Co-rotating scroll compressor

Abstract

In this compressor, a compression mechanism (9) has a drive scroll (30) and a driven scroll (40), and the drive scroll (30) and the driven scroll (40) form a compression chamber (12). In addition, a housing (6) has a case (39) provided therein. The case (39) has a discharge chamber (14) formed therein. The discharge chamber (14) has a separation mechanism (71) disposed therein. The separation mechanism (71) has a cylindrical member (77) and a spiral member (78). The spiral member (78) forms a separation passage (81) between the spiral member and the cylindrical member (77). By impinging on a compressed refrigerant circulating in the separation passage (81), the spiral member (78) separates lubricating oil (18) contained in the compressed refrigerant from the compressed refrigerant. The cylindrical member (77) has formed therein outflow passages (771-775) that are in communication with the separation passage (81) and the outside of the cylindrical member (77) and that allow the lubricating oil (18) to flow out to the outside of the cylindrical member (77).

Description

Double-rotating scroll compressor

[0001] The present invention relates to a double-rotating scroll compressor.

[0002] Patent Documents 1 and 2 disclose conventional double-rotating scroll compressors (hereinafter simply referred to as compressors). The compressor in Patent Document 1 includes a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism. The drive mechanism and drive scroll are accommodated in the housing. The housing also has a boss formed therein that protrudes toward the drive scroll. A support hole and a discharge communication port are formed inside the boss. The support hole is formed with a larger diameter than the discharge communication port and communicates with the discharge communication port. The discharge communication port communicates with the outside of the housing.

[0003] The drive scroll is provided with a drive shaft. The drive shaft is cylindrical and houses a boss therein. A bearing is provided between the drive shaft and the boss, more specifically, between the inner peripheral surface of the drive shaft and the outer peripheral surface of the boss. The outer peripheral surface of the drive shaft is fixed to the drive mechanism. Thus, the drive scroll is fixed to the drive mechanism within the housing and is supported by the boss via the bearing so as to be rotatable about the drive axis.

[0004] The driven scroll is accommodated in the housing. More specifically, the driven scroll is accommodated in the housing by being accommodated in the drive scroll. The driven scroll is accommodated in the drive scroll, thereby forming a compression chamber between the drive scroll and the driven scroll. The driven scroll also has a driven shaft that protrudes toward the boss. The driven shaft is inserted into the support hole. As a result, the driven scroll is supported by the boss so that it can rotate about the driven axis while being accommodated in the drive scroll. A discharge chamber is also formed inside the driven shaft. The discharge chamber communicates with the compression chamber and also with the discharge communication port. In other words, the compression chamber and the discharge communication port communicate with each other through the discharge chamber. The driven mechanism is disposed between the drive scroll and the driven scroll.

[0005] In this compressor, the drive scroll is rotationally driven about the drive axis by the drive mechanism, and the driven scroll is rotationally driven about the driven axis by the drive scroll and driven mechanism. As a result, the volume of the compression chamber changes depending on the rotationally driven drive scroll and the rotationally driven driven scroll. In this compressor, refrigerant is drawn into the compression chamber and compressed. The refrigerant compressed in the compression chamber is then discharged as compressed refrigerant into the discharge chamber and further discharged from the discharge chamber through a discharge connection port to the outside of the housing.

[0006] The compressor of Patent Document 2 includes a drive scroll that is driven to rotate about a drive shaft by a motor. The drive scroll is provided with a discharge port and a shaft having a hollow portion formed therein. One end of the hollow portion communicates with the compression chamber through the discharge port, and the other end communicates with the outside of the shaft. The compressor also includes a vortex inducing means disposed within the hollow portion. The vortex inducing means extends spirally around the drive shaft.

[0007] In this compressor, compressed refrigerant compressed in the compression chamber is discharged into the hollow portion from the discharge port. The compressed refrigerant then flows through the hollow portion and is discharged from the other end of the hollow portion to the shaft and ultimately to the outside of the drive scroll. Here, in this compressor, the compressed refrigerant in the hollow portion flows toward the other end of the hollow portion while flowing through the vortex inducing means. At this time, the vortex inducing means promotes the flow of the compressed refrigerant toward the other end of the hollow portion. This makes it easier for the compressed refrigerant to be discharged to the outside of the drive scroll.

[0008] JP-A-2-227575 Publication Special Publication No. 1987-502200

[0009] The refrigerant drawn into the compression chamber contains lubricating oil, which is discharged from the compression chamber together with the compressed refrigerant. Therefore, it is conceivable to use such lubricating oil to lubricate the driving scroll, the driven scroll, etc.

[0010] However, in the compressor of Patent Document 1, most of the lubricating oil discharged into the discharge chamber is discharged from the discharge chamber through the discharge port to the outside of the housing together with the compressed refrigerant, and therefore, in this compressor, the lubricating oil discharged into the discharge chamber cannot be used sufficiently to lubricate the driving scroll, the driven scroll, etc.

[0011] In the compressor of Patent Document 2, a vortex inducing device provided within the hollow portion promotes the flow of compressed refrigerant toward the other end of the hollow portion. As a result, in this compressor, lubricating oil is likely to be discharged to the outside of the drive scroll along with the compressed refrigerant, and therefore the lubricating oil cannot be fully used to lubricate the drive scroll, driven scroll, etc. Therefore, in such compressors, there is a concern that the durability of the drive scroll, driven scroll, etc. will be reduced due to insufficient lubrication.

[0012] The present invention has been made in view of the above-mentioned conventional circumstances, and an object to be achieved is to provide a double-rotation scroll compressor having excellent durability.

[0013] a double-rotating scroll compressor according to the present invention comprising a housing, a compression mechanism, a drive mechanism and a driven mechanism, the compression mechanism, the drive mechanism and the driven mechanism being accommodated within the housing, the compression mechanism having a drive scroll that is rotationally driven about a drive axis by the drive mechanism, and a driven scroll that is eccentric with respect to the drive scroll and is rotationally driven by the drive scroll and the driven mechanism about a driven axis, the drive scroll and the driven scroll forming compression chambers that compress a refrigerant by the rotational driving and the rotational driven, the housing having a discharge communication port through which compressed refrigerant that is refrigerant compressed in the compression chambers is discharged to the outside, a case rotatable together with the drive mechanism is provided within the housing, and a discharge chamber that communicates with the compression chamber and from which the compressed refrigerant is discharged is formed within the case, and a separation mechanism that can rotate integrally with the case is disposed within the discharge chamber, the compression mechanism having a discharge port that communicates with the compression chamber and discharges the compressed refrigerant from the compression chamber, The case is formed with a discharge passage for circulating the compressed refrigerant toward the discharge communication port, and the separation mechanism includes: a cylindrical member extending cylindrically in the direction of the drive shaft; and a helical member disposed inside the cylindrical member, extending helically around the drive shaft and forming a separation passage inside the cylindrical member that communicates with the discharge port and the discharge passage, the helical member separating lubricating oil contained in the compressed refrigerant from the compressed refrigerant by colliding with the compressed refrigerant flowing through the separation passage, and an outflow path formed in the cylindrical member that communicates with the separation passage and the outside of the cylindrical member and that allows the lubricating oil to flow out of the cylindrical member.

[0014] In the double rotary scroll compressor of the present invention, a separation mechanism is disposed within the discharge chamber. The separation mechanism includes a cylindrical member and a helical member. The cylindrical member extends cylindrically in the direction of the drive shaft. The helical member forms a separation passage within the cylindrical member. The separation passage extends helically around the drive shaft and communicates with the discharge port and the discharge passage. As a result, in this compressor, compressed refrigerant discharged from the compression chamber through the discharge port flows through the separation passage toward the discharge passage.

[0015] In this compressor, as the compression mechanism rotates, centrifugal force of the rotating compression mechanism acts on the compressed refrigerant. Furthermore, in this compressor, the compressed refrigerant flowing through the separation passage collides with the helical member while flowing through the separation passage toward the discharge passage. Thus, in this compressor, not only can the lubricating oil be separated from the compressed refrigerant by the action of centrifugal force, but also by the collision with the helical member.

[0016] The lubricating oil separated from the compressed refrigerant flows through the separation passage to the outside of the tubular member, i.e., to the discharge chamber, via an outflow path formed in the tubular member. As a result, in this compressor, the compressed refrigerant from which the lubricating oil has been separated is discharged to the outside through the discharge communication port via the separation passage and the discharge passage, while the lubricating oil separated from the compressed refrigerant is prevented from being discharged to the outside through the discharge communication port. As a result, in this compressor, the lubricating oil separated from the compressed refrigerant can be easily used to lubricate the drive scroll, driven scroll, etc.

[0017] Therefore, the double-rotating scroll compressor of the present invention has excellent durability.

[0018] The outflow passage is preferably formed in a spiral shape along the outer periphery of the helical member, so that the lubricating oil separated from the compressed refrigerant can be suitably discharged to the outside of the cylindrical member.

[0019] The discharge chamber is preferably connected to a return passage for returning the lubricating oil to a location in the housing where the pressure is lower than that of the discharge chamber. In this case, the lubricating oil separated from the compressed refrigerant can be suitably used to lubricate the driving scroll, the driven scroll, etc.

[0020] The cylindrical member is preferably formed with a larger diameter than the discharge passage. In this case, the compressed refrigerant discharged from the discharge port can be prevented from reaching the discharge passage without flowing through the separation passage. In addition, the separation passage can be preferably formed inside the cylindrical member.

[0021] It is preferable that a vent passage be provided in the case to allow the compressed refrigerant that has flowed out of the cylindrical member from the outflow passage to flow to the discharge passage downstream of the spiral member in the flow direction of the compressed refrigerant. In this case, the flow of compressed refrigerant between the outside of the cylindrical member and the discharge passage is ensured, so that the lubricating oil separated from the compressed refrigerant can be suitably discharged from the separation passage to the outside of the cylindrical member by the outflow passage.

[0022] The case may be formed with a supported member that protrudes toward the housing. The supported member may be rotatably supported on the housing via a bearing. Preferably, a discharge passage extends through the supported member.

[0023] In this case, the compression mechanism can be efficiently rotated within the housing. Also, the discharge passage can be efficiently formed by extending the discharge passage into the supported member. This allows the compressed refrigerant from which the lubricating oil has been separated to be efficiently discharged from the discharge chamber through the discharge passage and the discharge communication port to the outside of the housing.

[0024] The discharge chamber is preferably formed to have a larger diameter than the bearing, in which case the volume of the discharge chamber can be suitably secured, thereby increasing the degree of freedom in designing the separation mechanism.

[0025] The helical member may have a central shaft portion extending linearly in the drive shaft direction, and blade portions integral with the central shaft portion and extending helically around the drive shaft center. When viewed from the discharge port side, the direction in which the blade portions spiral preferably coincides with the direction in which the drive scroll is driven to rotate.

[0026] In this case, since the vanes tend to obstruct the flow of compressed refrigerant through the separation passage, the compressed refrigerant can be made to collide effectively with the spiral member including the vanes, which makes it easier to separate the lubricating oil from the compressed refrigerant.

[0027] The spiral member may have a central shaft portion extending linearly in the drive shaft direction, and blade portions integral with the central shaft portion and extending spirally around the drive shaft center. Preferably, the blade portions are inclined in the downstream direction of the separation passage as they approach the radially outer side from the central shaft portion.

[0028] In this case, the shape of the blades makes it easier for the lubricating oil separated from the compressed refrigerant to be pushed radially outward within the separation passage, allowing the compressor to efficiently discharge the lubricating oil from the outflow passage to the outside of the tubular member.

[0029] The double-rotating scroll compressor of the present invention is excellent in durability.

[0030] Fig. 1 is a cross-sectional view of a compressor according to an embodiment. Fig. 2 is an enlarged cross-sectional view of a main part of the compressor, showing a case, a separation mechanism, etc. Fig. 3 is a side view of a cylindrical member according to the compressor, Fig. 4 is a side view of a helical member according to the compressor, Fig. 5 is a cross-sectional view of the compressor according to the embodiment, showing the assembly of the cylindrical member and the helical member.

[0031] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A double rotary scroll compressor according to an embodiment of the present invention is mounted in a vehicle (not shown) and forms an air conditioning system for the vehicle.

[0032] 1, the compressor of the embodiment includes a housing 6, an electric motor 10, a compression mechanism 9, a driven mechanism 20, a case 39, and a separation mechanism 71. The electric motor 10 is an example of the "drive mechanism" of the present invention.

[0033] In this embodiment, the front-rear direction and the up-down direction of the compressor are defined by solid arrows shown in Fig. 1. The front-rear direction and the up-down direction are perpendicular to each other. In Fig. 2 and subsequent figures, the front-rear direction and the up-down direction of the compressor are defined in accordance with Fig. 1. Note that these front-rear directions are examples for the convenience of explanation, and the compressor's position can be changed as appropriate depending on the vehicle in which it is installed.

[0034] As shown in FIG. 1 , the housing 6 is composed of a housing main body 60 , a first housing cover 61 , and a second housing cover 62 .

[0035] The housing body 60 is made of an aluminum alloy and has a cylindrical shape with a drive axis O1 at its center, and is open at both the front and rear ends. The drive axis O1 is parallel to the front-to-rear direction.

[0036] An intake communication port 68 is also formed in the housing body 60. The intake communication port 68 extends in the radial direction of the housing body 60. The intake communication port 68 is connected to an evaporator (not shown) through a pipe (not shown).

[0037] The first housing cover 61 is made of steel and is located at the rear end of the housing main body 60. The first housing cover 61 is generally disk-shaped and centered on the drive shaft center O1. The first housing cover 61 has a front surface 61a facing forward and a rear surface 61b facing rearward and located on the opposite side of the front surface 61a.

[0038] A protrusion 64 is also provided inside the housing 6. More specifically, the protrusion 64 is integrally formed with the first housing cover 61. As a result, the protrusion 64 is also made of steel. The protrusion 64 has a cylindrical shape and protrudes forward from the center of the front surface 61a in the direction of the drive axis O1. The protrusion 64 has a first diameter portion 64a and a second diameter portion 64b.

[0039] The first diameter portion 64a constitutes the front portion of the protrusion 64. The first diameter portion 64a is formed to have a smaller diameter than an insertion hole 375, which will be described later. A pin hole 4 is formed in the first diameter portion 64a. The pin hole 4 extends inside the first diameter portion 64a in the direction of the drive axis O1 and opens at the front end surface of the first diameter portion 64a.

[0040] Further, the outer peripheral surface of the first diameter portion 64a is provided with a first radial ball bearing 51. Note that instead of the first radial ball bearing 51, a sliding bearing may be provided on the outer peripheral surface of the first diameter portion 64a.

[0041] The second diameter portion 64b is integral with the first diameter portion 64a and is located rearward of the first diameter portion 64a. As a result, the second diameter portion 64b constitutes the rear portion of the protrusion 64. The rear end of the second diameter portion 64b is connected to the front surface 61a of the first housing cover 61. The second diameter portion 64b is formed to have a larger diameter than the first diameter portion 64a.

[0042] The second housing cover 62 is disposed in front of the housing main body 60. The second housing cover 62 is made of an aluminum alloy. The second housing cover 62 is generally disk-shaped and centered on the drive shaft center O1. The second housing cover 62 has a front surface 62a facing forward and a rear surface 62b facing rearward and located opposite the front surface 62a.

[0043] The second housing cover 62 also has a support portion 66 and a discharge port 69. The support portion 66 is integrally formed approximately at the center of the rear surface 62b and protrudes rearward from the rear surface 62b. The support portion 66 is cylindrical and centered on the drive axis O1, and is provided therein with the second radial ball bearing 52 and a shaft seal member 63. The second radial ball bearing 52 is an example of the "bearing" in the present invention. Note that a sliding bearing may be provided inside the support portion 66 instead of the second radial ball bearing 52.

[0044] The shaft seal member 63 is disposed in front of the second radial ball bearing 52 within the support portion 66. The shaft seal member 63 is formed in an annular shape.

[0045] The discharge communication port 69 penetrates the second housing cover 62 in the direction of the drive axis O1 and communicates with the interior of the support portion 66. The discharge communication port 69 is also connected to a condenser (not shown) through piping (not shown).

[0046] In the housing 6, a front surface 61a of the first housing cover 61 abuts against the rear end of the housing main body 60, and a rear surface 62b of the second housing cover 62 abuts against the front end of the housing main body 60. Then, a plurality of bolts (not shown) secure the housing main body 60, the first housing cover 61, and the second housing cover 62 in the direction of the drive axis O1.

[0047] Thus, in the housing 6, the housing main body 60 is sandwiched in the front-to-rear direction between the first housing cover 61 and the second housing cover 62, and the front and rear ends of the housing main body 60 are closed by the first housing cover 61 and the second housing cover 62, respectively. As a result, a scroll chamber 65 is formed within the housing main body 60 in the housing 6. The scroll chamber 65 communicates with the suction communication port 68. Therefore, refrigerant is drawn into the scroll chamber 65 from outside the housing 6 through the suction communication port 68.

[0048] The protrusion 64 protrudes from the first housing cover 61 into the scroll chamber 65 in the direction of the drive axis O1. More specifically, the protrusion 64 protrudes forward from the first housing cover 61 toward the driving scroll 30 and the driven scroll 40.

[0049] The electric motor 10 is housed in the scroll chamber 65. As a result, the scroll chamber 65 also serves as a motor chamber that houses the electric motor 10.

[0050] The electric motor 10 is composed of a stator 17 and a rotor 11. The stator 17 has a stator core 17a and a winding 17b. The stator core 17a is formed in a cylindrical shape centered on the drive shaft center O1. The winding 17b is wound around the stator core 17a. As a result, the winding 17b forms a first coil end 171 and a second coil end 172.

[0051] The first coil end 171 protrudes forward from the stator core 17a in the direction of the drive axis O1 in a cylindrical shape. The second coil end 172 is located on the opposite side of the stator core 17a from the first coil end 171. The second coil end 172 protrudes rearward from the stator core 17a in the direction of the drive axis O1 in a cylindrical shape.

[0052] In the stator 17, the stator core 17a is fitted onto the outer peripheral surface of the second diameter portion 64b. In this way, the stator core 17a is fixed to the second diameter portion 64b and, ultimately, to the protrusion 64. Although not shown, the inner peripheral surface of the stator core 17a has a plurality of slits extending in the direction of the drive axis O1. As a result, when the stator core 17a is fixed to the second diameter portion 64b, the slits form a gap between the stator core 17a and the outer peripheral surface of the second diameter portion 64b.

[0053] The rotor 11 is cylindrical around the drive axis O1. Although not shown in detail, the rotor 11 is composed of a plurality of permanent magnets corresponding to the stator 17 and laminated steel plates that secure the permanent magnets. The rotor 11 has a larger diameter than the stator core 17a. As a result, the rotor 11 covers the stator core 17a from the outside within the scroll chamber 65. The rotor 11 also has a plurality of first bolt holes 11a. Each of the first bolt holes 11a penetrates the rotor 11 in the direction of the drive axis O1.

[0054] The compression mechanism 9 includes a driving scroll 30 and a driven scroll 40. The driving scroll 30 is housed in a scroll chamber 65. The driving scroll 30 is made of an aluminum alloy. The driving scroll 30 includes a driving end plate 31, a driving scroll 33, a driving peripheral wall 35, and a cover body 37.

[0055] The drive end plate 31 extends in a generally disk-like shape, perpendicular to the drive axis O1 and the driven axis O2. The driven axis O2 extends parallel to the drive axis O1 while being eccentric with respect to the drive axis O1. In other words, the driven axis O2 is also parallel to the front-to-rear direction. The drive end plate 31 has a first front surface 311 facing forward and a first rear surface 312 located opposite the first front surface 311 and facing rearward.

[0056] 2, the drive end plate 31 is formed with a first holding portion 73, an end plate recess 75, and a discharge port 32. The first holding portion 73 is recessed rearward from the first front surface 311. The first holding portion 73 is formed in a cylindrical shape centered on the drive axis O1.

[0057] The end plate recess 75 is connected to the first retaining portion 73 and recessed rearward from the first retaining portion 73. As shown in FIG. 1 , the end plate recess 75 is also formed in a cylindrical shape centered on the drive axis O1. The end plate recess 75 has a smaller diameter than the first retaining portion 73.

[0058] The discharge port 32 penetrates the drive end plate 31 in the direction of the drive axis O1 from the first front surface 311 to the first rear surface 312. As a result, the discharge port 32 opens into the end plate recess 75 on the first front surface 311 side.

[0059] Furthermore, the discharge reed valve 57 and the retainer 58 are fixed in the end plate recess 75 by fixing bolts 59. This allows the discharge reed valve 57 to open and close the discharge port 32 by elastically deforming. The retainer 58 is also capable of adjusting the opening degree of the discharge reed valve 57.

[0060] The drive scroll 33 is integral with the drive end plate 31 and protrudes rearward from the first rear surface 312, i.e., parallel to the drive axis O1 and the driven axis O2, toward the driven scroll 40. Although not shown in detail, the drive scroll 33 has a spiral center located on the central side of the drive end plate 31 and protrudes outward from the spiral center in a spiral shape.

[0061] The drive circumferential wall 35 is formed in a cylindrical shape centered on the drive axis O1 and extending parallel to the drive axis O1 and the driven axis O2. The drive circumferential wall 35 surrounds the drive scroll 33 from the outside and protrudes cylindrically rearward from the first rear surface 312. Although not shown, the outer circumferential ends of the spirals of the drive scroll 33 are connected to the inner circumferential surface of the drive circumferential wall 35.

[0062] The driving peripheral wall 35 is also formed with a first return path 35a extending to the driving end plate 31. The first return path 35a is an example of the "return path" defined in the present invention. The first return path 35a penetrates the driving end plate 31 and the driving peripheral wall 35 in the direction of the driving axis O1. As a result, the front end of the first return path 35a opens to the first front surface 311 at a location radially outward of the driving end plate 31 relative to the first retaining portion 73 and the end plate recess 75, and the rear end opens to the rear end surface of the driving peripheral wall 35.

[0063] The cover body 37 has a wall portion 37a, an inner cylindrical portion 37b, a connecting portion 37c, an outer cylindrical portion 37d, and a second return path 37f. The second return path 37f is also an example of the "return path" according to the present invention.

[0064] The wall portion 37a has a generally plate-like shape and extends in the radial direction of the cover body 37, i.e., in the radial direction of the driving scroll 30. The wall portion 37a has a second front surface 371 that faces forward and a second rear surface 372 that is located on the opposite side of the second front surface 371 and faces rearward.

[0065] The wall portion 37a is formed with a recess 373 and an intake port 374. The recess 373 is located approximately in the center of the second front surface 371, and is recessed from the second front surface 371 toward the rear.

[0066] The suction port 374 is disposed at a location radially outward of the cover body 37 relative to the recess 373. The suction port 374 penetrates the wall portion 37a in the front-rear direction, with its front end opening to the second front surface 371 and its rear end opening to the second rear surface 372. Note that a plurality of suction ports 374 may be formed in the wall portion 37a.

[0067] Additionally, a plurality of rings 22 are attached to the wall portion 37a between the recess 373 and the intake port 374. Although not shown in detail, the rings 22 are disposed at equal intervals around the circumferential direction of the recess 373 while facing forward, and surround the recess 373 from the outside. In this embodiment, the number of rings 22 is six. FIG. 1 illustrates one of the six rings 22.

[0068] The inner cylindrical portion 37b is formed at a position radially inward of the stator 17 on the cover body 37, and extends cylindrically rearward in the direction of the drive axis O1. The inner cylindrical portion 37b has a diameter larger than the first diameter portion 64a of the protrusion 64 and smaller than the second diameter portion 64b. The inner diameter of the inner cylindrical portion 37b is formed to be approximately the same as the outer diameter of the first radial ball bearing 51. The outer diameter of the inner cylindrical portion 37b may be approximately the same as the outer diameter of the second diameter portion 64b, or may be larger than the outer diameter of the second diameter portion 64b.

[0069] The connecting portion 37c is located between the wall portion 37a and the inner cylindrical portion 37b and is integral with the wall portion 37a and the inner cylindrical portion 37b. The connecting portion 37c connects the wall portion 37a and the inner cylindrical portion 37b while increasing in diameter from the inner cylindrical portion 37b toward the wall portion 37a in the direction of the drive axis O1. This allows the outer peripheral surface of the inner cylindrical portion 37b to be continuous with the second rear surface 372 of the wall portion 37a through the connecting portion 37c.

[0070] An insertion hole 375 is formed in the cover body 37 at a location inside the connecting portion 37c. The insertion hole 375 extends in the direction of the drive axis O1 and connects the inner cylindrical portion 37b and the recess 373.

[0071] The outer cylindrical portion 37d is integral with the wall portion 37a. As a result, the outer cylindrical portion 37d is connected to the wall portion 37a and extends cylindrically rearward from the wall portion 37a in the direction of the drive axis O1. The outer diameter of the outer cylindrical portion 37d is approximately the same as the outer diameter of the drive circumferential wall 35 and the outer diameter of the rotor 11.

[0072] The inner diameter of the outer cylindrical portion 37d is larger than those of the inner cylindrical portion 37b and the connecting portion 37c. As a result, in the cover body 37, the inner cylindrical portion 37b and the connecting portion 37c are disposed on the inner peripheral side of the outer cylindrical portion 37d while being spaced apart from the outer cylindrical portion 37d in the radial direction of the cover body 37. In this way, in the cover body 37, the wall portion 37a, the inner cylindrical portion 37b, the connecting portion 37c, and the outer cylindrical portion 37d form a storage portion 38. The storage portion 38 has an annular shape with a bottom and an open rearward end.

[0073] The suction port 374 formed in the wall portion 37a is located outside the inner cylindrical portion 37b and the connecting portion 37c and inside the outer cylindrical portion 37d in the radial direction of the cover body 37. As a result, the suction port 374 is in communication with the storage portion 38.

[0074] Additionally, a plurality of second bolt holes 376 extending to the wall portion 37a are formed in the outer cylindrical portion 37d. Each second bolt hole 376 penetrates the wall portion 37a and the outer cylindrical portion 37d in the direction of the drive axis O1. Although not shown, the number of second bolt holes 376 is equal to the number of first bolt holes 11a formed in the rotor 11. FIG. 1 illustrates only one of the plurality of first bolt holes 11a and one of the plurality of second bolt holes 376.

[0075] One end of the second return passage 37f opens to the second front surface 371 of the wall portion 37a. The second return passage 37f extends radially within the wall portion 37a of the cover body 37, and the other end communicates with the recess 373.

[0076] In the cover body 37, the second front surface 371 of the wall portion 37a abuts against the rear end surface of the drive peripheral wall 35. In addition, in the cover body 37, the rotor 11 abuts against the rear end of the outer cylindrical portion 37d. In this state, the first bolts 34a are inserted into the first bolt holes 11a and the second bolt holes 376 from the rotor 11 side and screwed into the drive peripheral wall 35. In this way, the cover body 37 is fixed to the drive peripheral wall 35 and the rotor 11 while being sandwiched between them. As a result, the drive scroll 30 is integral with the rotor 11.

[0077] Furthermore, by fixing the cover body 37 to the driving peripheral wall 35 and the rotor 11 in this manner, the first return path 35a and the second return path 37f are communicated with each other.

[0078] The driven scroll 40 is also made of an aluminum alloy. The driven scroll 40 has a driven end plate 41 and a driven scroll 43.

[0079] The driven end plate 41 has a generally disk-like shape and extends perpendicular to the drive axis O1 and the driven axis O2. The driven end plate 41 has a third front surface 411 facing forward and a third rear surface 412 located on the opposite side of the third front surface 411 and facing rearward.

[0080] An accommodating recess 15 is formed in the driven end plate 41. The accommodating recess 15 is located in the center of the driven end plate 41. The accommodating recess 15 is recessed in a cylindrical shape centered on the driven axis O2 and extends forward from the third rear surface 412 of the driven end plate 41. As a result, the accommodating recess 15 faces the rear of the driven end plate 41, and ultimately faces the first diameter portion 64a of the protrusion 64.

[0081] A driven shaft portion 16 is provided in the accommodation recess 15. The driven shaft portion 16 has a bushing 53 and a driven pin 55. The bushing 53 is accommodated in the accommodation recess 15 via the sliding bearing 13. The driven pin 55 is inserted into the bushing 53. More specifically, the driven pin 55 is inserted into the bushing 53 at a position eccentric to the center of the bushing 53, i.e., the driven axis O2. The driven pin 55 protrudes rearward from the bushing 53 and, therefore, from the driven end plate 41.

[0082] Furthermore, a rotation prevention pin 21 is fixed to the driven end plate 41 at a position facing the ring 22. The rotation prevention pin 21 protrudes rearward from the third rear surface 412. Six rotation prevention pins 21 are fixed to the driven end plate 41, the same number as the number of rings 22. Only one of the six rotation prevention pins 21 is shown in FIG. 1.

[0083] These rotation-preventing pins 21 and rings 22 constitute the driven mechanism 20. The number of rotation-preventing pins 21 and rings 22 can be appropriately designed as long as there are three or more of each.

[0084] The driven spiral body 43 is integral with the driven end plate 41 and extends forward from the third front surface 411 of the driven end plate 41 in parallel with the drive axis O1 and the driven axis O2. The driven spiral body 43 has a spiral center on the center side of the driven end plate 41 and extends spirally outward from the spiral center.

[0085] In this compressor, the driven scroll 40 is housed within the driving scroll 30, more specifically, in a location in the driving scroll 30 between the driving scroll 33 and the driving peripheral wall 35 and the cover body 37. The driving scroll 30 and the driven scroll 40 are arranged such that the driving scroll 33 and the driven scroll 43 are meshed with each other. As a result, the driving scroll 33 and the driven scroll 43 face each other to form a compression chamber 12.

[0086] Furthermore, an intake section 30a is formed between the driving peripheral wall 35 and the driven scroll 40. That is, the driving scroll 33 and the driven scroll 43 are located within the intake section 30a. The intake section 30a is separated from the scroll chamber 65 by the driving peripheral wall 35 and the cover body 37, and is also separated from the discharge chamber 14 (described later) by the driving end plate 31. The intake section 30a also communicates with an intake port 374. As a result, the intake section 30a communicates with the accommodation section 38 through the intake port 374.

[0087] Furthermore, by accommodating the driven scroll 40 within the driving scroll 30, each of the rotation-preventing pins 21 enters each of the rings 22. In this manner, the driving scroll 30 and the driven scroll 40 are assembled in the front-to-rear direction, and the driving scroll 30 and the driven scroll 40 form a scroll compression section 100. Strictly speaking, after the driving scroll 33 and the driven scroll 43 are engaged with each other and the rotation-preventing pins 21 enter each of the rings 22, the cover body 37 of the driving scroll 30 is fixed to the driving peripheral wall 35 and the rotor 11.

[0088] Furthermore, by assembling the driving scroll 30 and the driven scroll 40 together, the accommodating recess 15 of the driven end plate 41 and the driven shaft portion 16 face the recess 373 of the cover body 37 .

[0089] The case 39 is made of an aluminum alloy. The case 39 is a cylindrical member with a bottom and includes an outer peripheral wall 39a and a front wall 39b. The outer peripheral wall 39a is cylindrical and has its center on the drive axis O1. The outer diameter of the outer peripheral wall 39a is approximately the same as the outer diameter of the drive end plate 31. The case 39 may also be made of resin or the like.

[0090] The front wall 39b is located at the front end of the case 39. The front wall 39b extends in a generally disk-like shape in the radial direction of the case 39, perpendicular to the drive axis O1 and the driven axis O2. The front wall 39b has a fourth front surface 391 that faces forward, and a fourth rear surface 392 that faces rearward and is located on the opposite side of the fourth front surface 391. The front wall 39b is connected to the front end of the outer circumferential wall 39a.

[0091] 2, a second retaining portion 39c and a boss 39d are formed on the front wall 39b. The boss 39d is an example of a "supported object" in the present invention. The second retaining portion 39c is recessed forward from the fourth rear surface 392. The second retaining portion 39c is formed in a cylindrical shape centered on the drive axis O1.

[0092] The boss 39d is integrally formed at the center of the front wall 39b and protrudes forward from the fourth front surface 391 in the direction of the drive axis O1. The outer diameter of the boss 39d is substantially the same as the inner diameter of the second radial ball bearing 52 and the inner diameter of the shaft seal member 63. A discharge passage 390 is formed in the boss 39d. The discharge passage 390 penetrates the boss 39d in the direction of the drive axis O1. As a result, the rear end of the discharge passage 390 opens into the second retaining portion 39c.

[0093] Third bolt holes 39e are formed in the outer peripheral wall 39a and the front wall 39b. The third bolt holes 39e penetrate the outer peripheral wall 39a and the front wall 39b in the direction of the drive axis O1. Although not shown, a plurality of third bolt holes 39e are formed in the outer peripheral wall 39a and the front wall 39b. One of the plurality of third bolt holes 39e is shown in FIG. 1.

[0094] 2 to 5, the separation mechanism 71 is made up of a cylindrical member 77 and a spiral member 78. The cylindrical member 77 and the spiral member 78 are both made of resin. However, the cylindrical member 77 and the spiral member 78 may also be made of metal.

[0095] 3 and 5, the tubular member 77 is formed in a cylindrical shape centered on the drive axis O1. The tubular member 77 has a main body tubular portion 77a and a flange portion 77b. The main body tubular portion 77a extends in the direction of the drive axis O1. The flange portion 77b is integral with the main body tubular portion 77a and is located at the rear end of the main body tubular portion 77a. The flange portion 77b protrudes radially from the tubular member 77, i.e., in the radial direction of the driving scroll 30, beyond the main body tubular portion 77a.

[0096] 3, the main body cylindrical portion 77a is formed with first to fifth outlet passages 771 to 775, first and second ventilation passages 776 and 777, and an engagement groove 778. The first to fifth outlet passages 771 to 775 are an example of the "outlet passage" in the present invention. The first and second ventilation passages 776 and 777 are an example of the "ventilation passage" in the present invention. The numbers of the first to fifth outlet passages 771 to 775 and the first and second ventilation passages 776 and 777 can be designed as appropriate.

[0097] The first to fifth outlet passages 771 to 775 are each formed on the outer peripheral surface of the main body cylindrical portion 77a and penetrate the main body cylindrical portion 77a in the radial direction of the cylindrical member 77. The first to fifth outlet passages 771 to 775 each extend spirally around the drive axis O1 on the outer peripheral surface of the main body cylindrical portion 77a. Here, the shapes of the first to fifth outlet passages 771 to 775 are formed to follow the outer peripheral edges of the blade portions 78b, which will be described later.

[0098] The first outlet passage 771 is located at the rear end of the main body tubular portion 77a and extends spirally around the drive axis O1 while facing forward along the outer circumferential surface of the main body tubular portion 77a. The second outlet passage 772 is disposed at a regular interval from the first outlet passage 771 in the circumferential direction of the main body tubular portion 77a. The second outlet passage 772 extends spirally around the drive axis O1 while facing forward along the outer circumferential surface of the main body tubular portion 77a, following the shape of the first outlet passage 771. The third outlet passage 773 is disposed at a regular interval from the second outlet passage 772 in the circumferential direction of the main body tubular portion 77a. The third outlet passage 773 extends spirally around the drive axis O1 while facing forward along the outer circumferential surface of the main body tubular portion 77a, following the shape of the second outlet passage 772. The fourth outlet passage 774 is disposed at a regular interval from the third outlet passage 773 in the circumferential direction of the main body tubular portion 77a. The fourth outlet passage 774 extends spirally around the drive axis O1 while facing forward on the outer circumferential surface of the main body cylindrical portion 77a, following the shape of the third outlet passage 773. The fifth outlet passage 775 is disposed at a fixed interval in the circumferential direction of the main body cylindrical portion 77a from the fourth outlet passage 774. The fifth outlet passage 775 extends spirally around the drive axis O1 while facing forward on the outer circumferential surface of the main body cylindrical portion 77a, following the shape of the fourth outlet passage 774. The fifth outlet passage 775 is located at the front end of the main body cylindrical portion 77a.

[0099] The first and second ventilation passages 776, 777 are formed in the tubular main body portion 77a by cutting out the tubular main body portion 77a from the front end so that the passages extend rearward in a rectangular shape. The first ventilation passage 776 and the second ventilation passage 777 are disposed approximately 180° apart in the circumferential direction of the tubular main body portion 77a.

[0100] The engagement groove 778 is disposed at the front end of the main body tubular portion 77a, between the first air passage 776 and the second air passage 777. As shown in Fig. 5, the engagement groove 778 is formed in the main body tubular portion 77a by cutting out the main body tubular portion 77a from the front end so as to extend rearward in a rectangular shape. The engagement groove 778 extends further in the circumferential direction of the main body tubular portion 77a than the first air passage 776 and the second air passage 777.

[0101] 4 and 5, the helical member 78 has a central shaft portion 78a, blade portions 78b, and locking portions 78c. The central shaft portion 78a is formed in a cylindrical shape and extends linearly in the direction of the drive axis O1. The blade portions 78b are integral with the central shaft portion 78a and extend in a plate-like shape from the central shaft portion 78a toward the outside in the radial direction of the tubular member 77. The outer diameter of the blade portions 78b is approximately the same as the inner diameter of the main tubular portion 77a.

[0102] Furthermore, the blade portion 78b extends spirally around the drive axis O1 from its rear end to its front end in the direction of the drive axis O1, i.e., from the discharge port 32 side toward the discharge passage 390 side shown in FIG. 1 . More specifically, as shown by the solid arrow in FIG. 4 , in this compressor, the driving scroll 30 rotates in a rotational direction R1 during operation. When the rear end of the blade portion 78b is defined as the starting point of the spiral and the front end is defined as the end point of the spiral, the blade portion 78b extends spirally around the drive axis O1 from its rear end to its front end in the rotational direction R1. As a result, in this compressor, when the blade portion 78b is viewed from the rear, i.e., when the blade portion 78b is viewed from the discharge port 32 side, the spiral direction of the blade portion 78b coincides with the direction in which the driving scroll 30 rotates.

[0103] Furthermore, the blade portions 78b are inclined forward at a predetermined angle as they extend from the central shaft portion 78a outward in the radial direction of the cylindrical member 77. The angle at which the blade portions 78b are inclined can be designed as appropriate.

[0104] The locking portions 78c are formed integrally with the blade portions 78b and are located at the front ends of the blade portions 78b. The locking portions 78c extend in an arc along the inner circumferential surface of the main cylindrical portion 77a. Although not shown in detail, the locking portions 78c protrude radially outward from the cylindrical member 77a beyond the blade portions 78b.

[0105] As shown by the white arrow in Figure 5, in the separation mechanism 71, the helical member 78 is inserted into the main tubular portion 77a of the tubular member 77 from the front. The locking portions 78c of the helical member 78 engage with the engagement grooves 778 of the main tubular portion 77a, thereby assembling the helical member 78 with the tubular member 77 disposed inside the tubular member 77. As a result, the blade portions 78b of the helical member 78 are inclined forward of the tubular member 77 as they move from the central shaft portion 78a toward the outer edge, i.e., as they move radially outward from the central shaft portion 78a. Furthermore, the engagement of the locking portions 78c with the engagement grooves 778 prevents the helical member 78 from rotating relative to the tubular member 77 in the separation mechanism 71.

[0106] 1 and 2, by disposing the spiral member 78 inside the cylindrical member 77, a separation passage 81 is formed inside the cylindrical member 77. Due to the shape of the blade portions 78b of the spiral member 78, this separation passage 81 has a shape that extends spirally around the drive axis O1 from the rear end to the front end in the direction of the drive axis O1.

[0107] 2, in this compressor, the flange portion 77b of the cylindrical member 77 is inserted into the first holding portion 73 of the drive end plate 31. This positions the separation mechanism 71 relative to the drive end plate 31 and temporarily secures the separation mechanism 71 to the drive end plate 31.

[0108] The rear surface of the outer peripheral wall 39a of the case 39 is in contact with the first front surface 311 of the driving end plate 31. In this state, the second bolts 34b are inserted into the third bolt holes 39e, respectively, and are screwed into the driving end plate 31. In this manner, the case 39 of the driving scroll 30 is fixed to the driving end plate 31.

[0109] In this way, by fixing the case 39 to the drive end plate 31, a discharge chamber 14 is formed inside the outer peripheral wall 39a, between the front wall 39b of the case 39 and the drive end plate 31. In addition, by fixing the case 39 to the drive end plate 31, the front end of the cylindrical member 77 enters the second holding portion 39c of the front wall 39b.

[0110] Thus, in this compressor, the case 39 is fixed to the driving scroll 30, and the separation mechanism 71 is disposed in the discharge chamber 14. More specifically, the separation mechanism 71 is disposed in the discharge chamber 14 with the tubular member 77 abutting against the driving end plate 31 and the case 39, respectively, and held by the driving end plate 31 and the case 39. As a result, in the separation mechanism 71, the separation passage 81 communicates at its rear end with the end plate recess 75 of the driving end plate 31 and the discharge port 32, and at its front end with the discharge passage 390 of the case 39. In other words, in the driving scroll 30, the discharge port 32 and the discharge passage 390 communicate with each other through the separation passage 81 and the end plate recess 75. The separation passage 81 and the discharge chamber 14 are separated by the tubular member 77.

[0111] Furthermore, by disposing the separation mechanism 71 in the discharge chamber 14 in this manner, the first and second ventilation passages 776 , 777 formed in the cylindrical member 77 are located within the discharge chamber 14 , and therefore within the case 39 .

[0112] Furthermore, the separation passage 81 communicates with the outside of the cylindrical member 77, i.e., with the discharge chamber 14 located outside the cylindrical member 77, via the first to fifth outlet passages 771 to 775. Furthermore, the separation passage 81 also communicates with the outside of the cylindrical member 77 via the first and second ventilation passages 776, 777. In this case, the first and second ventilation passages 776, 777 communicate the separation passage 81 with the outside of the cylindrical member 77 at a location forward of the blade portions 78b of the spiral member 78.

[0113] In this compressor, the discharge chamber 14 has a larger diameter than the second radial ball bearing 52. The cylindrical member 77 has a larger diameter than the end plate recess 75, the boss 39d, and the discharge passage 390. The discharge chamber 14 is also in communication with the first return passage 35a. This allows the discharge chamber 14 to communicate with the recess 373 of the cover body 37 through the first return passage 35a and the second return passage 37f.

[0114] As shown in FIG. 1 , in this compressor, the driving scroll 30 is disposed in front of the stator 17 in the scroll chamber 65. Furthermore, in the driving scroll 30, the inner cylindrical portion 37b of the cover body 37 is inserted into the inner circumferential side of the first coil end 171. In this state, the first radial ball bearing 51 is inserted into the inner cylindrical portion 37b. As a result, the cover body 37 is rotatably supported by the first diameter portion 64a via the first radial ball bearing 51. The accommodating portion 38 communicates with the scroll chamber 65. Furthermore, the front portion of the first diameter portion 64a is inserted into the insertion hole 375.

[0115] The inner cylindrical portion 37b faces the second diameter portion 64b in the direction of the drive axis O1. Here, the outer diameter of the inner cylindrical portion 37b is smaller than the outer diameter of the second diameter portion 64b, so that when the cover body 37 is supported by the first diameter portion 64a, the inner cylindrical portion 37b and the first coil end 171 are spaced apart in the radial direction of the cover body 37.

[0116] Furthermore, with the cover body 37 supported by the first diameter portion 64a in this manner, the wall portion 37a of the cover body 37 faces the first coil end 171 from the front. Furthermore, the outer cylindrical portion 37d of the cover body 37 is located outside the first coil end 171 in the radial direction of the cover body 37. In this case, the outer cylindrical portion 37d and the first coil end 171 are spaced apart in the radial direction of the cover body 37.

[0117] In other words, with the cover body 37 supported by the first diameter portion 64a, the first coil end 171 is accommodated within the accommodation portion 38. As a result, within the accommodation portion 38, the first coil end 171 is covered from the front by the wall portion 37a and the connecting portion 37c, and is covered from the radially inside by the inner cylindrical portion 37b. Furthermore, within the accommodation portion 38, the first coil end 171 is covered from the radially outside by the outer cylindrical portion 37d.

[0118] Furthermore, in this compressor, when the cover body 37 is supported by the first diameter portion 64a, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37d are arranged in this order from the drive axis O1 side toward the outside in the radial direction of the cover body 37. The first diameter portion 64a, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37d are arranged while overlapping each other in the radial direction.

[0119] In this compressor, the boss 39d of the case 39 is inserted into the second radial ball bearing 52 and the shaft seal member 63. As a result, the case 39 is rotatably supported by the support portion 66 via the second radial ball bearing 52. In this way, the driving scroll 30 is disposed in the scroll chamber 65 and is supported by the housing 6 by both the protrusion 64 and the support portion 66 so as to be rotatable about the drive axis O1.

[0120] Furthermore, since the case 39 is supported by the support portion 66, the discharge passage 390 faces the discharge communication port 69 from the rear. As a result, the discharge chamber 14 and the discharge communication port 69 communicate with each other through the discharge passage 390. The shaft seal member 63 seals the discharge passage 390 and the discharge communication port 69 from the scroll chamber 65.

[0121] On the other hand, in the driven scroll 40, the driven pin 55 of the driven shaft portion 16 is inserted into the pin hole 4. As a result, the driven scroll 40 is disposed in the scroll chamber 65 and is supported rotatably around the driven axis O2 with respect to the first diameter portion 64a of the protruding body 64.

[0122] In the compressor configured as described above, as indicated by the dashed arrow in Fig. 1 , low-temperature, low-pressure refrigerant that has passed through the evaporator is drawn into the scroll chamber 65 through the suction port 68. When the electric motor 10 is operated and the rotor 11 rotates, the rotation of the rotor 11 is transmitted to the driving scroll 30, causing the driving scroll 30 to rotate about the drive axis O1 within the scroll chamber 65. In other words, the driving scroll 30 and the rotor 11 rotate integrally in the rotational direction R1 shown in Fig. 4 . At this time, as described above, in the separation mechanism 71, the cylindrical member 77 is held by the drive end plate 31 and the case 39, so the separation mechanism 71 rotates integrally with the drive end plate 31 and the case 39.

[0123] As the driving scroll 30 is rotated, in the driven mechanism 20, each rotation-preventing pin 21 slides against the inner circumferential surface of each ring 22, causing each ring 22 to rotate relatively around the center of each rotation-preventing pin 21. In this way, the driven mechanism 20 transmits the torque of the driving scroll 30 to the driven scroll 40.

[0124] As a result, the driven scroll 40 is rotated around the driven axis O2 by the driving scroll 30 and the driven mechanism 20. At this time, the driven mechanism 20 restricts the rotation of the driven scroll 40. As a result, the driven scroll 40 revolves around the driven axis O2 relative to the driving scroll 30. Then, as the driving scroll 33 and the driven scroll 43 each rotate within the suction section 30a, the driving scroll 33 and the driven scroll 43 change the volume of the compression chamber 12.

[0125] The refrigerant drawn into the scroll chamber 65 from the suction port 68 contains lubricating oil 18. The refrigerant in the scroll chamber 65 flows between the rotor 11 and the stator 17 and reaches the accommodation section 38. The refrigerant drawn into the scroll chamber 65 also flows into the accommodation section 38 by flowing through slits formed in the stator core 17a. In this way, the refrigerant in the accommodation section 38 is drawn into the compression chamber 12 from the suction port 374 through the suction section 30a. As a result, the lubricating oil 18 is also drawn into the compression chamber 12 together with the refrigerant from the suction port 374 through the suction section 30a.

[0126] The compression chambers 12 then reduce their volumes and compress the refrigerant while trapping the refrigerant and lubricating oil 18 therein due to the rotational drive of the drive scroll 30 and the driven rotation of the driven scroll 40. The high-pressure refrigerant compressed to the discharge pressure is discharged from the discharge port 32 to the end plate recess 75 as compressed refrigerant by the elastically deformed discharge reed valve 57 opening the discharge port 32. This compressed refrigerant contains the lubricating oil 18. The compressed refrigerant discharged to the end plate recess 75 flows through the separation passage 81 toward the discharge passage 390.

[0127] In addition, in this compressor, as the drive end plate 31 and therefore the drive scroll 30 are driven to rotate, the centrifugal force of the rotating drive scroll 30 acts on the compressed refrigerant discharged from the discharge port 32 into the end plate recess 75. As a result, the compressed refrigerant discharged into the end plate recess 75 separates the lubricating oil 18 contained therein due to the action of the centrifugal force.

[0128] In the separation mechanism 71, the helical member 78 is disposed inside the cylindrical member 77, and the compressed refrigerant flows in a spiral pattern around the drive shaft center O1 inside the separation passage 81 while colliding with the blades 78b of the helical member 78. In this way, in this compressor, not only can the lubricating oil 18 be separated from the compressed refrigerant by the action of centrifugal force, but also the lubricating oil 18 can be separated from the compressed refrigerant by the collision of the compressed refrigerant with the blades 78b as it flows through the separation passage 81.

[0129] In this manner, the lubricating oil 18 separated from the compressed refrigerant is guided toward the outer periphery of the separation passage 81 by the vanes 78b, as indicated by the solid arrows in FIGS. 1 and 2 . As described above, in this compressor, the vanes 78b are inclined toward the front of the tubular member 77 as they extend radially outward from the central shaft 78a. That is, the vanes 78b are inclined toward the downstream direction of the compressed refrigerant flowing through the separation passage 81 as they extend radially outward from the central shaft 78a. Therefore, the shape of the vanes 78b makes it easy for the lubricating oil 18 separated from the compressed refrigerant to be pushed radially outward from the tubular member 77 through the separation passage 81 toward the outer edge of the vanes 78b. As a result, the lubricating oil 18 separated from the compressed refrigerant flows from the separation passage 81 to the outside of the tubular member 77, i.e., into the discharge chamber 14, via the first to fifth outlet paths 771 to 775 formed in the tubular member 77.

[0130] Thus, in this compressor, the compressed refrigerant from which the lubricating oil 18 has been separated flows from the front end of the separation passage 81 to the discharge passage 390, passes through the discharge passage 390, and is discharged from the discharge communication port 69 to the outside of the housing 6. Meanwhile, the lubricating oil 18 separated from the compressed refrigerant flows into the discharge chamber 14 and flows radially outward within the discharge chamber 14 due to centrifugal force, while being stored within the discharge chamber 14. Thus, in this compressor, the lubricating oil 18 can be prevented from being discharged from the discharge communication port 69 to the outside of the housing 6 together with the compressed refrigerant.

[0131] Furthermore, in this compressor, because the first return path 35a is connected to the discharge chamber 14, the lubricating oil 18 stored in the discharge chamber 14 flows through the first return path 35a and the second return path 37f and reaches the recess 373. The recess 373 is under suction pressure due to the refrigerant drawn through the suction port 374, so its pressure is lower than that of the discharge chamber 14. The lubricating oil 18 that reaches the recess 373 lubricates the gap between the second front surface 371 of the wall portion 37a and the third rear surface 412 of the driven end plate 41, as well as the driven shaft portion 16 and the first radial ball bearing 51. After lubricating these components, the lubricating oil 18 flows between the first radial ball bearing 51 and the inner cylindrical portion 37b and flows into the scroll chamber 65. The lubricating oil 18 in the scroll chamber 65 is then drawn back into the suction section 30a and ultimately the compression chamber 12 together with the refrigerant through the suction port 374. As a result, in this compressor, the lubricating oil 18 can suitably lubricate the drive scroll 30, the driven scroll 40, etc., and therefore wear of these scrolls can be suitably prevented.

[0132] Therefore, the compressor of the embodiment has excellent durability.

[0133] In particular, in this compressor, the cylindrical member 77 has a larger diameter than the end plate recess 75, the boss 39d, and the discharge passage 390. Therefore, in this compressor, the compressed refrigerant discharged from the discharge port 32 to the end plate recess 75 easily flows into the separation passage 81. In this respect, too, this compressor can prevent the lubricating oil 18 from being discharged together with the compressed refrigerant from the discharge communication port 69 to the outside of the housing 6. Furthermore, because the cylindrical member 77 has such a large diameter, in this compressor, the separation passage 81 can be suitably formed inside the cylindrical member 77 by the cylindrical member 77 and the spiral member 78, and the flow rate of the compressed refrigerant flowing through the separation passage 81 can be suitably secured.

[0134] Furthermore, in this compressor, the discharge chamber 14 is formed to have a larger diameter than the second radial ball bearing 52, making it possible to suitably ensure the volume of the discharge chamber 14. This allows for greater freedom in the design of the separation mechanism 71 in this compressor.

[0135] Furthermore, in this compressor, the first to fifth outflow passages 771 to 775 are formed in a spiral shape along the outer periphery of the blade portion 78b of the spiral member 78. Therefore, in this compressor, the lubricating oil 18 guided to the outer periphery of the separation passage 81 by the blade portion 78b can be suitably caused to flow from the separation passage 81 into the discharge chamber 14 by the first to fifth outflow passages 771 to 775.

[0136] In this compressor, a portion of the compressed refrigerant flowing through the separation passage 81 inevitably flows out of the cylindrical member 77, i.e., into the discharge chamber 14, together with the lubricating oil 18, via the first to fifth outlet passages 771 to 775. In this regard, in this compressor, as described above, the first and second vent passages 776, 777 communicate with the separation passage 81 and the outside of the cylindrical member 77 at a location forward of the blade portion 78b in the separation mechanism 71. Therefore, the compressed refrigerant that flows out of the first to fifth outlet passages 771 to 775 into the discharge chamber 14 can merge with the compressed refrigerant in the separation passage 81 downstream of the blade portion 78b in the flow direction of the compressed refrigerant in the separation passage 81, by flowing through the first and second vent passages 776, 777. In this manner, in this compressor, the first and second vent passages 776, 777 ensure favorable flow of compressed refrigerant between the discharge chamber 14 and the discharge passage 390. In this respect, too, in this compressor, the lubricating oil 18 separated from the compressed refrigerant can be favorably discharged into the discharge chamber 14 from the separation passage 81 of the first to fifth outflow passages 771-775.

[0137] Furthermore, in this compressor, when the blade portion 78b is viewed from the discharge port 32 side, the spiral direction of the blade portion 78b coincides with the direction in which the drive scroll 30 is rotationally driven. As a result, in this compressor, since the blade portion 78b is likely to obstruct the flow of compressed refrigerant flowing through the separation passage 81, it is possible to cause the compressed refrigerant to preferably collide with the blade portion 78b.

[0138] Furthermore, in this compressor, the discharge passage 390 is formed inside the boss 39d, which makes it possible to easily form the discharge passage 390.

[0139] Furthermore, in this compressor, the second diameter portion 64b of the protruding body 64 is formed to have a larger diameter than the first diameter portion 64a. As a result, in this compressor, the rigidity of the protruding body 64 is suitably ensured by the second diameter portion 64b. Therefore, in this compressor, the second diameter portion 64b can suitably support the stator 17. Furthermore, because the first diameter portion 64a is smaller in diameter than the second diameter portion 64b, in this compressor, it is possible to prevent the first radial ball bearing 51 and the inner cylindrical portion 37b from becoming larger in diameter.

[0140] Although the present invention has been described above with reference to the examples, it goes without saying that the present invention is not limited to the above examples and can be modified and applied as appropriate within the scope of the invention.

[0141] For example, in the compressor of the embodiment, the first to fifth outflow passages 771 to 775 are formed in a spiral shape along the outer periphery of the blade portion 78b of the spiral member 78. However, this is not limiting, and the first to fifth outflow passages 771 to 775 may be formed in a round hole shape or the like.

[0142] In the compressor of the embodiment, the first and second ventilation passages 776, 777 are formed in the cylindrical member 77. However, this is not limiting, and the "ventilation passage" of the present invention may be formed in the front wall 39b of the case 39.

[0143] Furthermore, in the compressor of the embodiment, when the blade portion 78b is viewed from the discharge port 32 side, the spiral direction of the blade portion 78b coincides with the direction in which the driving scroll 30 is rotationally driven. However, this is not limiting, and the spiral direction of the blade portion 78b may be the opposite direction to the direction in which the driving scroll 30 is rotationally driven.

[0144] In the compressor of the embodiment, the blade portions 78b are inclined at a predetermined angle toward the downstream side of the compressed refrigerant flowing through the separation passage 81 as they extend from the central shaft portion 78a toward the outside in the radial direction of the cylindrical member 77. However, the blade portions 78b are not limited to this and may have other shapes.

[0145] In the compressor of the embodiment, the flange portion 77b of the tubular member 77 is inserted into the first retaining portion 73 of the drive end plate 31, and the front end of the tubular member 77 is inserted into the second retaining portion 39c of the front wall 39b, thereby fixing the tubular member 77 to the drive end plate 31 and the front wall 39b. However, this is not limiting, and the tubular member 77 may be fixed only to the drive end plate 31, or only to the front wall 39b, i.e., the case 39. Furthermore, the separation mechanism 71 may be disposed in the discharge chamber 14 with a gap between the tubular member 77 and the front wall 39b, or the separation mechanism 71 may be disposed in the discharge chamber 14 with a gap between the tubular member 77 and the drive end plate 31, so that the separation passage 81 communicates with the discharge chamber 14 through these gaps.

[0146] In the compressor of the embodiment, the case 39 is fixed to the driving end plate 31 of the driving scroll 30, but this is not limiting, and the case 39 may be fixed to the driven end plate 41 of the driven scroll 40. In this case, the discharge port 32 is formed in the driven end plate 41. The discharge reed valve 57 and the retainer 58 are fixed to the driven end plate 41 by fixing bolts 59.

[0147] In the compressor of the embodiment, the stator core 17a of the stator 17 is fixed to the protrusion 64, and the rotor 11 is disposed outside the stator core 17a. However, this is not limiting, and a configuration may be adopted in which the stator core 17a is fixed to the inner circumferential surface of the housing main body 60, while the rotor 11 is disposed inside the stator core 17a and is fixed to the inner cylindrical portion 37b of the cover body 37.

[0148] Furthermore, in the compressor of the embodiment, the protrusion 64 has a first diameter portion 64a and a second diameter portion 64b, but this is not limited to this, and the protrusion 64 may be formed only with the first diameter portion 64a, or the protrusion 64 may be formed only with the second diameter portion 64b.

[0149] Furthermore, in the compressor of the embodiment, the protrusion 64 is provided integrally with the first housing cover 61. However, this is not limiting, and the first housing cover 61 and the protrusion 64 may be formed separately, and the protrusion 64 may be fixed to the first housing cover 61. In this case, it is easy to form the first housing cover 61 and the protrusion 64 from different materials.

[0150] The present specification also includes the following inventions: (Supplementary Note 1) A double-rotating scroll compressor comprising a housing, a compression mechanism, a drive mechanism, and a driven mechanism, wherein the compression mechanism, the drive mechanism, and the driven mechanism are accommodated in the housing, the compression mechanism has a drive scroll that is rotationally driven about a drive axis by the drive mechanism, and a driven scroll that is eccentric with respect to the drive scroll and is rotationally driven by the drive scroll and the driven mechanism about a driven axis, the drive scroll and the driven scroll forming compression chambers that compress a refrigerant by the rotational driving and the rotational driven, the housing is formed with a discharge communication port through which compressed refrigerant that is refrigerant compressed in the compression chambers is discharged to the outside, a case is provided within the housing that can rotate together with the drive mechanism, a discharge chamber is formed within the case that is in communication with the compression chambers and from which the compressed refrigerant is discharged, and a separation mechanism that can rotate integrally with the case is disposed within the discharge chamber, the compression mechanism has a discharge port that is in communication with the compression chambers and discharges the compressed refrigerant from the compression chambers, a discharge passage formed in the case for passing the compressed refrigerant toward the discharge communication port, the separation mechanism including: a cylindrical member extending cylindrically in the direction of the drive shaft; and a helical member disposed inside the cylindrical member and extending helically around the drive shaft to form a separation passage inside the cylindrical member, the separation passage extending helically around the drive shaft and communicating with the discharge port and the discharge passage, the helical member separating lubricating oil contained in the compressed refrigerant from the compressed refrigerant flowing through the separation passage by collision with the compressed refrigerant flowing through the separation passage, and the cylindrical member being formed with an outflow passage that communicates with the separation passage and the outside of the cylindrical member and that allows the lubricating oil to flow out of the cylindrical member. (Appendix 2) The double rotary scroll compressor according to Appendices 1, wherein the outflow passage is formed in a helical shape along an outer circumferential edge of the helical member. (Supplementary Note 3) The double rotary scroll compressor according to Supplementary Note 1 or 2, wherein the discharge chamber is in communication with a return passage that returns the lubricating oil to a location in the housing that has a lower pressure than the discharge chamber.(Supplementary Note 4) The double-rotary scroll compressor according to any one of Supplementary Notes 1 to 3, wherein the cylindrical member is formed with a diameter larger than the discharge passage. (Supplementary Note 5) The double-rotary scroll compressor according to any one of Supplementary Notes 1 to 4, wherein an air passage is provided within the case, which allows the compressed refrigerant that has flowed out of the cylindrical member from the outflow passage to flow to the discharge passage downstream of the helical member in the flow direction of the compressed refrigerant. (Supplementary Note 6) The double-rotary scroll compressor according to any one of Supplementary Notes 1 to 5, wherein the case is formed with a supported member that protrudes toward the housing, the supported member is rotatably supported by the housing via a bearing, and the discharge passage extends inside the supported member. (Supplementary Note 7) The double-rotary scroll compressor according to Supplementary Note 6, wherein the discharge chamber is formed with a diameter larger than the bearing. (Supplementary Note 8) The double-rotary scroll compressor according to any one of Supplementary Notes 1 to 7, wherein the helical member has a central shaft portion extending linearly in the drive shaft direction and blade portions that are integral with the central shaft portion and extend helically around the drive shaft center, and when the blade portions are viewed from the discharge port side, the spiral direction of the blade portions coincides with the rotation direction of the drive mechanism. (Supplementary Note 9) The double-rotary scroll compressor according to any one of Supplementary Notes 1 to 8, wherein the helical member has a central shaft portion extending linearly in the drive shaft direction and blade portions that are integral with the central shaft portion and extend helically around the drive shaft center, and the blade portions incline in a downstream direction of the separation passage as they approach the radially outer side from the central shaft portion.

[0151] The present invention can be used in vehicle air conditioning systems and the like.

[0152] DESCRIPTION OF SYMBOLS 6 Housing 9 Compression mechanism 10 Electric motor (drive mechanism) 12 Compression chamber 14 Discharge chamber 18 Lubricating oil 20 Driven mechanism 30 Drive scroll 31 Drive end plate 32 Discharge port 35a First return path (return path) 37f Second return path (return path) 39 Case 39d Boss (supported member) 40 Driven scroll 52 Second radial ball bearing (bearing) 69 Discharge communication port 71 Separation mechanism 77 Cylindrical member 78 Helical member 78a Central shaft portion 78b Blade portion 81 Separation passage 390 Discharge passage 771 to 775 First to fifth outflow paths (outflow paths) 776, 777 First and second ventilation paths (ventilation paths) O1 Drive shaft center O2 Driven shaft center

Claims

1. A double-rotating scroll compressor comprising a housing, a compression mechanism, a drive mechanism, and a driven mechanism, wherein the compression mechanism, the drive mechanism, and the driven mechanism are contained within the housing, the compression mechanism having a drive scroll that is rotationally driven about a drive axis by the drive mechanism, and a driven scroll that is eccentric with the drive scroll and driven about a driven axis while being rotationally driven by the drive scroll and the driven mechanism, the drive scroll and the driven scroll forming a compression chamber that compresses a refrigerant by the rotational driving and the rotational driven, the housing having a discharge communication port that discharges to the outside the compressed refrigerant that is the refrigerant compressed in the compression chamber, the housing having a case that can rotate together with the drive mechanism, the case having a discharge chamber that is in communication with the compression chamber and from which the compressed refrigerant is discharged, and a separation mechanism that can rotate integrally with the case disposed within the discharge chamber, the compression mechanism having a discharge port that is in communication with the compression chamber and that discharges the compressed refrigerant from the compression chamber, a discharge passage for circulating the compressed refrigerant toward the discharge communication port is formed in the case; the separation mechanism includes: a cylindrical member extending cylindrically in the direction of the drive shaft; and a helical member disposed inside the cylindrical member, extending helically around the drive shaft and forming a separation passage inside the cylindrical member, the separation passage communicating with the discharge port and the discharge passage; the helical member separates lubricating oil contained in the compressed refrigerant from the compressed refrigerant by colliding with the compressed refrigerant flowing through the separation passage; and an outflow passage formed in the cylindrical member, which communicates with the separation passage and the outside of the cylindrical member and allows the lubricating oil to flow out of the cylindrical member.

2. A double-rotating scroll compressor according to claim 1, wherein said outflow passage is formed in a spiral shape along the outer periphery of said spiral member.

3. A double rotary scroll compressor according to claim 1 or 2, wherein the discharge chamber is connected to a return passage for returning the lubricating oil to a location in the housing where the pressure is lower than that of the discharge chamber.

4. A double rotary scroll compressor according to claim 1 or 2, wherein the cylindrical member is formed to have a diameter larger than that of the discharge passage.

5. A double-rotating scroll compressor as described in claim 1 or 2, wherein an air passage is provided within the case to allow the compressed refrigerant that has flowed out of the cylindrical member from the outflow passage to flow into the discharge passage downstream of the spiral member in the flow direction of the compressed refrigerant.

6. A double rotary scroll compressor according to claim 1 or 2, wherein the case is formed with a supported member that protrudes toward the housing, the supported member is rotatably supported on the housing via a bearing, and the discharge passage extends inside the supported member.

7. A double-rotating scroll compressor according to claim 6, wherein the discharge chamber is formed to have a diameter larger than that of the bearing.

8. A double-rotating scroll compressor according to claim 1 or 2, wherein the spiral member has a central shaft portion extending linearly in the direction of the drive shaft center, and a blade portion that is integral with the central shaft portion and extends spirally around the drive shaft center, and when the blade portion is viewed from the discharge port side, the spiral direction of the blade portion coincides with the rotation direction of the drive mechanism.

9. A double-rotating scroll compressor according to claim 1 or 2, wherein the spiral member has a central shaft portion extending linearly in the direction of the drive shaft center, and blade portions that are integral with the central shaft portion and extend spirally around the drive shaft center, and the blade portions incline in the downstream direction of the separation passage as they approach the radially outer side from the central shaft portion.

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