ax is located on the trailing side of the vane 131, and the second part chamber Ay is located on the leading side of the vane 131. Each end face 171, 172 of the vane body 170 has the body attachment groove 173, 174, which is a body attachment section. Each tip seal 180, 190 includes the seal attachment protrusion 182, 192, which is attached to the body attachment groove 173, 174. The seal attachment protrusion 182, 192 and the body attachment groove 173, 174 (specifically, the first body groove side surface 173b, 174b) face each other in the circumferential direction of the rotary shaft 12.

In this configuration, when the vane 131 (specifically, the vane body 170) rotates together with the rotating body 60, the seal attachment protrusion 182, 192 comes into contact with the body attachment groove 173, 174 in the circumferential direction. This area of contact, which is the side surface contact area Pb1, Pb2, ensures the sealing between the vane body 170 and the tip seal 180, 190, thereby limiting movement of fluid between the two part chambers Ax and Ay through the back pressure space 183, 193.

(1-3) The present embodiment uses the body attachment grooves 173 and 174, which are provided in the end faces 171 and 172 of the vane body 170, as body attachment sections. Each body attachment groove 173, 174 includes the first body groove side surface 173b, 174b, which is on the trailing side, and the second body groove side surface 173c, 174c, which is on the leading side.

Each tip seal 180, 190 has the seal body 181, 191, which is in contact with the fixed body surface 100, 120. The seal attachment protrusion 182, 192 protrudes from the seal body 181, 191 toward the end face 171, 172 of the vane body 170. The seal attachment protrusion 182, 192 includes the first seal protrusion side surface 182b, 192b, which is on the trailing side, and the second seal protrusion side surface 182c, 192c, which is on the leading side.

The tip seal 180, 190 is attached to the vane body 170 by inserting the seal attachment protrusion 182, 192 into the body attachment groove 173, 174. The first seal protrusion side surface 182b, 192b and the first body groove side surface 173b, 174b face each other in the circumferential direction.

In this configuration, the seal attachment protrusion 182, 192 is inserted in the body attachment groove 173, 174 so that the tip seal 180, 190 is attached to the vane body 170. As such, the rotation of the vane 131 (specifically, the vane body 170) brings the first seal protrusion side surface 182b, 192b into contact with the first body groove side surface 173b, 174b in the circumferential direction. This area of contact, which is the side surface contact area Pb1, Pb2, ensures the sealing between the vane body 170 and the tip seal 180, 190.

In the present embodiment, each side surface contact area Pb1, Pb2 extends in the axial direction Z. Thus, the contact between the first seal protrusion side surface 182b, 192b and the first body groove side surface 173b, 174b is likely to be maintained even when the tip seal 180, 190 moves toward the fixed body surface 100, 120. This limits leakage of fluid through the back pressure spaces 183 and 193 and removal of the tip seals 180 and 190.

(1-4) The contact between the first seal protrusion side surface 182b, 192b and the first body groove side surface 173b, 174b increases the likelihood that a clearance will separate the second seal protrusion side surface 182c, 192c from the second body groove side surface 173c, 174c. This clearance facilitates the flow of fluid into the back pressure space 183, 193 from the second part chamber Ay. The fluid in the second part chamber Ay tends to have a higher pressure than the fluid in the first part chamber Ax. For example, as for the vane 131 separating the third front compression chamber A4c from the second front compression chamber A4b, the second front compression chamber A4b has a higher pressure. This increases the force of the fluid pushing the tip seals 180 and 190 in the back pressure spaces 183 and 193. The sealing between the vane 131 and the fixed body surfaces 100 and 120 is thus enhanced.

(1-5) Each tip seal 180, 190 includes the introduction grooves 184, 194 for introducing the fluid into the back pressure space 183, 193 from the second part chamber Ay.

In this configuration, the introduction grooves 184 and 194 facilitate the introduction of the fluid into the back pressure spaces 183 and 193 from the second part chamber Ay. As such, the fluid in the second part chamber Ay, which tends to have a relatively high pressure, pushes each tip seal 180, 190 toward the fixed body surface 100, 120. This further enhances the sealing between the vane 131 and the fixed body surfaces 100 and 120.

(1-6) The introduction grooves 184, 194 are located closer to the second part chamber Ay than the side surface contact area Pb1, Pb2. The side surface contact area Pb1, Pb2 limits leakage of the fluid in the back pressure space 183, 193, which is introduced through the introduction grooves 184, 194, into the first part chamber Ax. This helps to solve the problem that the introduction grooves 184, 194 can cause leakage of fluid from the second part chamber Ay into the first part chamber Ax.

(1-7) Each introduction groove 184, 194 extends along the second seal protrusion side surface 182c, 192c and a section of the seal body bottom surface 181b, 191b that is on the leading side of the seal attachment protrusion 182, 192.

In this configuration, even if the seal body bottom surface 181b, 191b is in contact with the end face 171, 172 of the vane body 170, the fluid in the second part chamber Ay can still flow into the back pressure space 183, 193.

Second Embodiment

As shown in FIG. 16, in this embodiment, the first body groove side surfaces 212 and 215 and the second body groove side surfaces 213 and 216 are tilted with respect to the axial direction Z such that the body attachment grooves 211 and 214 become gradually narrower as they deepen. In the present embodiment, each first body groove side surface 212, 215 is displaced gradually toward the leading side in the rotation direction M as the body attachment groove 211, 214 deepens from the end face 171, 172 of the vane body 170 (in other words, as it extends toward the body groove bottom surface 173a, 174a).

In accordance with the body attachment groove 211, 214 becoming gradually narrower as it deepens, the seal attachment protrusion 221, 224 becomes gradually narrower from the proximal end to the distal end. Specifically, in accordance with the inclination of the first body groove side surface 212, 215 and the second body groove side surface 213, 216, the first seal protrusion side surface 222, 225 and the second seal protrusion side surface 223, 226 are tilted with respect to the axial direction Z. The first seal protrusion side surface 222, 225 is displaced gradually toward the leading side in the rotation direction M from the proximal end to the distal end.

The first seal protrusion side surface 222, 225 and the first body groove side surface 212, 215 face each other in the circumferential direction. In this embodiment, these side surfaces are inclined at the same angle. Likewise, the second seal protrusion side surface 223, 226 and the second body groove side surface 213, 216 face each other in the circumferential direction. In this embodiment, these side surfaces are inclined at the same angle.

In this configuration, when the vane 131 (specifically, the vane body 170) rotates together with the rotating body 60, each first seal protrusion side surface 222, 225 is brought into contact with the first body groove side surface 212, 215 in the circumferential direction. Accordingly, the side surface contact area Pb1, Pb2 is tilted with respect to the axial direction Z.

In the same manner as the first embodiment, the back pressure space 183, 193 is created between the tip seal 180, 190 and the vane body 170. The back pressure space 183, 193 pushes the tip seal 180, 190 toward the fixed body surface 100, 120.

The present embodiment has the following advantages.

(2-1) Each first body groove side surface 212, 215 is tilted with respect to the axial direction Z so as to be displaced gradually toward the leading side in the rotation direction M as the body attachment groove 211, 214 deepens. The first seal protrusion side surface 222, 225 is tilted with respect to the axial direction Z so as to be displaced gradually toward the leading side in the rotation direction M from the proximal end to the distal end. The first body groove side surface 212, 215 and the first seal protrusion side surface 222, 225 face each other in the circumferential direction.

In this configuration, when the vane body 170 rotates together with the rotating body 60, the first seal protrusion side surface 222, 225 is brought into contact with the first body groove side surface 212, 215, and the area of contact, which is the side surface contact area Pb1, Pb2, receives a pushing force F1, F2 acting in a direction orthogonal to the side surface contact area Pb1, Pb2.

The side surface contact area Pb1, Pb2 is tilted with respect to the axial direction Z so as to be displaced gradually toward the leading side in the rotation direction M as it extends away from the fixed body surface 100, 120. As such, the pushing force F1, F2 includes a component in the axial direction Z, specifically, a component in the direction toward the fixed body surface 100, 120. This pushes the tip seal 180, 190 toward the fixed body surface 100, 120, thereby enhancing the sealing at the distal end contact area Pa1, Pa2.

In the present embodiment, the second seal protrusion side surface 223, 226 and the second body groove side surface 213, 216 are tilted with respect to the axial direction Z, but these surfaces may be inclined in the same direction and at the same angle as the first seal protrusion side surface 222, 225 and the first body groove side surface 212, 215. In this case, the width of the body attachment groove 211, 214 and the width of the seal attachment protrusion 221, 224 are uniform. The second seal protrusion side surface 223, 226 and the second body groove side surface 213, 216 may be parallel to the axial direction Z. That is, the second seal protrusion side surface 223, 226 and the second body groove side surface 213, 216 may have any configurations.

Third Embodiment

As shown in FIG. 17, in this embodiment, the seal attachment protrusions 182 and 192 and the body attachment grooves 173 and 174 are closer to the first part chamber Ax than to the second part chamber Ay. Specifically, the center line passing through the circumferential center of the seal attachment protrusion 182, 192 and the body attachment groove 173, 174 is at a position displaced from the center line passing through the circumferential center of the tip seal 180, 190 toward the first part chamber Ax (in other words, at a position displaced toward the trailing side). In the present embodiment, the side surface contact area Pb1, Pb2 corresponds to the “area of contact between two attachment sections.”

The operation of the present embodiment will now be described.

As shown in FIG. 17, each tip seal 180, 190 receives a first pushing force Ff1, Fr1, which is applied by the fluid in the first part chamber Ax, and a second pushing force Ff2, Fr2, which is applied by the fluid in the second part chamber Ay. The first pushing force Ff1, Fr1 acts in a direction orthogonal to the line connecting the distal end contact area Pa1, Pa2 to the edge of the side surface contact area Pb1, Pb2 that is closer to the seal body bottom surface 181b, 191b. The second pushing force Ff2, Fr2 acts in a direction orthogonal to the line connecting the distal end contact area Pa1, Pa2 to the edge of the side surface contact area Pb1, Pb2 that is closer to the body groove bottom surface 173a, 174a. The second pushing force Ff2, Fr2 is likely to be larger than the first pushing force Ff1, Fr1.

Since the second pushing force Ff2, Fr2 differs from the first pushing force Ff1, Fr1 in magnitude and direction, there is an imbalance between these forces. Each tip seal 180, 190 receives the resultant of the first pushing force Ff1, Fr1 and the second pushing force Ff2, Fr2.

With this configuration, the inventors of the present application have found that each tip seal 180, 190 receives a pushing force acting in a direction away from the fixed body surface 100, 120 when the distal end contact area Pa1, Pa2, which is the area of contact between the seal surface 181a, 191a and the fixed body surface 100, 120, is closer to the first part chamber Ax than the side surface contact area Pb1, Pb2, in other words, when the distal end contact area Pa1, Pa2 is on the trailing side of the side surface contact area Pb1, Pb2 in the rotation direction M.

For example, as shown in the front part of FIG. 17, when the front tip seal 180 is in contact with the front curved surface 103 inclined upward with respect to the rotation direction M, the front distal end contact area Pa1 is likely to be positioned on the leading side in the rotation direction M of the front side surface contact area Pb1. Accordingly, the resultant of the front first pushing force Ff1 and the front second pushing force Ff2 is likely to act in the direction toward the front fixed body surface 100. This helps to push the front tip seal 180 toward the front fixed body surface 100, enhancing the sealing at the front distal end contact area P1a.

In contrast, at the rear side, the rear tip seal 190 is in contact with the rear curved surface 123 inclined downward with respect to the rotation direction M. Consequently, the rear distal end contact area Pa2 is likely to be positioned on the trailing side of the center in the width direction of the rear seal surface 191a. For this reason, the rear distal end contact area Pa2 can be positioned on the trailing side of the rear side surface contact area Pb2. In this case, the resultant of the first rear pushing force Fr1 and the second rear pushing force Fr2 is likely to act in a direction away from the rear fixed body surface 120.

In this respect, as shown in FIG. 17, the rear seal attachment protrusion 192 and the rear body attachment groove 174 of the present embodiment are arranged to be closer to the first part chamber Ax, so that the rear side surface contact area Pb2 is positioned near the first part chamber Ax. Accordingly, the rear distal end contact area Pa2 is less likely to be positioned on the trailing side of the rear side surface contact area Pb2, reducing the likelihood that the component in the axial direction Z in the resultant of the first rear pushing force Fr1 and the second rear pushing force Fr2 will act in a direction away from the rear fixed body surface 120. Further, even if the rear distal end contact area Pa2 is positioned on the trailing side of rear side surface contact area Pb2, the distance between these areas in the circumferential direction and therefore the component of the force acting in a direction away from the rear fixed body surface 120 would be small. This limits separation of the rear tip seal 190 from the rear fixed body surface 120.

The present embodiment has the following advantages.

(3-1) Each fixed body surface 100, 120 is a ring-shaped surface and includes the second flat surface 102, 122, which is a fixed body contact surface in contact with the rotating body surface 71, 72, and the two curved surfaces 103, 123 located on the opposite sides in the circumferential direction of the second flat surface 102, 122. The two curved surfaces 103, 123 are curved in the axial direction Z such that the distance to the rotating body surface 71, 72 gradually increases as the curved surfaces 103, 123 extend away from the second flat surface 102, 122 in the circumferential direction. The seal attachment protrusion 182, 192 and the body attachment groove 173, 174 are closer to the first part chamber Ax than to the second part chamber Ay. In other words, the seal attachment protrusion 182, 192 and the body attachment groove 173, 174 are displaced from the circumferential center of the tip seal 180, 190 toward the trailing side.

As such, the side surface contact area Pb1, Pb2 is displaced toward the trailing side, reducing the likelihood that the distal end contact area Pa1, Pa2 will be located on the trailing side of the side surface contact area Pb1, Pb2. Further, even if the distal end contact area Pa1, Pa2 is positioned on the trailing side of the side surface contact area Pb1, Pb2, the distance between these contact areas would be small. This prevents or reduces the force acting on the tip seal 180, 190 in a direction away from the fixed body surface 100, 120. Accordingly, when the tip seal 180, 190 moves along the curved surface 103, 123 inclined downward with respect to the rotation direction M, the sealing at the distal end contact area Pa1, Pa2 is less likely to decrease.

Fourth Embodiment

The fourth embodiment will now be described. The fourth embodiment differs from the first embodiment in the attachment configuration between the vane body and the tip seal.

As shown in FIG. 18, in this embodiment, each seal body 181, 191 has a seal attachment groove 231, 234, which is recessed toward the fixed body surface 100, 120 from the seal body bottom surface 181b, 191b. The seal attachment groove 231, 234, which serves as a seal attachment section, may have a width in the thickness direction of the vane 131 and extend in the radial direction R. Each seal attachment groove 231, 234 has a first seal groove side surface 232, 235, which is on the trailing side in the rotation direction M, and a second seal groove side surface 233, 236, which is on the leading side in the rotation direction M. The second seal groove side surface 233, 236 is tilted with respect to the axial direction Z so as to be displaced gradually toward the trailing side as the seal attachment groove 231, 234 deepens.

Each vane body 170 has body attachment protrusions 241 and 244 protruding from the respective end faces 171 and 172 of the vane body 170 toward the fixed body surfaces 100 and 120. Each body attachment protrusion 241, 244, which serves as a body attachment section, may be a ridge that has a width in the thickness direction of the vane 131 and extends in the radial direction R. The body attachment protrusion 241, 244 has a first body protrusion side surface 242, 245, which is on the trailing side in the rotation direction M, and a second body protrusion side surface 243, 246, which is on the leading side in the rotation direction M.

The second body protrusion side surface 243, 246 is tilted with respect to the axial direction Z so as to be displaced gradually toward the trailing side from the proximal end to the distal end of the body attachment protrusion 241, 244.

The body attachment protrusion 241, 244 is a part of the vane body 170. The body attachment protrusion 241, 244 is made of a material harder than the tip seal 180, 190, such as metal.

In this configuration, each body attachment protrusion 241, 244 is inserted in the seal attachment groove 231, 234 so that the tip seal 180, 190 is attached to the vane body 170. The first seal groove side surface 232, 235 and the first body protrusion side surface 242, 245 face each other in the circumferential direction, and the second seal groove side surface 233, 236 and the second body protrusion side surface 243, 246 face each other in the circumferential direction. Consequently, when the vane body 170 rotates together with the rotating body 60, the second body protrusion side surface 243, 246, which is the side surface on the leading side of the body attachment protrusion 241, 244, is brought into contact with the second seal groove side surface 233, 236, which is the side surface on the leading side of the seal attachment groove 231, 234, in the circumferential direction. This area of contact (specifically, the side surface contact area Pb1, Pb2) provides sealing and blocks the fluid.

In the same manner as the first embodiment, the back pressure space 183, 193 is created between each tip seal 180, 190 and the vane body 170. The back pressure space 183, 193 pushes the tip seal 180, 190 to the fixed body surface 100, 120.

The present embodiment has the following advantages.

(4-1) The tip seals 180 and 190 are made of a softer material than the vane body 170. Each tip seal 180, 190 has the seal body 181, 191, which is in contact with the fixed body surface 100, 120. The seal body 181, 191 has the seal body bottom surface 181b, 191b, which faces the end face 171, 172 of the vane body 170. Further, the tip seal 180, 190 has the seal attachment groove 231, 234, which is recessed from the seal body bottom surface 181b, 191b. The vane body 170 has the body attachment protrusion 241, 244 protruding from each end face 171, 172 of the vane body 170. The body attachment protrusion 241, 244 is inserted in the seal attachment groove 231, 234 so that the tip seal 180, 190 is attached to the vane body 170.

In this configuration, the body attachment protrusion 241, 244 is inserted in the seal attachment groove 231, 234 so that the tip seal 180, 190 is attached to the vane body 170. This configuration reduces removal of the tip seals 180 and 190, as compared to the first embodiment in which the seal attachment protrusions 182 and 192 are inserted in the respective body attachment grooves 173 and 174.

Specifically, in a configuration in which each seal attachment protrusion 182, 192 is inserted in the body attachment groove 173, 174 as in the first embodiment, the seal attachment protrusion 182, 192 may fail to have a high rigidity and thus deform, resulting in removal of the tip seal 180, 190 from the vane body 170.

The tip seal 180, 190, which serves as a sealing member, is made of a soft material that easily deforms to increase the sealing performance. For this reason, the tip seal 180, 190 is likely to have a low rigidity, which may result in the removal.

In contrast, the present embodiment inserts each body attachment protrusion 241, 244 of the vane body 170 into the seal attachment groove 231, 234. The body attachment protrusion 241, 244 is a part of the vane body 170, which is harder than the tip seals 180 and 190, and thus resists deformation as compared to the tip seals 180 and 190 (the seal attachment protrusions 182 and 192). Further, as compared to the configuration including the seal attachment protrusions 182 and 192, the configuration including the seal attachment grooves 231 and 234 allows the tip seals 180 and 190 to have a higher rigidity. This reduces the problem that the tip seals 180 and 190 are deformed and removed from the vane body 170.

(4-2) Each seal attachment groove 231, 234 has the first seal groove side surface 232, 235 on the trailing side and the second seal groove side surface 233, 236 on the leading side. Each body attachment protrusion 241, 244 has the first body protrusion side surface 242, 245 on the trailing side and the second body protrusion side surface 243, 246 on the leading side. The second body protrusion side surface 243, 246 and the second seal groove side surface 233, 236 face each other in the circumferential direction.

The second seal groove side surface 233, 236 is tilted with respect to the axial direction Z so as to be displaced gradually toward the trailing side as the seal attachment groove 231, 234 deepens. The second body protrusion side surface 243, 246 is tilted with respect to the axial direction Z so as to be displaced gradually toward the trailing side from the proximal end to the distal end of the body attachment protrusion 241, 244.

In this configuration, when the vane body 170 rotates together with the rotating body 60, each second body protrusion side surface 243, 246 is brought into contact with the second seal groove side surface 233, 236. Through this area of contact, which is the side surface contact area PM, Pb2, the tip seal 180, 190 receives the pushing force F1, F2 including a component acting in the direction toward the fixed body surface 100, 120. The pushing force F1, F2 pushes the tip seal 180, 190 against the fixed body surface 100, 120, thereby enhancing the sealing at the distal end contact area Pa1, Pa2.

The embodiments described above may be modified as follows. The embodiments and the following modifications may be combined to the extent that does not cause technical contradiction.

As shown in FIG. 19, in the configuration in which each body attachment groove 173, 174 is provided at the circumferential center (the center in the width direction) of the vane body 170, the width D1, D2 of the body attachment groove 173, 174 may be greater than half the vane width D0, which is the width of the vane 131. In this case, the width of the seal attachment protrusion 182, 192 may be increased according to the body attachment groove 173, 174.

In this configuration, the increased width D1, D2 of the body attachment groove 173, 174 allows the side surface contact area Pb1, Pb2 to be closer to the first part chamber Ax accordingly. This configuration thus has Advantage (3-1) described above.

The introduction grooves 184 and 194 may be provided in the vane body 170 instead of the tip seals 180 and 190, or may be provided in both of the tip seals 180 and 190 and the vane body 170. That is, any configuration may be used as long as an introduction groove 184, 194 is provided in at least one of the tip seal 180, 190 and the vane body 170.

The introduction grooves 184 and 194 may be omitted.

The shape and the position of the tip seals 180 and 190 may be changed freely as long as they are attached to the vane body 170 so as to be movable in the axial direction Z.

One of the tip seals 180 and 190 may be omitted. That is, the tip seal may be provided only on one of the front side and the rear side. In this case, the end of the vane body 170 that does not include a tip seal preferably has a seal surface that is in contact with a fixed body surface. That is, the vane 131 may be composed of two parts of a vane body and one tip seal.

As long as the seal attachment protrusion 182, 192 and the body attachment groove 173, 174 face each other, they may be in contact with each other in the circumferential direction or spaced apart from each other when the rotating body 60 is not rotating. The same applies to the body attachment protrusions 241 and 244 and the seal attachment grooves 231 and 234.

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 may be considered as the cylinder portion accommodating the rotating body and the fixed bodies, and the inner circumference surface of the rear housing member 22 may be considered as the cylinder inner surface defining the compression chambers together with the rotating body surfaces and the fixed body surfaces. 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 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 shown in FIG. 20, 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 FIG. 20, each vane 131 has the rear tip seal 190, but the rear tip seal 190 may be omitted.

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.

The fixed body contact surface may be omitted. For example, a small gap may separate the second front flat surface 102 from the front rotating body surface 71.

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.

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 includes a vane body inserted in the vane groove, and a sealing member attached to an end face in the axial direction of the vane body so as to be movable in the axial direction relative to the vane body,

a back pressure space is located between the sealing member and the vane body, and

the sealing member is configured to be pressed by the back pressure space toward the fixed body surface so as to be in contact with the fixed body surface.

2. The compressor according to claim 1, wherein

the compression chamber includes a first part chamber located on a trailing side of the vane in a rotation direction of the rotating body, and a second part chamber located on a leading side of the vane in the rotation direction,

the sealing member includes a seal attachment section attached to a body attachment section located in the end face of the vane body, and

the body attachment section and the seal attachment section face each other in a circumferential direction of the rotary shaft.

3. The compressor according to claim 2, wherein

the body attachment section is a body attachment groove that is located in the end face of the vane body, has a width in a thickness direction of the vane, and extends in a radial direction of the rotary shaft,

the body attachment groove includes a first body groove side surface and a second body groove side surface, which is on the leading side of the first body groove side surface in the rotation direction,

the sealing member includes a seal body that is in contact with the fixed body surface,

the seal attachment section is a seal attachment protrusion that protrudes from the seal body toward the end face of the vane body,

the seal attachment protrusion includes a first seal protrusion side surface and a second seal protrusion side surface, which is on the leading side of the first seal protrusion side surface in the rotation direction,

the seal attachment protrusion is inserted in the body attachment groove so that the sealing member is attached to the vane body, and

the first seal protrusion side surface and the first body groove side surface face each other in the circumferential direction.

4. The compressor according to claim 3, wherein at least one of the vane body and the sealing member has an introduction groove configured to introduce fluid into the back pressure space from the second part chamber.

5. The compressor according to claim 3, wherein

the first body groove side surface is tilted with respect to the axial direction so as to be displaced gradually toward the leading side in the rotation direction as the body attachment groove deepens, and

the first seal protrusion side surface is tilted with respect to the axial direction so as to be displaced gradually toward the leading side in the rotation direction from a proximal end to a distal end of the seal attachment protrusion.

6. The compressor according to claim 3, wherein

the fixed body surface includes a fixed body contact surface that is in contact with the rotating body surface; and two curved surfaces that are located on opposite sides of the fixed body contact surface in the circumferential direction and curved in the axial direction such that a distance to the rotating body surface gradually increases as the curved surfaces extend away from the fixed body contact surface in the circumferential direction, and

the body attachment groove and the seal attachment protrusion are closer to the first part chamber than to the second part chamber so that a side surface contact area, which is an area of contact between the first seal protrusion side surface and the first body groove side surface, is closer to the first part chamber than to the second part chamber.

7. The compressor according to claim 2, wherein

the sealing member is made of a material softer than the vane body,

the sealing member has a seal body that is in contact with the fixed body surface,

the seal body has a seal body bottom surface that faces the end face of the vane body,

the seal attachment section is a seal attachment groove recessed from the seal body bottom surface,

the body attachment section is a body attachment protrusion protruding from the end face of the vane body, and

the body attachment protrusion is inserted in the seal attachment groove so that the sealing member is attached to the vane body.

8. The compressor according to claim 7, wherein

the seal attachment groove includes a first seal groove side surface and a second seal groove side surface, which is located on the leading side of the first seal groove side surface in the rotation direction,

the body attachment protrusion includes a first body protrusion side surface and a second body protrusion side surface, which is located on the leading side of the first body protrusion side surface in the rotation direction,

the second seal groove side surface is tilted with respect to the axial direction so as to be displaced gradually toward the trailing side in the rotation direction as the seal attachment groove deepens,

the second body protrusion side surface is tilted with respect to the axial direction so as to be displaced gradually toward the trailing side from a proximal end to a distal end of the body attachment protrusion, and

the second body protrusion side surface and the second seal groove side surface face each other in the circumferential direction.