CN111536037A - Compressor with a compressor housing having a plurality of compressor blades - Google Patents

Abstract

A compressor is provided with a rotating shaft, a rotating body that rotates in accordance with the rotation of the rotating shaft, and a fixed body that does not rotate in accordance with the rotation of the rotating 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 inserted into a vane groove formed in the rotating body, and a compression chamber defined by the rotating body surface and the fixed body surface. The blade includes a blade body inserted into the blade groove, and a blade end seal movable in an axial direction with respect to the blade body.

Description

Compressor with a compressor housing having a plurality of compressor blades

Technical Field

The present disclosure relates to compressors.

Background

Jp 2015-14250 a describes an axial vane compressor including a rotary shaft, a cylindrical rotor having a plurality of slits formed therein, a plurality of vanes swingably fitted into the slits, and a side plate having a cam surface formed therein. The cam surface is formed on a fixing body surface of a side plate as a fixing body. In the axial vane compressor described in this publication, the plurality of vanes rotate while moving in the axial direction of the rotating shaft in accordance with the rotation of the rotating shaft and the rotor. Thereby, the fluid is sucked and compressed in the compression chamber defined by the axial end surface of the rotor and the cam surface.

Disclosure of Invention

Problems to be solved by the invention

When the blade is separated from the fixed body surface, the fluid may leak through a gap between the blade and the fixed body surface. In this case, the loss of the compressor increases, and the efficiency decreases.

The purpose of the present disclosure is to provide a compressor capable of suppressing the occurrence of a gap between a blade and a fixed body surface.

Means for solving the problems

In one aspect of the present disclosure, a compressor includes: a rotating shaft; a rotating body configured to rotate in accordance with rotation of the rotating shaft; and a fixed body configured to rotate without accompanying rotation of the rotating shaft. The rotating body has a rotating body surface intersecting with an axial direction of the rotating shaft, and a blade groove. The fixed body has a fixed body surface facing the rotating body surface in the axial direction. The compressor further includes: a blade inserted into the blade groove and configured to rotate while moving in the axial direction in accordance with rotation of the rotating body; and a compression chamber defined by the rotating body surface and the fixed body surface, the compression chamber being configured to suck and compress a fluid by rotating the vane while moving in the axial direction. The blade is provided with: a blade body inserted into the blade groove; and a seal member that is attached to an end surface of the blade body in the axial direction in a state of being movable in the axial direction with respect to the blade body. A back pressure space is formed between the sealing member and the vane main body. The seal member is configured to be pressed against the fixed body surface by the back pressure space, and thereby to be brought into contact with the fixed body surface.

Drawings

Fig. 1 is a schematic diagram showing an outline of a compressor according to embodiment 1.

Fig. 2 is an exploded perspective view of a main structure in the compressor of fig. 1.

Fig. 3 is an exploded perspective view of the main structure viewed from the opposite side to fig. 2.

Fig. 4 is a sectional view of a main structure in the compressor of fig. 1.

Fig. 5 is a side view of the main structure in the compressor of fig. 1.

Fig. 6 is a sectional view taken along line 6-6 of fig. 4.

Fig. 7 is a sectional view taken along line 7-7 of fig. 4.

Fig. 8 is an exploded perspective view of a front cylinder, a front valve, and a front retainer (english: front retainer) in the compressor of fig. 1.

Fig. 9 is an enlarged cross-sectional view of the periphery of a vane in the compressor of fig. 1.

Fig. 10 is a perspective view of a rotary body and blades in the compressor of fig. 1.

Fig. 11 is an exploded perspective view of the blade of fig. 10.

Fig. 12 is a cross-sectional view schematically showing a manner of contact between the vane and the surfaces of the two fixed bodies in the compressor of fig. 1.

Fig. 13 is a cross-sectional view taken along line 13-13 of fig. 9.

Fig. 14 is a development view schematically showing a rotating body, two fixed bodies, and blades in the compressor of fig. 1.

Fig. 15 is a development view schematically showing the rotating body, the two fixed bodies, and the blades in a phase different from that of fig. 14.

Fig. 16 is a cross-sectional view schematically showing the manner in which the blade and both fixture surfaces contact each other in embodiment 2.

Fig. 17 is a cross-sectional view schematically showing a manner of contact between the blade and the surfaces of the both fixed bodies in embodiment 3.

Fig. 18 is a cross-sectional view schematically showing a contact manner between the blade and the surfaces of the both fixed bodies in embodiment 4.

Fig. 19 is a sectional view schematically showing another example of a tip seal (english: tip seal).

Fig. 20 is a sectional view schematically showing a compressor of another example.

Detailed Description

(embodiment 1)

Hereinafter, embodiment 1 of the compressor will be described with reference to the drawings. The compressor according to the present embodiment is for example for a vehicle, and is specifically mounted on a vehicle for use. A compressor is used, for example, in an air conditioning apparatus for a vehicle, and a fluid to be compressed by the compressor is a refrigerant including oil. For convenience of illustration, fig. 1 shows the rotary shaft 12, the rotary body 60, and the fixed bodies 90 and 110 in a side view. In addition, in fig. 6 and 7, the plurality of blades 131 are schematically shown in a side view.

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

The casing 11 is, for example, cylindrical as a whole, and has a suction port 11a for sucking a suction fluid from the outside and a discharge port 11b for discharging a compressed fluid. 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 fixed bodies 90 and 110 are accommodated in the housing 11.

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 peripheral wall and an end wall disposed at one end in the axial direction of the peripheral wall, and has an open end opening toward the rear housing member 22. The suction port 11a is provided, for example, in the peripheral wall of the front housing member 21 at a position closer to the end wall than the open end. However, the position of the suction port 11a is arbitrary.

The cylindrical rear case member 22 has a rear case end wall 23 and a rear case peripheral wall 24 extending from the rear case end wall 23 toward the front case member 21. The front case member 21 and the rear case member 22 are combined and unitized with their open ends facing each other. The discharge port 11b is provided in the rear housing peripheral wall 24. However, the position of the discharge port 11b is arbitrary.

The inverter cover 25 is disposed on the opposite side of the front housing member 21 from the rear housing member 22. The inverter cover 25 is fixed to the front housing member 21 in a state of abutting against the end wall of the front housing member 21. The inverter 14 is accommodated in the inverter cover 25. The inverter 14 drives the electric motor 13.

As shown in fig. 1, the front cylinder 30 and the rear plate 40 cooperate to house the two fixed bodies 90, 110 and the rotating body 60. The front cylinder 30 is a cylindrical body having a diameter smaller than the diameter of the peripheral wall 24 of the rear housing member 22, and opens toward the rear housing end wall 23.

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

As shown in fig. 1 and 2, the front cylinder end wall 31 is stepped in the axial direction Z of the rotary shaft 12, and includes a1 st end wall 31a disposed on the center side and a2 nd end wall 31b disposed outside the 1 st end wall 31a in the radial direction R of the rotary shaft 12 and at a position offset from the 1 st end wall 31a toward the rear housing end wall 23. The 1 st end wall 31a is formed with a front insertion hole 31c through which the rotary shaft 12 can be inserted, and the rotary shaft 12 is inserted through the front insertion hole 31 c.

As shown in fig. 1, the front cylinder peripheral wall 32 enters the inside of the rear housing member 22. The front cylinder peripheral wall 32 has a front cylinder inner peripheral surface 33 and a front cylinder outer peripheral surface 34 disposed on the opposite side of the front cylinder inner peripheral surface 33.

The front cylinder inner circumferential surface 33 and the front cylinder outer circumferential surface 34 are, for example, cylindrical surfaces having an axis extending in the axial direction Z of the rotary shaft 12. The front cylinder outer peripheral surface 34 abuts against the inner peripheral surface of the rear housing peripheral wall 24 in the radial direction R.

A discharge recess 35 for partitioning the discharge chamber a1 is formed in the front cylinder outer peripheral surface 34. The discharge recess 35 is formed between both axial ends of the front cylinder outer peripheral surface 34, and is recessed radially inward. A discharge chamber a1 in which the compressed fluid exists is partitioned by the discharge recess 35 and the rear housing peripheral wall 24. The discharge chamber a1 is cylindrical having an axis extending in the axial direction Z of the rotary shaft 12. The discharge chamber a1 communicates with the discharge port 11 b. The compressed fluid in the discharge chamber a1 is discharged from the discharge port 11 b.

The front cylinder 30 has a bulging portion 36 that projects radially outward. The bulging portion 36 is provided at a position across both the front cylinder end wall 31 and the front cylinder peripheral wall 32. The bulge portion 36 bulges radially outward from the front cylinder outer peripheral surface 34. The front housing member 21 and the rear housing member 22 are coupled to each other with the bulging portion 36 interposed therebetween. The displacement in the axial direction Z of the front cylinder 30 is restricted by the housing members 21 and 22.

As shown in fig. 1, a motor chamber a2 partitioned by front housing member 21 and front cylinder end wall 31 is provided in housing 11, and electric motor 13 is housed in motor chamber a 2. Electric motor 13 is supplied with drive power from inverter 14, and thereby rotates rotary shaft 12 in the direction indicated by arrow M, specifically, in the clockwise direction when both fixed bodies 90 and 110 are viewed from electric motor 13.

Since the suction port 11a is provided in the front housing member 21 that partitions the motor chamber a2, the fluid sucked through the suction port 11a is sucked into the motor chamber a2 in the housing 11. That is, the fluid sucked from the suction port 11a exists in the motor chamber a 2. The motor chamber a2 is a suction chamber into which fluid is sucked.

In the compressor 10 of the present embodiment, the inverter 14, the electric motor 13, the front fixed body 90, the rotating body 60, and the rear fixed body 110 are arranged in this order in the axial direction Z. However, the positions of these components are arbitrary, and for example, the inverter 14 may be disposed radially outward of the electric motor 13.

The rear plate 40 is plate-shaped (in the present embodiment, disc-shaped), and is housed in the rear housing member 22 such that the plate thickness direction thereof coincides with the axial direction Z. The outer diameter of the rear plate 40 is, for example, the same as the diameter of the front cylinder outer peripheral surface 34 (or the inner peripheral surface of the rear housing peripheral wall 24). The rear plate 40 is fitted to the rear housing member 22 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 so that the front end portion (open end) of the front cylinder peripheral wall 32 abuts against the rear plate 40, and the opening portion of the front cylinder 30 is closed by the rear plate 40.

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

The rear plate 40 is supported by the housing 11. More specifically, the rear plate 40 is sandwiched between the front cylinder 30 supported by the housing 11 and the rear housing end wall 23 that is a part of the housing 11. The rear plate 40 may be supported by the housing 11, and a specific supporting method thereof may be arbitrary.

The rear plate 40 has a1 st plate surface 43 and a2 nd plate surface 44 as plate surfaces orthogonal to the axial direction Z. The 1 st plate surface 43 faces the opposite side of the rear housing end wall 23. The 2 nd plate surface 44 is opposed to the rear housing end wall 23 in the axial direction Z. In the present embodiment, since the plate recess 42 is formed, the 1 st plate surface 43 is smaller than the 2 nd plate surface 44.

In this specification, unless otherwise specified, "opposed" includes a mode in which 2 members are opposed to each other with a gap therebetween and a mode in which 2 members are in contact with each other, within a range where "opposed" is technically not contradictory. For example, the 2 nd plate surface 44 and the rear housing end wall 23 may be separate from each other or may abut each other. The term "opposed direction" includes a mode in which a part of 2 surfaces opposed to each other are in contact with each other and the other parts are separated from each other.

As shown in fig. 1, the compressor 10 includes bearings 51 and 53 that rotatably support the rotary shaft 12.

The front shaft bearing 51 is attached to a boss (boss) 52 provided on the end wall of the front housing member 21. The boss 52 is in the shape of a ring protruding from the end wall of the front housing member 21. The front shaft bearing 51 is disposed radially inward of the boss 52, and rotatably supports the front shaft end 12a of the two shaft ends 12a and 12b, which are both ends of the rotary shaft 12 in the axial direction.

A rear insertion hole 41 through which the rotary shaft 12 is inserted is formed in a central portion of the rear plate 40. The diameter of the rear insertion hole 41 is the same as or larger than the diameter of the rear shaft end portion 12 b. The rear shaft end portion 12b is inserted through the rear insertion hole 41.

The rear shaft bearing 53 is provided on the inner wall surface of the rear insertion hole 41, and rotatably supports the rear shaft end portion 12 b. The rear shaft bearing 53 is, for example, a coated bearing (japanese: コーティング rim) formed of a coating layer (japanese: コーティング body frame) formed on the inner wall surface of the rear insertion hole 41.

The coating layer is optional, and may be a layer containing a thermosetting resin and/or a lubricant, for example. The rear shaft bearing 53 is not limited to a coated bearing formed of a coated layer, and may be, for example, another sliding bearing, a rolling bearing, or the like. In fig. 1 and the like, the rear shaft bearing 53 is shown to be thicker than it is.

As described above, in the present embodiment, the both-axis ends 12a and 12b are rotatably supported by the both- axis bearings 51 and 53. In view of the fact that the front shaft bearing 51 is attached to the boss 52 of the front housing member 21 and the fact that the rear plate 40 on which the rear shaft bearing 53 is formed is supported by the rear housing member 22, it can be said that the rotary shaft 12 is supported by the housing 11 so as to be rotatable with respect to the housing 11 by the two shaft bearings 51, 53. In the present embodiment, the rotary shaft 12 has a cylindrical shape.

As shown in fig. 1, the rear housing end wall 23 has a housing recess 54 at a position facing the rotary shaft 12 in the axial direction Z. The housing recess 54 is, for example, a circular recess formed to be one step larger than the rear shaft end 12 b. A portion of the rear shaft end 12b enters the housing recess 54.

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

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

The motor chamber a2 and the housing chamber A3 are aligned in the axial direction Z in the housing 11. The motor chamber a2 and the housing chamber A3 are partitioned by the front cylinder end wall 31, and the fluid in the motor chamber a2 does not flow into the housing chamber A3. The front cylinder end wall 31 is a partition wall portion that partitions the motor chamber a2 and the housing chamber A3 such that the fluid in the motor chamber a2 does not easily flow into the housing chamber A3. The rotary shaft 12 penetrates the front cylinder end wall 31 as a partition wall portion, and is disposed across both the motor chamber a2 and the storage chamber A3. The rear plate 40 is a partition for partitioning the storage chamber a 3.

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

The rotating body 60 rotates in the rotation direction M in accordance with the rotation of the rotating shaft 12. The rotary body 60 is disposed in the housing 11 such that the rotation center axis thereof coincides with the center axis of the rotary shaft 12. That is, the rotating body 60 is disposed coaxially with the rotating shaft 12. Therefore, the present compressor 10 has a structure that performs an axial movement rather than an eccentric movement.

The rotating body 60 includes a rotating body cylindrical portion 61 through which the rotating shaft 12 is inserted, and a rotating body ring portion 70 extending radially outward from the rotating body cylindrical portion 61.

The rotating body tube 61 is attached to the rotating shaft 12 so as to rotate integrally with the rotating shaft 12. Thereby, the rotating body 60 rotates in accordance with the rotation of the rotating shaft 12. The attachment form of the rotating body tube 61 to the rotating shaft 12 is arbitrary, and for example, the rotating body tube 61 may be fixed to the rotating shaft 12 by press fitting, or the rotating body tube 61 may be fixed to the rotating shaft 12 by a fixing pin inserted across the rotating shaft 12 and the rotating body tube 61. Further, the rotary cylinder 61 and the rotary shaft 12 may be coupled to each other by a coupling member such as a key, and the rotary cylinder 61 and the rotary shaft 12 may be coupled to each other by engaging a concave portion provided in one of the rotary cylinder 61 and the rotary shaft 12 with a convex portion provided in the other of the rotary cylinder 61 and the rotary shaft 12.

The rotor cylindrical portion 61 is, for example, a cylindrical body having an axis extending in the axial direction Z. The rotating body cylindrical portion 61 has an inner diameter equal to or larger than the diameter of the rotating shaft 12, for example. The inner circumferential surface of the rotating body tube 61 and the outer circumferential surface of the rotating shaft 12 face each other in the radial direction R.

The rotor cylindrical portion 61 has a cylindrical outer peripheral surface 62, and the cylindrical outer peripheral surface 62 has an axis extending in the axial direction Z. The cylindrical portion outer peripheral surface 62 is curved radially outward, and in the present embodiment, is a cylindrical surface.

As shown in fig. 2 to 4, the rotor ring portion 70 is provided at an arbitrary position (in the present embodiment, near the center portion) between the two rotor end portions 61a and 61b, which are both end portions in the axial direction of the rotor cylindrical portion 61.

The rotor ring 70 is a circular plate-shaped member having a plate thickness in the axial direction Z, and has a front rotor surface 71 and a rear rotor surface 72, which are both end surfaces in the axial direction. The rotary body surfaces 71 and 72 are annular. The rotor surfaces 71 and 72 intersect the axial direction Z, and are flat surfaces orthogonal to the axial direction Z in the present embodiment. Therefore, the inner peripheral edge and the outer peripheral edge of each of the rotor surfaces 71 and 72 are linear when viewed in the radial direction R, and the position in the axial direction Z is constant over the entire circumferential direction.

A ring outer peripheral surface 73 as an outer peripheral surface of the rotor ring portion 70 is a surface intersecting the radial direction R, and the ring outer peripheral surface 73 faces the front cylinder inner peripheral surface 33 in the radial direction R. The ring outer peripheral surface 73 and the front cylinder inner peripheral surface 33 may abut against each other or may be separated from each other with a slight gap.

As shown in fig. 4, the compressor 10 includes thrust bearings 81 and 82 that support the rotary body 60 in the axial direction Z. The thrust bearings 81 and 82 are disposed on both sides of the rotating body tube 61 in the axial direction, and sandwich the rotating body tube 61 in the axial direction Z.

Specifically, the front thrust bearing 81 is disposed in a space created by the stepped formation of the front cylinder end wall 31. The front thrust bearing 81 supports the rotor tubular portion 61 (more specifically, the front rotor end portion 61a) from the axial direction Z in a state of being supported by the front cylinder end wall 31.

The rear thrust bearing 82 is disposed in a thrust receiving recess 83 formed in the rear plate 40. The thrust force accommodating recess 83 is formed in a portion of the inner wall surface of the rear insertion hole 41 close to the 1 st plate surface 43. The rear thrust bearing 82 supports the rotor tubular portion 61 (more specifically, the rear rotor end portion 61b) from the axial direction Z in a state of being supported by the rear plate 40.

The thrust bearings 81 and 82 are disc-shaped, and the rotary shaft 12 is inserted through the thrust bearings 81 and 82. In the present embodiment, the inner circumferential surfaces of the thrust bearings 81 and 82 and the outer circumferential surface of the rotary shaft 12 are in contact with each other. Thus, the thrust bearings 81 and 82 support the rotary shaft 12 by abutting against the rotary shaft 12 in the radial direction R. However, the thrust bearings 81 and 82 may be separated from the rotary shaft 12 in the radial direction R.

The fixed bodies 90 and 110 are disposed on both sides of the rotor ring 70 in the axial direction. In other words, the fixed bodies 90 and 110 are disposed apart in the axial direction Z with the rotor ring 70 disposed therebetween, or the rotor ring 70 is disposed between the fixed bodies 90 and 110.

Both the fixed bodies 90 and 110 are fixed to the front cylinder 30 (in other words, the housing 11) so as not to rotate with the rotation of the rotary shaft 12. For example, the fixing members 90 and 110 are fixed to the front cylinder 30 by fastening the front cylinder peripheral wall 32 to the fixing members 90 and 110 using a fastening member (not shown) penetrating the front cylinder peripheral wall 32.

However, the fixing method of both the fixing bodies 90 and 110 to the front cylinder 30 is not limited to this, and the fixing method may be press-fitting or fitting, for example. Further, the number of fastening portions for fastening the front fixing body 90 to the front cylinder end wall 31 may be 1 or more, and the number of fastening portions for fastening the rear fixing body 110 to the rear plate 40 may be 1 or more.

The structure of both fixing bodies 90 and 110 will be described in detail. In the present embodiment, the fixing bodies 90 and 110 have the same shape.

As shown in fig. 1 to 4, of the two fixed bodies 90 and 110, the front fixed body 90 disposed at a position close to the front cylinder end wall 31, in other words, at a position close to the motor chamber a2 is, for example, annular (annular in the present embodiment), and has a front fixed body insertion hole 91 into which the rotary shaft 12 is inserted. In the present embodiment, the front fixture insertion hole 91 is a through hole that penetrates the front fixture 90 in the axial direction Z. The front fixing body 90 is disposed in the front cylinder 30 in a state where the rotary shaft 12 is inserted into the front fixing 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 fixture body outer circumferential surface 92 and the front cylinder inner circumferential surface 33 abut against each other. However, the present invention is not limited to this, and the front cylinder inner circumferential surface 33 and the front stator outer circumferential surface 92 may be separated from each other.

The front fixing 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 separated from each other or may be in contact with each other.

As shown in fig. 1 to 4, of the two fixed bodies 90 and 110, the rear fixed body 110 disposed at a position close to the rear plate 40 as a partition portion, in other words, at a position apart from the motor chamber a2 is annular (annular in the present embodiment) like the front fixed body 90, and has a rear fixed body insertion hole 111 into which the rotary shaft 12 is inserted. In the present embodiment, the rear fixture insertion hole 111 is a through hole that penetrates the rear fixture 110 in the axial direction Z. The rear fixing body 110 is disposed in the front cylinder 30 in a state where the rotary shaft 12 is inserted into the rear fixing body insertion hole 111. That is, in the present embodiment, the rotary shaft 12 penetrates both the 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 and the front cylinder inner circumferential surface 33 abut against each other. However, the present invention is not limited to this, and the front cylinder inner circumferential surface 33 and the rear fixture outer circumferential surface 112 may be separated from each other.

The rear fixing body 110 includes a rear surface 113 facing the 1 st plate surface 43 of the rear plate 40 in the axial direction Z. The rear surface 113 and the 1 st plate surface 43 may be separated from each other or may be in contact with each other.

As shown in fig. 4, the rotor tube 61 is inserted into the stator insertion holes 91 and 111, whereby the rotor 60 is supported by the stators 90 and 110.

Specifically, the front rotor end 61a of the rotor tubular portion 61 is inserted into the front fixed body insertion hole 91 and penetrates the front fixed body 90.

The front fixing body insertion hole 91 has a shape and a size corresponding to the rotary body tube portion 61 (more specifically, the tube portion outer peripheral surface 62). In the present embodiment, the front fixed body insertion hole 91 corresponds to the cylindrical rotating body tube 61 and is circular when viewed in the axial direction Z. The diameter of the front fixture insertion hole 91 is the same as or slightly larger than the diameter of the outer peripheral surface 62 of the tube portion. The front rotator end 61a is rotatably supported by the front fixed body 90 by a front rotator bearing 94 formed on the inner wall surface of the front fixed body insertion hole 91.

Similarly, the rear rotating body end 61b is inserted into the rear fixed body insertion hole 111 and penetrates the rear fixed body 110.

The rear fixed body insertion hole 111 has a shape and a size corresponding to the rotary body tube portion 61 (more specifically, the tube portion outer peripheral surface 62). In the present embodiment, the rear fixed body insertion hole 111 corresponds to the cylindrical rotating body tube 61 and is circular when viewed in the axial direction Z. The rear fixture insertion hole 111 has a diameter equal to or slightly larger than the diameter of the cylindrical outer peripheral surface 62. The rear rotor end 61b is rotatably supported by the rear fixed body 110 by a rear rotor bearing 114 formed on the inner wall surface of the rear fixed body insertion hole 111.

That is, the rotary body ends 61a and 61b are supported by the fixed bodies 90 and 110 via the rotary body bearings 94 and 114. This allows the rotating body 60 to be supported by the fixed bodies 90 and 110, and prevents the rotating body 60 from being displaced from the fixed bodies 90 and 110.

The two rotor end portions 61a and 61b constitute both axial end portions of the rotor 60. Therefore, both axial ends of the rotor 60 are supported by the rotor bearings 94 and 114. Thereby, the rotating body 60 is stably held.

Further, since the fixed body insertion holes 91 and 111 are formed corresponding to the rotor tubular portion 61, a gap formed between the inner wall surfaces of the fixed body insertion holes 91 and 111 and the tubular portion outer peripheral surface 62 is small or hardly generated.

The rotating body bearings 94 and 114 are, for example, coated bearings formed of a coating layer formed on the inner wall surfaces of the fixed body insertion holes 91 and 111. In fig. 4 and the like, the rotary bearings 94 and 114 are shown to be thicker than they are. The specific structure of the rotary bearings 94 and 114 is not limited to the coated bearing, and may be any other sliding bearing, rolling bearing, or the like.

The front fixed body 90 has a front fixed body surface 100 as a fixed body surface facing the front rotating body surface 71 in the axial direction Z. The front fixing body surface 100 is a plate surface on the opposite side of the front back surface 93. The front fixture surface 100 is annular, and in the present embodiment, is annular when viewed in the axial direction Z.

As shown in fig. 3, the front fixture surface 100 includes a1 st front flat surface 101 and a2 nd front flat surface 102 intersecting with (orthogonal to) the axial direction Z, and 2 front curved surfaces 103 as curved surfaces connecting the front flat surfaces 101 and 102.

As shown in fig. 4, the front flat surfaces 101 and 102 are offset in the axial direction Z. Specifically, the 2 nd front flat surface 102, which is a fixed body contact surface, is disposed at a position closer to the front rotator surface 71 than the 1 st front flat surface 101, and contacts the front rotator surface 71. Further, the front fixture surface 100 is separated from the front rotator surface 71 by a portion other than the 2 nd front flat surface 102.

The front flat surfaces 101 and 102 are arranged apart from each other in the circumferential direction of the front fixed body 90, for example, shifted by 180 °. In the present embodiment, both front flat surfaces 101 and 102 have a fan shape. In the following description, the circumferential positions of both fixing bodies 90 and 110 are also referred to as angular positions.

The 2 front curved surfaces 103 are respectively fan-shaped. As shown in fig. 3, the 2 front curved surfaces 103 are arranged to oppose in the radial direction when viewed from 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, 102. Specifically, one of the front curved surfaces 103 connects circumferential 1 st end portions of the front flat surfaces 101 and 102 to each other, and the other connects circumferential 2 nd end portions of the front flat surfaces 101 and 102 to each other.

The angular position of the boundary between each front curved surface 103 and the 1 st front flat surface 101 is defined as a1 st angular position θ 1, and the angular position of the boundary between each front curved surface 103 and the 2 nd front flat surface 102 is defined as a2 nd angular position θ 2. In fig. 3, the respective angular positions θ 1 and θ 2 are indicated by broken lines, but in reality, the front curved surface 103 and the front flat surfaces 101 and 102 are smoothly continuous at the boundary portion.

Each front curved surface 103 is a curved surface whose position in the axial direction Z changes according to the circumferential position, in other words, according to the angular position of the front fixed body 90. Specifically, each front curved surface 103 is curved in the axial direction Z so as to gradually approach the front rotor surface 71 as it approaches from the 1 st angular position θ 1 to the 2 nd angular position θ 2. In other words, the 2 front curved surfaces 103 are provided on both sides in the circumferential direction with respect to the 2 nd front flat surface 102, and are curved in the axial direction Z so as to gradually separate from the front rotor surface 71 as they separate from the 2 nd front flat surface 102 in the circumferential direction.

Each front curved surface 103 has a front concave surface 103a curved in the axial direction Z so as to be concave with respect to the front rotor surface 71, and a front convex surface 103b curved in the axial direction Z so as to be convex toward the front rotor surface 71.

The front concave surface 103a is disposed closer to the 1 st front flat surface 101 than to the 2 nd front flat surface 102, and the front convex surface 103b is disposed closer to the 2 nd front flat surface 102 than to the 1 st front flat surface 101. The front concave surface 103a is connected to the front convex surface 103 b. That is, the front curved surface 103 is a curved surface having an inflection point.

Further, the angular range of the convex front surface 103b may be the same as or different from the angular range of the concave front surface 103 a. The position of the inflection point is arbitrary. Since the front curved surface 103 can be said to be a curved surface curved in a wave-like manner, the front anchor surface 100 can be said to be a front wave surface (japanese: フロントウェーブ surface) including a portion curved in a wave-like manner.

The rear stator 110 has a rear stator surface 120 as a stator surface facing the rear rotator surface 72 in the axial direction Z. The rear fixture surface 120 is a plate surface on the opposite side of the rear surface 113. The rear fixing body surface 120 is annular when viewed in the axial direction Z, and is annular in the present embodiment.

In the present embodiment, the rear fixture surface 120 and the front fixture surface 100 have the same shape. As shown in fig. 2, the rear fixing body surface 120 includes a1 st rear flat surface 121 and a2 nd rear flat surface 122 intersecting with (orthogonal to) the axial direction Z, and 2 rear curved surfaces 123 as curved surfaces connecting the two rear flat surfaces 121 and 122.

As shown in fig. 4, the rear flat surfaces 121 and 122 are offset in the axial direction Z. Specifically, the 2 nd rear flat surface 122 as the fixed body contact surface is disposed closer to the rear rotor surface 72 than the 1 st rear flat surface 121, and contacts the rear rotor surface 72. Further, the rear fixture surface 120 is separated from the rear rotator surface 72 by a portion other than the 2 nd rear flat surface 122.

The rear flat surfaces 121 and 122 are arranged apart from each other in the circumferential direction of the rear fixed body 110, for example, shifted by 180 °. In the present embodiment, both rear flat surfaces 121 and 122 have a fan shape.

The 2 back curved surfaces 123 are each fan-shaped. The 2 back curved surfaces 123 are arranged to oppose each other in the radial direction when viewed from the axial direction Z. One of the two rear curved surfaces 123 connects circumferential 1 st end portions of the two rear flat surfaces 121 and 122 to each other, and the other connects circumferential 2 nd end portions of the two rear flat surfaces 121 and 122 to each other.

The 2 rear curved surfaces 123 are provided on both sides of the 2 nd rear flat surface 122 in the circumferential direction, and are curved in the axial direction Z so as to gradually separate from the rear rotor surface 72 as they separate from the 2 nd rear flat surface 122 in the circumferential direction.

The two fixed body surfaces 100 and 120 are arranged so as to face each other with a gap therebetween in the axial direction Z and so as to be angularly displaced by 180 ° from each other.

The distance in the axial direction Z between the two fixture surfaces 100, 120 is constant regardless of the angular position (in other words, circumferential position) thereof. Specifically, as shown in fig. 4, the 1 st front flat surface 101 and the 2 nd rear flat surface 122 are opposed to each other in the axial direction Z, and the 2 nd front flat surface 102 and the 1 st rear flat surface 121 are opposed to each other in the axial direction Z. The amount of displacement in the axial direction Z between the front flat surfaces 101 and 102 is the same as the amount of displacement between the rear flat surfaces 121 and 122. Hereinafter, the amount of shift in the axial direction Z between the front flat surfaces 101 and 102 and the amount of shift between the rear flat surfaces 121 and 122 will be simply referred to as "shift amount Z1".

In addition, the front curved surface 103 is curved in the same manner as the rear curved surface 123. That is, the front curved surface 103 and the rear curved surface 123 are curved in the same manner so that the distance in the axial direction Z does not vary depending on the angular position thereof. Thus, the distance in the axial direction Z between the two fixture surfaces 100, 120 is constant at any angular position.

The specific shapes of the 1 st rear flat surface 121, the 2 nd rear flat surface 122, and the two rear curved surfaces 123 are the same as those of the 1 st front flat surface 101, the 2 nd front flat surface 102, and the two front curved surfaces 103, and therefore, detailed description thereof is omitted. In addition, since the back curved surface 123 can be said to be a curved surface curved in a wave-like manner as in the front curved surface 103, the back fixture surface 120 can be said to be a back wave surface including a portion curved in a wave-like manner.

The circumferential directions of the fixed bodies 90 and 110 and the rotating body 60 coincide with the circumferential direction of the rotating shaft 12, the radial directions of the fixed bodies 90 and 110 and the rotating body 60 coincide with the radial direction R of the rotating shaft 12, and the axial directions of the fixed bodies 90 and 110 and the rotating body 60 coincide with the axial direction Z of the rotating shaft 12. Therefore, the circumferential direction, the radial direction R, and the axial direction Z of the rotary shaft 12 may be appropriately replaced with the circumferential direction, the radial direction, and the axial direction of the rotary body 60, or with the circumferential direction, the radial direction, and the axial direction of the fixed bodies 90, 110.

As shown in fig. 4, the compressor 10 includes compression chambers a4 and a5 for sucking and compressing a fluid. The compression chambers a4 and a5 are provided in the storage chamber A3, and are disposed on both sides of the rotor ring 70 in the axial direction Z.

The front compression chamber a4 is defined by the front rotor surface 71 and the front stator surface 100, and more specifically, by the front rotor surface 71, the front stator surface 100, the tube outer peripheral surface 62, and the front cylinder inner peripheral surface 33.

The rear compression chamber a5 is defined by the rear rotor surface 72 and the rear stator surface 120, and more specifically, by the rear rotor surface 72, the rear stator surface 120, the cylindrical portion outer peripheral surface 62, and the front cylinder inner peripheral surface 33. In the present embodiment, the front compression chamber a4 and the rear compression chamber a5 are the same size.

The compression chambers a4 and a5 and the discharge chamber a1 are opposed to each other in the radial direction R with the front cylinder peripheral wall 32 disposed therebetween. That is, the discharge chamber a1 is disposed outside 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. In short, discharge chamber a1 may extend in axial direction Z so as to oppose at least a portion of front compression chamber a4 in radial direction R and at least a portion of rear compression chamber a5 in radial direction R.

As shown in fig. 2 to 5, the compressor 10 includes a plurality of (3) vane grooves 130 formed in the rotating body 60 and a plurality of (3) vanes 131 inserted into the vane grooves 130, respectively.

The vane grooves 130 are formed in the rotor ring portion 70. The vane grooves 130 penetrate the rotor ring portion 70 in the axial direction Z and open to both rotor surfaces 71 and 72. The vane groove 130 has a width in a direction perpendicular to both the axial direction Z and the radial direction R, extends in the radial direction R, and opens outward in the radial direction. On the other hand, the vane grooves 130 are not formed in the rotor cylindrical portion 61. The vane groove 130 has a pair of side surfaces facing each other while being separated from each other in the circumferential direction.

The rotor ring 70 is a portion located radially outward of the rotor tube 61. Therefore, the rotor cylindrical portion 61 is present radially inward of the rotor ring portion 70. That is, the rotor ring 70 is a portion that is provided on the cylindrical outer peripheral surface 62 and protrudes radially outward from the cylindrical outer peripheral surface 62.

The blades 131 have a rectangular plate shape as a whole, and have plate surfaces intersecting (orthogonal to) the circumferential direction of the rotating shaft 12. The blade 131 is disposed between the two fixed bodies 90 and 110 (in other words, the two fixed body surfaces 100 and 120). The vane 131 is a plate-like body having a thickness in the width direction of the vane groove 130, in other words, in the direction perpendicular to both the axial direction Z and the radial direction R.

Both plate surfaces of the blade 131 and both side surfaces of the blade groove 130 face each other in the circumferential direction (in other words, the width direction of the blade groove 130). The width of the vane groove 130 (in other words, the distance between both side surfaces of the vane groove 130) is equal to or slightly larger than the plate thickness of the vane 131. The blade 131 inserted into the blade groove 130 is sandwiched between both side surfaces of the blade groove 130. The vane 131 is allowed to move in the axial direction Z along the vane groove 130. In the present embodiment, the blade 131, more specifically, both axial end portions of the blade 131 are in contact with both the fixture surfaces 100 and 120.

The plurality of vane grooves 130 are arranged at equal intervals in the circumferential direction, specifically, at positions shifted by 120 ° from each other. Correspondingly, the plurality of blades 131 are arranged at equal intervals in the circumferential direction.

The blades 131 rotate in the rotation direction M as the rotor 60 rotates. Then, the blade 131 abutting the fixed body surfaces 100 and 120 moves (swings) in the axial direction Z along the curved fixed body surfaces 100 and 120. That is, the blade 131 rotates while moving in the axial direction Z. Thereby, the vane 131 enters the front compression chamber a4 and the rear compression chamber a 5. That is, the vane groove 130 arranges the vanes 131 in the compression chambers a4 and a5 while rotating the vanes 131 with the rotation of the rotor 60.

The movement distance (in other words, the swing distance) of the blade 131 in the axial direction Z is the displacement amount Z1 in the axial direction Z between the front flat surfaces 101 and 102 (or between the rear flat surfaces 121 and 122). The blades 131 are continuously in contact with the fixed body surfaces 100 and 120 during the rotation of the rotating body 60, and thus intermittent contact, or more specifically repetition of separation and contact, is unlikely to occur.

As shown in fig. 6, the front compression chamber A4 is partitioned into 3 partial (english: parts) chambers, i.e., the 1 st front compression chamber A4a, the 2 nd front compression chamber A4b, and the 3 rd front compression chamber A4c by 3 vanes 131.

For convenience of explanation, a partial chamber disposed on the leading side with respect to the 2 nd front flat surface 102 in the rotation direction M among the 3 partial chambers is referred to as a1 st front compression chamber A4 a.

Among the 3 partial chambers, a partial chamber located on the subsequent side in the rotation direction M with respect to the 1 st front compression chamber A4a is referred to as a2 nd front compression chamber A4 b. At least a part of the 2 nd front compression chamber A4b is disposed on the subsequent side with respect to the 2 nd front flat surface 102 in the rotation direction M.

Among the 3 partial chambers, a partial chamber disposed between the 1 st front compression chamber A4a and the 2 nd front compression chamber A4b in the circumferential direction is defined as a3 rd front compression chamber A4 c. Front 3 rd compression chamber A4c is disposed on the leading side with respect to front 1 st compression chamber A4a and on the trailing side with respect to front 2 nd compression chamber A4b in rotation direction M.

In the following description, the "preceding side in the rotation direction M" and the "succeeding side in the rotation direction M" may be referred to simply as the "preceding side" and the "succeeding side", respectively.

The front compression chambers A4a to A4c are formed 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 in the circumferential direction corresponds to an angular range of 120 °.

In addition, strictly speaking, when 1 blade 131 of the plurality of blades 131 abuts against the 2 nd front flat surface 102, the blade 131 does not enter the front compression chamber a 4. In this case, spaces at both circumferential sides of the blade 131 abutting against the 2 nd front flat surface 102 are partitioned by the abutting portions of the front rotor surface 71 and the 2 nd front flat surface 102, and the mutual communication is blocked. Therefore, even in the case where 1 blade 131 of the plurality of blades 131 abuts against the 2 nd front flat surface 102, the front compression chamber a4 is partitioned into 3 partial chambers. In the present embodiment, for convenience of explanation, the front compression chamber A4 is partitioned into the front compression chambers A4a to A4c by 3 vanes 131 even when 1 vane 131 of the plurality of vanes 131 abuts against the 2 nd front flat surface 102.

As shown in fig. 7, like the front compression chamber a4, the rear compression chamber A5 is partitioned into a1 st rear compression chamber A5a, a2 nd rear compression chamber A5b disposed on the rear side of the 1 st rear compression chamber A5a, and A3 rd rear compression chamber A5c disposed between the 1 st rear compression chamber A5a and the 2 nd rear compression chamber A5b in the circumferential direction by 3 vanes 131. Since 1 st rear compression chamber A5a, 2 nd rear compression chamber A5b, and 3 rd rear compression chamber A5c are the same as 1 st front compression chamber A4a, 2 nd front compression chamber A4b, and 3 rd front compression chamber A4c, detailed description thereof is omitted.

Next, the structure relating to the suction of the fluid into the compression chambers a4 and a5 and the discharge of the compressed fluid will be described. Fig. 4 schematically shows a front suction duct (port) 141 and a rear suction duct 142.

As shown in fig. 2 to 4 and 6, the compressor 10 includes a front suction passage 141 through which a fluid sucked into the front compression chamber a4 passes. The front suction passage 141 is formed in the front cylinder 30, for example, and extends in the axial direction Z over both the front cylinder end wall 31 and the front cylinder peripheral wall 32.

The front suction passage 141 extends in the circumferential direction along the front cylinder peripheral wall 32, and is formed in an arc shape when viewed in the axial direction Z. At least a part of the front suction passage 141 is disposed radially outward of the 1 st front compression chamber A4 a. In other words, the 1 st front compression chamber A4a includes a part or all of the space located at the radially inner side of the front suction passage 141.

The front suction passage 141 opens to the motor chamber a2 and opens to the front compression chamber a 4. The motor chamber a2 is communicated with the front compression chamber a4 through the front suction passage 141.

Specifically, as shown in fig. 6, the front suction passage 141 has a front suction opening portion 141a that opens at a position communicating with the 1 st front compression chamber A4 a. The front suction opening portion 141a extends in the rotation direction M from a position corresponding to the circumferential center portion of the 2 nd front flat surface 102 in the front cylinder inner circumferential surface 33. The length of the front suction opening 141a extending in the circumferential direction 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 portion 141a may extend in the circumferential direction from a position in the front cylinder inner circumferential surface 33 corresponding to the circumferential direction central portion of the 2 nd front flat surface 102 by substantially the same length as the circumferential direction interval of the vane 131.

The angular position of the circumferential center portion of the 2 nd front flat surface 102 is set to 0 °, and the angle increases from the angular position of 0 ° in the rotation direction M. In this case, the front suction opening 141a may be formed over at least a range from the end on the leading side in the rotation direction M of the 2 nd front flat surface 102 to an angular position of 120 °, for example.

As shown in fig. 6 and 8, the compressor 10 includes a plurality of front discharge passages 151 that discharge the fluid compressed in the front compression chamber a4, a front valve 152 that opens and closes the front discharge passages 151, and a front retainer 153 that adjusts the opening degree of the front valve 152.

As shown in fig. 6, the front discharge passage 151 is provided, for example, at a position radially outward of the front compression chamber a4 and on the rear side of the 2 nd front flat surface 102 in the front cylinder peripheral wall 32.

Specifically, a front seating surface (フロント seating surface) 154 recessed from the front cylinder outer peripheral surface 34 is formed on the curved front cylinder outer peripheral surface 34. The front seat face 154 is formed in a portion of the front cylinder outer peripheral face 34 between the front compression chamber a4 and the discharge chamber a1 on the rear side with respect to the 2 nd front flat face 102. The front seat surface 154 is a flat surface orthogonal to the radial direction R.

As shown in fig. 6, the front discharge passage 151 is provided to the front seat surface 154. The front discharge passage 151 passes through the front cylinder circumferential wall 32 in the radial direction R to communicate the 2 nd front compression chamber A4b with the discharge chamber a 1.

The plurality of front discharge channels 151 are arranged in the circumferential direction. The plurality of front discharge channels 151 are each circular. However, the number and shape of the front discharge channels 151 are arbitrary. For example, the number of the front discharge passages 151 may be 1. The front discharge duct 151 may have an elliptical shape. In the structure in which the plurality of front discharge channels 151 are provided, the sizes of the front discharge channels 151 may be the same or different from each other.

At least a part of the front discharge passage 151 is disposed radially outward of the 2 nd front compression chamber A4 b. In other words, the 2 nd front compression chamber A4b includes a part or all of the space at the radially inner side of the front discharge passage 151.

The front suction passage 141 and the front discharge passage 151 are circumferentially separated from each other in a state where a portion of the front cylinder peripheral wall 32, which is radially outward of the 2 nd front flat surface 102, is disposed therebetween.

That is, the 1 st front compression chamber A4a is configured to communicate with the front intake passage 141, but not with the front discharge passage 151.

The 2 nd front compression chamber A4b communicates with the front discharge passage 151. However, since the circumferential length of the 2 nd front compression chamber A4b is longer than the circumferential length of the 2 nd front flat surface 102, the 2 nd front compression chamber A4b may be disposed across both the radial inside of the front suction path 141 and the radial inside of the front discharge path 151 depending on the angular position of the vane 131. In this regard, in the present embodiment, between a space located radially inward of the front suction passage 141 and a space located radially inward of the front discharge passage 151, there is a contact portion of the front rotary body surface 71 and the 2 nd front flat surface 102. Accordingly, the communication between the two spaces is blocked by the contact portion regardless of the angular positions of the plurality of blades 131. Therefore, the communication of the front suction passage 141 with the front discharge passage 151 is restricted. That is, the 2 nd pre-compression chamber A4b may be further partitioned into a suction space and a compression space by the contact portion.

The 3 rd front compression chamber A4c changes from a state of not communicating with the front discharge passage 151 to a state of communicating with the front discharge passage 151 in accordance with the rotation of the rotary body 60.

As shown in fig. 8, the front valve 152 and the front retainer 153 are provided on the front seat surface 154. The front seating surface 154 has a threaded hole 154 a. The front valve 152 and the front retainer 153 are fixed to the front seat surface 154 by screwing bolts B penetrating both the front valve 152 and the front retainer 153 into screw holes 154 a.

The front valve 152 normally blocks the front discharge passage 151. When the pressure of the front compression chamber A4 (specifically, the 2 nd front compression chamber A4b) exceeds the threshold value, the front valve 152 transitions from the state of blocking the front discharge passage 151 to the state of opening the front discharge passage 151. Thereby, the fluid compressed in the front compression chamber a4 is discharged to the discharge chamber a 1. The opening angle of the front valve 152 is limited by the front holder 153.

As shown in fig. 2 to 4 and 7, the compressor 10 includes a rear suction passage 142 through which fluid sucked into the rear compression chamber a5 passes. The rear suction passage 142 is formed in the front cylinder 30, for example, and extends in the axial direction Z over both the front cylinder end wall 31 and the front cylinder peripheral wall 32.

The rear suction passage 142 extends in the circumferential direction along the front cylinder peripheral wall 32 and is formed in an arc shape when viewed in the axial direction Z. At least a part of the rear suction passage 142 is disposed radially outward of the 1 st rear compression chamber A5 a. In other words, the 1 st rear compression chamber A5a includes a part or all of the space at the radially inner side of the rear suction passage 142.

The rear suction passage 142 opens to the motor chamber a2 and opens to the rear compression chamber a 5. The motor chamber a2 is communicated with the rear compression chamber a5 through the rear suction passage 142.

Specifically, as shown in fig. 7, the rear suction passage 142 has a rear suction opening portion 142a that opens at a position communicating with the 1 st rear compression chamber A5 a. The rear suction opening portion 142a extends in the rotation direction M from a position corresponding to the circumferential center portion of the 2 nd rear flat surface 122 in the front cylinder inner circumferential surface 33.

The rear suction duct 142 and the rear suction opening 142a extend in the rotation direction M from a position corresponding to the circumferential center portion of the 2 nd rear flat surface 122 within a range not interfering with the front discharge duct 151, the front valve 152, and the front holder 153.

However, the present invention is not limited to this, and the circumferential lengths of the rear suction duct 142 and the rear suction opening 142a may be the same as the circumferential lengths of the front suction duct 141 and the front suction opening 141 a. In this case, in order to prevent the rear suction duct 142 and the rear suction opening 142a from interfering with the front discharge duct 151 and the like, the axial length of the front valve 152 and the like may be shortened, the front discharge duct 151 may be disposed at a different position, or the angular range of the 2 nd front flat surface 102 may be narrowed.

In the present embodiment, 2 suction passages 141 and 142 are provided corresponding to the 2 compression chambers a4 and a 5. The front suction duct 141 and the rear suction duct 142 are circumferentially offset so as not to communicate with each other, and more specifically, are offset by 180 °. This can suppress a problem caused by the communication between the suction passages 141 and 142, such as a decrease in the amount of fluid sucked into one of the compression chambers a4 and a5, for example, due to the suction of the fluid into the other compression chamber.

As shown in fig. 7, the compressor 10 includes a plurality of rear discharge passages 161 that discharge the fluid compressed in the rear compression chamber a5, a rear valve 162 that opens and closes the rear discharge passages 161, and a rear retainer 163 that adjusts the opening degree of the rear valve 162.

The rear discharge passage 161 is provided, for example, at a position radially outward of the rear compression chamber a5 and on the rear side of the 2 nd rear flat surface 122 in the front cylinder peripheral wall 32.

The rear discharge duct 161 is formed at a position shifted by 180 ° in the circumferential direction with respect to the front discharge duct 151, corresponding to the case where the 2 nd front flat surface 102 and the 2 nd rear flat surface 122 are shifted by 180 °. In addition, the rear discharge passage 161 is displaced in the axial direction Z with respect to the front discharge passage 151, corresponding to the case where the front compression chamber a4 and the rear compression chamber a5 are displaced in the axial direction Z.

The specific configurations of the rear discharge passage 161, the rear valve 162, and the rear holder 163 are basically the same as those of the front discharge passage 151, the front valve 152, and the front holder 153 except for the positions where they are provided, and therefore, detailed descriptions thereof are omitted. Note that "front" in the description of the front discharge passage 151, the front valve 152, and the front retainer 153 may be replaced with "rear". The discharge channels 151, 161 may also be referred to as discharge passages.

Next, the blade 131 will be explained. In the following description, of the 2 partial chambers partitioned by the vane 131, a partial chamber located on the subsequent side with respect to the vane 131 is referred to as a1 st partial chamber Ax, and a partial chamber located on the preceding side with respect to the vane 131 is referred to as a2 nd partial chamber Ay. Regarding the vane 131 partitioning the 1 st front compression chamber A4a and the 3 rd front compression chamber A4c, the 1 st part chamber Ax is the 1 st front compression chamber A4a, and the 2 nd part chamber Ay is the 3 rd front compression chamber A4 c. With respect to the vane 131 partitioning the 3 rd front compression chamber A4c and the 2 nd front compression chamber A4b, the 1 st part chamber Ax is the 3 rd front compression chamber A4c, and the 2 nd part chamber Ay is the 2 nd front compression chamber A4 b. With respect to the vane 131 partitioning the 2 nd front compression chamber A4b and the 1 st front compression chamber A4a, the 1 st part chamber Ax is the 2 nd front compression chamber A4b, and the 2 nd part chamber Ay is the 1 st front compression chamber A4 a. The same applies to the rear compression chamber a 5.

The pressures in the front compression chambers A4a to A4c are likely to be higher as they are arranged on the leading side in the rotation direction M. Specifically, it is easy to increase the number of the 1 st front compression chamber A4a, the 3 rd front compression chamber A4c, and the 2 nd front compression chamber A4b (particularly, a space on the rear side of the contact portion between the front rotor surface 71 and the 2 nd front flat surface 102). Therefore, the pressure of the 2 nd part chamber Ay at the advanced side with respect to the vane 131 is easily higher than the pressure of the 1 st part chamber Ax at the following side with respect to the vane 131.

As shown in fig. 9 to 13, the blade 131 is composed of a plurality of parts. Specifically, the vane 131 includes a vane main body 170 inserted into the vane groove 130, and 2 vane end seals 180 and 190 provided on both end surfaces 171 and 172 of the vane main body 170 in the axial direction Z. The both-blade- end seals 180 and 190 constitute both axial end portions of the blade 131, and the blade- end seals 180 and 190 are in contact with the stator surfaces 100 and 120.

The blade body 170 is made of, for example, the same material as the rotor 60 and the both fixed bodies 90 and 110, and is made of, for example, metal. The blade body 170 is plate-shaped, and is inserted into the blade groove 130 in a state where the thickness direction thereof coincides with the width direction of the blade groove 130. The blade body 170 extends in the axial direction Z and the radial direction R. In the present embodiment, the blade body 170 has a rectangular plate shape, but the present invention is not limited thereto, and the blade body 170 may have any shape as long as it has a plate shape. In addition, the vane main body 170 is inserted into the vane groove 130 regardless of the movement of the vane 131 in the axial direction Z.

Body attachment grooves 173 and 174 serving as body attachment portions are formed in both end surfaces 171 and 172 of the blade body 170. The body mounting grooves 173 and 174 extend in the radial direction R with a width in the thickness direction of the blade 131, and are open to both the inner side and the outer side in the radial direction R.

Each of the body mounting grooves 173 and 174 has a body groove bottom surface 173a and 174a, and a1 st body groove side surface 173b and 174b and a2 nd body groove side surface 173c and 174c extending from the body groove bottom surface 173a and 174 a. The 1 st body groove side surfaces 173b and 174b and the 2 nd body groove side surfaces 173c and 174c are surfaces intersecting with the circumferential direction (in other words, the direction orthogonal to both the axial direction Z and the radial direction R), and are 2 side surfaces facing each other while being separated from each other in the circumferential direction. The 2 nd body groove side surfaces 173c and 174c are arranged on the leading side of the 1 st body groove side surfaces 173b and 174b in the rotation direction M. That is, the 1 st body groove side 173b, 174b is a side of a subsequent side of the body mounting grooves 173, 174, and the 2 nd body groove side 173c, 174c is a side of an earlier side of the body mounting grooves 173, 174.

The tip seals 180, 190 are composed of a different material than the blade body 170, for example, a material that is more deformable (in other words, a softer material) than the blade body 170. For example, the tip seals 180, 190 are made of resin. The tip seals 180, 190 block the communication of the two partial chambers Ax, Ay at both sides of the blade 131 in the circumferential direction by abutting against the fixture faces 100, 120. In this embodiment, the leaf end seals 180, 190 are of the same shape. The contact portions between the tip seals 180 and 190 and the fixture surfaces 100 and 120 are referred to as tip contact portions Pa1 and Pa 2.

As shown in fig. 9 to 11, the tip seals 180 and 190 are, for example, elongated strips extending in the radial direction R. The tip seals 180, 190 include, for example, seal body portions 181, 191 that abut the fixture surfaces 100, 120, and seal attachment convex portions 182, 192 that are seal attachment portions attached to the blade body 170.

As shown in fig. 12, the seal body portions 181 and 191 have a width substantially equal to the thickness of the vane body 170, and are sandwiched between the end surfaces 171 and 172 of the vane body 170 and the fixture surfaces 100 and 120 in the axial direction Z. In other words, the seal body portions 181 and 191 are disposed between the end surfaces 171 and 172 of the vane body 170 and the fixture surfaces 100 and 120.

As shown in fig. 11 and 12, each of the seal body portions 181 and 191 has a seal surface 181a or 191a curved so as to project toward the stator surface 100 or 120, and a seal body bottom surface 181b or 191b facing the end surface 171 or 172 of the vane body 170 in the axial direction Z.

The sealing surfaces 181a, 191a face the fixture surfaces 100, 120 in the axial direction Z. The sealing surfaces 181a and 191a abut against the fixture surfaces 100 and 120. The curvature of the seal surfaces 181a and 191a is more gentle than the case where the seal main bodies 181 and 191 are formed in a semicircular shape. Specifically, the sealing surfaces 181a and 191a have a radius of curvature larger than 1/2, which is the thickness of the vane 131. However, the bending of the seal surfaces 181a and 191a is not limited to this.

The seal surfaces 181a, 191a extend in the radial direction R and abut against the fixture surfaces 100, 120 over the entire radial direction R. However, the present invention is not limited to this, and a part of the seal body portions 181 and 191 in the radial direction R may abut against the fixture surfaces 100 and 120.

The seal attachment convex portions 182 and 192 are protruding strips that protrude from the seal main body portions 181 and 191 toward the vane main body 170, have a width in the thickness direction of the vane 131, and extend in the radial direction R. The seal attachment convex portions 182, 192 have attachment tip end surfaces 182a, 192a, 1 st seal convex side surfaces 182b, 192b, and 2 nd seal convex side surfaces 182c, 192c arranged on the leading side with respect to the 1 st seal convex side surfaces 182b, 192 b. The 1 st and 2 nd sealing land surfaces 182b, 192b, 182c, 192c intersect with the circumferential direction. The 1 st sealing convex side surface 182b, 192b is a side surface on the subsequent side of the sealing attachment convex portions 182, 192, and the 2 nd sealing convex side surface 182c, 192c is a side surface on the preceding side of the sealing attachment convex portions 182, 192.

The tip seals 180, 190 are mounted to the blade body 170 by inserting the seal mounting bosses 182, 192 into the body mounting grooves 173, 174. The body mounting grooves 173 and 174 and the seal mounting convex portions 182 and 192 as body mounting portions face each other in the circumferential direction (in other words, the width direction of the vane groove 130). Specifically, the 1 st body groove side surfaces 173b and 174b and the 1 st sealing convex side surfaces 182b and 192b are circumferentially opposed to each other, and the 2 nd body groove side surfaces 173c and 174c and the 2 nd sealing convex side surfaces 182c and 192c are circumferentially opposed to each other. The tip seals 180, 190 are movable in the axial direction Z away from the blade body 170 or in the axial direction Z toward the blade body 170. 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 with respect to the vane body 170.

In view of the point that the tip seals 180 and 190 are movable in the axial direction Z with respect to the blade body 170 and the point that the blade 131 includes the blade body 170 and the tip seals 180 and 190, the blade 131 may be said to be configured to be expandable and contractible in the axial direction Z.

As shown in fig. 11 and 12, back pressure spaces 183, 193 for pressing the tip seals 180, 190 against the fixture surfaces 100, 120 are formed between the vane body 170 and the tip seals 180, 190.

The front back pressure space 183 is demarcated by a front mounting tip end face 182a, a front body groove bottom face 173a, a front 1 st body groove side face 173b, and a front 2 nd body groove side face 173 c. The width of the front seal mounting boss 182 is the same as or slightly shorter than the width of the front body mounting groove 173. Accordingly, the fluid can flow into the front back pressure space 183 through the gap between the front seal mounting convex portion 182 and the front body mounting groove 173. The same is true for the back pressure space 193.

As shown in fig. 11 and 12, the compressor 10 includes the introduction grooves 184 and 194 for introducing the fluid in the 2 nd part chamber Ay into the back pressure spaces 183 and 193.

A plurality of lead-in slots 184, 194 are formed in each tip seal 180, 190. A plurality of (2 in the present embodiment) introduction grooves 184 and 194 are provided in the tip seals 180 and 190 so as to be separated in the radial direction R. However, the number of the introduction grooves 184 and 194 is arbitrary, and may be 1, or 3 or more.

As shown in fig. 12, the introduction grooves 184 and 194 are formed over the seal body portions 181 and 191 and the seal attachment convex portions 182 and 192. More specifically, the introduction grooves 184 and 194 are formed over the portions of the seal body bottom surfaces 181b and 191b on the leading side of the seal attachment convex portions 182 and 192, and the 2 nd seal convex side surfaces 182c and 192 c.

The front guide groove 184 is provided on the leading side portion of the leading blade end seal 180 and opens to the 2 nd partial chamber Ay, which is a partial chamber located on the leading side. Similarly, the rear introduction groove 194 is provided in the front side portion of the trailing end seal 190 and opens to the 2 nd part chamber Ay. Thus, the fluid in the part 2 chamber Ay easily flows into the back pressure spaces 183, 193 through the introduction grooves 184, 194.

According to this structure, the tip seals 180 and 190 are pressed against the fixed body surfaces 100 and 120 by the fluid in the back pressure spaces 183 and 193, and therefore, it is difficult to generate a gap between the tip seals 180 and 190 and the fixed body surfaces 100 and 120.

Specifically, in the structure in which the rotating body 60 is supported by the rotating body cylindrical portion 61 on the two fixed bodies 90 and 110, a gap may be generated between at least one of the two fixed body surfaces 100 and 120 and the blade 131 due to a dimensional error, an assembly error, or the like at the time of manufacturing the rotating body 60 and the two fixed bodies 90 and 110. The gap may be generated over the entire angular range in which the blade 131 rotates, or may be generated only in a specific angular range.

In this regard, according to the present embodiment, as shown in fig. 12, when the blade main body 170 rotates in accordance with the rotation of the rotor 60, the tip seals 180 and 190 are pressed in the rotation direction M by the blade main body 170. As a result, the 1 st seal convex side surface 182b, 192b, which is the side surface on the subsequent side of the seal attachment convex portions 182, 192, abuts against the 1 st main body groove side surfaces 173b, 174b, which are the side surfaces on the subsequent side of the main body attachment grooves 173, 174, and the seal at the abutting portions (hereinafter, referred to as "side abutting portions Pb1, Pb 2") is secured. Therefore, the fluid is restricted from moving between the two partial chambers Ax, Ay through between the tip seals 180, 190 and the vane body 170.

In particular, in the present embodiment, the side surface contact portions Pb1, Pb2 extend in the axial direction Z. Therefore, even when the tip seals 180 and 190 are moved in the axial direction Z with respect to the vane main body 170, the 1 st seal convex side surfaces 182b and 192b are easily maintained in contact with the 1 st main body groove side surfaces 173b and 174 b.

In addition, since the body mounting grooves 173 and 174 constitute the body mounting portions, the side contact portions Pb1 and Pb2 can be said to be contact portions between the body mounting portions and the seal mounting convex portions 182 and 192.

On the other hand, a gap is formed on the leading side in the rotation direction M. Specifically, a gap is formed between the 2 nd seal convex side surfaces 182c and 192c and the 2 nd body groove side surfaces 173c and 174 c. As a result, as shown by the two-dot chain line in fig. 12, the fluid in the 2 nd partial chamber Ay is introduced into the back pressure spaces 183, 193 through the gap. In particular, in the present embodiment, the fluid in the part 2 chamber Ay easily flows into the back pressure spaces 183, 193 through the introduction grooves 184, 194.

The tip seals 180 and 190 are pressed against the stator surfaces 100 and 120 by the fluid flowing into the back pressure spaces 183 and 193. Therefore, the tip seals 180 and 190 (specifically, the seal surfaces 181a and 191a) are in contact with the stator surfaces 100 and 120, and the seal therebetween is ensured. This can prevent gaps from being formed between the tip seals 180 and 190 and the fixture surfaces 100 and 120.

The depth of the body mounting grooves 173, 174 is deeper than the protruding dimension of the seal mounting bosses 182, 192, for example. Therefore, even when the seal body bottom surfaces 181b and 191b abut against the end surfaces 171 and 172, the back pressure spaces 183 and 193 are secured. This can avoid the situation where the back pressure spaces 183 and 193 are not formed. However, the depth of the body mounting grooves 173 and 174 is not limited to this, and may be, for example, equal to or less than the protruding dimension of the seal mounting projections 182 and 192.

As shown in fig. 9 and 13, the blade 131 includes a blade outer peripheral end surface 201 and a blade inner peripheral end surface 202, which are both end surfaces in the radial direction R. The blade outer peripheral end surface 201 is an outer peripheral side (i.e., radially outer side) end surface of both end surfaces in the radial direction R, and the blade inner peripheral end surface 202 is an inner peripheral side (i.e., radially inner side) end surface of both end surfaces in the radial direction R.

The vane outer peripheral end surface 201 is constituted by an outer peripheral end surface of the vane main body 170 and outer peripheral end surfaces of both the vane end seals 180, 190. The outer peripheral end surface of the vane main body 170 is continuous with and coplanar with the outer peripheral end surfaces of the vane end seals 180 and 190 in the axial direction Z. Thereby, the blade outer peripheral end surface 201 becomes 1 surface.

The vane outer peripheral end surface 201 abuts against the front cylinder inner peripheral surface 33 regardless of the movement of the vane 131. In other words, the front cylinder inner peripheral surface 33 extends longer than the movement range of the vane 131 in the axial direction Z so as to abut against the vane outer peripheral end surface 201 regardless of the movement of the vane 131.

As shown in fig. 13, the vane outer peripheral end surface 201 may be curved convexly outward in the radial direction so as to be continuous with the ring outer peripheral surface 73 in the circumferential direction, for example, and may have the same curvature as the front cylinder inner peripheral surface 33. That is, the vane outer peripheral end surface 201 and the front cylinder inner peripheral surface 33 may be in surface contact. However, the shape of the blade outer peripheral end surface 201 is not limited to this.

The vane inner peripheral end surface 202 is constituted by an inner peripheral end surface of the vane main body 170 and inner peripheral end surfaces of both the vane end seals 180 and 190, similarly to the vane outer peripheral end surface 201. The inner peripheral end surface of the vane main body 170 is continuous with and coplanar with the inner peripheral end surfaces of the vane end seals 180 and 190 in the axial direction Z. Thereby, the vane inner peripheral end surface 202 has 1 surface.

As shown in fig. 13, the vane inner peripheral end surface 202 may be curved so as to be recessed radially outward, for example, and may have the same curvature as the curvature of the cylindrical portion outer peripheral surface 62. That is, the vane inner peripheral end surface 202 and the cylinder outer peripheral surface 62 may be in surface contact. However, the shape of the blade inner peripheral end surface 202 is not limited to this.

Next, a series of operations of the compressor 10 will be described with reference to fig. 14 and 15. Fig. 14 and 15 are developed views schematically showing the rotating body 60, the fixed bodies 90 and 110, and the blades 131, and the phases of the rotating body 60 and the blades 131 are different in the two views. In fig. 14 and 15, the respective channels 141, 142, 151, 161 are schematically shown.

As shown in fig. 14 and 15, when the rotary shaft 12 is rotated by the electric motor 13, the rotary body 60 is rotated accordingly. Thereby, the plurality of blades 131 rotate while moving in the axial direction Z along the both fixture surfaces 100 and 120 while maintaining the positional relationship with each other in the circumferential direction. In fig. 14 and 15, the plurality of blades 131 move downward while moving in the horizontal direction on the paper. As a result, the volumes of the front compression chambers A4a to A4c and the rear compression chambers A5a to A5c change, and the fluid is sucked, compressed, or expanded. That is, the vane 131 rotates while moving in the axial direction Z, and thereby the fluid is sucked and compressed in the compression chambers a4 and a 5.

Specifically, the volume of the space located on the leading side of the 2 nd front flat surface 102 in the 2 nd front compression chamber A4b and the 1 st front compression chamber A4a increases, and the fluid is sucked from the front suction passage 141.

On the other hand, in the space (subsequent side space) located on the subsequent side of the 2 nd front flat surface 102 in the 2 nd front compression chamber A4b and the 3 rd front compression chamber A4c, the volume decreases with the rotation of the rotary body 60, and the intake fluid is compressed. In detail, the suction fluid is compressed in the 3 rd front compression chamber A4c, and the fluid compressed in the 3 rd front compression chamber A4c is further compressed in the space subsequent to the 2 nd front compression chamber A4 b.

When the pressure in the space on the subsequent side of the 2 nd front compression chamber A4b exceeds the threshold value, the front valve 152 is opened, and the fluid compressed in the 2 nd front compression chamber A4b flows toward the discharge chamber a1 via the front discharge passage 151. The same applies to the rear compression chamber a 5.

As described above, the rotary body 60 and the vanes 131 rotate, and the cyclic operation of suction and compression is repeated in 1 cycle of 480 ° in 3 partial chambers in the compression chambers a4 and a 5. Specifically, in each of the compression chambers a4 and a5, the fluid is sucked or expanded in a phase of 0 ° to 240 °, and the fluid is compressed in a phase of 240 ° to 480 °.

For example, the angular position of the circumferential center of the 2 nd front flat surface 102 is set to 0 °, and the 1 st blade 131 is disposed in the circumferential center. The angle is set to increase from the angular position of 0 ° to the rotation direction M. In this case, before the 1 st blade 131 reaches the angular position of 240 ° from the angular position of 0 °, suction of the fluid is performed in the partial chamber located at the subsequent side with respect to the 1 st blade 131.

In particular, since the front suction opening 141a is formed at least over a range from the end portion on the leading side of the 2 nd front flat surface 102 to the angular position of 120 °, the fluid is sucked before the 1 st blade 131 reaches the angular position of 240 °. This can avoid expansion of the fluid in some of the chambers, and can improve efficiency.

Before the 2 nd blade 131 located on the subsequent side of the 1 st blade 131 reaches the angular position of 360 ° from the angular position of 120 °, the fluid is compressed in the partial chamber located on the preceding side with respect to the 2 nd blade 131.

The 3 front compression chambers A4a to A4c are compression chambers different in phase from each other. That is, the space defined by the front rotor surface 71, the front stator surface 100, the cylindrical portion outer peripheral surface 62, and the front cylinder inner peripheral surface 33 is partitioned into 3 compression chambers having mutually different phases by the plurality of vanes 131. In the present embodiment, while the rotary body 60 rotates 480 °, the fluid is sucked into and compressed in each of the front 3 compression chambers and the rear 3 compression chambers.

In the above description, the positional relationship between the front suction path 141 and the front discharge path 151, which is defined by dividing the 3 front compression chambers A4a to A4c by the plurality of vanes 131, has been described, but the present invention is not limited thereto. For example, the following description will be made with a focus on 1 cycle of 1 compression chamber.

The 1 st vane 131 moves toward the leading side with respect to the 2 nd front flat surface 102, and a compression chamber communicating with the front suction passage 141 is formed at a position on the trailing side with respect to the 1 st vane 131. The compression chamber increases in volume while maintaining a state of communication with the front suction passage 141 as the vane 131 rotates. Thereby, the fluid is sucked into the compression chamber.

Thereafter, the 2 nd vane 131 moves toward the leading side with respect to the 2 nd front flat surface 102, and the compression chamber is partitioned by the 1 st vane 131 and the 2 nd vane 131. The 2 nd vane 131 is sucked into the compression chamber before reaching the leading end of the front suction opening 141 a.

Then, when the 2 nd vane 131 moves further to the leading side beyond the leading end of the front suction opening 141a, the compression chamber does not communicate with the front suction path 141, and when the rotary body 60 further rotates, the compression chamber communicates with the front discharge path 151. In addition, since the volume of the compression chamber decreases with the rotation of the rotary body 60 at this stage, the fluid is compressed in the compression chamber. Then, when the 2 nd vane 131 reaches the position of abutting against the 2 nd front flat surface 102, the volume of the compression chamber becomes "0", and 1 cycle of suction and compression in the compression chamber ends.

According to the present embodiment described in detail above, the following effects are obtained.

(1-1) the compressor 10 includes a rotary shaft 12, a rotary body 60 that rotates in accordance with the rotation of the rotary shaft 12, fixed bodies 90 and 110 that do not rotate in accordance with the rotation of the rotary shaft 12, and blades 131 that are inserted into blade grooves 130 formed in the rotary body 60 and rotate while moving in the axial direction Z in accordance with the rotation of the rotary body 60. The rotor 60 has rotor surfaces 71, 72 intersecting the axial direction Z, and the stator 90, 110 has stator surfaces 100, 120 facing the rotor surfaces 71, 72 in the axial direction Z. The compressor 10 includes compression chambers a4, a5 defined by the rotor surfaces 71, 72 and the stator surfaces 100, 120. The vane 131 rotates while moving in the axial direction Z, and thereby the fluid is sucked into and compressed in the compression chambers a4 and a 5.

The vane 131 includes a vane main body 170 inserted into the vane groove 130, and vane end seals (seal members) 180 and 190 attached to end surfaces 171 and 172 of the vane main body 170 in the axial direction Z in a state movable in the axial direction Z relative to the vane main body 170. The tip seals 180, 190 are pressed against the stator surfaces 100, 120 by fluid (pressure) in back pressure spaces 183, 193 formed between the vane body 170 and the tip seals 180, 190, and thereby abut against the stator surfaces 100, 120.

According to this structure, the tip seals 180 and 190 are pressed by the fluid (pressure) in the back pressure spaces 183 and 193 to be in contact with the fixed body surfaces 100 and 120, and the seal between the vane 131 and the fixed body surfaces 100 and 120 is secured. Therefore, the generation of the gap between the blade 131 and the fixture surfaces 100 and 120 can be suppressed.

(1-2) the front compression chamber a4 includes a1 st part chamber Ax and a2 nd part chamber Ay provided at both sides of the vane 131 in the circumferential direction. The 1 st partial chamber Ax is disposed on the downstream side of the vane 131, and the 2 nd partial chamber Ay is disposed on the upstream side of the vane 131. End surfaces 171 and 172 of the blade body 170 are provided with body attachment grooves 173 and 174 as body attachment portions. The tip seals 180, 190 include seal attachment bosses 182, 192 that are attached to the body attachment grooves 173, 174. The seal-mounting convex portions 182 and 192 and the body-mounting grooves 173 and 174 (specifically, the 1 st body-groove side surfaces 173b and 174b) are opposed to each other in the circumferential direction of the rotary shaft 12.

According to this configuration, when the blade 131 (more specifically, the blade body 170) rotates in accordance with the rotation of the rotating body 60, the seal attachment convex portions 182 and 192 and the body attachment grooves 173 and 174 circumferentially contact each other, and the seal between the tip seals 180 and 190 and the blade body 170 is secured by the side contact portions Pb1 and Pb2 as the contact portions. This can prevent the fluid from moving between the two partial chambers Ax, Ay through the back pressure spaces 183, 193.

(1-3) in particular, in the present embodiment, body mounting grooves 173, 174 formed at end surfaces 171, 172 of the blade body 170 are employed as body mounting portions. The body mounting grooves 173, 174 have a1 st body groove side surface 173b, 174b as a side surface of the succeeding side, and a2 nd body groove side surface 173c, 174c as a side surface of the preceding side.

The tip seals 180, 190 have seal body portions 181, 191 that abut the fixture surfaces 100, 120. The seal attachment convex portions 182, 192 protrude from the seal body portions 181, 191 toward the end surfaces 171, 172 of the blade body 170. The seal-attaching convex portions 182, 192 have the 1 st seal convex side surface 182b, 192b as the side surface on the subsequent side and the 2 nd seal convex side surface 182c, 192c as the side surface on the preceding side.

The tip seals 180, 190 are mounted to the blade body 170 by inserting the seal mounting bosses 182, 192 into the body mounting grooves 173, 174. The 1 st sealing convex side surfaces 182b, 192b and the 1 st body groove side surfaces 173b, 174b are circumferentially opposed to each other.

According to this structure, the tip seals 180 and 190 are attached to the blade body 170 by inserting the seal attachment convex portions 182 and 192 into the body attachment grooves 173 and 174. In this case, the 1 st seal convex side surfaces 182b and 192b and the 1 st main body groove side surfaces 173b and 174b circumferentially contact each other with the rotation of the vane 131 (specifically, the vane main body 170), and the side contact portions Pb1 and Pb2 serving as contact portions ensure sealing between the vane main body 170 and the tip seals 180 and 190.

In the present embodiment, the side surface contact portions Pb1 and Pb2 extend in the axial direction Z. Therefore, even if the tip seals 180, 190 move toward the fixture surfaces 100, 120, the 1 st seal convex side surfaces 182b, 192b are easily maintained in contact with the 1 st body groove side surfaces 173b, 174 b. Therefore, the leakage of the fluid through the back pressure spaces 183, 193 or the dropping of the tip seals 180, 190 can be suppressed.

(1-4) particularly, since the 1 st sealing convex side surfaces 182b and 192b and the 1 st body groove side surfaces 173b and 174b are in contact with each other, a gap is easily generated between the 2 nd sealing convex side surfaces 182c and 192c and the 2 nd body groove side surfaces 173c and 174 c. Therefore, the fluid in the part 2 chamber Ay easily enters the back pressure spaces 183, 193 through the gap. The pressure of the fluid in the 2 nd partial chamber Ay is easily higher than the pressure in the 1 st partial chamber Ax. For example, with respect to the vane 131 separating the 3 rd and 2 nd front compression chambers A4c and A4b from each other, the 2 nd front compression chamber A4b is at a high pressure. Therefore, the force with which the fluid in the back pressure spaces 183, 193 presses the tip seals 180, 190 tends to increase. This improves the sealing property between the blade 131 and the fixture surfaces 100 and 120.

(1-5) introduction grooves 184 and 194 for introducing the fluid in the 2 nd part chamber Ay into the back pressure spaces 183 and 193 are formed in the tip seals 180 and 190.

With this configuration, the fluid in the 2 nd part chamber Ay can be easily introduced into the back pressure spaces 183, 193 through the introduction grooves 184, 194. Therefore, the tip seals 180 and 190 are easily pressed against the fixture surfaces 100 and 120 by the fluid in the 2 nd part chamber Ay, which is likely to be at a relatively high pressure. Therefore, the sealing property between the blade 131 and the fixture surfaces 100 and 120 can be further improved.

(1-6) the introduction grooves 184 and 194 are disposed closer to the 2 nd part chamber Ay than the side contact portions Pb1 and Pb 2. Accordingly, the fluid introduced into the back pressure spaces 183 and 193 through the introduction grooves 184 and 194 is less likely to leak into the 1 st partial chamber Ax due to the side surface contact portions Pb1 and Pb 2. Therefore, it is possible to suppress a problem that the fluid in the 2 nd partial chamber Ay is likely to leak into the 1 st partial chamber Ax due to the introduction grooves 184 and 194.

(1-7) the introduction grooves 184 and 194 are formed over the portions of the bottom surfaces 181b and 191b of the seal bodies located on the leading side of the seal attachment convex portions 182 and 192, and the 2 nd seal convex side surfaces 182c and 192 c.

With this configuration, even in a state where the seal body bottom surfaces 181b and 191b and the end surfaces 171 and 172 of the vane body 170 abut against each other, the fluid in the 2 nd part chamber Ay can be introduced into the back pressure spaces 183 and 193.

(embodiment 2)

As shown in fig. 16, in the present embodiment, the 1 st body groove side surfaces 212 and 215 and the 2 nd body groove side surfaces 213 and 216 are inclined with respect to the axial direction Z such that the body mounting grooves 211 and 214 gradually become narrower as they become deeper. In the present embodiment, the 1 st body groove side surfaces 212 and 215 are inclined so as to gradually displace toward the leading side in the rotational direction M from the end surfaces 171 and 172 of the blade body 170 as the body mounting grooves 211 and 214 become deeper (in other words, as they approach the body groove bottom surfaces 173a and 174 a).

The seal attachment convex portions 221, 224 are formed to be gradually narrowed in width as approaching from the base end to the tip end, corresponding to the case where the main body attachment grooves 211, 214 are gradually narrowed in width as becoming deeper. Specifically, the 1 st seal convex side surfaces 222, 225 and the 2 nd seal convex side surfaces 223, 226 are inclined with respect to the axial direction Z in accordance with the inclination of the 1 st body groove side surfaces 212, 215 and the 2 nd body groove side surfaces 213, 216. The 1 st seal convex side surfaces 222, 225 are inclined so as to gradually displace toward the leading side in the rotation direction M as approaching from the base end to the tip end.

The 1 st seal convex side surfaces 222, 225 and the 1 st body groove side surfaces 212, 215 are circumferentially opposed to each other, and the inclination angles thereof are the same in the present embodiment. Similarly, the 2 nd seal convex side surfaces 223 and 226 and the 2 nd main body groove side surfaces 213 and 216 are circumferentially opposed to each other, and the inclination angles thereof are the same in the present embodiment.

In this configuration, when the blades 131 (more specifically, the blade main bodies 170) rotate in accordance with the rotation of the rotating body 60, the 1 st seal convex side surfaces 222 and 225 and the 1 st main body groove side surfaces 212 and 215 circumferentially abut against each other. Thereby, the side surface contact portions Pb1, Pb2 are inclined with respect to the axial direction Z.

Further, as in embodiment 1, back pressure spaces 183, 193 are formed between the tip seals 180, 190 and the vane main body 170, and the tip seals 180, 190 are pressed against the fixture surfaces 100, 120 by the back pressure spaces 183, 193.

According to the present embodiment described in detail above, the following operational effects are exhibited.

(2-1) the 1 st body groove side surfaces 212 and 215 are inclined with respect to the axial direction Z so as to gradually displace toward the advanced side in the rotational direction M as the body mounting grooves 211 and 214 become deeper. The 1 st seal convex side surfaces 222, 225 are inclined with respect to the axial direction Z so as to gradually displace toward the leading side in the rotational direction M as approaching from the base end to the tip end. Also, the 1 st body groove side surfaces 212, 215 and the 1 st sealing convex side surfaces 222, 225 are circumferentially opposed to each other.

According to this configuration, when the blade body 170 rotates with the rotation of the rotating body 60, the 1 st seal convex side surfaces 222 and 225 and the 1 st body groove side surfaces 212 and 215 are brought into contact with each other, and the side surface contact portions Pb1 and Pb2, which are contact portions, are applied with the pressing forces F1 and F2 in the direction orthogonal to the side surface contact portions Pb1 and Pb 2.

The side surface contact portions Pb1, Pb2 are inclined with respect to the axial direction Z so as to gradually displace toward the advanced side in the rotational direction M as they are separated from the fixture surfaces 100, 120. Therefore, the pressing forces F1 and F2 include components in the axial direction Z, specifically, components in the direction toward the fixture surfaces 100 and 120. Accordingly, the tip seals 180 and 190 are pressed against the fixture surfaces 100 and 120, and therefore, the sealing performance of the tip contact portions Pa1 and Pa2 can be improved.

In the present embodiment, the 2 nd seal convex side surfaces 223 and 226 and the 2 nd body groove side surfaces 213 and 216 are inclined with respect to the axial direction Z, but the present invention is not limited thereto, and the 1 st seal convex side surfaces 222 and 225 and the 1 st body groove side surfaces 212 and 215 may be inclined at the same angle in the same direction. In this case, the width of the body mounting grooves 211, 214 and the width of the seal mounting protrusions 221, 224 are constant. The 2 nd seal convex side surfaces 223 and 226 and the 2 nd body groove side surfaces 213 and 216 may be parallel to the axial direction Z. That is, the 2 nd sealing convex side surfaces 223 and 226 and the 2 nd main body groove side surfaces 213 and 216 may have any structure.

(embodiment 3)

As shown in fig. 17, in the present embodiment, the seal attachment convex portions 182 and 192 and the body attachment grooves 173 and 174 are disposed closer to the 1 st partial chamber Ax than the 2 nd partial chamber Ay. Specifically, the center line passing through the circumferential centers of the seal attachment convex portions 182, 192 and the body attachment grooves 173, 174 is located at a position shifted toward the 1 st part chamber Ax (in other words, a position shifted toward the following side) from the center line passing through the circumferential centers of the tip seals 180, 190. In the present embodiment, the side surface contact portions Pb1 and Pb2 correspond to the "contact portions of both mounting portions".

Next, the operation of the present embodiment will be described.

As shown in fig. 17, the tip seals 180 and 190 are applied with the 1 st pressing forces Ff1 and Fr1 as the pressing forces applied from the fluid in the 1 st part chamber Ax, and the 2 nd pressing forces Ff2 and Fr2 as the pressing forces applied from the fluid in the 2 nd part chamber Ay. The 1 st pressing forces Ff1, Fr1 act in a direction orthogonal to a line connecting the distal end contact portions Pa1, Pa2 and the ends of the side surface contact portions Pb1, Pb2 close to the seal body bottom surfaces 181b, 191 b. The 2 nd pressing forces Ff2, Fr2 act in a direction orthogonal to a line connecting the distal end contact portions Pa1, Pa2 and the ends of the side surface contact portions Pb1, Pb2 close to the body groove bottom surfaces 173a, 174 a. The 2 nd pressing forces Ff2 and Fr2 are likely to be larger than the 1 st pressing forces Ff1 and Fr 1.

As described above, the magnitude and direction of the force are different between the 2 nd pressing forces Ff2 and Fr2 and the 1 st pressing forces Ff1 and Fr1, and therefore, there is imbalance between the two. The tip seals 180, 190 are subjected to the combined forces of the 2 nd pressing force Ff2, Fr2 and the 1 st pressing force Ff1, Fr 1.

In this configuration, the inventors of the present application have found that when the tip end contact portions Pa1, Pa2, which are contact portions of the seal surfaces 181a, 191a and the stator surfaces 100, 120, are disposed closer to the 1 st partial chamber Ax than the side surface contact portions Pb1, Pb2, in other words, when the tip end contact portions Pa1, Pa2 are disposed further to the rear side in the rotational direction M than the side surface contact portions Pb1, Pb2, a pressing force in a direction of separating from the stator surfaces 100, 120 is applied to the tip seals 180, 190.

For example, as shown in the front side of fig. 17, when the tip seal 180 abuts against the front curved surface 103 inclined upward with respect to the rotational direction M, the front tip abutting portion Pa1 is likely to be located on the leading side in the rotational direction M with respect to the front side abutting portion Pb 1. Therefore, the resultant force of the front 1 st pressing force Ff1 and the front 2 nd pressing force Ff2 is likely to act in the direction toward the front fixture surface 100. Thus, the tip seal 180 is easily pressed against the front fixture surface 100, and thus the sealing performance of the tip contact portion Pa1 can be improved.

On the other hand, as on the rear side, when the trailing edge seal 190 abuts against the curved rear surface 123 inclined downward with respect to the rotation direction M, the rear tip end abutment portion Pa2 is likely to be located on the rear side with respect to the widthwise central portion of the rear seal surface 191 a. Therefore, there may be a case where the rear tip end abutment portion Pa2 is located at the subsequent side from the rear side abutment portion Pb 2. In this case, the resultant force of the rear 1 st pressing force Fr1 and the rear 2 nd pressing force Fr2 tends to be in a direction away from the rear fixture surface 120.

In this regard, in the present embodiment, as shown in fig. 17, the rear seal attachment convex portion 192 and the rear body attachment groove 174 are disposed offset close to the 1 st partial chamber Ax, and therefore the rear side surface contact portion Pb2 is disposed in the vicinity of the 1 st partial chamber Ax. Thus, the rear distal end contact portion Pa2 is less likely to be located on the rear side of the rear side surface contact portion Pb2, and therefore, the component in the axial direction Z of the resultant force of the rear 1 st pressing force Fr1 and the rear 2 nd pressing force Fr2 is less likely to be in the direction away from the rear fixture surface 120. Even when the rear distal end contact portion Pa2 is disposed on the rear side of the rear side surface contact portion Pb2, the difference in the circumferential direction between the two portions is likely to be small, and therefore the force component in the direction away from the rear anchor surface 120 is likely to be small. Thus, the trailing lobe seal 190 is difficult to separate from the trailing anchor face 120.

According to the present embodiment described in detail above, the following effects are obtained.

(3-1) the fixed body surfaces 100 and 120 are annular surfaces including the 2 nd flat surfaces 102 and 122 as fixed body contact surfaces that contact the rotating body surfaces 71 and 72, and the pair of curved surfaces 103 and 123 provided on both sides in the circumferential direction with respect to the 2 nd flat surfaces 102 and 122. The pair of curved surfaces 103 and 123 are curved in the axial direction Z so as to gradually separate from the rotor surfaces 71 and 72 as they separate from the 2 nd flat surfaces 102 and 122 in the circumferential direction. The seal-mounting convex portions 182 and 192 and the body-mounting grooves 173 and 174 are disposed closer to the 1 st partial chamber Ax than to the 2 nd partial chamber Ay. In other words, the seal mounting bosses 182, 192 and the body mounting grooves 173, 174 are disposed offset to the subsequent side from the center in the circumferential direction of the tip seals 180, 190.

With this structure, the side surface contact portions Pb1, Pb2 are biased to the subsequent side. This can suppress the distal end contact portions Pa1, Pa2 from being located on the rear side of the side contact portions Pb1, Pb 2. Further, even in the case where the distal end contact portions Pa1, Pa2 are disposed on the rear side of the side surface contact portions Pb1, Pb2, the difference in the circumferential direction between the two contact portions can be reduced. This can suppress the force acting on the tip seals 180 and 190 in the direction away from the fixture surfaces 100 and 120, or reduce the force itself. Therefore, when the tip end seals 180 and 190 pass through the curved surfaces 103 and 123 inclined downward with respect to the rotation direction M, the sealability of the tip end contact portions Pa1 and Pa2 can be prevented from being lowered.

(embodiment 4)

Next, embodiment 4 will be explained. In embodiment 4, the structure for attaching the blade body and the tip seal is different from that in embodiment 1.

As shown in fig. 18, in the present embodiment, the seal body portions 181 and 191 have seal attachment grooves 231 and 234 recessed from the seal body bottom surfaces 181b and 191b toward the fixture surfaces 100 and 120. The seal mounting grooves 231, 234 as seal mounting portions have a width in the thickness direction of the blade 131 and extend in the radial direction R, for example. The seal attachment grooves 231 and 234 include 1 st seal groove side surfaces 232 and 235 as the side surfaces on the subsequent side in the rotation direction M, and 2 nd seal groove side surfaces 233 and 236 as the side surfaces on the preceding side in the rotation direction M. The 2 nd seal groove side surfaces 233, 236 are inclined with respect to the axial direction Z, for example, in such a manner as to be gradually displaced rearward as the seal mounting grooves 231, 234 become deeper.

Correspondingly, the blade body 170 includes body attachment convex portions 241 and 244 protruding from the end surfaces 171 and 172 of the blade body 170 toward the fixture surfaces 100 and 120. The body mounting convex portions 241 and 244 as the body mounting portions are, for example, ribs having a width in the thickness direction of the blade 131 and extending in the radial direction R. The main body attachment convex portions 241 and 244 have 1 st main body convex side surfaces 242 and 245 which are side surfaces on the subsequent side in the rotational direction M, and 2 nd main body convex side surfaces 243 and 246 which are side surfaces on the preceding side in the rotational direction M.

The 2 nd main body convex side surfaces 243 and 246 are inclined with respect to the axial direction Z so as to be gradually displaced rearward as approaching the tip from the base ends of the main body mounting convex portions 241 and 244, for example.

The body mounting bosses 241, 244 are part of the blade body 170. Therefore, the main body attachment projections 241 and 244 are made of a material harder than the blade end seals 180 and 190, and are made of metal, for example.

In this configuration, the tip seals 180 and 190 are attached to the blade body 170 by inserting the body attachment convex portions 241 and 244 into the seal attachment grooves 231 and 234. The 1 st seal groove side surfaces 232 and 235 and the 1 st main body convex side surfaces 242 and 245 circumferentially oppose each other, and the 2 nd seal groove side surfaces 233 and 236 and the 2 nd main body convex side surfaces 243 and 246 circumferentially oppose each other. Therefore, when the blade body 170 rotates in accordance with the rotation of the rotating body 60, the 2 nd body convex side surfaces 243 and 246, which are the leading side surfaces of the body attachment convex portions 241 and 244, and the 2 nd seal groove side surfaces 233 and 236, which are the leading side surfaces of the seal attachment grooves 231 and 234, are circumferentially abutted against each other. Further, at the contact portions (specifically, the side contact portions Pb1 and Pb2), the sealing is ensured so that the fluid does not move.

Further, as in embodiment 1, back pressure spaces 183, 193 are formed between the tip seals 180, 190 and the vane main body 170, and the tip seals 180, 190 are pressed against the fixture surfaces 100, 120 by the back pressure spaces 183, 193.

According to the present embodiment described in detail above, the following operational effects are exhibited.

(4-1) the tip seals 180, 190 are constructed of a material that is softer than the blade body 170. The tip seals 180, 190 have seal body portions 181, 191 that abut the fixture surfaces 100, 120. The seal body portions 181, 191 have seal body bottom surfaces 181b, 191b that face the end surfaces 171, 172 of the vane body 170. Moreover, the tip seals 180, 190 have seal mounting grooves 231, 234 recessed from the seal body bottom surfaces 181b, 191 b. The blade body 170 has body attachment convex portions 241, 244 protruding from the end surfaces 171, 172 of the blade body 170. Then, the tip seals 180 and 190 are attached to the blade body 170 by inserting the body attachment convex portions 241 and 244 into the seal attachment grooves 231 and 234.

According to this structure, the tip seals 180 and 190 are attached to the blade body 170 by inserting the body attachment convex portions 241 and 244 into the seal attachment grooves 231 and 234. In this case, as compared with the structure in which the seal attachment convex portions 182 and 192 are inserted into the main body attachment grooves 173 and 174 as in embodiment 1, it is possible to suppress the problem that the tip seals 180 and 190 fall off.

Specifically, in the structure in which the seal-attaching convex portions 182 and 192 are inserted into the main body attachment grooves 173 and 174 as in embodiment 1, the rigidity of the seal-attaching convex portions 182 and 192 cannot be secured, and there is a possibility that the tip seals 180 and 190 may be detached from the blade main body 170 due to the deformation of the seal-attaching convex portions 182 and 192.

In particular, the tip seals 180 and 190 as the seal members are formed of a flexible material that is easily deformed to improve sealing performance. Therefore, the rigidity of the tip seals 180 and 190 tends to be low, and the above-described problem tends to occur.

In contrast, according to the present embodiment, the main body attachment convex portions 241 and 244 of the blade main body 170 are inserted into the seal attachment grooves 231 and 234. The body mounting projections 241, 244 are a part of the blade body 170 that is harder than the tip seals 180, 190, and therefore are less likely to deform than the tip seals 180, 190 (seal mounting projections 182, 192). In addition, the rigidity of the tip seals 180, 190 tends to be higher in the structure in which the seal mounting grooves 231, 234 are provided, as compared with the structure in which the seal mounting convex portions 182, 192 are provided. Therefore, the problem that the tip seals 180 and 190 are deformed and detached from the blade body 170 can be suppressed.

(4-2) the seal installation grooves 231, 234 have 1 st seal groove side surfaces 232, 235 as the side surfaces on the subsequent side, and 2 nd seal groove side surfaces 233, 236 as the side surfaces on the preceding side. The body attachment convex portions 241 and 244 have 1 st body convex side surfaces 242 and 245 as the side surfaces on the subsequent side and 2 nd body convex side surfaces 243 and 246 as the side surfaces on the preceding side. The 2 nd body convex side surfaces 243, 246 and the 2 nd seal groove side surfaces 233, 236 are circumferentially opposed to each other.

The 2 nd seal groove side surfaces 233, 236 are inclined with respect to the axial direction Z in such a manner as to be gradually displaced rearward as the seal installation grooves 231, 234 become deeper. The 2 nd main body convex side surfaces 243 and 246 are inclined with respect to the axial direction Z so as to be gradually displaced rearward as approaching the tip from the base ends of the main body mounting convex portions 241 and 244.

According to this configuration, when the vane body 170 rotates with the rotation of the rotating body 60, the 2 nd body convex side surfaces 243 and 246 and the 2 nd seal groove side surfaces 233 and 236 abut against each other. Pressing forces F1 and F2 including components in the direction toward the fixture surfaces 100 and 120 are applied to the tip seals 180 and 190 through side contact portions Pb1 and Pb2 as contact portions thereof. Accordingly, the tip seals 180 and 190 can be pressed against the fixture surfaces 100 and 120 by the pressing forces F1 and F2, and thus the sealing properties of the tip contact portions Pa1 and Pa2 can be improved.

The above embodiments may be modified as follows. In addition, the above embodiments and other examples described below may be combined with each other within a range not technically contradictory.

As shown in fig. 19, in the configuration in which the body attachment grooves 173, 174 are formed in the circumferential center (widthwise center) of the blade body 170, the widths D1, D2 of the body attachment grooves 173, 174 may be wider than the width of the blade 131, that is, 1/2 of the blade width D0. In this case, the seal attachment convex portions 182 and 192 may be formed to have a wide width corresponding to the body attachment grooves 173 and 174.

According to this structure, the side surface contact portions Pb1, Pb2 are offset closer to the 1 st part chamber Ax by the amount of widening from the widths D1, D2 of the body mounting grooves 173, 174. This produces the effect (3-1) described above.

O introduction grooves 184 and 194 may be formed in blade body 170 instead of being formed in tip seals 180 and 190, or may be formed in both of tip seals 180 and 190 and blade body 170. In short, the introduction grooves 184 and 194 may be formed in at least one of the tip seals 180 and 190 and the blade body 170.

The lead-in grooves 184 and 194 may be omitted.

The blade tip seals 180 and 190 may be mounted so as to be movable in the axial direction Z with respect to the blade body 170, and their specific shapes and positions may be arbitrary.

One of the leaf seals 180 and 190 may be omitted. That is, the tip seal may be provided only on either the front side or the rear side. In this case, the end of the blade body 170 on the side where the tip seal is not provided may have a seal surface that abuts against the stationary body surface. That is, the blade 131 may also be constructed of 2 parts including a blade body and 1 tip seal.

The seal attachment convex portions 182 and 192 and the body attachment grooves 173 and 174 may circumferentially face each other, and may or may not circumferentially abut each other when the rotating body 60 is not rotated. The same applies to the main body attachment convex portions 241 and 244 and the seal attachment grooves 231 and 234.

The rotor surfaces 71, 72 may also be inclined 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 flat surfaces perpendicular to the axial direction Z, or may be inclined at the same angle as the rotor surfaces 71 and 72 so as to be in surface contact with the rotor surfaces 71 and 72.

A part of the rotator cylinder 61 may be notched or protruded. The rotating body tube 61 has a cylindrical shape, that is, a circular cross section, but is not limited thereto, and may have a non-circular cross section. The fixing body insertion holes 91 and 111 are not limited to circular shapes, as long as they are formed in accordance with the shape of the rotating body tube 61 so that the gap between the inner wall surface thereof and the rotating body tube 61 is reduced. When the rotor cylindrical portion 61 has a notch portion, another member may be fitted into the notch portion.

The rotator may have a disk shape without a portion extending from the rotator surfaces 71 and 72 in the axial direction Z, and may not be supported by the two anchors 90 and 110. In this case, the front compression chamber a4 may be partitioned by the outer peripheral surface of the rotary shaft 12. That is, the front compression chamber a4 is not limited to the structure defined by the cylindrical outer peripheral surface 62, and may be defined by the front rotor surface 71 and the front stator surface 100. The same applies to the rear compression chamber a 5.

The number of omicron bearings 51, 53 is not limited to 2, and may be 1. For example, the rear axle bearing 53 may be omitted. In addition, more than 3 shaft bearings may be provided.

In the present embodiment, the housing chamber A3 is partitioned by the front cylinder 30 and the rear plate 40, but the specific configuration of the partitioned housing chamber A3 is arbitrary.

For example, the compressor 10 may be configured to include a plate-shaped front plate instead of the front cylinder 30 and a rear cylinder having a peripheral wall and an end wall instead of the rear plate 40. In this case, the storage chamber a3 is partitioned by abutting the rear cylinder to the front plate.

The compressor 10 may have 2 cylindrical cylinders, and the storage chamber a3 may be defined by the two cylinders. The rear plate 40 may be omitted, and the front cylinder 30 and the rear case end wall 23 may define the storage chamber a 3.

O compression chambers a4, a5 may be defined by rotor surfaces 71, 72 and stator surfaces 100, 120, and any other surface used to define compression chambers a4, a5 may be used. For example, in a configuration in which front cylinder 30 is omitted and rotary body 60 and both fixed bodies 90 and 110 are accommodated in rear housing member 22 (or housing 11), compression chambers a4 and a5 may be defined by the inner peripheral surface of rear housing member 22 instead of front cylinder inner peripheral surface 33. In this case, the rear housing member 22 or the housing 11 may be said to be a cylinder portion that houses the rotating body and the fixed body, and the inner circumferential surface of the rear housing member 22 may be said to be a cylinder inner circumferential surface that partitions the compression chamber in cooperation with the rotating body surface and the fixed body surface. The compression chambers a4 and a5 may be defined by the outer peripheral surface of the rotary shaft 12 instead of the cylindrical outer peripheral surface 62.

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

The configuration for introducing the fluid into compression chambers a4 and a5 and the configuration for discharging the fluid compressed in compression chambers a4 and a5 are not limited to the configurations illustrated in embodiment 1, but may be any configuration. For example, at least one of the suction passage and the discharge passage may be provided in the fixed bodies 90 and 110.

Both anchors 90, 110 have the same shape, but not limited to this, and for example, the front anchor 90 may have a larger diameter than the rear anchor 110, or vice versa. In this case, the front cylinder inner peripheral surface 33 may be stepped in accordance with the shape of both the fixed bodies 90, 110, or a front cylinder accommodating the front fixed body 90 and a rear cylinder accommodating the rear fixed body 110 may be provided separately. That is, the volumes of the compression chambers a4, a5 may be the same or different.

The compressor 10 of the embodiment is provided with 2 compression chambers a4, a5, but is not limited thereto.

For example, as shown in fig. 20, the rear fixed body 110, the rear compression chamber a5, the rear suction passage 142, and the rear discharge passage 161 may be omitted. In this case, the 1 st front flat surface 101 may be omitted from the front fixture surface 100. Further, in fig. 20, the blade 131 has the trailing end seal 190, but the trailing end seal 190 may be omitted.

In this configuration, for example, a biasing portion 300 that biases the blade 131 toward the front fixed body 90 may be provided. The biasing portion 300 can be supported by a biasing support portion 301 provided in the rotor cylindrical portion 61 so as to be rotatable in accordance with rotation of the rotor 60, for example. The biasing support portion 301 is, for example, provided on the rear rotor end 61b of the rotor tubular portion 61 and has a plate shape protruding radially outward. Accordingly, the blades 131 rotate while moving in the axial direction Z while maintaining the state of contact with the front fixed body surface 100 in accordance with the rotation of the rotating body 60. Note that, instead of omitting the rear structure, the front structure may be omitted. In other words, the number of the anchors may be 1.

The fixture insertion holes 91 and 111 need not be through holes as long as the rotary shaft 12 can be inserted therein, and may be non-through.

O may omit at least one of the two thrust bearings 81, 82. That is, the thrust bearings 81, 82 are not essential.

O may omit at least one of the two rotary bearings 94, 114.

Discharge chamber a1 need not be in the shape of a cylinder having an axis extending in axial direction Z. For example, the discharge chamber a1 may have a C-shape when viewed in the axial direction Z, or 2 discharge chambers a1 may be arranged facing each other. In other words, the discharge chamber a1 may be formed over at least a part of the circumferential range.

The number of leaves 131 is arbitrary, and may be 1, 2, or 4 or more. In the case of 1 vane 131, the front compression chamber a4 is partitioned into a suction chamber for suction and a compression chamber for compression by the contact portion between the 2 nd front flat surface 102 and the front rotor surface 71 and the vane 131.

The portion (fixture contact surface) of the front fixture surface 100 that contacts the front rotator surface 71 may not be a flat surface as in the front flat surface 2 102. The same applies to the rear fixture surface 120. However, from the viewpoint of sealing properties, a flat surface is preferable.

The anchor abutment surface is not essential. For example, the 2 nd front flat surface 102 may be separated from the front rotator surface 71 by a slight gap.

The specific shape of omicron housing 11 is arbitrary.

The specific shape of the rotation axis 12 is arbitrary. For example, at least a part of the rotary shaft 12 may be formed in a hollow shape or a prism shape.

The electric motor 13 and the inverter 14 may also be omitted. That is, the electric motor 13 and the inverter 14 are not essential to the compressor 10. In this case, the rotary shaft 12 can be rotated by, for example, belt driving.

The compressor 10 may be used other than the air-conditioning apparatus. For example, the compressor 10 may be used to supply compressed air to a fuel cell mounted on a fuel cell vehicle. That is, the fluid to be compressed by the compressor 10 is not limited to the refrigerant including oil, and may be any fluid.

The object to which the compressor 10 is mounted is not limited to a vehicle but is arbitrary.

Claims (8)

1. A compressor is provided with:

a rotating shaft;

a rotating body configured to rotate in accordance with rotation of the rotating shaft, the rotating body having a rotating body surface intersecting with an axial direction of the rotating shaft, and a blade groove;

a fixed body configured to rotate without rotating along with the rotation shaft and having a fixed body surface facing the rotating body surface in the axial direction;

a blade inserted into the blade groove and configured to rotate while moving in the axial direction in accordance with rotation of the rotating body; and

a compression chamber defined by the rotor surface and the stationary surface, the compression chamber being configured to suck and compress a fluid by rotating the vane while moving in the axial direction,

the blade is provided with:

a blade body inserted into the blade groove; and

a seal member that is attached to an end surface of the blade body in the axial direction in a state of being movable in the axial direction with respect to the blade body,

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

the seal member is configured to be pressed against the fixed body surface by the back pressure space, and thereby to be brought into contact with the fixed body surface.

2. The compressor of claim 1, wherein the compressor is a compressor,

the compression chamber includes:

a1 st partial chamber, the 1 st partial chamber being disposed on a subsequent side with respect to the blade in a rotation direction of the rotating body; and

a2 nd partial chamber arranged on a leading side with respect to the vane in the rotation direction,

the seal member includes a seal mounting portion mounted to a body mounting portion provided on the end surface of the blade body,

the main body mounting portion and the seal mounting portion are opposed to each other in a circumferential direction of the rotary shaft.

3. The compressor of claim 2, wherein the compressor is a compressor,

the body mounting part is a body mounting groove formed at the end surface of the blade body, having a width in a thickness direction of the blade and extending in a radial direction of the rotation shaft,

the body mounting groove has a1 st body groove side surface and a2 nd body groove side surface located on a leading side with respect to the 1 st body groove side surface in the rotation direction,

the seal member includes a seal body portion abutting against the fixed body surface,

the seal attachment portion is a seal attachment convex portion protruding from the seal main body portion toward the end surface of the blade main body,

the seal-mounting boss has a1 st seal-convex side surface and a2 nd seal-convex side surface located on a leading side in the rotation direction with respect to the 1 st seal-convex side surface,

the seal member is attached to the blade body by inserting the seal attachment convex portion into the body attachment groove, the 1 st seal convex side surface and the 1 st body groove side surface being opposed to each other in the circumferential direction.

4. The compressor of claim 3, wherein said compressor is a compressor,

at least one of the blade body and the seal member has an introduction groove configured to introduce the fluid in the 2 nd part chamber into the back pressure space.

5. The compressor of claim 3 or 4,

the 1 st body groove side surface is inclined with respect to the axial direction so as to be gradually displaced toward a leading side in the rotational direction as the body mounting groove becomes deeper,

the 1 st seal convex side surface is inclined with respect to the axial direction so as to gradually displace toward a leading side in the rotational direction as approaching from a base end to a tip end of the seal attachment convex portion.

6. A compressor according to any one of claims 3 to 5,

the fixture face includes:

a fixed body abutting surface abutting against the rotating body surface; and

a pair of curved surfaces provided on both sides of the fixed body contact surface in the circumferential direction and curved in the axial direction so as to gradually separate from the rotating body surface as the curved surfaces separate from the fixed body contact surface in the circumferential direction,

the body attachment groove and the seal attachment convex portion are disposed closer to the 1 st part chamber than the 2 nd part chamber so that a side surface contact portion, which is a contact portion of the 1 st seal convex side surface and the 1 st body groove side surface, is disposed closer to the 1 st part chamber than the 2 nd part chamber.

7. The compressor of claim 2, wherein the compressor is a compressor,

the sealing member is composed of a material softer than the blade body,

the seal member has a seal body portion abutting against the fixed body surface,

the seal body portion has a seal body bottom surface opposed to the end surface of the blade body,

the seal installation part is a seal installation groove recessed from the bottom surface of the seal main body,

the body mounting portion is a body mounting protrusion protruding from the end surface of the blade body,

the seal member is mounted to the blade body by inserting the body mounting boss into the seal mounting groove.

8. The compressor of claim 7, wherein said compressor is a compressor,

the seal installation groove has a1 st seal groove side surface and a2 nd seal groove side surface located on a leading side with respect to the 1 st seal groove side surface in the rotation direction,

the body mounting boss has a1 st body convex side and a2 nd body convex side located on a leading side with respect to the 1 st body convex side in the rotational direction,

the 2 nd seal groove side surface is inclined with respect to the axial direction so as to be gradually displaced to the subsequent side in the rotational direction as the seal mounting groove becomes deeper,

the 2 nd main body convex side surface is inclined with respect to the axial direction so as to be gradually displaced to the subsequent side in the rotational direction as approaching from the base end to the tip end of the main body mounting convex portion,

the 2 nd main body convex side surface and the 2 nd seal groove side surface are opposed to each other in the circumferential direction.

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