Co-rotating scroll compressor

Abstract

In this compressor, a compression mechanism (9) comprises a driving scroll (30) and a driven scroll (40), and the driving scroll (30) and the driven scroll (40) form a compression chamber (12). A housing (6) has formed therein a discharge communication port (69) for discharging, to the exterior, a compressed refrigerant that is a refrigerant compressed in the compression chamber (12). In the housing (6), a rotatable case (39) is also provided along with a drive mechanism (9). A discharge chamber (14) is formed in the case (39). The case (39) comprises a wall (39b). A discharge passage (390) and guide protrusions (71-76) are provided to the wall (39b). The guide protrusions (71-76) cause lubricating oil (18) that is contained in the compressed refrigerant to be separated out from the compressed refrigerant by colliding with the compressed refrigerant, and also guide the compressed refrigerant and the lubricating oil (18) more radially outward than the discharge passage (390).

Description

Double-rotating scroll compressor

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

[0002] Patent Document 1 discloses a conventional double-rotating scroll compressor (hereinafter simply referred to as a compressor). This compressor includes a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism. The drive mechanism and the 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] Japanese Patent Application Publication No. 2-227575

[0007] The refrigerant drawn into the compression chamber contains lubricating oil, which is discharged from the compression chamber to the discharge chamber along with the compressed refrigerant. Therefore, it is conceivable to use such lubricating oil to lubricate the driving scroll, the driven scroll, etc.

[0008] However, in the conventional compressor, 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. As a result, in this compressor, the lubricating oil discharged into the discharge chamber cannot be used sufficiently to lubricate the driving scroll, the driven scroll, etc. Therefore, there is a concern that the durability of such a compressor will be reduced due to insufficient lubrication of the driving scroll, the driven scroll, etc.

[0009] 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.

[0010] The double-rotating scroll compressor of the present invention comprises 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 within the housing, and 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, and the drive scroll and the driven scroll form compression chambers that compress a refrigerant by the rotational driving and the rotational driven, and 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, and a case is provided within the housing that can rotate together with the drive mechanism, and a discharge chamber that communicates with the compression chamber and from which the compressed refrigerant is discharged is formed within the case, and the case has a wall portion extending radially of the case, and the wall portion is provided with a discharge passage that communicates the discharge chamber with the discharge communication port, and The compressor is characterized by having a guide protrusion that protrudes into the discharge chamber and collides with the compressed refrigerant to separate the lubricating oil contained in the compressed refrigerant from the compressed refrigerant, and that guides the compressed refrigerant and the lubricating oil radially outward beyond the discharge passage.

[0011] In the double-rotary scroll compressor of the present invention, a case is provided within a housing, and the case is rotatable together with a drive mechanism. The case also has a discharge chamber formed therein. The discharge chamber communicates with the compression chamber, and discharges compressed refrigerant.

[0012] In addition, the compressor has a discharge passage and a guide protrusion in the wall of the case. The guide protrusion protrudes into the discharge chamber. In this compressor, the guide protrusion collides with the compressed refrigerant in the discharge chamber, separating the lubricating oil contained in the compressed refrigerant. Furthermore, the guide protrusion guides the compressed refrigerant and the lubricating oil radially outward from the wall beyond the discharge passage.

[0013] In addition, in this compressor, the case rotates together with the compression mechanism, and the centrifugal force of the rotating case acts on the compressed refrigerant in the discharge chamber. Therefore, in this compressor, in addition to collision with the guide protrusions, the centrifugal force of the case acting on the compressed refrigerant also separates the lubricating oil from the compressed refrigerant. Therefore, the lubricating oil separated from the compressed refrigerant flows radially outward of the wall portion due to the centrifugal force.

[0014] As a result, in this compressor, the compressed refrigerant from which the lubricating oil has been separated is discharged from the discharge chamber through the discharge passage and the discharge communication port to the outside of the housing. Meanwhile, the lubricating oil separated from the compressed refrigerant is prevented from being discharged to the outside of the housing through the discharge passage and 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 driving scroll, driven scroll, etc.

[0015] Therefore, the double-rotating scroll compressor of the present invention has excellent durability.

[0016] In the compressor of the present invention, there may be a plurality of guide protrusions. Preferably, the guide protrusions are arranged circumferentially around the wall portion. In this case, the rotation of the case causes the plurality of guide protrusions to preferably collide with the compressed refrigerant in the discharge chamber, thereby preferably separating the lubricating oil contained in the compressed refrigerant from the compressed refrigerant. Furthermore, in this compressor, the guide protrusions can preferably guide the lubricating oil and compressed refrigerant radially outward from the wall portion beyond the discharge passage, thereby more preferably preventing the lubricating oil from being discharged to the outside of the housing via the discharge passage and the discharge communication port.

[0017] The guide protrusions preferably have curved portions that curve rearward in the direction of rotation of the case as they approach the radially outer side, thereby enabling the lubricating oil and compressed refrigerant to be suitably guided radially outward from the wall portion.

[0018] The wall portion may be formed with a supported member that protrudes toward the housing and is rotatably supported on the housing via a bearing. A discharge passage preferably extends within the supported member. In this case, the case can be suitably rotated within the housing. Furthermore, by extending the discharge passage within the supported member, the discharge passage can be suitably formed.

[0019] It is preferable that a collision wall that overlaps with the discharge passage in the drive shaft direction and that collides with the compressed refrigerant is provided in the discharge chamber. In this case, the compressed refrigerant in the discharge chamber also collides with the collision wall, so that the lubricating oil contained in the compressed refrigerant can be more effectively separated from the compressed refrigerant.

[0020] The wall portion preferably has a cylindrical protrusion that is connected to the guide protrusion, protrudes into the discharge chamber, and has a discharge passage formed therein. In this case, lubricating oil separated from the compressed refrigerant is less likely to reach the discharge passage. Furthermore, in this compressor, the lubricating oil can be stored between the guide protrusion and the cylindrical protrusion. As a result, in this compressor, the lubricating oil can be more effectively prevented from being discharged to the outside of the housing through the discharge passage and the discharge communication port.

[0021] The compression mechanism may have a discharge port that discharges compressed refrigerant from the compression chamber to the discharge chamber, a discharge reed valve that opens and closes the discharge port, and a retainer that adjusts the opening of the discharge reed valve. The retainer may have a base end fixed to the compression mechanism and extend away from the compression mechanism as it moves from the base end to the tip end. Preferably, the guide protrusion is located on an extension of the tip end of the retainer.

[0022] In this case, the shape of the retainer can effectively guide the compressed refrigerant discharged from the discharge port into the discharge chamber to the guide protrusions, thereby allowing the compressed refrigerant to effectively collide with the guide protrusions.

[0023] The discharge chamber is preferably connected to a return passage for returning the lubricating oil from the discharge chamber 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.

[0024] The double-rotating scroll compressor of the present invention is excellent in durability.

[0025] Fig. 1 is a cross-sectional view of a compressor according to a first embodiment. Fig. 2 is a rear view of the compressor according to the first embodiment, in which the case is seen from the rear. Fig. 3 is an enlarged cross-sectional view of the main parts of Fig. 1, showing the discharge chamber, the guide protrusion, the impingement plate, etc., in the compressor according to the first embodiment. Fig. 4 is a cross-sectional view of a compressor according to a second embodiment. Fig. 5 is a rear view of the compressor according to the second embodiment, in which the case is seen from the rear.

[0026] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First and second embodiments of the present invention will now be described with reference to the accompanying drawings. The compressors of the first and second embodiments are mounted on a vehicle (not shown) and form an air conditioning system for the vehicle.

[0027] 1, the compressor of the first embodiment includes a housing 6, an electric motor 10, a compression mechanism 9, and a case 39. The electric motor 10 is an example of the "drive mechanism" of the present invention.

[0028] 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.

[0029] 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 .

[0030] 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.

[0031] 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).

[0032] 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.

[0033] 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.

[0034] 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.

[0035] 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.

[0036] 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.

[0037] 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.

[0038] The second housing cover 62 is also formed with a support portion 66 and a discharge communication 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 formed in a cylindrical shape centered on the drive axis O1, and is provided therein with the second radial ball bearing 52 and a shaft seal member 63. Note that a sliding bearing may be provided inside the support portion 66 instead of the second radial ball bearing 52.

[0039] 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.

[0040] 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).

[0041] 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.

[0042] 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.

[0043] 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.

[0044] 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.

[0045] 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.

[0046] 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.

[0047] 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.

[0048] 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.

[0049] 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.

[0050] 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.

[0051] A discharge port 32 is formed in the drive end plate 31. The discharge port 32 penetrates the drive end plate 31 in the direction of the drive axis O1. Furthermore, a discharge reed valve 57 and a retainer 58 are provided on the first front surface 311 of the drive end plate 31.

[0052] The base ends of the discharge reed valve 57 and the retainer 58 are fixed to the first front surface 311 by fixing bolts 59. As a result, the tip end of the discharge reed valve 57 is elastically deformed between the open position shown in Figure 1 and the closed position shown in Figure 3, thereby allowing the discharge port 32 to be opened and closed.

[0053] The retainer 58 is fixed to the first front surface 311 by a fixing bolt 59, and the tip side of the retainer 58 is spaced forward in the direction of the drive axis O1 from the first front surface 311. More specifically, the retainer 58 extends from the base end side toward the tip side so as to gradually become spaced forward in the direction of the drive axis O1 from the first front surface 311, i.e., the driving scroll 30. As a result, the retainer 58 abuts against the elastically deformed discharge reed valve 57, thereby making it possible to adjust the opening degree of the discharge reed valve 57.

[0054] 1, 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 center on the central side of the drive end plate 31 and protrudes outward in a spiral shape from the center.

[0055] 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.

[0056] The driving peripheral wall 35 is 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 of the driving end plate 31, and the rear end opens to the rear end surface of the driving peripheral wall 35.

[0057] 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.

[0058] The wall portion 37a extends in a generally plate-like shape in the radial direction of the cover body 37. 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.

[0059] 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.

[0060] 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.

[0061] 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. The same applies to FIG. 4, which will be described later.

[0062] 1, 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.

[0063] 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.

[0064] 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.

[0065] 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.

[0066] 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.

[0067] 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.

[0068] 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. FIGS. 1 and 4 illustrate only one of the plurality of first bolt holes 11a and one of the plurality of second bolt holes 376.

[0069] 1, 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 thereof communicates with the recess 373.

[0070] 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.

[0071] 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.

[0072] 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.

[0073] 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.

[0074] 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.

[0075] 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.

[0076] 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 FIGS. 1 and 4.

[0077] 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.

[0078] 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.

[0079] 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.

[0080] 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.

[0081] 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.

[0082] 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 .

[0083] 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 peripheral wall 35. The case 39 may also be made of resin or the like.

[0084] 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.

[0085] A boss 39d is formed on the front wall 39b. The boss 39d is an example of the "supported member" of the present invention. 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 at the fourth rear surface 392.

[0086] 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. Only one of the plurality of third bolt holes 39e is shown in FIGS. 1, 3, and 4.

[0087] 2, guide protrusions 71 to 76 are integrally formed on the front wall 39b. The guide protrusions 71 to 76 have the same shape and each extend radially toward the outer peripheral wall 39a while protruding rearward from a location on the fourth rear surface 392 of the front wall 39b that is radially outward of the front wall 39b relative to the discharge passage 390. The guide protrusions 71 to 76 are connected to the outer peripheral wall 39a at their radially outer ends.

[0088] The guide protrusions 71 to 76 are arranged at equal intervals around the circumferential direction of the front wall 39b. Furthermore, the guide protrusions 71 to 76 are each provided with a curved portion 71a to 76a. The curved portions 71a to 76a are each curved rearward in the rotational direction R1 of the case 39 and, ultimately, the compression mechanism 9, as they approach the outer peripheral wall 39a in the radial direction from the discharge passage 390 of the front wall 39b. As a result, when the case 39 is viewed from the rear, the guide protrusions 71 to 76 are each curved rearward in the rotational direction R1 as they approach the outer peripheral wall 39a in the radial direction from the discharge passage 390 of the front wall 39b. In other words, the guide protrusions 71 to 76 are shaped to surround the discharge passage 390 and extend radially while curving from the discharge passage 390 side toward the outer peripheral wall 39a side in the radial direction. The guide protrusions 71 to 76 have guide surfaces 71b to 76b on the front side in the rotation direction R1, respectively. The number of guide protrusions 71 to 76 can be designed as appropriate.

[0089] A collision wall 77 is fixed to the guide protrusions 71 to 76 by a plurality of bolts 77a. As shown in Figure 1, the collision wall 77 is made of metal and is formed in a disk shape with a diameter larger than that of the discharge passage 390. By being fixed to the guide protrusions 71 to 76, the collision wall 77 overlaps with the discharge passage 390 in the direction of the drive shaft center O1. The collision wall 77 may also be made of resin.

[0090] 1 and 3 , the rear surface of the outer peripheral wall 39a of the case 39 abuts against 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 is fixed to the driving end plate 31, and ultimately to the driving scroll 30.

[0091] By fixing the case 39 to the drive end plate 31 in this manner, 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. The discharge chamber 14 communicates with the discharge port 32 and also with the discharge passage 390. The discharge chamber 14 also communicates with the first return path 35a. As a result, the discharge chamber 14 communicates with the recess 373 of the cover body 37 via the first return path 35a and the second return path 37f.

[0092] The guide protrusions 71 to 76 and the collision wall 77 are disposed within the discharge chamber 14. Within the discharge chamber 14, the guide protrusions 71 to 76 and the collision wall 77 are spaced forward from the drive end plate 31 and face the drive end plate 31. In this compressor, as shown in Figure 3, when an imaginary extension line L is defined that extends from the tip of the retainer 58 along the shape of the retainer 58, the guide protrusion 74 is positioned to overlap this extension line L.

[0093] The driving scroll 30 is disposed in front of the stator 17 within 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.

[0094] 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.

[0095] 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.

[0096] 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.

[0097] 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.

[0098] 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.

[0099] 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.

[0100] 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 supported rotatably about the driven axis O2 with respect to the first diameter portion 64a of the protruding body 64. In other words, unlike the driving scroll 30, the driven scroll 40 is supported rotatably about the driven axis O2 in the housing 6 only by the protruding body 64.

[0101] In the compressor configured as described above, as shown 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. At this time, in the driven mechanism 20, each rotation-preventing pin 21 slides against the inner circumferential surface of each ring 22, causing the rings 22 to rotate relatively about the center of the rotation-preventing pin 21. In this way, the driven mechanism 20 transmits the torque of the driving scroll 30 to the driven scroll 40.

[0102] 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.

[0103] 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.

[0104] The compression chamber 12 compresses the refrigerant by reducing its volume 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 discharge chamber 14 as compressed refrigerant contains the lubricating oil 18 when the discharge reed valve 57 opens the discharge port 32 due to elastic deformation.

[0105] Here, as the retainer 58 moves from the base end to the tip end, it gradually extends forward in the direction of the drive axis O1 from the first front surface 311. Therefore, when the compressed refrigerant is discharged from the discharge port 32 into the discharge chamber 14, the refrigerant follows the shape of the retainer 58, and is therefore more easily guided from the discharge port 32 toward the radially outer side of the case 39.

[0106] In this compressor, when the case 39 and therefore the drive scroll 30 are rotated, the centrifugal force of the rotating case 39 acts on the compressed refrigerant in the discharge chamber 14 .

[0107] Furthermore, in this compressor, the guide protrusions 71 to 76 face the drive end plate 31 within the discharge chamber 14. Therefore, the compressed refrigerant discharged into the discharge chamber 14 collides with the guide protrusions 71 to 76. Here, the guide protrusions 71 to 76 within the discharge chamber 14 rotate integrally with the case 39 around the drive axis O1. As a result, the guide protrusions 71 to 76 collide with the compressed refrigerant while rotating around the drive axis O1. More specifically, as the compressed refrigerant collides with the guide surfaces 71b to 76b, the compressed refrigerant is guided radially outward along the guide surfaces 71b to 76b.

[0108] In particular, in this compressor, among the guide protrusions 71-76, the guide protrusion 74 is positioned so as to overlap with the extension line L extending from the tip of the retainer 58, and is therefore likely to collide with the compressed refrigerant discharged from the discharge port 32 and guided into the retainer 58. In this way, the guide protrusions 71-76 that collide with the compressed refrigerant guide the compressed refrigerant radially outward of the front wall 39b beyond the discharge passage 390, i.e., toward the outer periphery of the discharge chamber 14. At this time, due to the overall shape of the guide protrusions 71-76, including the curved portions 71a-76a, the guide protrusions 71-76 guide the compressed refrigerant rearward in the rotational direction R1 as it moves from the discharge passage 390 toward the radially outward side of the front wall 39b.

[0109] During the process of colliding with the compressed refrigerant and guiding the compressed refrigerant radially outward from front wall 39b, guide protrusions 71-76 separate lubricating oil 18 contained in the compressed refrigerant from the compressed refrigerant. Therefore, guide protrusions 71-76 also guide lubricating oil 18 separated from the compressed refrigerant radially outward from front wall 39b beyond discharge passage 390.

[0110] Furthermore, as described above, in this compressor, the centrifugal force of the rotating case 39 acts on the compressed refrigerant in the discharge chamber 14. Therefore, in this compressor, in addition to collision with the guide protrusions 71-76, the centrifugal force of the case 39 acting on the compressed refrigerant also separates the lubricating oil 18 from the compressed refrigerant.

[0111] Furthermore, in this compressor, the compressed refrigerant in the discharge chamber 14 may also collide with the collision wall 77. As a result, the collision wall 77 separates the lubricating oil 18 contained in the compressed refrigerant from the compressed refrigerant. As a result, the lubricating oil 18 from the compressed refrigerant also flows radially outward of the front wall 39b beyond the discharge passage 390, similar to the lubricating oil 18 separated from the compressed refrigerant upon collision with the guide protrusions 71-76.

[0112] Thus, in this compressor, the compressed refrigerant from which the lubricating oil 18 has been separated flows between the guide protrusions 71-76 and the front of the collision wall 77, and is then discharged from the discharge chamber 14 through the discharge passage 390 and the discharge communication port 69 to the outside of the housing 6. Meanwhile, the lubricating oil 18 separated from the compressed refrigerant tends to remain in the discharge chamber 14 due to the centrifugal force of the case 39 acting on the compressed refrigerant, such as by adhering to the inner circumferential surface of the outer circumferential wall 39a. As a result, in this compressor, the lubricating oil 18 can be prevented from being discharged to the outside of the housing 6 through the discharge passage 390 and the discharge communication port 69.

[0113] Because the first return path 35a is connected to the discharge chamber 14, the lubricating oil 18 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, and therefore is at a lower pressure than 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.

[0114] Therefore, the compressor of Example 1 has excellent durability.

[0115] In particular, in this compressor, the guide protrusions 71 to 76 are formed on the front wall 39b of the case 39, so that the guide protrusions 71 to 76 also function as beam members that reinforce the front wall 39b. Therefore, in this compressor, it is possible to ensure the rigidity of the front wall 39b and, ultimately, the case 39.

[0116] Furthermore, in this compressor, collision walls 77 are fixed to the guide protrusions 71 to 76, and the collision walls 77 overlap with the discharge passage 390 in the direction of the drive axis O1. Therefore, in this compressor, the compressed refrigerant in the discharge chamber 14 can be effectively prevented from reaching the discharge passage 390 without colliding with the guide protrusions 71 to 76.

[0117] 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.

[0118] 4 and 5, in the compressor of the second embodiment, a cylindrical protrusion 78 is formed on the front wall 39b of the case 39. In addition, in this compressor, the collision wall 77 is not fixed to the guide protrusions 71 to 76.

[0119] 4, the cylindrical protrusion 78 is integrally formed with the front wall 39b and protrudes from the fourth rear surface 392 toward the discharge chamber 14 in a cylindrical shape centered on the drive axis O1. In this compressor, the discharge passage 390 extends from inside the boss 39d to inside the cylindrical protrusion 78. In other words, the cylindrical protrusion 78 surrounds the discharge passage 390 from the outside within the discharge chamber 14.

[0120] 5, the cylindrical protrusion 78 is integral with the guide protrusions 71 to 76. As a result, a barrier portion 701 is formed between the guide protrusions 71 and 72 and the outer peripheral surface of the cylindrical protrusion 78. Similarly, a barrier portion 702 is formed between the guide protrusions 72 and 73 and the outer peripheral surface of the cylindrical protrusion 78, and a barrier portion 703 is formed between the guide protrusions 73 and 74 and the outer peripheral surface of the cylindrical protrusion 78. Furthermore, a barrier portion 704 is formed between the guide protrusions 74 and 75 and the outer peripheral surface of the cylindrical protrusion 78, and a barrier portion 705 is formed between the guide protrusions 75 and 76 and the outer peripheral surface of the cylindrical protrusion 78. Furthermore, a barrier portion 706 is formed between the guide protrusions 76 and 71 and the outer peripheral surface of the cylindrical protrusion 78. Other configurations of this compressor are the same as those of the compressor of the first embodiment, and the same components are denoted by the same reference numerals, and detailed description of the configurations will be omitted.

[0121] As in the compressor of Example 1, in this compressor, the compressed refrigerant in the discharge chamber 14 collides with the guide protrusions 71 to 76, which then separate the lubricating oil 18 from the compressed refrigerant and guide the compressed refrigerant and the lubricating oil 18 toward the outer periphery of the discharge chamber 14.

[0122] Here, in this compressor, the cylindrical protrusion 78 protrudes into the discharge chamber 14. Therefore, in this compressor, the lubricating oil 18 guided toward the outer periphery of the discharge chamber 14 by the guide protrusions 71-76 must overcome the cylindrical protrusion 78 to reach the discharge passage 390 in order to flow from the discharge passage 390 to the outside of the discharge chamber 14. Therefore, in this compressor, most of the lubricating oil 18 heading from the outer periphery of the discharge chamber 14 toward the discharge passage 390 is blocked by the barrier portions 701-704. As a result, this compressor also prevents the lubricating oil 18 from being discharged to the outside of the housing 6 via the discharge passage 390 and the discharge communication port 69. Note that the lubricating oil 18 blocked from flowing to the discharge passage 390 by the barrier portions 701-704 flows toward the outer periphery of the discharge chamber 14 due to the centrifugal force of the case 39.

[0123] Furthermore, in this compressor, in addition to the guide protrusions 71 to 76, the cylindrical protrusion 78 is also formed on the front wall 39b of the case 39, so that the rigidity of the front wall 39b can be more suitably ensured by the guide protrusions 71 to 76 and the cylindrical protrusion 78. Other functions of this compressor are the same as those of the compressor of the first embodiment.

[0124] Although the present invention has been described above in accordance with Examples 1 and 2, it goes without saying that the present invention is not limited to the above Examples 1 and 2, and can be appropriately modified and applied within the scope of the invention.

[0125] For example, in the compressor of the first embodiment, the guide protrusions 71 to 76 are formed integrally with the front wall 39b of the case 39. However, this is not limiting, and the guide protrusions 71 to 76 may be formed as separate parts from the front wall 39b and fixed to the front wall 39b. The same applies to the guide protrusions 71 to 76 and the cylindrical protrusion 78 in the compressor of the second embodiment.

[0126] Furthermore, in the compressor of the first embodiment, the guide protrusions 71 to 76 have curved portions 71 a to 76 a. However, this is not limiting, and the guide protrusions 71 to 76 may be shaped to extend linearly in the radial direction of the front wall 39 b without providing the curved portions 71 a to 76 a. Furthermore, the guide protrusions 71 to 76 may be shaped as appropriate as long as they can utilize the rotation of the case 39 to guide the compressed refrigerant and lubricating oil 18 to the radial outside of the case 39. The same applies to the compressor of the second embodiment.

[0127] In the compressor of the first 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.

[0128] In the compressor of the first 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. The same applies to the compressor of the second embodiment.

[0129] In the compressor of the first embodiment, the protruding body 64 has the first diameter portion 64 a and the second diameter portion 64 b, but this is not limiting, and the protruding body 64 may be formed only with the first diameter portion 64 a, or the protruding body 64 may be formed only with the second diameter portion 64 b. The same applies to the compressor of the second embodiment.

[0130] Furthermore, in the compressor of Example 1, 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. The same applies to the compressor of Example 2.

[0131] The present specification also includes the following inventions: (Supplementary Note 1) A double-rotating scroll compressor includes 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, wherein 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, and a discharge chamber that communicates with the compression chamber and from which the compressed refrigerant is discharged is formed within the case, the case has a wall portion extending in a radial direction of the case, and the wall portion is provided with a discharge passage that communicates the discharge chamber with the discharge communication port, a guide protrusion that protrudes into the discharge chamber and collides with the compressed refrigerant to separate lubricating oil contained in the compressed refrigerant from the compressed refrigerant, and that guides the compressed refrigerant and the lubricating oil radially outward beyond the discharge passage. (Appendix 2) The double-rotary scroll compressor according to Appendix 1, wherein there are a plurality of guide protrusions, and the guide protrusions are arranged in the circumferential direction of the wall portion. (Appendix 3) The double-rotary scroll compressor according to Appendix 1 or 2, wherein the guide protrusions are provided with a curved portion that curves rearward in the rotation direction of the case as it approaches the radially outward. (Appendix 4) The double-rotary scroll compressor according to any one of Appendixes 1 to 3, wherein the wall portion is formed with a supported member that protrudes toward the housing and is rotatably supported by the housing via a bearing, and the discharge passage extends within the supported member. (Supplementary Note 5) The double-rotary scroll compressor according to any one of Supplementary Notes 1 to 4, wherein a collision wall that overlaps with the discharge passage in the drive shaft direction and that collides with the compressed refrigerant is provided in the discharge chamber.(Supplementary Note 6) The double-rotary scroll compressor according to any one of Supplements 1 to 5, wherein the wall portion is provided with a cylindrical protrusion that is connected to the guide protrusion and protrudes cylindrically into the discharge chamber, and the discharge passage is formed therein. (Supplementary Note 7) The compression mechanism has a discharge port that discharges the compressed refrigerant from the compression chamber to the discharge chamber, a discharge reed valve that can open and close the discharge port, and a retainer that can adjust the opening of the discharge reed valve, the retainer has a base end fixed to the compression mechanism and extends from the base end to a tip end while being separated from the compression mechanism, and the guide protrusion is located on an extension line of the tip end of the retainer. (Supplementary Note 8) The double-rotary scroll compressor according to any one of Supplements 1 to 7, wherein the discharge chamber is connected to a return passage that returns the lubricating oil in the discharge chamber to a portion of the housing that has a lower pressure than the discharge chamber.

[0132] The present invention can be used in vehicle air conditioning systems and the like.

[0133] 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 32 Discharge port 35a First return path (return path) 37f Second return path (return path) 39 Case 39b Front wall (wall portion) 39d Boss (supported member) 40 Driven scroll 52 Second radial ball bearing (bearing) 57 Discharge reed valve 58 Retainer 69 Discharge communication port 71 to 76 Guide protrusions 71a to 76a Curved portion 77 Collision wall 78 Cylindrical protrusion 390 Discharge passage L Extension line O1 Drive axis O2 Driven axis R1 Rotation direction

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 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, wherein the housing is formed with a discharge communication port through which compressed refrigerant that is refrigerant compressed in the compression chamber is discharged to the outside, a case is provided within the housing that can rotate together with the drive mechanism, and a discharge chamber that communicates with the compression chamber and from which the compressed refrigerant is discharged is formed within the case, the case has a wall portion extending radially of the case, and the wall portion has a discharge passage that communicates the discharge chamber with the discharge communication port, a guide protrusion that protrudes into the discharge chamber and collides with the compressed refrigerant to separate lubricating oil contained in the compressed refrigerant from the compressed refrigerant, and that guides the compressed refrigerant and the lubricating oil radially outward beyond the discharge passage.

2. A double-rotating scroll compressor according to claim 1, wherein the guide protrusions are plural, and each guide protrusion is arranged in the circumferential direction of the wall portion.

3. A double-rotating scroll compressor according to claim 1 or 2, wherein the guide projection is provided with a curved portion that curves rearward in the direction of rotation of the case as it approaches the radially outer side.

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

5. A double rotary scroll compressor according to claim 1 or 2, wherein a collision wall that collides with the compressed refrigerant is provided within the discharge chamber and overlaps with the discharge passage in the direction of the drive shaft.

6. A double-rotating scroll compressor according to claim 1 or 2, wherein the wall portion is provided with a cylindrical convex portion that is connected to the guide convex portion and protrudes cylindrically into the discharge chamber, with the discharge passage formed inside.

7. A double rotary scroll compressor according to claim 1 or 2, wherein the compression mechanism has a discharge port that discharges the compressed refrigerant from the compression chamber to the discharge chamber, a discharge reed valve that can open and close the discharge port, and a retainer that can adjust the opening of the discharge reed valve, the base end of the retainer is fixed to the compression mechanism and extends away from the compression mechanism as it moves from the base end to the tip, and the guide protrusion is located on an extension of the tip of the retainer.

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

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