Rotary compressor

Abstract

A shaft (20) has a main shaft portion (21) that is supported by a housing (10) and an eccentric portion (26) that is eccentric relative to the center axis line (O1) of the main shaft portion (21). A rotating body (30) is rotatably supported by the shaft (20) with the center axis line (O1) serving as a rotation axis line. A stator (41) is fixed to the shaft (20), and the rotating body (30) is fixed to a rotor (42) that is disposed on the outer peripheral side of the stator (41). The rotating body (30) has a cylinder (31) and a vane (33). The cylinder (31) forms therein an operating chamber (54) together with the outer peripheral surface of the eccentric portion (26) and rotates along the outer peripheral surface of the eccentric portion (26). The vane (33) advances and retracts relative to the operating chamber (54) in accordance with rotation of the cylinder (31) and partitions the operating chamber (54) into a suction chamber (54a) and a compression chamber (54b). The shaft (20) is supported by the housing (10) via vibration-prevention materials (76, 77).

Description

Rotary Compressor

[0001] The present invention relates to a rotary compressor.

[0002] A conventional rotary compressor (hereinafter simply referred to as a compressor) is disclosed in Patent Document 1. This compressor includes a housing, a drive shaft, a drive mechanism, a cylinder, rollers, vanes, and a shaft support member.

[0003] The support member is fixed to the housing, has a cylinder fixed thereto, and supports the drive shaft so that the drive shaft can rotate about its axis.

[0004] The drive shaft has a main shaft portion and an eccentric shaft portion that is eccentric with respect to the central axis of the main shaft portion, and the drive shaft rotates around the central axis of the main shaft portion.

[0005] The drive mechanism is an electric motor that rotates the drive shaft. The electric motor has a cylindrical stator fixed to a housing and a cylindrical rotor disposed inside the stator. The rotor is fixed to the main shaft portion of the drive shaft.

[0006] The roller is cylindrical and fixed to the eccentric shaft of the drive shaft. The cylinder has an inner circumferential surface whose cross section perpendicular to the drive axis is a perfect circle. The central axis of the inner circumferential surface of the cylinder is coaxial with the central axis of the main shaft. The cylinder, together with the outer circumferential surface of the roller, forms an internal working chamber. A portion of the outer circumferential surface of the roller is in contact with the inner circumferential surface of the cylinder.

[0007] A plate-shaped vane extending radially of the roller is integrally formed on the outer circumferential surface of the roller, and is slidably received in a vane receiving hole provided in the inner circumferential surface of the cylinder.

[0008] In this compressor, the roller rotates along the inner circumferential surface of the cylinder as the drive shaft rotates about the drive axis. As the roller rotates, the vane moves back and forth relative to the working chamber, dividing the working chamber into a suction chamber and a compression chamber. In this way, in this compressor, the refrigerant is drawn into the suction chamber and compressed in the compression chamber.

[0009] Japanese Patent Application Laid-Open No. 2019-39418

[0010] When a compressor is installed in a vehicle, for example, vibrations generated by the compressor are transmitted to the vehicle and cause noise inside the vehicle. Therefore, there is a demand for improving the quietness of the compressor and suppressing the transmission of vibrations from the compressor to the vehicle. In particular, with the recent spread of electric vehicles, this demand has become even greater than before.

[0011] However, in the conventional compressor, the cylinder is fixed, and the shaft support member that supports the drive shaft and the stator of the motor are fixed to the housing. Therefore, in the conventional compressor, vibrations generated by these members are easily transmitted to the vehicle via the housing, making it difficult to suppress the transmission of vibrations from the compressor to the vehicle.

[0012] The present invention has been made in view of the above-described conventional circumstances, and an object to be achieved is to provide a rotary compressor that can effectively suppress transmission of vibrations to the outside.

[0013] a rotary compressor according to the present invention comprising: a housing; a shaft accommodated in the housing and having a main shaft portion supported by the housing and an eccentric portion eccentric with respect to the central axis of the main shaft portion; a rotor accommodated within the housing and rotatably supported on the shaft with the central axis as the axis of rotation; and a drive mechanism accommodated in the housing for rotationally driving the rotor, wherein the drive mechanism has a stator fixed to the shaft and a rotor disposed on the outer periphery of the stator and fixed to the rotor so as to be rotatable integrally therewith; the rotor has a cylinder which, together with the outer periphery of the eccentric portion, forms a working chamber therein and rotates along the outer periphery; and vanes which move back and forth relative to the working chamber as the cylinder rotates, thereby separating the working chamber into a suction chamber into which a refrigerant is sucked and a compression chamber which compresses the refrigerant; and the shaft is supported by the housing via vibration-damping material which suppresses transmission of vibration from the shaft to the housing.

[0014] In the rotary compressor of the present invention, a stator is fixed to a shaft supported by a housing, and a rotor is fixed to a rotor disposed on the outer periphery of the stator so as to rotate integrally with the shaft. The shaft is supported by the housing via a vibration-damping material. In this rotary compressor, vibrations are generated from sliding parts and collision parts of the rotor. The stator can also vibrate due to fluctuations in electromagnetic force generated by the stator, making the stator a vibration source. In this rotary compressor, these vibration sources are isolated from the housing. Therefore, vibrations generated by these vibration sources are transmitted to the shaft but are not directly transmitted to the housing. A vibration-damping material is interposed between the shaft and the housing. Therefore, transmission of vibrations from the shaft to the housing is suppressed by the vibration-damping material.

[0015] Therefore, the rotary compressor of the present invention can effectively suppress the transmission of vibrations to the outside.

[0016] It is preferable that both ends of the shaft are supported by the housing via vibration-isolating materials, in which case transmission of vibration from the shaft to the housing can be further suppressed.

[0017] The vibration-proof material is preferably disposed in the housing in an atmosphere of the suction refrigerant that communicates with the suction chamber, in order to prevent thermal deterioration of the vibration-proof material.

[0018] The rotating body preferably has a cover body. The cover body may be disposed on the outer periphery of the main shaft portion. The cover body may also have a discharge chamber that communicates with the compression chamber and from which refrigerant compressed in the compression chamber is discharged. The housing may have a discharge communication port that communicates with the outside. The shaft preferably has an internal shaft discharge passage that communicates between the discharge chamber and the discharge communication port. It is also preferable that an annular seal member be disposed between the connection between the internal shaft discharge passage and the discharge communication port and the vibration-damping material.

[0019] In this case, the refrigerant compressed in the compression chamber is discharged into the discharge chamber and then discharged to the outside via the shaft discharge passage and the discharge communication port. A seal is disposed between the connection between the shaft discharge passage and the discharge communication port and the vibration-damping material. This isolates the vibration-damping material from the discharge refrigerant atmosphere that communicates with the compression chambers within the housing. As a result, thermal degradation of the vibration-damping material in the suction refrigerant atmosphere can be more reliably suppressed.

[0020] The rotating body preferably has a cover body. The cover body may be disposed on the outer periphery of the main shaft portion. The cover body may also have a discharge chamber communicating with the compression chamber and through which refrigerant compressed in the compression chamber is discharged. The housing may have a discharge communication port extending in a direction intersecting the central axis and communicating with the outside. The shaft preferably has an internal discharge passage communicating between the discharge chamber and the discharge communication port. The internal discharge passage may have an axial passage portion extending in the direction of the central axis, a first radial passage portion extending in a direction intersecting the central axis and communicating between the discharge chamber and the axial passage portion, and a second radial passage portion extending in a direction intersecting the central axis and communicating between the discharge communication port and the axial passage portion. An annular seal member attached to the outer periphery of the shaft is preferably disposed between a connection portion between the discharge communication port and the second radial passage portion and an end of the shaft closer to the connection portion. Both ends of the shaft are preferably exposed to an intake refrigerant atmosphere communicating with the suction chamber within the housing.

[0021] In this case, since both ends of the shaft are exposed to the suction refrigerant atmosphere, the differential pressure acting on both ends of the shaft in the direction of the central axis can be suppressed, which prevents the shaft from being pushed in one direction along the central axis due to the action of the differential pressure, and prevents the vibration-damping material on that side from being deteriorated due to the application of an excessive load.

[0022] The rotating body preferably has a cover body. The cover body may be disposed on the outer periphery of the main shaft portion. The cover body may also have a discharge chamber that communicates with the compression chamber and from which the refrigerant compressed in the compression chamber is discharged. The housing may have a discharge communication port that communicates with the outside. The shaft preferably has an internal discharge passage that communicates between the discharge chamber and the discharge communication port. The internal discharge passage preferably extends in the direction of the central axis and has open ends that open to both ends of the shaft. An annular seal member is preferably disposed around each open end to surround the open end.

[0023] In this case, both ends of the shaft are exposed to the discharged refrigerant atmosphere, which suppresses the differential pressure acting on both ends of the shaft in the direction of the central axis, preventing the shaft from being pushed to one side in the direction of the central axis due to the action of the differential pressure.

[0024] The rotary compressor of the present invention can effectively suppress the transmission of vibrations to the outside.

[0025] FIG. 1 is a cross-sectional view of a rotary compressor according to a first embodiment. FIG. 2 is a partial cross-sectional view of the rotary compressor according to the first embodiment, mainly illustrating a suction passage and an oil supply passage. FIG. 3 is a cross-sectional view of the rotary compressor according to the first embodiment, taken along line A-A in FIG. 1. FIG. 4 is a cross-sectional view of the rotary compressor according to the first embodiment, taken along line B-B in FIG. 1. FIG. 5 is a cross-sectional view of a rotary compressor according to a second embodiment. FIG. 6 is a cross-sectional view of a portion corresponding to line A-A in FIG. 1, of a rotary compressor according to a third embodiment.

[0026] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First to third embodiments of the present invention will be described below with reference to the accompanying drawings. The rotary compressors of the first to third embodiments are applied to the refrigeration cycle of an air conditioner mounted on a vehicle (not shown).

[0027] As shown in FIG. 1 , the rotary compressor (hereinafter simply referred to as “compressor”) of the first embodiment includes a housing 10 , a shaft 20 , a rotor 30 , and a drive mechanism 40 .

[0028] In this embodiment, the front-to-rear direction of the compressor is defined by the solid arrow shown in Fig. 1. Note that the front-to-rear direction is an example for convenience of explanation, and the compressor's position can be changed as appropriate depending on the vehicle in which it is installed. The same applies to the compressors shown in Figs. 2 and 5.

[0029] 1, the housing 10 is made up of a housing body 11 and a housing cover 12. The housing body 11 and the housing cover 12 are made of an aluminum alloy.

[0030] The housing body 11 is a bottomed, tubular member having an outer peripheral wall 11a and a rear wall 11b. The outer peripheral wall 11a is cylindrical and centered on a central axis O1 of a main shaft portion 21 (described later) of the shaft 20. The central axis O1 is parallel to the front-to-rear direction. An intake communication port 13 is formed in the outer peripheral wall 11a. The intake communication port 13 penetrates the outer peripheral wall 11a in the radial direction of the housing body 11. A pipe (not shown) is connected to the intake communication port 13. As a result, the intake communication port 13 is connected to the outside of the housing 10, i.e., the outside of the compressor, via the pipe. The intake communication port 13 may also be formed in the rear wall 11b.

[0031] The rear wall 11b is located at the rear end of the housing body 11. The rear wall 11b extends in a generally circular, flat plate shape perpendicular to the central axis O1. The outer peripheral edge of the rear wall 11b is connected to the rear end of the outer peripheral wall 11a.

[0032] A first support recess 14 is formed in the center of the inner surface of the rear wall 11b. The first support recess 14 has a cylindrical inner surface shape centered on the central axis O1 and is recessed rearward from the center of the inner surface of the rear wall 11b.

[0033] A first communication hole 14a is formed on the inner surface of the rear wall 11b. The first communication hole 14a extends obliquely with respect to the direction of the central axis O1 from the side surface connected to the bottom surface of the first support recess 14 toward the inner surface of the rear wall 11b. The front end of the first communication hole 14a opens into the suction communication chamber 15. The first communication hole 14a communicates with the suction communication chamber 15 and a first thrust space 14b (described later) within the first support recess 14.

[0034] The housing cover 12 is disposed in front of the housing main body 11. The housing cover 12 extends in a generally circular, flat plate shape perpendicular to the central axis O1. The housing cover 12 is fixed to the housing main body 11 with bolts (not shown) with its outer peripheral edge abutting against the front end of the outer peripheral wall 11a of the housing main body 11. In this way, the housing cover 12 closes the housing main body 11 from the front. In this way, an intake communication chamber 15 is formed within the housing main body 11.

[0035] The suction communication chamber 15 is in communication with the suction communication port 13. As a result, low-pressure refrigerant is drawn into the suction communication chamber 15 from outside the compressor through a pipe connected to the suction communication port 13. As a result, the suction communication chamber 15 is filled with a suction refrigerant atmosphere. In Figures 1 and 2, the flow of refrigerant within the compressor is indicated by dashed arrows, and the flow of lubricating oil 39 (described later) within the compressor is indicated by solid arrows.

[0036] A second support recess 16 is formed in the center of the inner surface of the housing cover 12. The second support recess 16 has a first recess 16a and a second recess 16b. The first recess 16a has an annular inner surface shape centered on the central axis O1. The first recess 16a is recessed forward from the center of the inner surface of the housing cover 12. The second recess 16b has a cylindrical inner surface shape centered on the central axis O1. The second recess 16b is connected to the front of the first recess 16a, and the bottom surface of the second recess 16b forms the bottom surface of the second support recess 16. The second recess 16b is sized to accommodate a second small diameter portion 21d of the shaft 20, which will be described later.

[0037] A second communication hole 16c is formed on the inner surface of the housing cover 12. The second communication hole 16c extends obliquely with respect to the direction of the central axis O1 from the side surface connected to the bottom surface of the second recess 16b toward the inner surface of the housing cover 12. The rear end of the second communication hole 16c opens into the suction communication chamber 15. The second communication hole 16c communicates with the suction communication chamber 15 and a second thrust space 16d (described later) within the second recess 16b.

[0038] A discharge communication port 17 is also formed in the housing cover 12. The discharge communication port 17 extends from the second recess 16b of the second support recess 16 to the outside of the compressor in a direction perpendicular to the central axis O1. That is, the discharge communication port 17 connects the second recess 16b to the outside of the compressor. The discharge communication port 17 also faces a second radial passage portion 75c of an intra-shaft discharge passage 75 (described later) formed inside the shaft 20 in a direction perpendicular to the central axis O1. A pipe (not shown) is connected to the discharge communication port 17. As a result, the discharge communication port 17 is connected to the outside of the compressor via the pipe.

[0039] The shaft 20 is a substantially cylindrical member accommodated in the housing 10. The shaft 20 has a main shaft portion 21, a first eccentric shaft portion 22, and a second eccentric shaft portion 23. The main shaft portion 21, the first eccentric shaft portion 22, and the second eccentric shaft portion 23 all have a cylindrical shape with a circular cross section perpendicular to the central axis O1.

[0040] The main shaft portion 21 has a medium diameter portion 21a, a large diameter portion 21b that is larger than the medium diameter portion 21a, a first small diameter portion 21c that is smaller than the medium diameter portion 21a, and a second small diameter portion 21d that is smaller than the medium diameter portion 21a. The outer diameter of the first small diameter portion 21c is equal to the outer diameter of the second small diameter portion 21d. The medium diameter portion 21a, the large diameter portion 21b, the first small diameter portion 21c, and the second small diameter portion 21d are integrally formed. The medium diameter portion 21a is connected to the rear of the second small diameter portion 21d, the large diameter portion 21b is connected to the rear of the medium diameter portion 21a, and the first small diameter portion 21c is connected to the rear of the large diameter portion 21b. The first small diameter portion 21c is fixed in the first support recess 14, and the second small diameter portion 21d is fixed in the second support recess 16.

[0041] A first vibration-isolating material 76 is disposed within the first support recess 14. The first vibration-isolating material 76 is a thick, disk-shaped material with an outer surface shape that corresponds to the inner surface shape of the first support recess 14. The outer diameter of the first vibration-isolating material 76 is slightly larger than the inner diameter of the first support recess 14. The first vibration-isolating material 76 is inserted into and fixed in the first support recess 14 while being elastically deformed. A first thrust space 14b is formed between the bottom surface of the first support recess 14 and the rear surface of the first vibration-isolating material 76.

[0042] As described above, the first thrust space 14b communicates with the suction communication chamber 15 through the first communication hole 14a. Therefore, the first thrust space 14b has the same suction refrigerant atmosphere as the suction communication chamber 15. In other words, the first vibration-damping material 76, which is arranged in the first support recess 14 so as to face the suction communication chamber 15, is arranged in the suction refrigerant atmosphere.

[0043] A shaft support recess 76a is recessed in the center of the front surface of the first vibration-damping material 76. The shaft support recess 76a has a cylindrical inner shape that corresponds to the outer surface shape of the first small diameter portion 21c of the shaft 20. The inner diameter of the shaft support recess 76a is slightly smaller than the outer diameter of the first small diameter portion 21c.

[0044] The first small diameter portion 21c of the shaft 20 is inserted into and fixed in the shaft support recess 76a of the first vibration-isolating material 76. The rear end surface of the first small diameter portion 21c abuts against the bottom surface of the shaft support recess 76a. In this way, the first small diameter portion 21c of the shaft 20 is supported by the first support recess 14 via the first vibration-isolating material 76.

[0045] A second vibration-isolating material 77 is disposed within the first recess 16a of the second support recess 16. The second vibration-isolating material 77 is a thick, disk-shaped material having an outer surface shape corresponding to the inner surface shape of the first recess 16a. The outer diameter of the second vibration-isolating material 77 is slightly larger than the inner diameter of the first recess 16a of the second support recess 16. The second vibration-isolating material 77 is inserted into and fixed in the first recess 16a while being elastically deformed. The front surface of the second vibration-isolating material 77 abuts against the annular bottom surface of the first recess 16a.

[0046] A shaft support hole 77a is formed through the center of the second vibration-damping material 77. The shaft support hole 77a has a cylindrical inner surface shape that corresponds to the outer surface shape of the second small diameter portion 21d of the shaft 20. The inner diameter of the shaft support hole 77a is slightly smaller than the outer diameter of the second small diameter portion 21d.

[0047] The second small diameter portion 21d of the shaft 20 is inserted into and fixed in the shaft support hole 77a of the second vibration-isolating material 77. The second small diameter portion 21d penetrates the second vibration-isolating material 77. The front end of the second small diameter portion 21d extends into the second recess 16b of the second support recess 16, but is spaced apart from the bottom surface of the second recess 16b. The annular front end surface of the medium diameter portion 21a of the shaft 20 abuts against the rear end surface of the second vibration-isolating material 77. In this way, the second small diameter portion 21d of the shaft 20 is supported by the second support recess 16 via the second vibration-isolating material 77.

[0048] Both the first vibration-isolating material 76 and the second vibration-isolating material 77 are made of a rubber elastic body having a rigidity lower than that of the housing 10. The hardness, size, etc. of both the first vibration-isolating material 76 and the second vibration-isolating material 77 are set so that they can effectively suppress the transmission of vibration from the shaft 20 to the housing 10 and can support the shaft 20 with appropriate support rigidity relative to the housing 10.

[0049] The first eccentric shaft portion 22 and the second eccentric shaft portion 23 are provided in the medium diameter portion 21 a. Specifically, the second eccentric shaft portion 23 is disposed in front of the boundary between the medium diameter portion 21 a and the large diameter portion 21 b. The first eccentric shaft portion 22 is disposed in a portion of the medium diameter portion 21 a separated forward from the second eccentric shaft portion 23. Specifically, the first eccentric shaft portion 22 and the second eccentric shaft portion 23 are separated in the direction of the central axis O1 by a distance equal to the combined length of a first intermediate plate 52 and a second intermediate plate 62 (described later).

[0050] An intra-shaft discharge passage 75 is formed in the shaft 20. The intra-shaft discharge passage 75 has an axial passage portion 75a extending in the direction of the central axis O1, a first radial passage portion 75b extending in the radial direction of the central axis O1, and a second radial passage portion 75c extending in the radial direction of the central axis O1.

[0051] The front end of the axial passage portion 75a extends to the front end of the shaft 20 and opens to the front end surface. A disc-shaped closure plate 78 that closes the axial passage portion 75a is fixed to the front end surface of the shaft 20. A second thrust space 16d is formed between the bottom surface of the second recess 16b and the front surface of the closure plate 78. One end of the first radial passage portion 75b opens to the outer peripheral surface of the medium diameter portion 21a of the shaft 20 in the first discharge chamber 37 (described later). The other end of the first radial passage portion 75b is connected to the rear end of the axial passage portion 75a. One end of the second radial passage portion 75c opens to the outer peripheral surface of the second small diameter portion 21d of the shaft 20 in the second recess 16b. The other end of the second radial passage portion 75c is connected near the front end of the axial passage portion 75a. In this way, the intra-shaft discharge passage 75 communicates between the first discharge chamber 37 and the discharge communication port 17.

[0052] An annular first seal member 43 and an annular second seal member 44 are attached to the outer peripheral surface of the second small diameter portion 21d of the shaft 20. Both the first seal member 43 and the second seal member 44 provide a seal between the outer peripheral surface of the second small diameter portion 21d and the inner peripheral surface of the second recess 16b.

[0053] The first seal member 43 is disposed between the second vibration-isolating material 77 and a connection portion 79 between the second radial passage portion 75c of the intra-shaft discharge passage 75 and the discharge communication port 17. That is, the first seal member 43 seals the connection portion 79 and the second vibration-isolating material 77. This prevents the pressure of the compressed refrigerant at the connection portion 79 from leaking toward the second vibration-isolating material 77. Therefore, the second vibration-isolating material 77, which is disposed within the second support recess 16 so as to face the suction communication chamber 15, is disposed in the suction refrigerant atmosphere.

[0054] The second seal member 44 is disposed between the connecting portion 79 and the front end of the shaft 20. As a result, the second seal member 44 seals the space between the connecting portion 79 and the second thrust space 16d.

[0055] The first eccentric shaft portion 22 and the second eccentric shaft portion 23 both have an outer diameter equal to the outer diameter of the large diameter portion 21b. The first eccentric axis O2 of the first eccentric shaft portion 22 is eccentric with respect to the central axis O1 of the main shaft portion 21 by a first eccentric amount E1. The second eccentric axis O3 of the second eccentric shaft portion 23 is eccentric with respect to the central axis O1 of the main shaft portion 21 by a second eccentric amount E2. The first eccentric amount E1 and the second eccentric amount E2 are equal. The first eccentric shaft portion 22 and the second eccentric shaft portion 23 are eccentric in opposite directions. For example, when the first eccentric shaft portion 22 is eccentric directly upward with respect to the central axis O1, the second eccentric shaft portion 23 is eccentric directly downward, which is the opposite direction.

[0056] As shown in FIG. 3 , a cylindrical first roller 24 is disposed on the outer peripheral surface of the first eccentric shaft portion 22. Specifically, the first roller 24 is loosely fitted to the outer peripheral surface of the first eccentric shaft portion 22 with a slight gap. As shown in FIG. 4 , a cylindrical second roller 25 is disposed on the outer peripheral surface of the second eccentric shaft portion 23. Specifically, the second roller 25 is loosely fitted to the outer peripheral surface of the second eccentric shaft portion 23 with a slight gap. The first roller 24 and the second roller 25 have the same shape and size. The first eccentric shaft portion 22 and the first roller 24 form a first eccentric portion 26. Similarly, the second eccentric shaft portion 23 and the second roller 25 form a second eccentric portion 27. The first eccentric portion 26 and the second eccentric portion 27 are examples of the "eccentric portion" in the present invention. The first eccentric portion 26 has a circular outer peripheral surface 26a centered on the first eccentric axis O2. Similarly, the second eccentric portion 27 has a circular outer peripheral surface 27a centered on the second eccentric axis O3.

[0057] The rotating body 30 has a first cylinder 31, a second cylinder 32, a first vane 33, a second vane 34, a first cover body 35, and a second cover body 36. The first cylinder 31 and the second cylinder 32 are an example of a "cylinder" in the present invention. The first vane 33 and the second vane 34 are an example of a "vane" in the present invention. The first cover body 35 and the second cover body 36 are an example of a "cover body" in the present invention.

[0058] The first cylinder 31 has a first cylinder body 51 , a first intermediate plate 52 , and a first side plate 53 .

[0059] As shown in FIG. 3 , the first cylinder body 51 is disposed on the outer circumferential side of the first eccentric portion 26 so as to cover the first eccentric portion 26. The first cylinder body 51 is generally cylindrical and has an inner circumferential surface 51a with a circular cross section centered on the central axis O1. That is, the inner circumferential surface 51a of the first cylinder body 51 is coaxial with the central axis O1 and has a larger diameter than the outer circumferential surface 26a of the first eccentric portion 26. The inner circumferential surface 51a of the first cylinder body 51 and the outer circumferential surface 26a of the first eccentric portion 26 abut against each other at one point in the circumferential direction. Thus, a first working chamber 54 is formed between the inner circumferential surface 51a of the first cylinder body 51 and the outer circumferential surface 26a of the first eccentric portion 26. The first working chamber 54 is an example of the “working chamber” in the present invention.

[0060] A first vane accommodating hole 55 is formed in the first cylinder body 51. The first vane accommodating hole 55 extends radially outward from the inner circumferential surface 51 a of the first cylinder body 51 and penetrates the first cylinder body 51 in the radial direction. The first vane accommodating hole 55 also penetrates the first cylinder body 51 from the front surface to the rear surface of the first cylinder body 51 in the direction of the central axis O1.

[0061] A first closure plate 56 that closes first vane accommodating hole 55 is fixed to the radially outer end of first vane accommodating hole 55. Furthermore, a first spring 57 that urges first vane 33 radially inward of first cylinder body 51 is arranged within first vane accommodating hole 55, radially outward of first vane 33. One end of first spring 57 is fixed to first closure plate 56, and the other end of first spring 57 abuts against first vane 33.

[0062] The first vane 33 has a rectangular flat plate shape and is slidably accommodated in the first vane accommodation hole 55. The first vane 33 is biased radially inward of the first cylinder body 51 by a first spring 57, so that the first vane 33 is constantly in contact with the outer peripheral surface 26a of the first eccentric portion 26. As a result, as shown in Figure 3, the first working chamber 54 is divided into a first suction chamber 54a that draws in the refrigerant and a first compression chamber 54b that compresses the refrigerant.

[0063] The first eccentric shaft portion 22, the first roller 24, the first cylinder body 51, and the first vane 33 have the same length in the direction of the central axis O1.

[0064] The first intermediate plate 52 is disposed on the outer circumferential side of the medium diameter portion 21 a located rearward of the first cylinder body 51 and between the first eccentric shaft portion 22 and the second eccentric shaft portion 23, and the front surface of the first intermediate plate 52 abuts against the rear surface of the first cylinder body 51. The first intermediate plate 52 is generally disk-shaped, and a first insertion hole 52 a is formed in the center of the first intermediate plate 52, through which the first eccentric shaft portion 22 can be inserted.

[0065] The first side plate 53 is disposed on the outer periphery of the medium diameter portion 21a in front of the first cylinder body 51, and the rear surface of the first side plate 53 abuts against the front surface of the first cylinder body 51. The first side plate 53 is generally disk-shaped, and a second insertion hole 53a is formed in the center of the first side plate 53, through which the medium diameter portion 21a can be inserted.

[0066] A first discharge port 58 is formed in the first side plate 53. The first discharge port 58 penetrates the first side plate 53 in the direction of the central axis O1 and connects the first compression chamber 54b with a first discharge chamber 37, which will be described later. A first discharge valve 59 is fixed to the front surface of the first side plate 53. The first discharge valve 59 has a discharge reed valve, a retainer, and a fixing bolt that fixes the discharge reed valve and the retainer to the first side plate 53. The discharge reed valve opens and closes the first discharge port 58, with its opening degree adjusted by the retainer.

[0067] The first cover body 35 is disposed on the outer periphery of the medium diameter portion 21a, in front of the first cylinder 31. The first cover body 35 includes a cylindrical first outer periphery wall 35a, a substantially disk-shaped first front wall 35b, and a cylindrical first boss 35c. The first boss 35c is disposed on the outer periphery of the medium diameter portion 21a and is rotatably supported by the medium diameter portion 21a. A third insertion hole 35d, formed together with the inner periphery of the first boss 35c, is provided at the center of the first front wall 35b and through which the medium diameter portion 21a can be inserted. The front end of the first outer periphery wall 35a is connected to the outer periphery of the first front wall 35b, and the rear end of the first boss 35c is connected to the inner periphery of the first front wall 35b. The rear end of the first outer periphery wall 35a abuts against the front surface of the first side plate 53. As a result, a first discharge chamber 37 is formed inside the first cover body 35 by the first outer peripheral wall 35a and the first front wall 35b of the first cover body 35 and the first side plate 53. The first discharge chamber 37 is an example of the "discharge chamber" according to the present invention.

[0068] The second cylinder 32 has a second cylinder body 61 , a second intermediate plate 62 , and a second side plate 63 .

[0069] As shown in FIG. 4 , the second cylinder body 61 is disposed on the outer circumferential side of the second eccentric portion 27 so as to cover the second eccentric portion 27. Like the first cylinder body 51, the second cylinder body 61 is generally cylindrical and has an inner circumferential surface 61a with a circular cross section centered on the central axis O1. That is, the inner circumferential surface 61a of the second cylinder body 61 is coaxial with the central axis O1 and has a larger diameter than the outer circumferential surface 27a of the second eccentric portion 27. The inner circumferential surface 61a of the second cylinder body 61 and the outer circumferential surface 27a of the second eccentric portion 27 abut against each other at one point in the circumferential direction. Thus, a second working chamber 64 is formed between the inner circumferential surface 61a of the second cylinder body 61 and the outer circumferential surface 27a of the second eccentric portion 27. The second working chamber 64 is an example of the “working chamber” in the present invention.

[0070] A second vane accommodating hole 65 is formed in the second cylinder body 61. The second vane accommodating hole 65 extends radially outward from the inner circumferential surface 61 a of the second cylinder body 61 and penetrates the second cylinder body 61 in the radial direction. The second vane accommodating hole 65 also penetrates the second cylinder body 61 from the front surface to the rear surface of the second cylinder body 61 in the direction of the central axis O1.

[0071] A second closure plate 66 that closes the second vane accommodating hole 65 is fixed to the radially outer end of the second vane accommodating hole 65. Furthermore, a second spring 67 that urges the second vane 34 radially inward of the second cylinder body 61 is arranged within the second vane accommodating hole 65 on the radially outer side of the second vane 34. One end of the second spring 67 is fixed to the second closure plate 66, and the other end of the second spring 67 abuts against the second vane 34.

[0072] The second vane 34 has a rectangular flat plate shape and is slidably accommodated in the second vane accommodation hole 65. The second vane 34 is biased radially inward of the second cylinder body 61 by a second spring 67, so that the second vane 34 is always in contact with the outer peripheral surface 27a of the second eccentric portion 27. As a result, as shown in Figure 4, the second working chamber 64 is divided into a second suction chamber 64a that draws in the refrigerant and a second compression chamber 64b that compresses the refrigerant.

[0073] The second eccentric shaft portion 23, the second roller 25, the second cylinder body 61, and the second vane 34 have the same length in the direction of the central axis O1.

[0074] The second intermediate plate 62 is disposed on the outer circumferential side of the medium diameter portion 21 a located in front of the second cylinder body 61 between the first eccentric shaft portion 22 and the second eccentric shaft portion 23, and the rear surface of the second intermediate plate 62 abuts against the front surface of the second cylinder body 61. The second intermediate plate 62 is substantially disk-shaped, and a fourth insertion hole 62 a is formed in the center of the second intermediate plate 62, through which the first eccentric shaft portion 22 can be inserted.

[0075] The second side plate 63 is disposed on the outer circumferential side of the large diameter portion 21b behind the second cylinder body 61, and the front surface of the second side plate 63 abuts against the rear surface of the second cylinder body 61. The second side plate 63 is generally disk-shaped, and a fifth insertion hole 63a is formed in the center of the second side plate 63, through which the large diameter portion 21b can be inserted.

[0076] A second discharge port 68 is formed in the second side plate 63. The second discharge port 68 penetrates the second side plate 63 in the direction of the central axis O1 and connects the second compression chamber 64b with a second discharge chamber 38, which will be described later. A second discharge valve 69 is fixed to the rear surface of the second side plate 63. Similar to the first discharge valve 59, the second discharge valve 69 has a discharge reed valve, a retainer, and a fixing bolt that fixes the discharge reed valve and the retainer to the second side plate 63.

[0077] The second cover body 36 is disposed rearward of the second cylinder 32 and on the outer circumferential side of the large diameter portion 21b. The second cover body 36 includes a cylindrical second outer circumferential wall 36a, a generally disk-shaped second rear wall 36b, and a cylindrical second boss 36c. The inner diameter of the second boss 36c is equal to the outer diameter of the rotor 42 (described later). A sixth insertion hole 36d is provided in the center of the second rear wall 36b, through which the large diameter portion 21b can be inserted. The rear end of the second outer circumferential wall 36a is connected to the outer circumferential edge of the second rear wall 36b, and the front end of the second boss 36c is connected near the outer circumferential edge of the second rear wall 36b. The front end of the second outer circumferential wall 36a abuts against the rear surface of the second side plate 63. As a result, the second outer peripheral wall 36a and the second rear wall 36b of the second cover body 36, and the second side plate 63 form a second discharge chamber 38 inside the second cover body 36. The second discharge chamber 38 is an example of the "discharge chamber" according to the present invention.

[0078] As shown in Fig. 3, the first cylinder body 51 has two female thread portions 91 and six bolt insertion portions 92. As shown in Fig. 4, the second cylinder body 61 also has two female thread portions 91 and six bolt insertion portions 92. Although not shown, the first side plate 53 and the second side plate 63 each have eight bolt insertion portions.

[0079] Although not shown, two first bolts are inserted into two bolt insertion portions of the first side plate 53 and screwed into two female threaded portions 91 of the first cylinder body 51, thereby fixing the first cylinder body 51 and the first side plate 53 together. Similarly, although not shown, two second bolts are inserted into two bolt insertion portions of the second side plate 63 and screwed into two female threaded portions 91 of the second cylinder body 61, thereby fixing the second cylinder body 61 and the second side plate 63 together.

[0080] Although not shown, the first intermediate plate 52, the first cover body 35, the second intermediate plate 62, and the second cover body 36 each have six bolt insertion portions.

[0081] Although not shown, six through-bolts are sequentially inserted into the six bolt insertion portions 92 of the first cover body 35, first side plate 53, first cylinder body 51, first intermediate plate 52, second intermediate plate 62, second cylinder body 61, second side plate 63, and second cover body 36, thereby fastening and fixing the first cover body 35, first side plate 53, first cylinder body 51, first intermediate plate 52, second intermediate plate 62, second cylinder body 61, second side plate 63, and second cover body 36. In this manner, the rotating body 30 is integrally formed.

[0082] A first plain bearing 71, a second plain bearing 72, a third plain bearing 73, and a fourth plain bearing 74 are interposed between the rotating body 30 and the shaft 20. The first plain bearing 71 is disposed between the third insertion hole 35d of the first cover body 35 and the medium diameter portion 21a of the shaft 20. The second plain bearing 72 is disposed between the second insertion hole 53a of the first side plate 53 and the medium diameter portion 21a. The third plain bearing 73 is disposed between the fifth insertion hole 63a of the second side plate 63 and the large diameter portion 21b. The fourth plain bearing 74 is disposed between the sixth insertion hole 36d of the second cover body 36 and the large diameter portion 21b. In this way, the rotating body 30 is rotatably supported relative to the shaft 20, with the central axis O1 of the main shaft portion 21 serving as the rotation axis.

[0083] The drive mechanism 40 is specifically an electric motor and is housed in the suction communication chamber 15. As a result, the suction communication chamber 15 also serves as a motor chamber that houses the drive mechanism 40. The drive mechanism 40 is composed of a stator 41 and a rotor 42. The stator 41 has a stator core 41a and coil ends 41b. The stator core 41a is cylindrical and has a center on the central axis O1. The coil ends 41b are formed by part of the coil wound around the stator core 41a and have an annular shape that protrudes from the stator core 41a in the direction of the central axis O1. The stator 41 is fixed to the shaft 20 by fitting the stator core 41a onto the outer peripheral surface of the large diameter portion 21b.

[0084] The rotor 42 is cylindrical around the central axis O1 and is disposed on the outer circumferential side of the stator 41. Although not shown in detail, the rotor 42 is composed of a plurality of permanent magnets corresponding to the stator 41 and a plurality of electromagnetic steel plates or the like that secure the respective permanent magnets.

[0085] The rotor 42 is fitted into the second boss 36c of the second cover body 36 of the rotating body 30, and the second boss 36c is fixed to the outer peripheral surface of the rotor 42. By fixing the second cover body 36 to the rotor 42 in this manner, the rotating body 30 can rotate integrally with the rotor 42 around the central axis O1 of the main shaft portion 21 of the shaft 20 within the suction communication chamber 15.

[0086] As shown in FIG. 1, the rotor 30 is formed with a suction passage 81, a rotor internal discharge passage 82, a first oil supply passage 83, and a second oil supply passage 84.

[0087] As also shown in FIG. 2, the suction passage 81 has an axial suction hole 81a, a radial suction groove 81b, a first suction port 81c, and a second suction port 81d.

[0088] The axial suction hole 81a extends in the direction of the central axis O1 from the rear surface of the second rear wall 36b of the second cover body 36 to the front surface of the second intermediate plate 62, penetrating the second cover body 36, the second side plate 63, the second cylinder body 61, and the second intermediate plate 62. In other words, the rear end of the axial suction hole 81a opens into the suction communication chamber 15.

[0089] The radial suction groove 81b is recessed in the front surface of the second intermediate plate 62 and extends radially of the second intermediate plate 62. One end of the radial suction groove 81b is connected to the front end of the axial suction hole 81a. The other end of the radial suction groove 81b is connected to the front end of the second suction port 81d. In other words, the radial suction groove 81b communicates between the axial suction hole 81a and the second suction port 81d.

[0090] The first suction port 81c extends in the direction of the central axis O1 and penetrates the first intermediate plate 52. The second suction port 81d extends in the direction of the central axis O1 and penetrates the second intermediate plate 62. The rear end of the first suction port 81c and the front end of the second suction port 81d face each other in the direction of the central axis O1. The front end of the first suction port 81c opens into the first suction chamber 54a. The rear end of the second suction port 81d opens into the second suction chamber 64a.

[0091] Thus, the suction passage 81 communicates the suction communication chamber 15 with the first suction chamber 54a, and also communicates the suction communication chamber 15 with the second suction chamber 64a.

[0092] 1 , the inner rotor discharge passage 82 extends in the direction of the central axis O1 from the rear surface of the second side plate 63 to the front surface of the first side plate 53, penetrating the second side plate 63, the second cylinder body 61, the second intermediate plate 62, the first intermediate plate 52, the first cylinder body 51, and the first side plate 53. The rear end of the inner rotor discharge passage 82 opens to the second discharge chamber 38, and the front end of the inner rotor discharge passage 82 opens to the first discharge chamber 37. In other words, the inner rotor discharge passage 82 connects the first discharge chamber 37 and the second discharge chamber 38.

[0093] The opening position of the inner discharge passage 82 in the first discharge chamber 37 is located a predetermined distance D away from the inner peripheral surface 35e of the first outer peripheral wall 35a inward in the radial direction of the first cover body 35. This minimizes the refrigerant flowing from the inner discharge passage 82 into the first discharge chamber 37 from directly hitting the lubricating oil 39 accumulated on the outer peripheral side in the first discharge chamber 37.

[0094] The opening position of the rotor internal discharge passage 82 in the second discharge chamber 38 is located a predetermined distance D away from the inner peripheral surface 36 e of the second outer peripheral wall 36 a inward in the radial direction of the second cover body 36. This makes it difficult for the lubricating oil 39 accumulated on the outer peripheral side in the second discharge chamber 38 to flow into the rotor internal discharge passage 82.

[0095] As shown in FIG. 2, the first oil supply passage 83 has a first axial supply hole 83a and a first radial supply groove 83b.

[0096] The first axial supply hole 83a extends in the direction of the central axis O1 and penetrates the first side plate 53. That is, the first axial supply hole 83a communicates between the first discharge chamber 37 and the first vane accommodating hole 55. The opening position of the first axial supply hole 83a in the first discharge chamber 37 is located near the inner circumferential surface 35e of the first outer circumferential wall 35a. This allows the lubricating oil 39 that accumulates on the outer circumferential side of the first discharge chamber 37 to flow into the first axial supply hole 83a.

[0097] The first radial supply groove 83b is recessed in the rear surface of the first side plate 53 and extends radially of the first side plate 53 while facing the first vane accommodating hole 55, the first vane 33, and the first roller 24. One end of the first radial supply groove 83b is connected to the rear end of the first axial supply hole 83a. The other end of the first radial supply groove 83b opens to the second insertion hole 53a. In other words, the first radial supply groove 83b communicates between the first axial supply hole 83a and the second insertion hole 53a.

[0098] In this way, first oil supply passage 83 communicates between first discharge chamber 37 and second insertion hole 53a while facing first vane accommodating hole 55, first vane 33, first roller 24, and second plain bearing 72. First vane accommodating hole 55, first vane 33, first roller 24, and second plain bearing 72 are an example of a "sliding part" in the present invention. As a result, as shown by solid arrows in Figures 1 and 2 , lubricating oil 39 in first discharge chamber 37 is supplied via first oil supply passage 83 to first vane accommodating hole 55, first vane 33, first roller 24, and second plain bearing 72, which are sliding parts in rotor 30, by the pressure difference with first discharge chamber 37.

[0099] As shown in FIG. 2, the second oil supply passage 84 has a second axial supply hole 84a, a second radial supply groove 84b, and a supply hole 84c.

[0100] The second axial supply hole 84a extends in the direction of the central axis O1 and penetrates the second side plate 63. That is, the second axial supply hole 84a communicates between the second discharge chamber 38 and the second vane accommodating hole 65. The opening position of the second axial supply hole 84a in the second discharge chamber 38 is located near the inner circumferential surface 36e of the second outer circumferential wall 36a. This allows the lubricating oil 39 that accumulates on the outer circumferential side of the second discharge chamber 38 to flow into the second axial supply hole 84a.

[0101] The second radial supply groove 84b is recessed in the front surface of the second side plate 63 and extends radially of the second side plate 63 while facing the second vane accommodating hole 65, the second vane 34, and the second roller 25. One end of the second radial supply groove 84b is connected to the front end of the second axial supply hole 84a. The other end of the second radial supply groove 84b opens to the fifth insertion hole 63a. In other words, the second radial supply groove 84b communicates with the second axial supply hole 84a and the fifth insertion hole 63a.

[0102] The supply holes 84c include an axial supply hole 84d extending in the direction of the central axis O1 and a radial supply hole 84e extending in the radial direction of the second cover body 36. The front end of the axial supply hole 84d opens into the second discharge chamber 38. The opening position of the axial supply hole 84d in the second discharge chamber 38 is near the inner circumferential surface 36e of the second outer circumferential wall 36a. This allows the lubricating oil 39 accumulated on the outer circumferential side of the second discharge chamber 38 to flow into the axial supply hole 84d. One end of the radial supply hole 84e is connected to the rear end of the axial supply hole 84d. The other end of the radial supply hole 84e opens into the sixth through-hole 36d. In other words, the radial supply hole 84e communicates between the axial supply hole 84d and the sixth through-hole 36d.

[0103] Thus, the second axial supply hole 84a and the second radial supply groove 84b of the second oil supply passage 84 communicate with the second discharge chamber 38 and the fifth insertion hole 63a while facing the second vane accommodating hole 65, the second vane 34, the second roller 25, and the third plain bearing 73. Furthermore, the supply hole 84c of the second oil supply passage 84 communicates with the second discharge chamber 38 and the sixth insertion hole 36d while facing the fourth plain bearing 74. The second vane accommodating hole 65, the second vane 34, the second roller 25, the third plain bearing 73, and the fourth plain bearing 74 are an example of the "sliding part" according to the present invention. As a result, as shown by the solid arrows in Figures 1 and 2, the lubricating oil 39 in the second discharge chamber 38 is supplied via the second oil supply passage 84 to the sliding parts within the rotating body 30, namely the second vane accommodating hole 65, the second vane 34, the second roller 25, the third plain bearing 73 and the fourth plain bearing 74, due to the pressure difference with the second discharge chamber 38.

[0104] In the compressor configured as described above, rotation of the rotor 42 of the drive mechanism 40 causes the rotating body 30 to rotate about the central axis O1 within the suction communication chamber 15. The rotation of the rotating body 30 causes the first cylinder body 51 and the first vane 33, etc., and the second cylinder body 61 and the second vane 34, etc., to rotate integrally. The first cylinder body 51 and the first vane 33, etc., and the second cylinder body 61 and the second vane 34, etc., function in the same manner, so the following description will only explain the function of the first cylinder body 51 and the first vane 33, etc., and will omit a description of the function of the second cylinder body 61 and the second vane 34, etc.

[0105] Furthermore, each time the rotating body 30 rotates once, the first cylinder body 51 and the first vane 33 and the second cylinder body 61 and the second vane 34 are displaced periodically, but the period of displacement of the first cylinder body 51, etc. and the period of displacement of the second cylinder body 61, etc. are shifted by 180 degrees, which is half a period.

[0106] Rotation of the rotor 30 causes the first cylinder body 51 to rotate about the central axis O1 as the rotation axis along the outer peripheral surface 26a of the first eccentric portion 26. Rotation of the first cylinder body 51 also causes the first vane 33 to rotate along the outer peripheral surface 26a of the first eccentric portion 26. At this time, the first vane 33 is urged radially inward by the urging force of the first spring 57, and moves forward and backward relative to the first working chamber 54 with its tip abutting against the outer peripheral surface 26a. This divides the first working chamber 54 into a first suction chamber 54a and a first compression chamber 54b.

[0107] That is, in this compressor, the rotation of the first cylinder body 51 and the advancement and retreat of the first vane 33 relative to the first working chamber 54 increase the volume of the first suction chamber 54a and decrease the volume of the first compression chamber 54b in the first working chamber 54. As a result, as shown by the dashed arrows in Figures 1 and 2, low-pressure refrigerant is drawn into the suction communication chamber 15 from outside the compressor through the piping and the suction communication port 13. The refrigerant drawn into the suction communication chamber 15 contains lubricating oil 39.

[0108] The refrigerant in the suction communication chamber 15 is drawn into the first suction chamber 54a through the suction passage 81, and is compressed in the first compression chamber 54b from which the refrigerant is compressed. The high-pressure refrigerant compressed to discharge pressure is then discharged from the first discharge port 58 into the first discharge chamber 37.

[0109] Meanwhile, the rotation of the second cylinder body 61 and the movement of the second vane 34 toward and away from the second working chamber 64 act in the same way in the second working chamber 64. That is, the refrigerant drawn in and compressed in the second working chamber 64 is discharged from the second discharge port 68 to the second discharge chamber 38. The refrigerant discharged to the second discharge chamber 38 then flows through the inner rotor discharge passage 82 and is discharged to the first discharge chamber 37.

[0110] In this way, high-pressure refrigerant is discharged into the first discharge chamber 37 and the second discharge chamber 38, so the first discharge chamber 37 and the second discharge chamber 38 are at a higher pressure than the suction communication chamber 15. In other words, the suction communication chamber 15 has a lower pressure suction atmosphere than the first discharge chamber 37 and the second discharge chamber 38.

[0111] The refrigerant in the first discharge chamber 37 flows through the intra-shaft discharge passage 75 and is discharged to the outside of the compressor through a pipe connected to the discharge communication port 17. As a result, the refrigerant compressed in the first compression chamber 54b and discharged to the first discharge chamber 37 and the refrigerant compressed in the second compression chamber 64b and discharged to the second discharge chamber 38 can be combined and discharged to the outside of the compressor from the discharge communication port 17 via the intra-shaft discharge passage 75.

[0112] In this compressor, a stator 41 is fixed to a shaft 20 supported by a housing 10. A rotating body 30, which rotates integrally with a rotor 42, is supported rotatably relative to the shaft 20. In other words, the stator 41 and the rotating body 30 are not in contact with the housing 10. Therefore, even if vibrations occur in the stator 41 or in sliding or collision parts of the rotating body 30, these vibrations are transmitted to the shaft 20 but are not transmitted directly to the housing 10.

[0113] The first small diameter portion 21c and the second small diameter portion 21d, which are both ends of the shaft 20, are supported by the housing 10 via the first vibration-isolating material 76 and the second vibration-isolating material 77, respectively, and the shaft 20 itself does not contact the housing 10. Therefore, vibrations transmitted from the stator 41 and the rotating body 30 to the shaft 20 are attenuated by the elastic deformation of the first vibration-isolating material 76 and the second vibration-isolating material 77, thereby suppressing the transmission of vibrations from the shaft 20 to the housing 10.

[0114] Therefore, this compressor can effectively suppress the transmission of vibrations to the outside.

[0115] In particular, in this compressor, both the first vibration-isolating material 76 and the second vibration-isolating material 77 are disposed in the intake refrigerant atmosphere, which can suppress thermal deterioration of the first vibration-isolating material 76 and the second vibration-isolating material 77. As a result, transmission of vibration from the shaft 20 to the housing 10 can be suppressed for a long period of time.

[0116] Furthermore, in this compressor, the first thrust space 14b located behind the shaft 20 is filled with a refrigerant intake atmosphere, and the second thrust space 16d located in front of the shaft 20 is filled with a refrigerant intake atmosphere. That is, both ends of the shaft 20 are filled with a refrigerant intake atmosphere. This suppresses the differential pressure acting on both ends of the shaft 20. As a result, the shaft 20 is prevented from being pushed in one direction along the central axis O1 due to the differential pressure. This suppresses the first vibration-damping material 76 and the second vibration-damping material 77 from being deteriorated due to an excessive load.

[0117] Furthermore, in this compressor, the rotation of the rotating body 30, which rotates integrally with the rotor 42, causes the first cover body 35 to rotate within the suction communication chamber 15. This generates centrifugal force in response to the rotation of the first cover body 35 in the first discharge chamber 37 formed inside the first cover body 35. As a result, this centrifugal force acts on the refrigerant discharged into the first discharge chamber 37. As a result, in this compressor, the refrigerant and the lubricating oil 39 can be effectively separated in the first discharge chamber 37. The centrifugal force in the first discharge chamber 37 causes the lubricating oil 39 separated from the refrigerant to easily adhere to the inner circumferential surface 35e of the first outer circumferential wall 35a and to easily remain within the first discharge chamber 37 on the radially outer side of the first cover body 35. As a result, the lubricating oil 39 is less likely to be included in the refrigerant discharged from the shaft discharge passage 75 through the piping of the discharge communication port 17 to the outside of the compressor.

[0118] These factors also apply to the second discharge chamber 38 formed inside the second cover body 36. That is, in the second discharge chamber 38, the lubricating oil 39 suitably separated from the refrigerant is likely to adhere to the inner circumferential surface 36e of the second outer circumferential wall 36a due to centrifugal force within the second discharge chamber 38, and is also likely to accumulate within the second discharge chamber 38 on the radially outer side of the second cover body 36. For this reason, it is difficult for the lubricating oil 39 to flow into the inner discharge passage 82 located a predetermined distance D away from the inner circumferential surface 36e.

[0119] Therefore, this compressor effectively separates the lubricating oil 39 from the compressed refrigerant and prevents the lubricating oil 39 from leaking out together with the refrigerant, thereby preventing a decrease in the heat exchange efficiency of the air conditioner due to the leakage of the lubricating oil 39 to the outside.

[0120] Furthermore, in this compressor, the lubricating oil 39 stored in the first discharge chamber 37 and the second discharge chamber 38 can be supplied to each sliding part in the rotating body 30. Specifically, the lubricating oil 39 in the first discharge chamber 37 can be supplied to the first vane accommodating hole 55, the first vane 33, the first roller 24, and the second plain bearing 72 through the first oil supply passage 83. The lubricating oil 39 in the second discharge chamber 38 can be supplied to the second vane accommodating hole 65, the second vane 34, the second roller 25, the third plain bearing 73, and the fourth plain bearing 74 through the second oil supply passage 84. As a result, each sliding part in the rotating body 30 can be suitably lubricated.

[0121] Furthermore, in this compressor, as the first cylinder body 51 rotates, the first vane 33 rotates along the outer peripheral surface of the first roller 24, and the sliding friction force between the first roller 24 and the first vane 33 causes the first roller 24 to rotate naturally around the first eccentric shaft portion 22. The rotation speed of the first roller 24 is lower than the rotation speed of the first vane 33. This accompanying rotation of the first roller 24 can reduce wear on the first vane 33. Similarly, the accompanying rotation of the second roller 25 can reduce wear on the second vane 34.

[0122] Furthermore, in this compressor, the first discharge chamber 37 is formed inside the first cover body 35. Therefore, by appropriately setting the size of the first cover body 35, it is possible to ensure a suitable volume for the first discharge chamber 37. As a result, in this compressor, it is possible to suitably reduce discharge pulsation in the first discharge chamber 37 when refrigerant is discharged from the first compression chamber 54b to the first discharge chamber 37. This operation will be described in detail.

[0123] As described above, the refrigerant compressed in the first compression chamber 54b flows through the first discharge port 58 and is discharged into the first discharge chamber 37. Here, because the first discharge port 58 has a smaller diameter than the first discharge chamber 37, the refrigerant compressed in the first compression chamber 54b flows through the first discharge port 58 and is then discharged into the first discharge chamber 37, which is a space with a larger volume than the first discharge port 58. The refrigerant discharged into the first discharge chamber 37 flows through the intra-shaft discharge passage 75, which is a space with a smaller volume than the first discharge chamber 37, and is discharged to the outside of the compressor.

[0124] Therefore, the refrigerant compressed in the first compression chamber 54b flows through the first discharge port 58, the first discharge chamber 37, and the in-shaft discharge passage 75 in that order, flowing through a narrow space to a wide space, and then flowing through another narrow space before being discharged to the outside of the compressor. In this way, the muffler effect of the first discharge chamber 37 is fully exhibited in this compressor.

[0125] Furthermore, by appropriately setting the length of the first discharge chamber 37 in the direction of the central axis O1, it is possible to ensure a suitable length of the first discharge chamber 37 in the direction of the central axis O1 in this compressor. As a result, it is possible to suitably cancel out, within the first discharge chamber 37, the low-frequency wavelength of the refrigerant compressed in the first compression chamber 54b.

[0126] As a result, in this compressor, discharge pulsation occurring when refrigerant is discharged from the first compression chamber 54b to the first discharge chamber 37 can be suitably reduced in the first discharge chamber 37. Similarly, discharge pulsation occurring when refrigerant is discharged from the second compression chamber 64b to the second discharge chamber 38 can also be suitably reduced in the second discharge chamber 38.

[0127] For these reasons, this compressor can achieve a very quiet operation.

[0128] 5, in the compressor of the second embodiment, the first communication hole 14a and the first thrust space 14b are not formed in the rear wall 11b of the housing body 11, and the second communication hole 16c and the second thrust space 16d are not formed in the housing cover 12. In addition, the housing cover 12 is formed with a second support recess 160 and a discharge communication port 170.

[0129] In this compressor, a first vibration-isolating material 97 and a second vibration-isolating material 98 are disposed in the first support recess 14 and the second support recess 160, respectively.

[0130] The first vibration-isolating material 97 is in the shape of a thick disk having an outer surface shape that corresponds to the inner surface shape of the first support recess 14. The outer diameter of the first vibration-isolating material 97 is slightly larger than the inner diameter of the first support recess 14. The first vibration-isolating material 97 is inserted into and fixed in the first support recess 14 while being elastically deformed.

[0131] A first shaft support recess 97a is recessed in the center of the first vibration-isolating material 97. The first shaft support recess 97a has a cylindrical inner surface shape that corresponds to the outer surface shape of the first small diameter portion 21c of the shaft 20. The inner diameter of the first shaft support recess 97a is slightly smaller than the outer diameter of the first small diameter portion 21c. Furthermore, a first through-hole 97b is formed in the center of the first vibration-isolating material 97, penetrating the first vibration-isolating material 97 in the direction of the central axis O1.

[0132] The first small diameter portion 21c of the shaft 20 is inserted into and fixed in the first shaft support recess 97a of the first vibration-isolating material 97. The rear end surface of the first small diameter portion 21c abuts against the bottom surface of the first shaft support recess 97a. In this way, the first small diameter portion 21c of the shaft 20 is supported by the first support recess 14 via the first vibration-isolating material 97.

[0133] The second support recess 160 is recessed forward from the center of the inner surface of the housing cover 12. The second support recess 160 has the same shape and size as the first support recess 14. The discharge communication port 170 extends in the direction of the central axis O1 at the position of the central axis O1, and connects the interior of the second support recess 160 to the outside of the compressor.

[0134] The second vibration-isolating material 98 has the same shape and size as the first vibration-isolating material 97. That is, like the first vibration-isolating material 97, the second vibration-isolating material 98 has a second shaft support recess 98a and a second through-hole 98b, and is inserted into and fixed in the second support recess 160 while being elastically deformed.

[0135] The second small diameter portion 21d of the shaft 20 is inserted into and fixed in the second shaft support recess 98a of the second vibration-isolating material 98. The front end face of the second small diameter portion 21d abuts against the bottom surface of the second shaft support recess 98a. In this way, the second small diameter portion 21d of the shaft 20 is supported by the second support recess 160 via the second vibration-isolating material 98.

[0136] In addition, in this compressor, an intra-shaft discharge passage 750 is formed inside the shaft 20. The intra-shaft discharge passage 750 has an axial passage portion 751 extending in the direction of the central axis O1 and a radial passage portion 752 extending in the radial direction of the central axis O1.

[0137] The front end of the axial passage portion 751 extends to the front end of the shaft 20, opens at the front end surface, and communicates with the second through hole 98b of the second vibration isolator 98. The rear end of the axial passage portion 751 extends to the rear end of the shaft 20, opens at the rear end surface, and communicates with the first through hole 97b of the first vibration isolator 97. One end of the radial passage portion 752 opens at the outer circumferential surface of the medium diameter portion 21a of the shaft 20 in the first discharge chamber 37. The other end of the radial passage portion 752 is connected to the axial passage portion 751. In this way, the intra-shaft discharge passage 750 communicates between the first discharge chamber 37 and the discharge communication port 170 via the second through hole 98b of the second vibration isolator 98.

[0138] An annular third seal member 45 is attached to the rear end surface of the shaft 20 so as to surround the open end of the axial passage portion 751. Furthermore, an annular fourth seal member 46 is attached to the bottom surface of the first support recess 14 so as to surround the open end of the first through hole 97b of the first vibration-damping material 97. Similarly, an annular fifth seal member 47 is attached to the front end surface of the shaft 20 so as to surround the open end of the axial passage portion 751. Furthermore, an annular sixth seal member 48 is attached to the bottom surface of the second support recess 160 so as to surround the open end of the second through hole 98b of the second vibration-damping material 98.

[0139] In this compressor, both ends of the shaft 20 are exposed to the discharge refrigerant atmosphere. This reduces the pressure difference acting on both ends of the shaft 20 in the direction of the central axis O1. As a result, the shaft 20 is prevented from being pushed in one direction in the direction of the central axis O1 by the pressure difference, thereby preventing the first vibration-isolating material 97 and the second vibration-isolating material 98 from being deteriorated due to an excessive load.

[0140] The other configurations and effects are the same as those of the first embodiment.

[0141] As shown in FIG. 6, the compressor of the third embodiment employs a first oscillator 93 in which a vane and a roller are integrated, instead of the first roller 24 and the first vane 33 of the compressor of the first embodiment.

[0142] The first oscillator 93 has a first roller body 94 and a first vane body 95 .

[0143] The first roller body 94 is cylindrical and is disposed on the outer peripheral surface of the first eccentric shaft portion 22. The first roller body 94 is rotatable relative to the first eccentric shaft portion 22. The first eccentric shaft portion 22 and the first roller body 94 form a first eccentric portion 26. The first eccentric portion 26 has a circular outer peripheral surface 26a centered on the first eccentric axis O2.

[0144] The first vane body 95 is formed integrally with the first roller body 94. The first vane body 95 has a rectangular flat plate shape and extends radially outward from the outer circumferential surface of the first roller body 94.

[0145] In this compressor, first vane accommodating hole 55 has a pair of first bushing accommodating portions 55 a. The radially outer side of first bushing accommodating portion 55 a in first vane accommodating hole 55 is shaped so as not to interfere with the oscillation of first vane body 95.

[0146] Each first bushing accommodating portion 55a has an arc-shaped cross section perpendicular to the central axis O1. A first bushing 96 is accommodated in each first bushing accommodating portion 55a. Each first bushing 96 is a plate-shaped member having flat surfaces facing each other and an arc-shaped surface facing away from the flat surfaces. The arc-shaped surface of each first bushing 96 slides against the inner surface of the first bushing accommodating portion 55a. The pair of first bushings 96 sandwich the first vane body 95 accommodated in the first vane accommodating hole 55 from both sides, and the flat surfaces of each first bushing 96 slide against both side surfaces of the first vane body 95.

[0147] The first eccentric shaft portion 22, the first roller body 94 and the first vane body 95 of the first oscillator 93, the first cylinder body 51, and the first bush 96 have the same length in the direction of the central axis O1.

[0148] In this compressor, rotation of the rotor 30 causes the first cylinder body 51 to rotate about the central axis O1 and the first oscillator 93 to rotate about the first eccentric axis O2. That is, the first oscillator 93 rotates eccentrically relative to the first cylinder body 51. During this rotation, the first vane body 95 of the first oscillator 93 moves back and forth within the first vane receiving hole 55 while oscillating. In other words, the first vane body 95 moves back and forth relative to the first working chamber 54. As a result, the volume of the first suction chamber 54a in the first working chamber 54 is expanded and the volume of the first compression chamber 54b is reduced. In this way, the refrigerant drawn into the first suction chamber 54a through the first suction port 81c and compressed in the first compression chamber 54b in the first working chamber 54 is discharged from the first discharge port 58 to the first discharge chamber 37.

[0149] Although not shown in the figures, a second oscillator similar to the first oscillator 93 is used in place of the second roller 25 and second vane 34 in the compressor of the first embodiment, and the second vane accommodating hole has a pair of second bushing accommodating portions similar to the first bushing accommodating portion 55a, and each second bushing accommodating portion accommodates a second bushing similar to the first bushing 96. The second oscillator, the second bushing, etc. act in the same way as the first oscillator 93, the first bushing 96, etc. As a result, the second working chamber also acts in the same way as the first working chamber 54, and refrigerant is sucked and compressed in the second working chamber.

[0150] In particular, in this compressor, first roller body 94 and first vane body 95 are integrally formed, and therefore the roller and vane do not slide, thereby eliminating sliding wear and leakage between the roller and vane. Also, first vane body 95 is accommodated in first vane accommodating hole 55 via first bushing 96, and the sliding portions between first bushing 96 and first vane body 95 and first bushing accommodating portion 55a are in surface contact, which is advantageous in ensuring wear resistance and sealing performance at these sliding portions.

[0151] The other configurations and effects are the same as those of the first embodiment.

[0152] Although the present invention has been described above in accordance with Examples 1 to 3, it goes without saying that the present invention is not limited to the above Examples 1 to 3, and can be appropriately modified and applied within the scope of the spirit of the present invention.

[0153] For example, in the compressors of the first to third embodiments, a rubber elastic body is used as the vibration-isolating material, but the present invention is not limited to this, and low-rigidity materials such as resin or metal springs may also be used.

[0154] Furthermore, in the compressors of Examples 1 to 3, both ends of the shaft are supported by vibration-damping material, but this is not limited to this. It is also possible to have one end of the shaft supported by vibration-damping material and the other end of the shaft directly fixed to the housing.

[0155] In the compressor of the first embodiment, the first discharge chamber 37 and the second discharge chamber 38 are connected to each other by the inner-rotor discharge passage 82, and the first discharge chamber 37 and the discharge communication port 17 are connected to each other by the inner-shaft discharge passage 75. However, this is not limitative. For example, a second discharge communication port may be provided in the rear wall 11b of the housing body 11, and a second inner-shaft discharge passage may be provided in the shaft 20 that connects the second discharge communication port with the second discharge chamber 38. In this way, compressed refrigerant discharged from the second compression chamber 64b to the second discharge chamber 38 is discharged from the second discharge communication port through the second inner-shaft discharge passage to the outside of the compressor. The same applies to the compressor of the third embodiment.

[0156] Furthermore, the compressor of the first embodiment is provided with the second cover body 36 that forms the second discharge chamber 38. However, this is not limiting, and for example, the second discharge port 68 and the second discharge valve 69 may be provided inside the second intermediate plate 62, and the second discharge port 68 and the first discharge chamber 37 may be connected to each other through an internal rotor discharge passage 82, thereby eliminating the second discharge chamber 38 and the second cover body 36. In this case, the second boss fixed to the rotor 42 may be provided integrally with the second side plate 63. The same applies to the compressors of the second and third embodiments.

[0157] Furthermore, in the compressor of the first embodiment, the second suction port 81d is provided in the second intermediate plate 62, but this is not limiting. For example, the second suction port 81d may be provided in the second side plate 63. The same applies to the compressors of the second and third embodiments.

[0158] Although the compressor of the first embodiment is a two-cylinder single-stage compression type having a first cylinder 31 and a second cylinder 32, the present invention is not limited to this. For example, the compressor may be a multi-cylinder multi-stage compression type that compresses the refrigerant in stages. Furthermore, the number of cylinders is not limited, and the compressor may be a one-cylinder or a multi-cylinder type having three or more cylinders. The same applies to the compressors of the second and third embodiments.

[0159] In the compressors of the first and second embodiments, the first eccentric shaft portion 22 and the first roller 24 may be integrated together. The same applies to the second eccentric shaft portion 23 and the second roller 25.

[0160] In the compressor of Example 1, the first cover body 35 has the first boss 35c, but this is not limited thereto. For example, a first boss may be integrally formed extending forward from the inner peripheral edge of the first side plate 53, and the inner peripheral edge of the first front wall 35b of the first cover body 35 may be fixed to the outer peripheral surface of this first boss. In this case, a radial through-hole may be provided radially penetrating the first boss, and an annular groove may be provided in the outer peripheral surface of the medium diameter portion 21a that connects the radial through-hole to the radial passage portion 75b of the intra-shaft discharge passage 75, thereby communicating the first discharge chamber 37 with the discharge communication port 17. The same applies to the compressors of Examples 2 and 3.

[0161] The following technical ideas can be extracted from the disclosure of the specification, drawings, etc.

[0162] a shaft accommodated in the housing and supported by the housing, the shaft having a main shaft portion and an eccentric portion eccentric with respect to a central axis of the main shaft portion; a rotor accommodated within the housing and supported rotatably relative to the shaft with the central axis as a rotation axis; and a drive mechanism accommodated within the housing for rotationally driving the rotor, wherein the drive mechanism has a stator fixed to the shaft, and a rotor disposed on the outer periphery of the stator and fixed to the rotor so as to be rotatable integrally therewith, the rotor having a cylinder which forms a working chamber together with an outer periphery of the eccentric portion and rotates along the outer periphery, and vanes which move back and forth relative to the working chamber as the cylinder rotates, thereby separating the working chamber into a suction chamber into which a refrigerant is sucked and a compression chamber which compresses the refrigerant, and the shaft is supported by the housing via a vibration-damping material which suppresses transmission of vibration from the shaft to the housing.

[0163] (Supplementary Note 2) The rotary compressor according to Supplementary Note 1, wherein both ends of the shaft are supported by the housing via the vibration-proofing material.

[0164] (Supplementary Note 3) The rotary compressor according to Supplementary Note 1 or 2, wherein the vibration-proofing material is disposed in an intake refrigerant atmosphere that communicates with the suction chamber within the housing.

[0165] (Appendix 4) The rotary compressor according to Appendix 3, wherein the rotating body has a cover body arranged on the outer periphery of the main shaft portion, the cover body has a discharge chamber that communicates with the compression chamber and from which refrigerant compressed in the compression chamber is discharged, the housing has a discharge communication port that communicates with the outside, the shaft has an internal shaft discharge passage that communicates between the discharge chamber and the discharge communication port, and an annular seal member is arranged between the connection between the internal shaft discharge passage and the discharge communication port and the vibration-damping material.

[0166] (Note 5) The rotating body has a cover body arranged on the outer circumferential side of the main shaft portion, the cover body having a discharge chamber communicating with the compression chamber and from which refrigerant compressed in the compression chamber is discharged, the housing having a discharge communication port extending in a direction intersecting with the central axis and communicating with the outside, the shaft having an in-shaft discharge passage communicating between the discharge chamber and the discharge communication port, the in-shaft discharge passage having an axial passage portion extending in the direction of the central axis, a first radial passage portion extending in a direction intersecting with the central axis and communicating between the discharge chamber and the axial passage portion, and a second radial passage portion extending in a direction intersecting with the central axis and communicating between the discharge communication port and the axial passage portion, and an annular seal member attached to the outer circumferential surface of the shaft is arranged between a connection portion between the discharge communication port and the second radial passage portion and an end of the shaft closer to the connection portion, 5. The rotary compressor according to claim 2, wherein both ends of the shaft are in an intake refrigerant atmosphere that communicates with the suction chamber within the housing.

[0167] (Appendix 6) The rotary compressor according to Appendix 2, wherein the rotating body has a cover body arranged on the outer periphery of the main shaft portion, the cover body has a discharge chamber that communicates with the compression chamber and from which refrigerant compressed in the compression chamber is discharged, the housing has a discharge communication port that communicates with the outside, the shaft has an internal shaft discharge passage that communicates between the discharge chamber and the discharge communication port, the internal shaft discharge passage extends in the direction of the central axis and has open ends that open to both ends of the shaft, and annular seal members are arranged around each of the open ends to surround each of the open ends.

[0168] The present invention can be used in vehicle air conditioning systems and the like.

[0169] 10 Housing 17, 170 Discharge communication port 20 Shaft 21 Main shaft portion 26 First eccentric portion (eccentric portion) 27 Second eccentric portion (eccentric portion) 30 Rotating body 31 First cylinder 32 Second cylinder 33 First vane (vane) 34 Second vane (vane) 35 First cover body (cover body) 36 Second cover body (cover body) 37 First discharge chamber (discharge chamber) 38 Second discharge chamber (discharge chamber) 39 Lubricating oil 40 Drive mechanism 41 Stator 42 Rotor 43 First seal member 44 Second seal member 45 Third seal member 46 Fourth seal member 47 Fifth seal member 48 Sixth seal member 54 First working chamber (working chamber) 54a First suction chamber (suction chamber) 54b First compression chamber (compression chamber) 64 Second working chamber (working chamber) 64a Second suction chamber (suction chamber) 64b Second compression chamber (compression chamber) 75, 750 In-shaft discharge passage 75a, 751 Axial passage portion 75b First radial passage portion 75c Second radial passage portion 752 Radial passage portion 76, 97 First vibration-isolating material (vibration-isolating material) 77, 98 Second vibration-isolating material (vibration-isolating material) 79 Connection portion O1 Central axis

Claims

1. A rotary compressor comprising: a housing; a shaft accommodated in the housing and having a main shaft portion supported by the housing and an eccentric portion eccentric with respect to the central axis of the main shaft portion; a rotor accommodated within the housing and rotatably supported on the shaft with the central axis as the axis of rotation; and a drive mechanism accommodated in the housing for rotationally driving the rotor, wherein the drive mechanism has a stator fixed to the shaft and a rotor disposed on the outer periphery of the stator and fixed to the rotor so as to be rotatable integrally therewith, the rotor having a cylinder which forms a working chamber together with the outer periphery of the eccentric portion and rotates along the outer periphery, and vanes which move back and forth relative to the working chamber as the cylinder rotates, thereby separating the working chamber into a suction chamber into which a refrigerant is sucked and a compression chamber which compresses the refrigerant, and wherein the shaft is supported by the housing via vibration-damping material which reduces the transmission of vibration from the shaft to the housing.

2. A rotary compressor according to claim 1, wherein both ends of said shaft are supported by said housing via said vibration-isolating material.

3. A rotary compressor according to claim 1 or 2, wherein said vibration-isolating material is disposed in said housing in an atmosphere of suction refrigerant that communicates with said suction chamber.

4. A rotary compressor as described in claim 3, wherein the rotating body has a cover body arranged on the outer periphery of the main shaft portion, the cover body having a discharge chamber communicating with the compression chamber and from which refrigerant compressed in the compression chamber is discharged, the housing having a discharge communication port communicating with the outside, the shaft having an internal shaft discharge passage that communicates between the discharge chamber and the discharge communication port, and an annular sealing member being arranged between the connection between the internal shaft discharge passage and the discharge communication port and the vibration-damping material.

5. The rotating body has a cover body arranged on the outer periphery of the main shaft portion, the cover body having a discharge chamber communicating with the compression chamber and from which refrigerant compressed in the compression chamber is discharged, the housing having a discharge communication port extending in a direction intersecting the central axis and communicating with the outside, the shaft having an in-shaft discharge passage communicating between the discharge chamber and the discharge communication port, the in-shaft discharge passage having an axial passage portion extending in the direction of the central axis, a first radial passage portion extending in a direction intersecting the central axis and communicating between the discharge chamber and the axial passage portion, and a second radial passage portion extending in a direction intersecting the central axis and communicating between the discharge communication port and the axial passage portion, and an annular seal member attached to the outer periphery of the shaft is arranged between a connection portion between the discharge communication port and the second radial passage portion and an end of the shaft closer to the connection portion, 3. The rotary compressor according to claim 2, wherein both ends of said shaft are in an intake refrigerant atmosphere communicating with said suction chamber within said housing.

6. A rotary compressor as described in claim 2, wherein the rotating body has a cover body arranged on the outer periphery of the main shaft portion, the cover body has a discharge chamber that communicates with the compression chamber and from which refrigerant compressed in the compression chamber is discharged, the housing has a discharge communication port that communicates with the outside, the shaft has an internal shaft discharge passage that communicates between the discharge chamber and the discharge communication port, the internal shaft discharge passage extends in the direction of the central axis and has open ends that open to both ends of the shaft, and annular sealing members are arranged around each of the open ends to surround each of the open ends.

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