CO-ROTATING SCROLL COMPRESSOR

Description

This application claims priority to Japanese Patent Application No. 2024-203659 filed on Nov. 22, 2024, the entire disclosure of which is incorporated herein by reference.

The present disclosure relates to a co-rotating scroll compressor.

BACKGROUND ART

Japanese Patent Application Publication No. H02-227575 discloses a known co-rotating scroll compressor (hereinafter, simply referred to as a compressor). The compressor includes a housing, a driving scroll, a driven scroll, a driving mechanism, and a driven mechanism. The housing has a scroll chamber in which the driving scroll, the driven scroll, the driving mechanism, and the driven mechanism are accommodated. Fluid is drawn from the outside of the housing into the scroll chamber. In Japanese Patent Application Publication No. H02-227575, a refrigerant serves as the fluid.

The driving scroll is configured to be driven to rotate about a driving axis by the driving mechanism. The driven scroll is eccentric to the driving scroll, and is driven to rotate about a driven axis by the driving scroll and the driven mechanism. The driving scroll and the driven scroll are both rotated to change the volume of the compression chamber to compress the fluid with the rotation of the driving scroll and the rotation of the driven scroll. The driving mechanism includes a stator and a rotor. The stator has a cylindrical shape and extends in the direction of the driving axis, and is fixed in the scroll chamber. The rotor has a cylindrical shape and extends in the direction of the driving axis. The rotor has a diameter smaller than a diameter of the stator, and is disposed in the stator.

The housing of the compressor includes a protrusion. The protrusion protrudes into the scroll chamber in the direction of the driving axis toward the driving scroll and the driven scroll. The protrusion has therein a discharge passage that extends in the direction of the driving axis. The discharge passage has opposite ends that define the discharge passage in the direction of the driving axis, and one and the other of the opposite ends of the discharge passage are respectively in communication with the discharge chamber and the outside of the housing.

The driving scroll of the compressor includes a cover body. The cover body includes an extending portion that has a cylindrical shape. The extending portion has an outer peripheral surface to which the rotor is fixed. The protrusion extends into the extending portion. The driving scroll is rotatably supported by the protrusion via the cover body. The driving scroll has a suction port. The suction port is in communication with the scroll chamber and the compression chamber.

In the compressor, the rotor of the driving mechanism rotates, so that the driving scroll is rotated together with the rotor about the driving axis. The driven scroll is driven to rotate about the driven axis by the driving scroll and the driven mechanism. The driving scroll and the driven scroll are both rotated to change the volume of the compression chamber. The fluid in the scroll chamber flows from one side of the compressor to the other side of the compressor along the direction of the driving axis, and is drawn into the compression chamber through the suction port. The fluid is compressed in the compression chamber, and is discharged to the outside of the housing through the discharge passage.

In this type of compressor, it is necessary to suppress the performance degradation of the driving mechanism due to heat generation during operation of the driving mechanism. In such a known compressor, when the fluid in the scroll chamber is drawn into the suction port, the fluid flows between the stator and the rotor along the direction of the driving axis. The fluid may cool the stator and the rotor of the compressor, i.e., the driving mechanism, but the fluid may not sufficiently cool the driving mechanism. Accordingly, this compressor may be unlikely to achieve sufficient reliability.

The present disclosure, which has been made in light of the above-mentioned problem, is directed to providing a co-rotating scroll compressor that has excellent reliability.

SUMMARY

In accordance with an aspect of the present disclosure, there is provided a co-rotating scroll compressor comprising: a housing having a scroll chamber into which fluid is drawn from outside of the housing; a driving mechanism accommodated in the scroll chamber; a driven mechanism accommodated in the scroll chamber; a driving scroll accommodated in the scroll chamber; and a driven scroll accommodated in the scroll chamber. The driving mechanism includes: a stator; and a rotor disposed outward of the stator to surround the stator. The rotor is rotated by the stator. The stator includes: a stator core; a first coil end; and a second coil end. The stator core has a cylindrical shape centered about a driving axis and extends in a direction of the driving axis. The first coil end has a cylindrical shape and extends from the stator core toward one side of the co-rotating scroll compressor along the direction of the driving axis. The second coil end has a cylindrical shape and extends from the stator core toward the other side of the co-rotating scroll compressor opposite to the one side along the direction of the driving axis. The driving scroll is configured to be rotated by the driving mechanism about the driving axis. The driven scroll is eccentric to the driving scroll. The driven scroll is configured to be rotated by the driving scroll and the driven mechanism about a driven axis. The driving scroll and the driven scroll form a compression chamber for compressing the fluid with rotation of the driving scroll and rotation of the driven scroll. A protrusion is provided in the scroll chamber. The protrusion protrudes toward the driving scroll and the driven scroll in the direction of the driving axis, and is fixed to the stator core. The driving scroll includes a cover body that rotates together with the rotor. The cover body includes a wall portion that extends in a radial direction of the driving scroll and faces the first coil end in the direction of the driving axis. The wall portion is connected to a cylindrical portion having a cylindrical shape. The cylindrical portion extends in the direction of the driving axis and surrounds the first coil end that is radially inward of the cylindrical portion in the radial direction of the driving scroll. Rotation of the rotor is transmitted to the cover body via the cylindrical portion. The wall portion has a suction port that is radially inward of the cylindrical portion in the radial direction of the driving scroll. The fluid in the scroll chamber is drawn into the compression chamber through the suction port. A first suction passage is formed between the housing and the rotor in the radial direction of the driving scroll. The fluid flows from the cover body toward the rotor through the first suction passage in the direction of the driving axis in the scroll chamber. A second suction passage is formed between the rotor and the stator in the radial direction of the driving scroll. The fluid that has flowed through the first suction passage flows from the rotor toward the cover body in the direction of the driving axis and is guided to the suction port through the second suction passage.

Other aspects and advantages of the disclosure will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

The disclosure, together with objects and advantages thereof, may best be understood by reference to the following description of the embodiments together with the accompanying drawings in which:

FIG. 1 is a sectional view of a compressor according to a first embodiment;

FIG. 2 is an enlarged sectional view of the compressor according to the first embodiment, illustrating a main part of the compressor including a stator and a rotor;

FIG. 3 is a sectional view of a compressor according to a second embodiment; and

FIG. 4 is a sectional view of a compressor according to a third embodiment.

DETAILED DESCRIPTION OF THE EMBODIMENTS

The following will describe first to third embodiments of the present disclosure in detail with reference to the accompanying drawings. A compressor according to each of the first to third embodiments is mounted on a vehicle (not illustrated) and included in an air conditioning device for the vehicle.

First Embodiment

FIG. 1 illustrates a compressor according to the first embodiment. The compressor includes a housing 6, an electric motor 10, a driving scroll 30, a driven scroll 40, and a driven mechanism 20. The electric motor 10 serves as the driving mechanism of the present disclosure, for example.

In the present embodiment, the front-rear direction of the compressor is defined by an arrow in FIG. 1. In FIG. 2 and thereafter, the front-rear direction of the compressor corresponds to the front-rear direction in FIG. 1. It is noted that the front-rear direction of the compressor is merely one example for convenience of explanation, and a posture of the compressor may be changed, as appropriate, depending on a vehicle on which the compressor is mounted.

As illustrated in FIG. 1, the housing 6 includes a housing body 60, a first housing cover 61, and a second housing cover 62. The housing body 60 servers as the main body of the present disclosure, for example.

The housing body 60 is made of aluminum alloy. The housing body 60 has a cylindrical shape centered about a driving axis O1, and extends in the direction of the driving axis O1. The front end and the rear end of the housing body 60 are open ends. The driving axis O1 is parallel to the front-rear direction. In the present embodiment, the front side and the rear side of the compressor respectively serve as one side and the other side of the compressor along the direction of the driving axis of the present disclosure, for example.

The housing body 60 has an outer peripheral surface 601 and an inner peripheral surface 602. The housing body 60 includes: a first housing portion 60a having a first inner diameter L1; and a second housing portion 60b having a second inner diameter L2. The second inner diameter L2 is greater than the first inner diameter L1. The second housing portion 60b extends from the first housing portion 60a in the direction of the driving axis O1.

The first housing portion 60a is located at the front end of the housing body 60 (i.e., on the one side along the direction of the driving axis O1 with respect to a rotor 11), and the second housing portion 60b is located at the rear end of the housing body 60 (i.e., on the other side along the direction of the driving axis O1 with respect to the first housing portion 60a). The housing body 60 has an inner diameter that gradually increases from the first housing portion 60a to the second housing portion 60b in the direction of the driving axis O1, so that the second inner diameter L2 of the second housing portion 60b is greater than the first inner diameter L1 of the first housing portion 60a. That is, the housing body 60 is shaped so that the inner diameter of the housing body 60 increases from the first inner diameter L1 at the front end of the housing body 60 to the second inner diameter L2 at the rear end of the housing body 60. Although the inner diameter of the housing body 60 is enlarged in such a manner, an outer diameter of the housing body 60 remains constant. The second housing portion 60b faces the rotor 11 in the radial direction of the driving scroll 30.

The housing body 60 has a suction communication port 81. The suction communication port 81 is located on the other side with respect to the center of the housing body 60 in the direction of the driving axis O1. That is, the suction communication port 81 is located on the rear side with respect to the center of the housing body 60 in the direction of the driving axis O1. The suction communication port 81 extends in the radial direction of the housing body 60 and connects the inside and the outside of the housing body 60. The suction communication port 81 is connected to an evaporator (not illustrated) via a pipe (not illustrated).

The first housing cover 61 is made of steel. The first housing cover 61 is located at the rear end of the housing body 60. The first housing cover 61 has an approximately disc shape centered about the driving axis O1. The first housing cover 61 has opposite surfaces, i.e., a front surface 61a facing forward and a rear surface 61b facing rearward, which define the first housing cover 61 in the front-rear direction.

The housing 6 includes a protrusion 64 located within the housing 6. Specifically, the protrusion 64 is formed integrally with the first housing cover 61. The protrusion 64 is made of steel. The protrusion 64 has a solid cylindrical shape, and protrudes forward from the center of the front surface 61a in the direction of the driving axis O1. The protrusion 64 has a first diameter portion 64a and a second diameter portion 64b.

The first diameter portion 64a forms the front portion of the protrusion 64. As illustrated in FIG. 2, the first diameter portion 64a has a diameter smaller than a diameter of an insertion hole 375, which will be described later. The first diameter portion 64a has a pin hole 4. The pin hole 4 extends inside the first diameter portion 64a in the direction of the driving axis O1, and opens at the front end surface of the first diameter portion 64a.

The first diameter portion 64a has an outer peripheral surface on which a first radial ball bearing 51 is provided. Instead of the first radial ball bearing 51, a plain bearing may be provided on the outer peripheral surface of the first diameter portion 64a.

The second diameter portion 64b is formed integrally with the first diameter portion 64a and located behind the first diameter portion 64a. That is, the second diameter portion 64b forms 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 has a diameter greater than a diameter of the first diameter portion 64a.

As illustrated in FIG. 1, the second housing cover 62 is disposed in front of the housing body 60. The second housing cover 62 is made of aluminum alloy. The second housing cover 62 has an approximately disc shape centered about the driving axis O1. The second housing cover 62 has opposite surfaces, i.e., a front surface 62a facing forward and a rear surface 62b facing rearward, which define the second housing cover 62 in the front-rear direction.

The second housing cover 62 has a support portion 66 and a discharge communication port 83. The support portion 66 is formed integrally with the rear surface 62b at approximately the center of the rear surface 62b, and extends rearward from the rear surface 62b. The support portion 66 has a cylindrical shape centered about the driving axis O1, and has therein a second radial ball bearing 52 and a shaft seal member 63. In the support portion 66, the shaft seal member 63 is in front of the second radial ball bearing 52. The shaft seal member 63 has an annular shape. Instead of the second radial ball bearing 52, a plain bearing may be disposed inside the support portion 66.

The discharge communication port 83 is formed through the second housing cover 62 in the direction of the driving axis O1, and connects the inside of the support portion 66 and the outside of the second housing cover 62. The discharge communication port 83 is connected to a condenser (not illustrated) via a pipe (not illustrated).

In the housing 6, the front surface 61a of the first housing cover 61 and the rear surface 62b of the second housing cover 62 are respectively in contact with the rear end of the housing body 60 and the front end of the housing body 60. The first housing cover 61 and the second housing cover 62 are fixed to the housing body 60 in the direction of the driving axis O1 by a plurality of bolts (not illustrated).

Accordingly, the housing body 60 of the housing 6 is held by and between the first housing cover 61 and the second housing cover 62 in the front-rear direction, and the front end and the rear end of the housing body 60 are closed by the first housing cover 61 and the second housing cover 62, respectively. A scroll chamber 65 is formed inside the housing body 60 of the housing 6. The scroll chamber 65 is in communication with the suction communication port 81. Accordingly, a refrigerant is drawn into the scroll chamber 65 from the outside of the housing 6 through the suction communication port 81. The refrigerant serves as the fluid of the present disclosure, for example.

The protrusion 64 is provided in the scroll chamber 65, and protrudes from the first housing cover 61 in the direction of the driving axis O1. Specifically, the protrusion 64 protrudes forward from the first housing cover 61 toward the driving scroll 30 and the driven scroll 40.

The electric motor 10 is accommodated in the scroll chamber 65. The scroll chamber 65 serves as a motor chamber in which the electric motor 10 is accommodated.

As illustrated in FIG. 2, the electric motor 10 includes a stator 17 and the rotor 11. The stator 17 includes a stator core 17a and a winding 17b. The stator core 17a has a cylindrical shape centered about the driving axis O1, and extends in the direction of the driving axis O1. The winding 17b is wound around the stator core 17a. The winding 17b of the stator 17 includes a first coil end 171 and a second coil end 172.

The first coil end 171 has a cylindrical shape, and extends forward (i.e., toward the one side) from the stator core 17a along the direction of the driving axis O1. 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 has a cylindrical shape, and extends rearward from the stator core 17a along the direction of the driving axis O1. That is, the first coil end 171 and the second coil end 172 respectively extend from the stator core 17a toward the one side and the other side opposite to the one side along the direction of the driving axis O1.

The stator core 17a of the stator 17 is fitted onto the outer peripheral surface of the second diameter portion 64b. Accordingly, the stator core 17a is fixed to the second diameter portion 64b of the protrusion 64. Although not illustrated, a plurality of slits extending in the direction of the driving axis O1 is formed on the inner peripheral surface of the stator core 17a. This configuration allows a space to be formed between the slits and the outer peripheral surface of the second diameter portion 64b with the stator core 17a fixed to the second diameter portion 64b.

As illustrated in FIG. 2, the rotor 11 includes a rotor body 11a, a plurality of magnetic cores 11b, a first holding plate 11c, and a second holding plate 11d. FIG. 2 illustrates one of the magnetic cores 11b. In FIGS. 1, 3, and 4, the shape of the rotor 11 is illustrated in a simplified form.

As illustrated in FIG. 2, the rotor body 11a of the rotor 11 is formed of a plurality of electromagnetic steel sheets 111 stacked on top of each other in the direction of the driving axis O1, and each of the electromagnetic steel sheets 111 has an approximately disc shape. Accordingly, the rotor body 11a has an approximately cylindrical shape and extends in the direction of the driving axis O1. The electromagnetic steel sheets 111 (i.e., the rotor body 11a) have a plurality of magnetic core chambers 112 and a plurality of first bolt holes 113.

Each of the magnetic cores 11b has a columnar shape, and extends in the direction of the driving axis O1. Each of the magnetic cores 11b is accommodated in a corresponding one of the magnetic core chambers 112. The first holding plate 11c and the second holding plate 11d each have a disc shape and are made of a metal plate. The first holding plate 11c is disposed in front of the rotor body 11a. The second holding plate 11d is disposed behind the rotor body 11a. The first holding plate 11c has a plurality of through holes 114 corresponding to the plurality of first bolt holes 113, and the second holding plate 11d has a plurality of through holes 115. The through holes 114 and the through holes 115 correspond to the first bolt holes 113.

The first holding plate 11c and the second holding plate 11d hold therebetween the rotor body 11a in the front-rear direction with each of the through holes 114 and each of the through holes 115 aligned with the corresponding first bolt hole 113 in the front-rear direction. The rotor body 11a is fastened with the first holding plate 11c and the second holding plate 11d in the front-rear direction by rivets (not illustrated) so that the rotor body 11a is integrated with the first holding plate 11c and the second holding plate 11d. The front end and the rear end of each of the magnetic core chambers 112 are closed by the first holding plate 11c and the second holding plate 11d. This configuration prevents the magnetic core 11b from falling off from the magnetic core chamber 112. In this way, the rotor 11 is formed.

Each of the electromagnetic steel sheet 111, the first holding plate 11c, and the second holding plate 11d has a diameter that is greater than a diameter of the stator core 17a. That is, the rotor 11 has a cylindrical shape, and has a diameter greater than the diameter of the stator core 17a. The rotor 11 has an outer peripheral surface 110a and an inner peripheral surface 110b. In the scroll chamber 65, the rotor 11 is disposed outward of the stator 17 to surround the stator core 17a of the stator 17 in the radial direction of the driving scroll 30. The rotor 11 is rotated by the stator 17.

As illustrated in FIG. 1, the driving scroll 30 is accommodated in the scroll chamber 65. The driving scroll 30 is made of metal, such as aluminum alloy. The driving scroll 30 includes a driving scroll end plate 31, a driving scroll body 33, a driving scroll peripheral wall 35, a cover body 37, and a case 39.

The driving scroll end plate 31 has an approximately disc shape, and is perpendicular to the driving axis O1 and a driven axis O2. The driven axis O2 is eccentric and parallel to the driving axis O1. That is, the driven axis O2 is parallel to the front-rear direction. The driving scroll end plate 31 has opposite surfaces, i.e., a first front surface 311 facing forward and a first rear surface 312 facing rearward, which define the driving scroll end plate 31 in the front-rear direction.

The driving scroll end plate 31 has a discharge port 32. The discharge port 32 is formed through the driving scroll end plate 31 in the direction of the driving axis O1. A discharge reed valve 57 and a retainer 58 are fixed to the first front surface 311 of the driving scroll end plate 31 by a fixing bolt 59. This configuration allows the discharge reed valve 57 to open and close the discharge port 32. The retainer 58 adjusts the opening degree of the discharge reed valve 57.

The driving scroll body 33 is integrated with the driving scroll end plate 31, and extends rearward from the first rear surface 312 of the driving scroll end plate 31 toward the driven scroll 40 and parallel to the driving axis O1 and the driven axis O2. Although not illustrated in detail, the driving scroll body 33 has a spirally extending shape centered about the center of the driving scroll end plate 31, and radially outwardly extending from the center of the spiral shape.

The driving scroll peripheral wall 35 has a cylindrical shape centered about the driving axis O1, and extends in parallel to the driving axis O1 and the driven axis O2. The front end of the driving scroll peripheral wall 35 is integrated with the outer peripheral edge of the driving scroll end plate 31. The driving scroll peripheral wall 35 has a cylindrical shape, extends rearward from the first rear surface 312, and radially surrounds the driving scroll body 33. Although not illustrated, the outer peripheral end of the driving scroll body 33 is connected to the inner peripheral surface of the driving scroll peripheral wall 35.

The cover body 37 includes a wall portion 37a, an inner cylindrical portion 37b, and an outer cylindrical portion 37c. The outer cylindrical portion 37c serves as the cylindrical portion of the present disclosure, for example.

The wall portion 37a has an approximately plate-like shape, and extends in the radial direction of the driving scroll 30. The wall portion 37a faces the first coil end 171 in the direction of the driving axis O1. The wall portion 37a has opposite surfaces, i.e., a second front surface 371 facing forward and a second rear surface 372 facing rearward, which define the wall portion 37a in the front-rear direction.

The wall portion 37a has a recess 373 and a suction port 374. The recess 373 is located approximately in the center of the second front surface 371 and recessed rearward in the second front surface 371.

The suction port 374 is located radially outward of the recess 373 in the radial direction of the driving scroll 30. The suction port 374 is formed through the wall portion 37a in the front-rear direction, and the front end and the rear end of the suction port 374 are respectively open at the second front surface 371 and the second rear surface 372. The suction port 374 is formed only in the wall portion 37a. In the present embodiment, the single suction port 374 is formed in the wall portion 37a, however; a plurality of the suction ports 374 may be formed in the wall portion 37a.

In the wall portion 37a, a plurality of rings 22 is disposed between the recess 373 and the suction port 374. Although not illustrated in detail, the rings 22 are arranged at equal intervals in the circumferential direction of the recess 373 so as to surround the recess 373 with the rings 22 facing forward. In the present embodiment, the six rings 22 are provided. FIGS. 1, 3, and 4 illustrate one of the six rings 22.

The inner cylindrical portion 37b is located inward of the stator 17 in the radial direction of the cover body 37. The inner cylindrical portion 37b has a cylindrical shape, and extends rearward from the second rear surface 372 of the wall portion 37a in the direction of the driving axis O1. The inner cylindrical portion 37b has a diameter greater than the diameter of the first diameter portion 64a of the protrusion 64 and smaller than the diameter of the second diameter portion 64b. The inner cylindrical portion 37b has an inner diameter that is approximately equal to an outer diameter of the first radial ball bearing 51. An outer diameter of the inner cylindrical portion 37b may be approximately equal to or greater than the outer diameter of the second diameter portion 64b.

The cover body 37 has an insertion hole 375. The insertion hole 375 extends in the direction of the driving axis O1, and connects the inner cylindrical portion 37b and the recess 373.

The outer cylindrical portion 37c is integrated with the wall portion 37a at the outer peripheral edge of the wall portion 37a. Accordingly, the outer cylindrical portion 37c is connected to the wall portion 37a, has a cylindrical shape, and extends rearward from the wall portion 37a in the direction of the driving axis O1. The outer cylindrical portion 37c has an outer diameter that is approximately equal to an outer diameter of the driving scroll peripheral wall 35 and an outer diameter of the rotor 11.

The outer cylindrical portion 37c has an inner diameter that is greater than the outer diameter of the inner cylindrical portion 37b. In the cover body 37, the inner cylindrical portion 37b is disposed radially inward of the outer cylindrical portion 37c and spaced apart from the outer cylindrical portion 37c in the radial direction of the driving scroll 30. Accordingly, an accommodation portion 38 is formed in the cover body 37 by the wall portion 37a, the inner cylindrical portion 37b, and the outer cylindrical portion 37c. The accommodation portion 38 has a bottomed annular shape, and opens rearward.

The suction port 374 of the wall portion 37a is located radially outward of the inner cylindrical portion 37b and inward of the outer cylindrical portion 37c in the radial direction of the driving scroll 30. Accordingly, the suction port 374 is in communication with the accommodation portion 38 at a position between the inner cylindrical portion 37b and the outer cylindrical portion 37c.

The outer cylindrical portion 37c has a plurality of second bolt holes 376. Each of the second bolt holes 376 is formed through the outer cylindrical portion 37c in the direction of the driving axis O1. Although not illustrated, the number of second bolt holes 376 is equal to the number of first bolt holes 113 of the rotor 11. FIGS. 1 to 4 illustrate one of the first bolt holes 113 and one of the second bolt holes 376.

As illustrated in FIG. 1, the front end of the outer cylindrical portion 37c of the cover body 37 is in contact with the rear end of the driving scroll peripheral wall 35. The rear end of the outer cylindrical portion 37c of the cover body 37 is in contact with the rotor 11, more specifically, in contact with the first holding plate 11c. The first bolt 34a is inserted through the through hole 115 of the second holding plate 11d, the first bolt hole 113 of the rotor 11, the through hole 114 of the first holding plate 11c, and the second bolt hole 376 of the outer cylindrical portion 37c in this order, and is screwed into the driving scroll peripheral wall 35. In this way, the cover body 37 is held by and fixed to the driving scroll peripheral wall 35 and the rotor 11 in the front-rear direction. Accordingly, the driving scroll 30 is integrated with the rotor 11, so that the cover body 37 rotates together with the rotor 11.

The case 39 is a bottomed tubular member, and has an outer peripheral wall 39a and a front wall 39b. The outer peripheral wall 39a has a cylindrical shape centered about the driving axis O1. The outer peripheral wall 39a has an outer diameter that is approximately equal to the outer diameter of the driving scroll peripheral wall 35.

The front wall 39b is located at the front end of the case 39. The front wall 39b has an approximately disc shape, and is perpendicular to the driving axis O1 and the driven axis O2. The outer peripheral edge of the front wall 39b is connected to the front end of the outer peripheral wall 39a. The front wall 39b has a boss 39c. The boss 39c is formed integrally with the front wall 39b at the center of the front wall 39b, and extends forward from the front wall 39b in the direction of the driving axis O1. The boss 39c has an outer diameter that is approximately equal to an inner diameter of the second radial ball bearing 52 and an inner diameter of the shaft seal member 63. The boss 39c has a discharge passage 390. The discharge passage 390 is formed through the boss 39c in the direction of the driving axis O1.

The outer peripheral wall 39a and the front wall 39b cooperate to have a plurality of third bolt holes 39d. Each of the third bolt holes 39d is formed through the outer peripheral wall 39a and the front wall 39b in the direction of the driving axis O1. FIGS. 1, 3, and 4 illustrate one of the third bolt holes 39d.

As illustrated in FIG. 1, the rear surface of the outer peripheral wall 39a of the case 39 is in contact with the front end of the driving scroll peripheral wall 35. A second bolt 34b is inserted through the third bolt hole 39d, and is screwed into the driving scroll peripheral wall 35. In this way, the case 39 is fixed to the driving scroll peripheral wall 35 of the driving scroll 30.

The case 39 has a discharge chamber 14 that is defined by the driving scroll end plate 31 and the outer peripheral wall 39a and the front wall 39b of the case 39. The discharge chamber 14 is in communication with the discharge port 32 and the discharge passage 390.

The case 39 is spaced apart from the cover body 37 in the front-rear direction, and the driving scroll body 33 and the driving scroll peripheral wall 35 of the driving scroll 30 are disposed between the case 39 and the cover body 37. That is, in the present embodiment, the case 39 is located on the front side (i.e., on the one side) along the direction of the driving axis O1 with respect to the cover body 37. Since the rotor 11 is fixed to the outer cylindrical portion 37c of the cover body 37, the case 39 having the discharge chamber 14 is spaced apart from the rotor 11 in the front-rear direction.

The driven scroll 40 is made of aluminum alloy. The driven scroll 40 includes a driven scroll end plate 41 and a driven scroll body 43.

The driven scroll end plate 41 has an approximately disc shape, and is perpendicular to the driving axis O1 and the driven axis O2. The driven scroll end plate 41 has opposite surfaces, i.e., a third front surface 411 facing forward and a third rear surface 412 facing rearward, which define the driven scroll end plate 41 in the front-rear direction.

The driven scroll end plate 41 has an accommodation recess 15. The accommodation recess 15 is located in the center of the driven scroll end plate 41. The accommodation recess 15 has a circular shape centered about the driven axis O2, and is recessed forward in the third rear surface 412 of the driven scroll end plate 41. The accommodation recess 15 faces rearward, i.e., faces the first diameter portion 64a of the protrusion 64.

As illustrated in FIG. 2, a driven shaft 16 is disposed in the accommodation recess 15. The driven shaft 16 includes a bushing 53 and a driven pin 55. The bushing 53 is accommodated in the accommodation recess 15 via a plain bearing 13. The driven pin 55 is inserted through the bushing 53. Specifically, the driven pin 55 is inserted into the center of the bushing 53 eccentric to the driven axis O2. The driven pin 55 protrudes rearward from the bushing 53, i.e., the driven scroll end plate 41.

As illustrated in FIG. 1, a plurality of pivot pins 21, which, in the present embodiment, six pivot pins 21, is each fixed to the driven scroll end plate 41 at a position facing the ring 22. The pivot pins 21 protrude rearward from the third rear surface 412. The number of pivot pins 21 corresponds to the number of rings 22. FIGS. 1, 3, and 4 illustrate one of the six pivot pins 21.

As illustrated in FIG. 1, the pivot pins 21 and the rings 22 cooperate to form the driven mechanism 20. The driven mechanism 20 is accommodated in the scroll chamber. As long as at least three pivot pins 21 and three rings 22 are provided, their numbers may be appropriately designed.

The driven scroll body 43 is integrated with the driven scroll end plate 41, and extends forward from the third front surface 411 of the driven scroll end plate 41 and parallel to the driving axis O1 and the driven axis O2. The driven scroll body 43 has a spirally extending shape centered about the center of the driven scroll end plate 41 and radially outwardly extending from the center of the spiral shape.

In the compressor, the driven scroll 40 is accommodated in the driving scroll 30, more specifically, accommodated between the cover body 37 and the driving scroll body 33 and the driving scroll peripheral wall 35 of the driving scroll 30. The driving scroll body 33 is meshed with the driven scroll body 43. The driving scroll body 33 faces and cooperates with the driven scroll body 43 to form a compression chamber 12.

A suction space 30a is formed between the driving scroll peripheral wall 35 and the driven scroll 40. That is, the driving scroll body 33 and the driven scroll body 43 are located within the suction space 30a. The suction space 30a is separated from the scroll chamber 65 by the driving scroll peripheral wall 35 and the cover body 37, and is also separated from the discharge chamber 14 by the driving scroll end plate 31. The suction space 30a is in communication with the suction port 374.

The driven scroll 40 is accommodated in the driving scroll 30, so that each of the pivot pins 21 is disposed in a corresponding one of the rings 22. The driving scroll 30 is assembled with the driven scroll 40 in the front-rear direction, so that the driving scroll 30 and the driven scroll 40 cooperate to form a scroll compression part 100. Specifically, the driving scroll body 33 is meshed with the driven scroll body 43, and the pivot pin 21 is placed in the ring 22. The cover body 37 of the driving scroll 30 is then fixed to the driving scroll peripheral wall 35 and the rotor 11.

This configuration allows the accommodation recess 15 and the driven shaft 16 of the driven scroll end plate 41 to face the recess 373 of the cover body 37.

In the scroll chamber 65, the driving scroll 30 is in front of the stator 17. As illustrated in FIG. 2, in the driving scroll 30, the inner cylindrical portion 37b of the cover body 37 is radially inward of the first coil end 171. The first radial ball bearing 51 is inserted into the inner cylindrical portion 37b. Accordingly, the cover body 37 is rotatably supported by the first diameter portion 64a via the first radial ball bearing 51. The accommodation portion 38 is in communication with the scroll chamber 65. The front portion of the first diameter portion 64a is inserted into the insertion hole 375.

The cover body 37 is supported by the first diameter portion 64a, so that the first coil end 171 is accommodated in the accommodation portion 38. Accordingly, the first coil end 171 is covered from the front by the wall portion 37a in the accommodation portion 38, and is radially covered from the inside by the inner cylindrical portion 37b of the driving scroll 30. In the accommodation portion 38, the first coil end 171 is radially inward of and surrounded by the outer cylindrical portion 37c in the radial direction of the driving scroll 30. The rotation of the rotor 11 is transmitted to the cover body 37 via the outer cylindrical portion 37c.

In the compressor, 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 37c are radially arranged in this order from the driving axis O1 along the radial direction of the driving scroll 30 with the cover body 37 supported by the first diameter portion 64a. 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 37c overlap each other in the radial direction of the driving scroll 30.

As illustrated in FIG. 1, in the driving scroll 30, the boss 39c of the case 39 is inserted through the second radial ball bearing 52 and the shaft seal member 63. The case 39 is rotatably supported by the support portion 66 via the second radial ball bearing 52. Accordingly, the driving scroll 30 is disposed in the scroll chamber 65 and supported by both the protrusion 64 and the support portion 66 of the housing 6 such that the driving scroll 30 is rotatable about the driving axis O1.

In the driven scroll 40, the driven pin 55 is inserted into the pin hole 4 of the driven shaft 16. The driven scroll 40 is disposed in the scroll chamber 65 and supported by the first diameter portion 64a of the protrusion 64 such that the driven scroll 40 is rotatable about the driven axis O2. That is, unlike the driving scroll 30, the driven scroll 40 is supported only by the protrusion 64 of the housing 6 such that the driven scroll 40 is rotatable about the driven axis O2.

In the compressor, in order to ensure the rotations of the rotor 11 and the driving scroll 30 about the driving axis O1, the outer peripheral surface 110a of the rotor 11 is spaced apart from the inner peripheral surface 602 of the housing body 60 in the radial direction of the driving scroll 30 with the rotor 11 and the driving scroll 30 disposed in the scroll chamber 65. Similarly, the outer cylindrical portion 37c of the cover body 37, the driving scroll peripheral wall 35, and the outer peripheral wall 39a of the case 39 are spaced apart from the inner peripheral surface 602 of the housing 6 in the radial direction of the driving scroll 30.

The rotor 11 is disposed radially outward of the stator 17 in the radial direction of the driving scroll 30, and the inner peripheral surface 110b of the rotor 11 is spaced apart from the outer peripheral surface of the stator core 17a in the radial direction of the driving scroll 30.

The compressor has a first suction passage 71 that is formed between the outer peripheral surface 110a of the rotor body 11a of the rotor 11 and the inner peripheral surface 602 of the housing body 60 of the housing 6 in the radial direction of the driving scroll 30. The compressor also has a second suction passage 72 formed between the inner peripheral surface 110b of the rotor body 11a of the rotor 11 and the outer peripheral surface of the stator core 17a of the stator 17 in the radial direction of the driving scroll 30.

As previously described, the housing body 60 is shaped so that the inner diameter of the housing body 60 increases from the first inner diameter L1 at the front end of the housing body 60 to the second inner diameter L2 at the rear end of the housing body 60. Accordingly, the distance between the outer peripheral surface 110a of the rotor 11 and the inner peripheral surface 602 of the housing body 60 in the radial direction of the driving scroll 30 (i.e., a width of the first suction passage 71) is wider than the distance between the outer cylindrical portion 37c and the inner peripheral surface 602, the distance between the driving scroll peripheral wall 35 and the inner peripheral surface 602, and the distance between the outer peripheral wall 39a and the inner peripheral surface 602 in the radial direction of the driving scroll 30. The width of the first suction passage 71 gradually increases toward the rear in the direction of the driving axis O1.

The width of the first suction passage 71 is wider than the distance between the inner peripheral surface 110b of the rotor 11 and the stator core 17a in the radial direction of the driving scroll 30 (i.e., a width of the second suction passage 72). Unlike the width of the first suction passage 71, the width of the second suction passage 72 remains constant.

In the compressor, the width of the first suction passage 71 allows the rotation of the rotor 11 to generate shear force in the refrigerant flowing through the first suction passage 71. That is, in the present embodiment, the housing 6 is spaced apart from the rotor 11 in the radial direction of the driving scroll 30 by a distance that allows the rotation of the rotor 11 to generate shear force in the refrigerant flowing through the first suction passage 71. Specifically, the maximum width of the first suction passage 71 is approximately 1 mm. The maximum width of the second suction passage 72 is approximately 0.5 mm. The width of the first suction passage 71 may be appropriately designed, as long as the width of the first suction passage 71 is sufficient to allow the rotation of the rotor 11 to generate shear force in the refrigerant flowing through the first suction passage 71. For ease of explanation, in FIGS. 1 to 4, the width of the first suction passage 71 and the width of the second suction passage 72 are exaggeratedly illustrated.

In the compressor, the driving scroll 30 and the rotor 11 are disposed in the scroll chamber 65, and the suction communication port 81 faces the front portion of the rotor 11 in the radial direction of the driving scroll 30. That is, the suction communication port 81 is located closer to the rotor 11 (i.e., the cover body 37) than to the case 39 in the direction of the driving axis O1. The suction communication port 81 is in direct communication with the first suction passage 71.

In the compressor, the refrigerant at low temperature and low pressure via the evaporator is drawn into the scroll chamber 65 through the suction communication port 81 as indicated by dashed arrows in FIGS. 1 and 2. In the scroll chamber 65, the rotation of the rotor 11 of the electric motor 10 is transmitted to the driving scroll 30, so that the driving scroll 30 rotates about the driving axis O1. That is, the driving scroll 30 and the rotor 11 rotate together about the driving axis O1. In the driven mechanism 20, the pivot pin 21 slides on the inner peripheral surface of the ring 22 and allows the ring 22 to rotate about and relative to the center of the pivot pin 21. Thus, the driven mechanism 20 transmits torque of the driving scroll 30 to the driven scroll 40.

Accordingly, the driven scroll 40 is driven to rotate about the driven axis O2 by the driving scroll 30 and the driven mechanism 20. The driven mechanism 20 prevents the driven scroll 40 from rotating relative to the driving scroll 30 about its own axis. Accordingly, the driven scroll 40 orbits relative to the driving scroll 30 about the driven axis O2. The driving scroll body 33 and the driven scroll body 43 each rotate in the suction space 30a such that the driving scroll body 33 and the driven scroll body 43 vary the volume of the compression chamber 12.

In the cover body 37 of the compressor, the suction port 374 is located radially inward of the outer cylindrical portion 37c in the radial direction of the driving scroll 30. Accordingly, the refrigerant drawn into the scroll chamber 65 from the suction communication port 81 flows rearward through the first suction passage 71 in the scroll chamber 65. Then, the refrigerant flows toward the suction port 374 (see the dashed arrows in FIGS. 1 and 2). The refrigerant drawn into the scroll chamber 65 through the suction communication port 81 contains lubricating oil. Accordingly, the refrigerant containing the lubricating oil flows rearward through the first suction passage 71 in the scroll chamber 65.

In the compressor, not only a gaseous refrigerant, which is a vapor phase refrigerant, but also a liquid refrigerant, which is a liquid phase refrigerant, may be drawn into the scroll chamber 65 from the suction communication port 81. Accordingly, the liquid refrigerant also flows through the first suction passage 71. In this regard, the compressor according to the present embodiment is capable of evaporating the liquid refrigerant to a gaseous refrigerant in the first suction passage 71, since the rotation of the rotor 11 generates shear force in the refrigerant flowing through the first suction passage 71.

The refrigerant and the lubricating oil flow through the first suction passage 71, and come into contact with the front surface 61a of the first housing cover 61. The refrigerant and the lubricating oil then change their directions toward the front (i.e., from the cover body 37 toward the rotor 11) in the direction of the driving axis O1 in the scroll chamber 65. Accordingly, the refrigerant and the lubricating oil that have flowed through the first suction passage 71 frow toward the front (i.e., from the rotor 11 toward the cover body 37) in the direction of the driving axis O1 in the scroll chamber 65 through the second suction passage 72.

In this way, the refrigerant and the lubricating oil flowing through the second suction passage 72 are guided to the suction port 374 through the second suction passage 72. The refrigerant and the lubricating oil that have flowed through the second suction passage 72 reach the suction port 374 through the accommodation portion 38, and is drawn into the compression chamber 12 from the suction port 374 through the suction space 30a. The refrigerant and the lubricating oil are drawn into the suction space 30a and the compression chamber 12 from the outside of the driven scroll end plate 41 through the suction port 374.

In the compressor, the rotation of the rotor 11 also generates shear force in the refrigerant flowing through the second suction passage 72. Accordingly, even if the liquid refrigerant does not fully evaporate in the first suction passage 71, the remaining liquid refrigerant evaporates in the second suction passage 72. Furthermore, the refrigerant and the lubricating oil, which have flowed through the first suction passage 71, partly flow through the slits of the stator core 17a and reach the accommodation portion 38. The refrigerant and the lubricating oil are then drawn into the compression chamber 12 through the suction port 374.

The compression chamber 12 compresses the gaseous refrigerant enclosed in the compression chamber 12 while reducing its volume with the rotation of the driving scroll 30 and the rotation of the driven scroll 40. The refrigerant highly compressed to a discharge pressure in the compression chamber 12 is discharged into the discharge chamber 14 through the discharge port 32. The lubricating oil in the compression chamber 12 is discharged into the discharge chamber 14 through the discharge port 32 together with the high-pressure refrigerant. The high-pressure refrigerant is then discharged from the discharge chamber 14 to the outside of the compressor through the discharge passage 390 and a discharge communication port 83. In the compressor, the shaft seal member 63 seals the discharge passage 390 and the discharge communication port 83 from the scroll chamber 65, thereby preventing the refrigerant flowing from the discharge passage 390 toward the discharge communication port 83 from flowing into the scroll chamber 65.

In the compressor, the rotor 11 is suitably cooled by the low-temperature refrigerant, which is drawn into the scroll chamber 65 from the suction communication port 81 and flows rearward through the first suction passage 71. Furthermore, the rotor 11 and the stator 17 are suitably cooled by the low-temperature refrigerant flowing forward through the second suction passage 72.

That is, in the compressor, the rotor 11 is cooled not only from the outer peripheral surface 110a of the rotor 11 by the refrigerant flowing through the first suction passage 71, but also cooled from the inner peripheral surface 110b of the rotor 11 by the refrigerant flowing through the second suction passage 72. Thus, the rotor 11 of the compressor is sufficiently cooled by the low-temperature refrigerant.

In the compressor, the second coil end 172 of the stator 17 is suitably cooled by the refrigerant flowing toward the second suction passage 72 through the first suction passage 71. The first coil end 171 of the stator 17 is suitably cooled by the refrigerant in the accommodation portion 38 before the suction port 374. Accordingly, the stator core 17a, the first coil end 171, and the second coil end 172 of the stator 17 are sufficiently cooled by the low-temperature refrigerant.

In this way, the compressor sufficiently cools the electric motor 10 with the refrigerant flowing through the first suction passage 71 and the second suction passage 72, thereby suppressing the performance degradation of the electric motor 10 due to heat generation.

Therefore, the compressor according to the first embodiment has excellent reliability.

In particular, in the compressor, the rotor body 11a is formed of the electromagnetic steel sheets 111 stacked in the direction of the driving axis O1. The refrigerant flows through the first suction passage 71 and the second suction passage 72, so that the refrigerant comes into direct contact with the rotor body 11a, i.e., the electromagnetic steel sheets 111. This allows the rotor 11 of the electric motor 10 of the compressor to be sufficiently cooled by the refrigerant.

This eliminates the need to increase the size of the rotor body 11a of the rotor 11 to suppress core loss in the rotor body 11a due to heat. Furthermore, this eliminates the need to employ a magnetic core with excessively high resistance to demagnetization in order to suppress demagnetization due to heat. This therefore allows miniaturization of the compressor, and reduces manufacturing costs of the compressor.

Furthermore, the high-temperature refrigerant is discharged from the compression chamber 12 into the discharge chamber 14, so that the discharge chamber 14 and the case 39 likely to become hot. In the compressor, the suction communication port 81 is located closer to the rotor 11 (i.e., closer to the cover body 37) than to the case 39 in the direction of the driving axis O1. This configuration reduces the effect of the heat of the discharge chamber 14 and the case 39 on the refrigerant that is drawn into the scroll chamber 65 through the suction communication port 81.

In the compressor, the suction communication port 81 faces the front portion of the rotor 11 in the radial direction of the driving scroll 30, so that the suction communication port 81 is in direct communication with the first suction passage 71. This configuration enables a change in the flow direction of the refrigerant drawn through the suction communication port 81 while causing the refrigerant to come into direct contact with a part of the outer peripheral surface 110a of the rotor 11 in the radial direction of the driving scroll 30, thereby allowing the refrigerant to flow through the first suction passage 71. This allows the rotor 11 of the compressor to be sufficiently cooled by the refrigerant.

In the compressor, the housing body 60 is shaped so that the inner diameter of the housing body 60 increases from the first inner diameter L1 at the front end of the housing body 60 to the second inner diameter L2 at the rear end of the housing body 60. Accordingly, the width of the first suction passage 71 (i.e., the distance between the outer peripheral surface 110a of the rotor 11 and the inner peripheral surface 602 of the housing body 60 in the radial direction of the driving scroll 30) is wider than the distance between the outer cylindrical portion 37c and the inner peripheral surface 602, the distance between the driving scroll peripheral wall 35 and the inner peripheral surface 602, and the distance between the outer peripheral wall 39a and the inner peripheral surface 602 in the radial direction of the driving scroll 30. This configuration causes the lubricating oil to be less likely to remain in the first suction passage 71, thereby facilitating the flow of the refrigerant in the first suction passage 71.

In particular, the width of the first suction passage 71 gradually increases toward the rear in the front-rear direction. In such a way, the inner surface of the first suction passage 71, i.e., the inner peripheral surface 602 of the housing body 60 gradually becomes distant from the rotor 11 in the radial direction of the driving scroll 30. This shape suitably guides the lubricating oil to flow rearward in the first suction passage 71. This therefore causes the lubricating oil to be less likely to remain in the first suction passage 71.

Furthermore, in the compressor, the rotation of the rotor 11 of the compressor generates shear force in the refrigerant flowing through the first suction passage 71 and the refrigerant flowing through the second suction passage 72 in order to evaporate the liquid refrigerant. This allows the compressor to suitably prevent the liquid refrigerant from being drawn into the compression chamber 12.

Second Embodiment

As illustrated in FIG. 3, in a compressor according to the second embodiment, the housing body 60 does not have the suction communication port 81. Instead, the second housing cover 62 has a suction communication port 82. The suction communication port 82 is connected to an evaporator (not illustrated) through a pipe (not illustrated).

In the second housing cover 62, the suction communication port 82 is disposed radially outward of the discharge communication port 83. The suction communication port 82 is in communication with the scroll chamber 65 in the direction of the driving axis O1. Accordingly, the suction communication port 82 is in front of and faces the front wall 39b of the case 39 in the direction of the driving axis O1.

The compressor has a third suction passage 73 formed in the scroll chamber 65. The third suction passage 73 is defined by the inner peripheral surface 602 of the housing body 60, the outer peripheral wall 39a of the case 39, the driving scroll peripheral wall 35, and the outer cylindrical portion 37c of the cover body 37. The third suction passage 73 is located in front of the first suction passage 71 in the direction of the driving axis O1 (i.e., on the one side along the direction of the driving axis O1 with respect to the first suction passage 71). The width of the third suction passage 73 gradually increases toward the rear in the direction of the driving axis O1. The rear end of the third suction passage 73 is in communication with the front end of the first suction passage 71. It is to be noted that other components of the compressor according to the second embodiment are the same as those of the compressor according to the first embodiment, and components of the second embodiment that correspond to those of the first embodiment are designated by the same reference numerals and will not be further elaborated here.

The refrigerant flows into the scroll chamber 65 from the suction communication port 82. The refrigerant comes into contact with the outer peripheral wall 39a of the case 39 along the direction of the driving axis O1, and flows through the third suction passage 73. The refrigerant flows through the third suction passage 73 rearward toward the first suction passage 71 in the direction of the driving axis O1. Accordingly, in the compressor according to the second embodiment, the electric motor 10 is suitably cooled by the refrigerant flowing into the compression chamber 12 through the first suction passage 71 and the second suction passage 72.

In the compressor according to the second embodiment, the suction communication port 82 is in front of the first suction passage 71. However, the presence of the third suction passage 73 allows the refrigerant flowed into the scroll chamber 65 from the suction communication port 82 to suitably flow into the first suction passage 71. This therefore suitably prevents the refrigerant flowed into the scroll chamber 65 through the suction communication port 82 from remaining in the scroll chamber 65 without flowing through the first suction passage 71.

Furthermore, the lubricating oil in the refrigerant drawn into the scroll chamber 65 from the suction communication port 82 is suitably separated from the refrigerant when the refrigerant in the scroll chamber 65 comes into contact with the outer peripheral wall 39a. Accordingly, the scroll chamber 65 of the driving scroll 30, the first radial ball bearing 51, the second radial ball bearing 52, and the like are suitably lubricated by the lubricating oil. Other operations of this compressor are the same as those of the compressor according to the first embodiment.

Third Embodiment

As illustrated in FIG. 4, in a compressor according to the third embodiment, the housing 6 includes a housing body 68, instead of the housing body 60. Specifically, the housing 6 includes the housing body 68, the first housing cover 61, and the second housing cover 62.

The housing body 68 is made of aluminum alloy, and has a cylindrical shape centered about the driving axis O1. The housing body 68 has an outer peripheral surface 681 and an inner peripheral surface 682. The housing body 68 has: a first housing portion 68a having the first inner diameter L1; and a second housing portion 68b having the second inner diameter L2. The first housing portion 68a forms the front portion and the center portion of the housing body 68, and the second housing portion 68b forms the rear portion of the housing body 68.

The housing body 68 has a step portion 68c. The step portion 68c is located between the first housing portion 68a and the second housing portion 68b in the direction of the driving axis O1. The step portion 68c is located behind the center of the housing body 68 in the direction of the driving axis O1.

The housing body 68 has a suction communication port 84. The suction communication port 84 is located approximately in the center of the housing body 68 in the front-rear direction. The suction communication port 84 is in front of the step portion 68c. The suction communication port 84 is connected to the evaporator (not illustrated) via the pipe (not illustrated).

The compressor has a first suction passage 75 between the outer peripheral surface 110a of the rotor body 11a of the rotor 11 and an inner peripheral surface 682 of the housing body 68 in the radial direction of the driving scroll 30. The step portion 68c is disposed in the first suction passage 75. The presence of the step portion 68c causes the distance between the outer peripheral surface 110a of the rotor 11 and the inner peripheral surface 682 of the housing body 68 in the radial direction of the driving scroll 30 (i.e., a width of the first suction passage 75) to be wider on the rear side than on the front side in the direction of the driving axis O1. That is, the width of the first suction passage 75 changes at the step portion 68c. In other words, the width of the first suction passage 75 changes in a stepwise manner. Other operations of this compressor are the same as those of the compressor according to the first embodiment.

In the compressor according to the third embodiment, the refrigerant drawn into the scroll chamber 65 from the suction communication port 84 flows into the compression chamber 12 through the first suction passage 75 and the second suction passage 72. Accordingly, the electric motor 10 is suitably cooled by the refrigerant flowing through the first suction passage 75 and the second suction passage 72.

Furthermore, the width of the first suction passage 75 is wider on the rear side than on the front side in the radial direction of the driving scroll 30, so that the lubricating oil is less likely to remain in the first suction passage 75. Other operations of this compressor are the same as those of the compressor according to the first embodiment.

Although the present disclosure has been described based on the first to third embodiments, the present disclosure is not limited to the first to third embodiments, and may be modified within the scope of the present disclosure.

For example, according to the compressor of each of the first to third embodiments, the protrusion 64 is formed integrally with the first housing cover 61. However, the present disclosure is not limited to this configuration. The protrusion 64 may be formed separately from the first housing cover 61, and may be fixed to the first housing cover 61. This configuration allows the protrusion 64 and the first housing cover 61 to be made of different materials.

According to the compressor of each of the first to third embodiments, the cover body 37 includes the outer cylindrical portion 37c. However, the present disclosure is not limited to this configuration. The cover body 37 is provided without the outer cylindrical portion 37c, and the rotor 11 may serve as the cylindrical portion of the present disclosure. In this configuration, the rotor 11 is extended in the direction of the driving axis O1 so as to be connected to the wall portion 37a of the cover body 37.

According to the compressor of each of the first to third embodiments, the outer cylindrical portion 37c may be formed separately from the rotor 11 and the wall portion 37a of the cover body 37.

According to the compressor of each of the first to third embodiments, the compressor may have a return passage so that the lubricating oil contained in the refrigerant discharged into the discharge chamber 14 returns to and lubricates the first radial ball bearing 51 and the like.

This Specification Includes the Following Embodiments.

Supplementary Note 1

A co-rotating scroll compressor comprising:

• • a housing having a scroll chamber into which fluid is drawn from outside of the housing;
  • a driving mechanism accommodated in the scroll chamber and including:
    • a stator including:
      • a stator core having a cylindrical shape centered about a driving axis and extending in a direction of the driving axis;
      • a first coil end having a cylindrical shape and extending from the stator core toward one side of the co-rotating scroll compressor along the direction of the driving axis; and
      • a second coil end having a cylindrical shape and extending from the stator core toward the other side of the co-rotating scroll compressor opposite to the one side along the direction of the driving axis; and
      • a rotor disposed outward of the stator to surround the stator, the rotor being rotated by the stator;
  • a driven mechanism accommodated in the scroll chamber;
  • a driving scroll accommodated in the scroll chamber and configured to be rotated by the driving mechanism about the driving axis; and
  • a driven scroll accommodated in the scroll chamber and eccentric to the driving scroll, the driven scroll being configured to be rotated by the driving scroll and the driven mechanism about a driven axis, the driving scroll and the driven scroll forming a compression chamber for compressing the fluid with rotation of the driving scroll and rotation of the driven scroll, wherein
  • a protrusion is provided in the scroll chamber, protrudes toward the driving scroll and the driven scroll in the direction of the driving axis, and is fixed to the stator core,
  • the driving scroll includes a cover body that rotates together With the rotor,
  • the cover body includes a wall portion that extends in a radial direction of the driving scroll and faces the first coil end in the direction of the driving axis,
  • the wall portion is connected to a cylindrical portion having a cylindrical shape, the cylindrical portion extends in the direction of the driving axis and surrounds the first coil end that is radially inward of the cylindrical portion in the radial direction of the driving scroll, and rotation of the rotor is transmitted to the cover body via the cylindrical portion,
  • the wall portion has a suction port that is radially inward of the cylindrical portion in the radial direction of the driving scroll, and the fluid in the scroll chamber is drawn into the compression chamber through the suction port,
  • a first suction passage is formed between the housing and the rotor in the radial direction of the driving scroll, and the fluid flows from the cover body toward the rotor through the first suction passage in the direction of the driving axis in the scroll chamber, and
  • a second suction passage is formed between the rotor and the stator in the radial direction of the driving scroll, and the fluid that has flowed through the first suction passage flows from the rotor toward the cover body in the direction of the driving axis and is guided to the suction port through the second suction passage.

Supplementary Note 2

The co-rotating scroll compressor according to supplementary note 1, wherein

• • the housing has a suction communication port through which the fluid is drawn into the scroll chamber from the outside of the housing,
  • the driving scroll includes a case that has a discharge chamber into which the fluid compressed in the compression chamber is discharged,
  • the case is located on the one side along the direction of the driving axis with respect to the cover body, and
  • the suction communication port is located closer to the cover body than to the case in the direction of the driving axis.

Supplementary Note 3

The co-rotating scroll compressor according to supplementary note 2, wherein

• • the suction communication port faces a portion of the rotor in the radial direction of the driving scroll.

Supplementary Note 4

The co-rotating scroll compressor according to supplementary note 1, wherein

• • the housing has a suction communication port through which the fluid is drawn into the scroll chamber from the outside of the housing,
  • the driving scroll includes a case that has a discharge chamber into which the fluid compressed in the compression chamber is discharged,
  • the case is located on the one side along the direction of the driving axis with respect to the cover body,
  • the suction communication port faces the case in the direction of the driving axis,
  • a third suction passage is formed in the scroll chamber, and the third suction passage is located on the one side along the direction of the driving axis with respect to the first suction passage, and
  • the fluid flows through the third suction passage toward the first suction passage in the direction of the driving axis.

Supplementary Note 5

The co-rotating scroll compressor according to any one of supplementary notes 1 to 4, wherein

• • a refrigerant serves as the fluid, and
  • the housing is spaced apart from the rotor in the radial direction of the driving scroll by a distance that allows the rotation of the rotor to generate shear force in the refrigerant flowing through the first suction passage.

Supplementary Note 6

The co-rotating scroll compressor according to any one of supplementary notes 1 to 5, wherein

the housing includes a main body that extends in the direction of the driving axis,

• • the main body includes:
    • a first housing portion located on the one side along the direction of the driving axis with respect to the rotor; and
    • a second housing portion located on the other side along the direction of the driving axis with respect to the first housing portion and extending from the first housing portion in the direction of the driving axis, the second housing portion facing the rotor in the radial direction of the driving scroll, and
    • an inner diameter of the second housing portion is greater than an inner diameter of the first housing portion.

Supplementary Note 7

The co-rotating scroll compressor according to supplementary note 6, wherein

• • the main body has an inner diameter that gradually increases from the first housing portion to the second housing portion in the direction of the driving axis.

Supplementary Note 8

The co-rotating scroll compressor according to any one of supplementary notes 1 to 7, wherein

• • the rotor includes a rotor body that has a cylindrical shape and is formed of a plurality of electromagnetic steel sheets stacked in the direction of the driving axis,
  • the first suction passage is formed between an inner peripheral surface of the housing and an outer peripheral surface of the rotor body in the radial direction of the driving scroll, and
  • the second suction passage is formed between an inner peripheral surface of the rotor body and an outer peripheral surface of the stator in the radial direction of the driving scroll.

The present disclosure is applicable to the air conditioner for the vehicle, or the like.