Rotary compressor

Abstract

A shaft (20) has a main shaft part (21) that is supported by a housing (10) and an eccentric part (26) that is eccentric with respect to the center axis (O1) of the main shaft part (21). A rotary body (30) is supported so as to be capable of rotation with respect to the shaft (20), with the center axis (O1) as a rotation axis. The rotary body (30) has a cylinder (31), a vane (33), and a cover body (35). The cylinder (31) forms an operation chamber (54) therein with the outer peripheral surface of the eccentric part (26), and rotates along the outer peripheral surface of the eccentric part (26). The vane (33) advances and retreats with respect to the operation chamber (54) along with rotation of the cylinder (31) and partitions the operation chamber (54) into an intake chamber (54a) and a compression chamber (54b). The cover body (35) is disposed to the outer peripheral side of the main shaft part (21) and defines, on the outer peripheral side of the main shaft part (21), a discharge chamber (37) for discharge of lubricating oil (39) along with a compressed coolant.

Description

Rotary Compressor

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

[0002] Patent Document 1 discloses a conventional rotary compressor (hereinafter referred to as "compressor" where appropriate). This compressor includes a housing, a drive shaft, a drive mechanism, a cylinder, rollers, vanes, a separation chamber, and an oil storage chamber. The drive shaft is supported by the housing so as to be rotatable about its drive axis. The drive mechanism rotates the drive shaft.

[0003] In a cross section perpendicular to the drive axis, the cylinder has a perfectly circular interior space, and the roller has a perfectly circular outer circumferential surface. The roller is fixed to the drive shaft and rotates together with the drive shaft within the cylinder's interior space. The axis of the cylinder's interior space is eccentric from the drive axis, and part of the roller's outer circumferential surface contacts the cylinder's inner circumferential surface. This forms a working chamber between the roller's outer circumferential surface and the cylinder's inner circumferential surface.

[0004] The vane moves back and forth relative to the working chamber as the roller rotates, thereby dividing the working chamber into a suction chamber into which the refrigerant is drawn and a compression chamber into which the refrigerant is compressed.

[0005] A separation chamber and an oil reservoir are defined within the housing. The compression chamber and the separation chamber are in communication with each other, and the separation chamber and the oil reservoir are in communication with each other.

[0006] In this compressor, the drive shaft rotates about the drive axis, causing the roller to rotate along the inner circumferential surface of the cylinder. This causes the vane to move back and forth relative to the working chamber, dividing the working chamber into a suction chamber and a compression chamber. In this compressor, refrigerant is drawn into the suction chamber and compressed in the compression chamber. The refrigerant compressed in the compression chamber is discharged into the separation chamber. In the separation chamber, the lubricating oil contained in the refrigerant is separated by centrifugal force. The lubricating oil separated from the refrigerant in the separation chamber is stored in the oil reservoir.

[0007] Japanese Patent Application Laid-Open No. 2003-336588

[0008] In this type of compressor, it is necessary to properly lubricate the sliding parts, such as the bearings that support the drive shaft. To achieve this, it is desirable to seal a sufficient amount of lubricating oil inside the compressor. However, even in compressors with a separation chamber, it is difficult to completely separate the lubricating oil from the compressed refrigerant. Any lubricating oil that is not completely separated in the separation chamber will leak out together with the compressed refrigerant. This leakage of lubricating oil to the outside can lead to a decrease in the heat exchange efficiency of air conditioners and other devices that use the rotary compressor.

[0009] The present invention has been made in consideration of the above-described conventional situation, and an object to be achieved is to provide a rotary compressor that can effectively separate lubricating oil from compressed refrigerant and prevent the lubricating oil from leaking out together with the refrigerant.

[0010] a rotary compressor according to the present invention comprising: a housing; a shaft accommodated in the housing and supported by the housing, the shaft having an eccentric portion eccentric with respect to the central axis of the main shaft; 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 within the housing for rotationally driving the rotor, wherein the rotor has a cylinder which, together with the outer peripheral surface of the eccentric portion, forms a working chamber therein and rotates along the outer peripheral surface; 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 refrigerant is sucked and a compression chamber which compresses the refrigerant; and a cover body arranged on the outer peripheral side of the main shaft, the cover body communicating with the compression chamber and defining a discharge chamber on the outer peripheral side of the main shaft from which lubricating oil is discharged together with the refrigerant compressed in the compression chamber.

[0011] In the rotary compressor of the present invention, lubricating oil is discharged into the discharge chamber together with the refrigerant compressed in the compression chamber. During operation of the rotary compressor, the cover rotates, generating centrifugal force within the discharge chamber. This centrifugal force acts on the refrigerant discharged into the discharge chamber. As a result, the rotary compressor of the present invention can effectively separate the refrigerant and the lubricating oil in the discharge chamber.

[0012] Therefore, the rotary compressor of the present invention can effectively separate the lubricating oil from the compressed refrigerant, and can prevent the lubricating oil from leaking out together with the refrigerant.

[0013] The rotating body preferably has a sliding portion and an oil supply passage for supplying the lubricating oil in the discharge chamber to the sliding portion.

[0014] In this case, the lubricating oil in the discharge chamber can be supplied to the sliding parts of the rotating body through the oil supply passage, thereby making it possible to suitably lubricate the sliding parts of the rotating body.

[0015] The drive mechanism may have a cylindrical motor. A cylindrical portion having an oil reservoir formed therein is preferably disposed on the inner periphery of the motor. The rotor and the shaft preferably have an oil return passage for returning the lubricating oil in the discharge chamber to the oil reservoir. The cylindrical portion preferably has a return passage within the housing for returning the lubricating oil in the oil reservoir to the outside of the cylindrical portion.

[0016] In this case, the lubricating oil in the discharge chamber is returned to the oil reservoir formed inside the cylindrical portion through an oil return passage. The lubricating oil in the oil reservoir is returned to the outside of the cylindrical portion within the housing through a return passage and supplied to the sliding parts of the rotating body, etc. This allows the sliding parts of the rotating body, etc. to be suitably lubricated. In addition, the cylindrical portion forming the oil reservoir is located on the inner periphery of the motor, making effective use of the space on the inner periphery of the motor. This allows the lubricating oil storage area to be expanded without increasing the size of the rotary compressor.

[0017] The housing may have a discharge communication port that communicates with the outside, and the shaft preferably has an internal discharge passage that connects the discharge chamber with the discharge communication port.

[0018] In this case, the refrigerant discharged into the discharge chamber can be discharged to the outside from the discharge communication port via the shaft discharge passage.

[0019] The eccentric portion may have a first eccentric portion and a second eccentric portion. The working chamber may have a first working chamber and a second working chamber. The cylinder may have a first cylinder arranged on the outer circumferential side of the first eccentric portion and forming a first working chamber between it and the first eccentric portion, and a second cylinder arranged on the outer circumferential side of the second eccentric portion and forming a second working chamber between it and the second eccentric portion. The suction chamber may have a first suction chamber and a second suction chamber. The compression chamber may have a first compression chamber and a second compression chamber. The vanes may have a first vane dividing the first working chamber into a first suction chamber and a first compression chamber, and a second vane dividing the second working chamber into a second suction chamber and a second compression chamber. The discharge chamber may have a first discharge chamber and a second discharge chamber. The cover body may include a first cover body fixed to the first cylinder and having a first discharge chamber formed therein that communicates with the first compression chamber, and a second cover body fixed to the second cylinder and having a second discharge chamber formed therein that communicates with the second compression chamber. The housing may have a discharge communication port that communicates with the outside. The rotor preferably has an internal rotor discharge passage that communicates with the first discharge chamber and the second discharge chamber. The shaft preferably has an internal shaft discharge passage that communicates with the first discharge chamber and the discharge communication port.

[0020] In this case, the refrigerant compressed in the second compression chamber and discharged to the second discharge chamber is introduced into the first discharge chamber through the internal discharge passage. The refrigerant compressed in the first compression chamber and discharged to the first discharge chamber, and the refrigerant introduced from the second discharge chamber to the first discharge chamber, are discharged to the outside from the discharge communication port through the internal discharge passage. This allows the refrigerant compressed in the first compression chamber and the refrigerant compressed in the second compression chamber to be discharged to the outside together from the discharge communication port.

[0021] The discharge chamber is preferably formed to have a diameter larger than that of a support portion of a shaft that supports the rotor.

[0022] In this case, since the volume of the discharge chamber can be suitably secured, discharge pulsation occurring when refrigerant is discharged from the compression chamber to the discharge chamber can be suitably reduced in the discharge chamber.

[0023] The rotary compressor of the present invention can effectively separate the lubricating oil from the compressed refrigerant, and can prevent the lubricating oil from leaking out together with the refrigerant.

[0024] 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.

[0025] 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.

[0026] 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 .

[0027] 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 can change its own position as appropriate depending on the vehicle in which it is installed. The same applies to the compressors shown in Figs. 2 and 5.

[0028] 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.

[0029] 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.

[0030] 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.

[0031] A first support portion 14 is formed at the center of the inner surface of the rear wall 11b. The first support portion 14 has a cylindrical shape centered on the central axis O1 and protrudes forward from the center of the inner surface of the rear wall 11b, i.e., into a suction communication chamber 15 described below.

[0032] 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.

[0033] 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.

[0034] A second support portion 16 is formed at the center of the inner surface of the housing cover 12. The second support portion 16 has a cylindrical shape centered on the central axis O1 and protrudes rearward from the center of the inner surface of the housing cover 12.

[0035] A discharge communication port 17 is formed in the housing cover 12. The discharge communication port 17 is located at the center of the housing cover 12 and penetrates the housing cover 12 in the direction of the central axis O1. The discharge communication port 17 faces the front end surface 20a of the shaft 20 in the direction of 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 through the pipe.

[0036] 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.

[0037] 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, and a small diameter portion 21c that is smaller than the medium diameter portion 21a. The medium diameter portion 21a, the large diameter portion 21b, and the small diameter portion 21c are integrally formed. The large diameter portion 21b is connected to the rear of the medium diameter portion 21a, and the small diameter portion 21c is connected to the rear of the large diameter portion 21b. The small diameter portion 21c is fixed by fitting into the first support portion 14, and the front end of the medium diameter portion 21a is fixed by fitting into the second support portion 16.

[0038] 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).

[0039] 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 and a radial passage portion 75b extending in the radial direction of the central axis O1. The front end of the axial passage portion 75a opens to the front end face 20a of the shaft 20. One end of the radial passage portion 75b opens to the outer circumferential surface of the medium diameter portion 21a of the shaft 20 in a first discharge chamber 37 described below. The other end of the radial passage portion 75b is connected to the rear 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.

[0040] 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.

[0041] 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.

[0042] 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.

[0043] The first cylinder 31 has a first cylinder body 51 , a first intermediate plate 52 , and a first side plate 53 .

[0044] 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.

[0045] 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.

[0046] 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.

[0047] 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.

[0048] 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.

[0049] 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.

[0050] 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.

[0051] 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.

[0052] 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.

[0053] The second cylinder 32 has a second cylinder body 61 , a second intermediate plate 62 , and a second side plate 63 .

[0054] 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.

[0055] 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.

[0056] 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.

[0057] 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.

[0058] 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.

[0059] 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.

[0060] 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.

[0061] 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.

[0062] The second cover body 36 is disposed on the outer periphery of the large-diameter portion 21b, rearward of the second cylinder 32. The second cover body 36 includes a cylindrical second outer periphery wall 36a, a generally disk-shaped second rear wall 36b, and a cylindrical second boss 36c. The second boss 36c is disposed on the outer periphery of the large-diameter portion 21b and rotatably supported by the large-diameter portion 21b. A sixth insertion hole 36d, formed together with the inner periphery of the second boss 36c, is provided in the center of the second rear wall 36b and allows the large-diameter portion 21b to pass through. The rear end of the second outer periphery wall 36a is connected to the outer periphery of the second rear wall 36b, and the front end of the second boss 36c is connected to the inner periphery of the second rear wall 36b. The front end of the second outer periphery 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.

[0063] 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.

[0064] 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.

[0065] 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.

[0066] 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.

[0067] 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.

[0068] The outer diameters of the first plain bearing 71 and the second plain bearing 72 are equal, and the outer diameters of the third plain bearing 73 and the fourth plain bearing 74 are equal. The first discharge chamber 37 and the second discharge chamber 38 are formed with diameters larger than the support portion of the shaft 20 that rotationally supports the rotating body 30. Specifically, the inner diameter L2 of the first discharge chamber 37 is larger than the outer diameter of the first plain bearing 71 that is fitted to the medium diameter portion 21 a of the shaft 20 that rotationally supports the first cover body 35 of the rotating body 30. The inner diameter of the second discharge chamber 38 is larger than the outer diameter of the fourth plain bearing 74 that is fitted to the large diameter portion 21 b of the shaft 20 that rotationally supports the second cover body 36 of the rotating body 30.

[0069] The drive mechanism 40 is specifically an electric motor and is housed within 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 housing main body 11 by fitting the stator core 41a against the inner circumferential surface of the outer circumferential wall 11a.

[0070] The rotor 42 is cylindrical around the central axis O1 and is disposed within 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.

[0071] The second boss 36c of the second cover body 36 of the rotating body 30 is inserted into the rotor 42 and fixed to the inner 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.

[0072] 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.

[0073] 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.

[0074] 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.

[0075] 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.

[0076] 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.

[0077] 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.

[0078] 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.

[0079] 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.

[0080] 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.

[0081] 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.

[0082] 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.

[0083] 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.

[0084] 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.

[0085] 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.

[0086] 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.

[0087] 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.

[0088] 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.

[0089] 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.

[0090] 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.

[0091] 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.

[0092] 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.

[0093] 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.

[0094] 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.

[0095] 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.

[0096] 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.

[0097] 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.

[0098] In this compressor, the rotation of the rotor 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. This allows the refrigerant and the lubricating oil 39 to be effectively separated from each other 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 adhere to the inner circumferential surface 35e of the first outer circumferential wall 35a and to remain in the first discharge chamber 37 radially outside 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.

[0099] 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.

[0100] Therefore, this compressor can effectively separate the lubricating oil 39 from the compressed refrigerant, and can prevent the lubricating oil 39 from leaking out together with the refrigerant.

[0101] Furthermore, since the outflow of the lubricating oil 39 to the outside of the compressor can be suppressed, a decrease in the heat exchange efficiency of the air conditioner can be suppressed.

[0102] In particular, in this compressor, lubricating oil 39 stored in first discharge chamber 37 and second discharge chamber 38 can be supplied to each sliding part in rotating body 30. Specifically, lubricating oil 39 in first discharge chamber 37 can be supplied to first vane accommodating hole 55, first vane 33, first roller 24, and second plain bearing 72 through first oil supply passage 83. Furthermore, lubricating oil 39 in second discharge chamber 38 can be supplied to second vane accommodating hole 65, second vane 34, second roller 25, third plain bearing 73, and fourth plain bearing 74 through second oil supply passage 84. As a result, each sliding part in rotating body 30 can be suitably lubricated.

[0103] Furthermore, in this compressor, the inner diameter L2 of the first discharge chamber 37 is larger than the outer diameter L1 of the first plain bearing 71, and the inner diameter of the second discharge chamber 38 is larger than the outer diameter of the fourth plain bearing 74. Therefore, the volumes of the first discharge chamber 37 and the second discharge chamber 38 can be suitably secured, and discharge pulsation in the first discharge chamber 37 and the second discharge chamber 38 can be suitably reduced. Furthermore, even if the diameters of the first discharge chamber 37 and the second discharge chamber 38 are increased, the diameters of the first plain bearing 71, the fourth plain bearing 74, etc. can be prevented from increasing, and therefore the rotating body 30, which rotates at high speed, can be suitably supported.

[0104] 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.

[0105] 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.

[0106] 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.

[0107] 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.

[0108] 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.

[0109] 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.

[0110] For these reasons, this compressor can achieve a very quiet operation.

[0111] 5, in the second cover body 36 of the compressor of the second embodiment, the radial connection position of the second boss 36c to the second rear wall 36b is changed from that of the compressor of the first embodiment. In addition, this compressor includes a shaft 201 instead of the shaft 20.

[0112] In this compressor, the front end of the second boss 36c of the second cover body 36 is connected to a position approximately midway between the inner and outer circumferential edges of the second rear wall 36b. The inner diameter of the second boss 36c is at least twice the outer diameter of the large diameter portion 21b of the shaft 201.

[0113] The shaft 201 has a main shaft portion 211, a first eccentric shaft portion 22, and a second eccentric shaft portion 23. The main shaft portion 211 has a medium diameter portion 21a, a large diameter portion 21b larger than the medium diameter portion 21a, and a cylindrical tubular portion 21d larger than the large diameter portion 21b. In the direction of the central axis O1, the large diameter portion 21b is slightly longer than the combined length of the second side plate 63 and the second outer peripheral wall 36a and second rear wall 36b of the second cover body 36. The tubular portion 21d is longer than the length of the second boss 36c of the second cover body 36. The outer diameter of the tubular portion 21d is at least twice the outer diameter of the large diameter portion 21b. The rear end of the tubular portion 21d is fixed by fitting within the first support portion 14. A sixth insertion hole 36d, through which the large diameter portion 21b can be inserted, is formed in the second rear wall 36b of the second cover body 36. The inner peripheral surface of the second boss 36c forms a seventh insertion hole 36f, through which the cylindrical portion 21d can be inserted.

[0114] The cylindrical portion 21d is integrally formed with the rear end of the large diameter portion 21b. The cylindrical portion 21d is disposed on the inner peripheral side of the second boss 36c, which is fixed to the inner peripheral surface of the rotor 42. A fifth plain bearing 76 is interposed between the cylindrical portion 21d and the seventh insertion hole 36f of the second boss 36c. This allows the second boss 36c to be rotatably supported relative to the cylindrical portion 21d.

[0115] An oil storage chamber 77 is formed inside the cylindrical portion 21d by the inner surface of the cylindrical portion 21d and the inner surface of the rear wall 11b. A return passage 78 is also formed in the cylindrical portion 21d, extending radially downward from the inner circumferential surface of the cylindrical portion 21d and penetrating the cylindrical portion 21d. The return passage 78 opens into the suction communication chamber 15.

[0116] An oil return passage 79 is formed inside the rotor 30 and the shaft 201 to return the lubricating oil 39 in the second discharge chamber 38 to the oil reservoir chamber 77 .

[0117] The oil return passage 79 is composed of a supply hole 84c formed in the second cover body 36, and an annular groove 79a and an in-shaft passage 79b formed inside the shaft 201. In other words, the supply hole 84c also serves as part of the oil return passage 79.

[0118] The annular groove 79a is recessed into the outer peripheral surface of the large diameter portion 21b. The annular groove 79a is provided in a position in the direction of the central axis O1 corresponding to a radial supply hole 84e formed in the second cover body 36. Although not shown, the fourth plain bearing 74 has a communication passage that communicates with the radial supply hole 84e. In other words, the annular groove 79a and the radial supply hole 84e communicate via the fourth plain bearing 74.

[0119] The shaft passage 79b extends from the annular groove 79a radially inward of the large diameter portion 21b and then extends rearward in the direction of the central axis O1. One end of the shaft passage 79b is connected to the annular groove 79a. The other end of the shaft passage 79b opens to the oil reservoir chamber 77. In other words, the shaft passage 79b connects the annular groove 79a and the oil reservoir chamber 77.

[0120] Thus, the oil return passage 79 connects the second discharge chamber 38 to the oil reservoir chamber 77. The pressure in the suction communication chamber 15 is lower than the pressure in the oil reservoir chamber 77, which is connected to the second discharge chamber 38 via the oil return passage 79. Therefore, the lubricating oil 39 in the second discharge chamber 38 flows through the supply hole 84c, the annular groove 79a, and the in-shaft passage 79b and returns to the oil reservoir chamber 77. The lubricating oil 39 in the oil reservoir chamber 77 then returns to the suction communication chamber 15 via the return passage 78.

[0121] Therefore, in this compressor, the lubricating oil 39 in the second discharge chamber 38 is returned to the oil reservoir chamber 77 via the oil return passage 79, and the lubricating oil 39 in the oil reservoir chamber 77 is returned to the suction communication chamber 15 via the return passage 78. The lubricating oil 39 in the suction communication chamber 15 is then drawn into the first suction chamber 54a and the second suction chamber 64a via the suction passage 81 and supplied to each sliding part of the rotor 30. This allows each sliding part of the rotor 30 to be suitably lubricated.

[0122] In addition, the oil reservoir 77 is provided on the inner peripheral side of the rotor 42, effectively utilizing the space on the inner peripheral side of the rotor 42. This allows the storage area for the lubricating oil 39 to be expanded without increasing the size of the compressor.

[0123] The other configurations and effects are the same as those of the first embodiment.

[0124] 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.

[0125] The first oscillator 93 has a first roller body 94 and a first vane body 95 .

[0126] 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.

[0127] 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.

[0128] 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.

[0129] 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.

[0130] 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.

[0131] 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.

[0132] 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.

[0133] 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.

[0134] The other configurations and effects are the same as those of the first embodiment.

[0135] 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.

[0136] For example, in the compressor of Example 1, 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 Example 3.

[0137] Furthermore, the compressor of Example 1 is provided with the second cover body 36 that forms the second discharge chamber 38. However, this is not limiting, and for example, a configuration may be adopted in which the second discharge port 68 and the second discharge valve 69 are provided inside the second intermediate plate 62 and the second discharge port 68 and the first discharge chamber 37 are 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, a second boss that is fixed to the rotor 42 and rotatably supported by the large diameter portion 21 b may be provided integrally with the second side plate 63. The same applies to the compressor of Example 3. The same applies to the compressor of Example 2, but an annular groove 79a connected to the shaft passage 79b is provided at the position of the fifth insertion hole 63a of the second side plate 63, and as part of the oil return passage 79, a passage connecting the first discharge chamber 37 and the annular groove 79a is provided in the first side plate 53, the first cylinder body 51, the first intermediate plate 52, the second intermediate plate 62, the second cylinder body 61 and the second side plate 63.

[0138] 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.

[0139] 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.

[0140] 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.

[0141] 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.

[0142] In the compressor of the first embodiment, a motor is disposed as the drive mechanism 40 on the outer periphery of the second boss 36c, which is rotatably supported on the large diameter portion 21b. However, the present invention is not limited to this, and the motor may be disposed on the outer periphery of the first cylinder 31 and the second cylinder 32, for example. In this case, the rotor 42 may be fixed to the outer periphery of the first cylinder 31 and the outer periphery of the second cylinder 32. The same applies to the compressor of the third embodiment.

[0143] In the compressor of the first embodiment, an inner rotor type motor in which the rotor 42 is disposed on the inner circumferential side of the stator 41 is used as the drive mechanism 40. However, this is not limiting, and an outer rotor type motor in which the rotor is disposed on the outer circumferential side of the stator may also be used. In this case, for example, the stator may be fixed to the outer circumferential surface of the shaft 20, and a rotor fixed to the inner circumferential surface of the second boss 36c of the second cover body 36 may be disposed on the outer circumferential side of the stator.

[0144] In the compressor of Example 2, the cylindrical portion 21d is integrally formed with the rear end of the large diameter portion 21b. However, this is not limiting, and for example, a cylindrical portion may be integrally formed extending forward from the rear wall 11b of the housing body 11, and the large diameter portion 21b of a shaft inserted into the front end of this cylindrical portion may be fixed to the inner circumferential surface of the cylindrical portion.

[0145] The following technical ideas can be extracted from the disclosure of the specification, drawings, etc.

[0146] a housing; a shaft accommodated in the housing and supported by the housing, the shaft having an eccentric portion eccentric with respect to a central axis of the main shaft; a rotor accommodated within the housing and rotatably supported on 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 rotor has a cylinder which, together with an outer peripheral surface of the eccentric portion, forms an operating chamber therein and rotates along the outer peripheral surface; vanes which move back and forth relative to the operating chamber as the cylinder rotates, thereby separating the operating chamber into a suction chamber into which refrigerant is sucked and a compression chamber which compresses the refrigerant; and a cover body arranged on the outer peripheral side of the main shaft, the cover body communicating with the compression chamber and defining a discharge chamber on the outer peripheral side of the main shaft from which lubricating oil is discharged together with the refrigerant compressed in the compression chamber.

[0147] (Supplementary Note 2) The rotary compressor according to Supplementary Note 1, wherein the rotating body has a sliding portion and an oil supply passage that supplies the lubricating oil in the discharge chamber to the sliding portion.

[0148] (Supplementary Note 3) The rotary compressor according to Supplementary Note 1 or 2, wherein the drive mechanism has a cylindrical motor, a cylindrical portion having an oil storage chamber formed therein is disposed on the inner peripheral side of the motor, the rotor and the shaft have an oil return passage that returns the lubricating oil in the discharge chamber to the oil storage chamber, and the cylindrical portion has a return flow path within the housing that returns the lubricating oil in the oil storage chamber to the outside of the cylindrical portion.

[0149] (Supplementary Note 4) The rotary compressor according to any one of Supplementary Notes 1 to 3, wherein the housing has a discharge communication port that communicates with the outside, and the shaft has an internal discharge passage that communicates between the discharge chamber and the discharge communication port.

[0150] (Supplementary Note 5) The eccentric portion has a first eccentric portion and a second eccentric portion; the working chamber has a first working chamber and a second working chamber; the cylinder has a first cylinder arranged on the outer circumferential side of the first eccentric portion and forming the first working chamber between it and the first eccentric portion, and a second cylinder arranged on the outer circumferential side of the second eccentric portion and forming the second working chamber between it and the second eccentric portion; the suction chamber has a first suction chamber and a second suction chamber; the compression chamber has a first compression chamber and a second compression chamber; the vanes have a first vane dividing the first working chamber into the first suction chamber and the first compression chamber, and a second vane dividing the second working chamber into a second suction chamber and a second compression chamber; the discharge chamber has a first discharge chamber and a second discharge chamber; the cover body includes a first cover body fixed to the first cylinder and having the first discharge chamber formed therein that communicates with the first compression chamber, and a second cover body fixed to the second cylinder and having the second discharge chamber formed therein that communicates with the second compression chamber; the housing has a discharge communication port that communicates with the outside; the rotating body has an internal rotor discharge passage that communicates between the first discharge chamber and the second discharge chamber; and the shaft has an internal shaft discharge passage that communicates between the first discharge chamber and the discharge communication port.

[0151] (Supplementary Note 6) The rotary compressor according to any one of Supplementary Notes 1 to 5, wherein the discharge chamber is formed to have a diameter larger than that of a support portion of the shaft that supports the rotor in rotation.

[0152] The present invention can be used in vehicle air conditioning systems and the like.

[0153] DESCRIPTION OF SYMBOLS 10 Housing 17 Discharge communication port 20, 201 Shaft 21, 211 Main shaft portion 21d Cylindrical 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 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 In-shaft discharge passage 77 Oil storage chamber 78 Return passage 79 Oil return passage 82 Discharge passage in rotating body 83 First oil supply passage (oil supply passage) 84 Second oil supply passage (oil supply passage) O1 Center axis line

Claims

1. A rotary compressor comprising: a housing; a shaft accommodated in said housing and supported by said housing, and having an eccentric portion eccentric with respect to the central axis of said main shaft; a rotor accommodated within said housing and rotatably supported on said shaft with said central axis as the axis of rotation; and a drive mechanism accommodated within said housing for rotationally driving said rotor, wherein said rotor has a cylinder which, together with the outer peripheral surface of said eccentric portion, forms an internal working chamber, and which rotates along said outer peripheral surface; vanes which move back and forth relative to said working chamber as said cylinder rotates, thereby separating said working chamber into a suction chamber into which refrigerant is sucked and a compression chamber into which the refrigerant is compressed; and a cover body arranged on the outer peripheral side of said main shaft, wherein said cover body communicates with said compression chamber and defines a discharge chamber on the outer peripheral side of said main shaft from which lubricating oil is discharged together with the refrigerant compressed in the compression chamber.

2. A rotary compressor according to claim 1, wherein the rotor has a sliding portion and an oil supply passage for supplying the lubricating oil in the discharge chamber to the sliding portion.

3. A rotary compressor as claimed in claim 1 or 2, wherein the drive mechanism has a cylindrical motor, a cylindrical section having an oil storage chamber formed therein is disposed on the inner peripheral side of the motor, the rotor and the shaft have an oil return passage for returning the lubricating oil in the discharge chamber to the oil storage chamber, and the cylindrical section has a return flow path within the housing for returning the lubricating oil in the oil storage chamber to the outside of the cylindrical section.

4. A rotary compressor according to claim 1 or 2, wherein the housing has a discharge communication port communicating with the outside, and the shaft has an internal discharge passage that connects the discharge chamber with the discharge communication port.

5. The eccentric portion has a first eccentric portion and a second eccentric portion, the working chamber has a first working chamber and a second working chamber, the cylinder has a first cylinder arranged on the outer circumferential side of the first eccentric portion and forming the first working chamber between it and the first eccentric portion, and a second cylinder arranged on the outer circumferential side of the second eccentric portion and forming the second working chamber between it and the second eccentric portion, the suction chamber has a first suction chamber and a second suction chamber, the compression chamber has a first compression chamber and a second compression chamber, the vanes have a first vane that divides the first working chamber into the first suction chamber and the first compression chamber and a second vane that divides the second working chamber into the second suction chamber and the second compression chamber, and the discharge chamber has a first discharge chamber and a second discharge chamber, 3. The rotary compressor according to claim 1, wherein the cover body includes a first cover body fixed to the first cylinder and having the first discharge chamber formed therein that communicates with the first compression chamber, and a second cover body fixed to the second cylinder and having the second discharge chamber formed therein that communicates with the second compression chamber; the housing has a discharge communication port that communicates with the outside; the rotating body has an internal rotor discharge passage that communicates between the first discharge chamber and the second discharge chamber; and the shaft has an internal shaft discharge passage that communicates between the first discharge chamber and the discharge communication port.

6. A rotary compressor according to claim 1 or 2, wherein the discharge chamber is formed to have a diameter larger than that of a support portion of the shaft that supports the rotation of the rotor.

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