CO-ROTATING SCROLL COMPRESSOR

Description

CROSS REFERENCE TO RELATED APPLICATION

This application claims priority to Japanese Patent Application No. 2024-201382 filed on Nov. 19, 2024, the entire disclosure of which is incorporated herein by reference.

BACKGROUND ART

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

Japanese Patent Application Publication No. 2002-310073 discloses a conventional co-rotating scroll compressor (hereinafter simply referred to as a compressor). The compressor includes a housing and a compression mechanism disposed in the housing. The housing has a discharge portion through which fluid is discharged to an outside, an intake portion through which fluid is drawn from the outside, and an intake chamber in communication with the intake portion.

The compression mechanism includes a driving scroll, and a driven scroll. The driving scroll is formed with a drive shaft. The driving shaft is rotatably supported by the housing via a bearing. The driving scroll is driven to rotate around a rotation axis by a driving mechanism. The driving scroll has a driving scroll end plate, and a driving scroll spiral body that is formed integrally with the driving scroll end plate and protrudes in a spiral shape toward the driven scroll.

The driven scroll faces the driving scroll. The driven scroll is formed with a driven shaft. The driven shaft is rotatably supported by the housing via a bearing. The driven scroll is disposed eccentric with respect to the driving scroll, and rotated around a driven axis by the driving scroll and the driven mechanism. A compression chamber is defined between the driven scroll and the driving scroll. The driven scroll has a driven scroll end plate, and a driven scroll spiral body that is formed integrally with the driven scroll end plate and protrudes in a spiral shape toward the driving scroll. In addition, a discharge chamber is formed inside the driven shaft. The discharge chamber is in communication with the compression chamber and also with the discharge portion.

In this compressor, fluid is drawn into the intake chamber from the outside of the housing through the intake portion. In this compression mechanism, the volume of the compression chamber changes with rotation of the driving scroll and rotation of the driven scroll. As a result, in this compressor, fluid is drawn from the intake chamber into the compression chamber, and compressed in the compression chamber with the volume of the compression chamber reduced. The fluid compressed in the compression chamber is discharged from the compression chamber to the discharge chamber and then from the discharge portion to the outside of the housing.

In this type of compressor, it is required to reduce noise caused by discharge pulsation during operation. Therefore, in the above-mentioned conventional compressor, it is considered to reduce discharge pulsation by increasing the volume of the discharge chamber and enhancing a muffler effect of the discharge chamber. However, in the above-mentioned conventional compressor, since the discharge chamber is formed inside the driven shaft of the driven scroll, the diameter of the driven shaft increases as the volume of the discharge chamber increases, thereby increasing the diameter of the bearing supporting the driven shaft. This increases power loss in the bearing, which leads to a decrease in compressor efficiency.

The present disclosure, which has been made in view of the above-described conventional circumstances, is directed to providing a co-rotating scroll compressor that achieves high quietness and suppresses a decrease in efficiency.

SUMMARY

According to one aspect of the present disclosure, there is provided a co-rotating scroll compressor including: a housing having a discharge portion through which fluid is discharged to an outside; and a compression mechanism disposed in the housing. The compression mechanism has a compression chamber in which fluid is compressed while a volume of the compression chamber is reduced, a discharge chamber that is in communication with the compression chamber and to which the fluid compressed in the compression chamber is discharged, and a rotating shaft portion that is supported by the housing via a bearing so as to be rotatable around a rotation axis. The compression mechanism including a driving scroll and a driven scroll, the driving scroll being configured to be rotated by a drive mechanism, and having a driving scroll end plate and a driving scroll spiral body that is formed integrally with the driving scroll end plate and protrudes in a spiral shape toward the driven scroll, the driven scroll facing the driving scroll, and configured to be rotated by the driving scroll and a driven mechanism at a position eccentric with respect to the driving scroll to form the compression chamber between the driving scroll and the driven scroll, the driven scroll having a driven scroll end plate, and a driven scroll spiral body that is formed integrally with the driven scroll end plate and protrudes toward the driving scroll in a spiral shape. The discharge chamber has a diameter larger than an outer diameter of the bearing. The rotating shaft portion has a discharge communication portion through which the fluid discharged into the discharge chamber to flow to the discharge portion. A change of a phase between the discharge portion and the discharge communication portion with rotation of the rotating shaft portion changes a flow resistance for the fluid flowing from the discharge communication portion to the discharge portion. The discharge portion and the discharge communication portion reaches a phase in which the flow resistance increases as a flow rate of the fluid discharged from the compression chamber to the discharge chamber approaches a maximum.

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 cross-sectional view of a co-rotating scroll compressor of a first embodiment;

FIG. 2 is a partially enlarged cross-sectional view illustrating a main part of the co-rotating scroll compressor of the first embodiment including a discharge communication portion, a second insertion hole, and discharge passage;

FIG. 3 is a graph showing a relationship between a change in rotational phase between a driving scroll and a driven scroll and a change in volume of a compression chamber in the co-rotating scroll compressor of the first embodiment;

FIG. 4 is a graph showing a relationship between the change in rotational phase between the driving scroll and the driven scroll and a change in pressure in the compression chamber in the co-rotating scroll compressor of the first embodiment;

FIG. 5 is a cross-sectional view of the co-rotating scroll compressor of the first embodiment, taken along line V-V of FIG. 1, when the rotational phase between the driving scroll and the driven scroll is at phase X1;

FIG. 6 is a cross-sectional view of the co-rotating scroll compressor of the first embodiment, taken along line V-V of FIG. 1, when the rotational phase between the driving scroll and the driven scroll is at phase X2;

FIG. 7 is a cross-sectional view of the co-rotating scroll compressor of the first embodiment, taken along line V-V of FIG. 1, when the rotational phase between the driving scroll and the driven scroll is at phase X3;

FIG. 8 is a cross-sectional view of the co-rotating scroll compressor of the first embodiment, taken along line V-V of FIG. 1, when the rotational phase between the driving scroll and the driven scroll is at phase X4;

FIG. 9 is a cross-sectional view of the co-rotating scroll compressor of the first embodiment, taken along line IX-IX of FIG. 1, when the rotational phase between the driving scroll and the driven scroll is at phase X4;

FIG. 10 is a cross-sectional view of the co-rotating scroll compressor of the first embodiment, taken along line V-V of FIG. 1, when the rotational phase between the driving scroll and the driven scroll is at phase X5;

FIG. 11 is a cross-sectional view of the co-rotating scroll compressor of the first embodiment, taken along line IX-IX of FIG. 1, when the rotational phase between the driving scroll and the driven scroll is at phase X5;

FIG. 12 is a graph showing a waveform of discharge pulsation and a waveform of canceling pulsation during operation of the co-rotating scroll compressor of the first embodiment;

FIG. 13 is a partial cross-sectional view of the co-rotating scroll compressor of the first embodiment, illustrating a state in which lubricating oil is accumulated in the discharge chamber when the compression mechanism rotates at a high speed;

FIG. 14 is a cross-sectional view of a co-rotating scroll compressor of a second embodiment;

FIGS. 15A to 15D each are a schematic view of the co-rotating scroll compressor of the second embodiment, illustrating a change in phase between a discharge portion and a discharge communication portion in accordance with rotational driving of the driving scroll when the discharge portion and the discharge communication portion are viewed in a D1 direction in FIG. 14, specifically, FIG. 15A illustrates a phase between the discharge portion and the discharge communication portion when a rotation angle of the driving scroll is zero, FIG. 15B illustrates the phase between the discharge portion and the discharge communication portion when the driving scroll rotates by approximately 90 degrees from the state illustrated in FIG. 15A, FIG. 15C illustrates the phase between the discharge portion and the discharge communication portion when the driving scroll rotates by approximately 90 degrees from the state illustrated in FIG. 15B, and FIG. 15D illustrates the phase between the discharge portion and the discharge communication portion when the driving scroll rotates by approximately 90 degrees from the state illustrated in FIG. 15C;

FIG. 16 is an enlarged cross-sectional view, illustrating a main part of a co-rotating scroll compressor of a third embodiment;

FIG. 17 is a cross-sectional view of a co-rotating scroll compressor of a fourth embodiment; and

FIG. 18 is a cross-sectional view of a co-rotating scroll compressor of a fifth embodiment.

DESCRIPTION OF EMBODIMENTS

The following will describe first to fifth embodiments of the present disclosure with reference to the drawings. A co-rotating scroll compressor according to each of the first to fifth embodiments is mounted on a vehicle (not illustrated), and serves as a component of an air conditioner of the vehicle.

First Embodiment

As illustrated in FIG. 1, the co-rotating scroll compressor (hereinafter, simply referred to as a compressor) of the first embodiment includes a housing 6, an electric motor 10, and a compression mechanism 14. The electric motor 10 is an example of a “driving mechanism” of the present disclosure.

In the present embodiment, a front-rear direction of the compressor is defined by a solid arrow illustrated in FIG. 1. The front-rear directions of the compressor in FIG. 2 and thereafter correspond to the front-rear direction in FIG. 1. It is noted that the front-rear direction is an 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 and a housing cover 62. The housing body 60 and the housing cover 62 are made of an aluminum alloy.

The housing body 60 is a bottomed tubular member, and has an outer peripheral wall 60a and a rear wall 60b. The outer peripheral wall 60a has a cylindrical shape extending around a rotation axis O1. The rotation axis O1 is parallel to the front-rear direction.

In addition, an intake communication port 68 is formed in the outer peripheral wall 60a. The intake communication port 68 extends in a radial direction of the housing body 60. The intake communication port 68 is connected to an evaporator (not illustrated) via a pipe (not illustrated).

The rear wall 60b is located at a rear end of the housing body 60. The rear wall 60b extends in a substantially circular flat plate shape, perpendicularly to the rotation axis O1. An outer peripheral edge of the rear wall 60b is connected to a rear end of the outer peripheral wall 60a. The intake communication port 68 may be formed in the rear wall 60b.

The rear wall 60b has a first support portion 64 at the center of an inner surface of the rear wall 60b. The first support portion 64 protrudes forward from the center of the inner surface of the rear wall 60b. The first support portion 64 has a columnar shape extending around the rotation axis O1.

The first support portion 64 has a pin hole 4. The pin hole 4 extends in a columnar shape, is opened at a front end face of the first support portion 64, and extends rearward linearly inside the first support portion 64. This pin hole 4 does not extend through the first support portion 64 in the front-rear direction.

A first sliding bearing 51 is provided on an outer peripheral surface of the first support portion 64. The first sliding bearing 51 has a cylindrical shape with a diameter larger than that of the first support portion 64. The first sliding bearing 51 is disposed on the outer peripheral surface of the first support portion 64. The first sliding bearing 51 may be replaced with a ball bearing.

The housing cover 62 is disposed in front of the housing body 60. The housing cover 62 has a substantially disk shape extending around the rotation axis O1. The housing cover 62 has a front surface 62a facing forward, a rear surface 62b facing rearward and located opposite from the front surface 62a, and an outer peripheral surface 62c connected to the front surface 62a and the rear surface 62b and located between the front surface 62a and the rear surface 62b.

Further, the housing cover 62 has a second support portion 66, a second insertion hole 61, and a discharge portion 63.

The second support portion 66 is integrally formed with approximately the center of the rear surface 62b, and protrudes rearward from the rear surface 62b. The second insertion hole 61 is formed in a columnar shape extending around the rotation axis O1, and extends in the housing cover 62 in a direction of the rotation axis O1 extends. A rear end of the second insertion hole 61 is opened at a rear end of the second support portion 66, that is, at the rear end of the housing cover 62. Since the second insertion hole 61 is formed in this manner, the second support portion 66 has a cylindrical shape extending around the rotation axis O1.

On the other hand, a front end of the second insertion hole 61 is not opened at the front end of the housing cover 62. Furthermore, a second sliding bearing 52 is provided in the second insertion hole 61. The second sliding bearing 52 is an example of the “bearing” of the present disclosure. An outer diameter of the second sliding bearing 52 is defined as a first length L1, which is smaller than that of the second support portion 66. The second sliding bearing 52 has a cylindrical shape and is disposed in a front portion of the second insertion hole 61. It is noted that a ball bearing may be used as the “bearing” of the present disclosure.

The discharge portion 63 is formed of a discharge communication port 69 and a discharge passage 67. The discharge communication port 69 is formed in the outer peripheral surface 62c. The discharge communication port 69 is opened to an outside from the outer peripheral surface 62c in the radial direction of the housing cover 62. The discharge communication port 69 is connected to a condenser (not illustrated) via a pipe (not illustrated).

The discharge passage 67 is formed inside the housing cover 62. The discharge passage 67 extends inside the housing cover 62 in the radial direction of the housing cover 62. The discharge passage 67 is connected to the discharge communication port 69 at one end and to the second insertion hole 61 at the other end. As a result, the discharge passage 67 is in communication with the discharge communication port 69 and the second insertion hole 61, thereby connecting the second insertion hole 61 to the discharge communication port 69.

In the housing 6, the housing cover 62 is disposed in front of the housing body 60, and the rear surface 62b of the housing cover 62 is in contact with the front end of the outer peripheral wall 60a of the housing body 60. In this state, the housing cover 62 is fixed to the housing body 60 by a plurality of bolts (not illustrated) from the housing cover 62 side. Thus, in the housing 6, the housing body 60 and the housing cover 62 are integrated together.

In addition, in the housing 6, the front of the housing body 60 is closed by the housing cover 62 to form an intake chamber 65 inside the housing body 60. The intake chamber 65 is in communication with the intake communication port 68. Refrigerant gas is drawn into the intake chamber 65 through the intake communication port 68 from the outside of the housing 6. The refrigerant gas is an example of the “fluid” of the present disclosure. The refrigerant gas drawn into the intake chamber 65 contains lubricating oil 18. The intake chamber 65 is also in communication with an intake port 35b, which will be described later. Therefore, refrigerant gas in the intake chamber 65 is drawn into an intake space 30a, which will be described later, through the intake port 35b.

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

The electric motor 10 includes a stator 17 and a rotor 11. The stator 17 has a cylindrical shape extending around the rotation axis O1, and has a winding 17a. The stator 17 is fitted into an inner peripheral surface of the outer peripheral wall 60a, so that the stator 17 is fixed to the housing body 60, and hence the housing 6.

The rotor 11 has a cylindrical shape extending around the rotation axis O1 and is disposed inside the stator 17. Although a detailed illustration is omitted, the rotor 11 is formed of a plurality of permanent magnets corresponding to the stator 17 and stacking steel plates for fixing the permanent magnets.

The compression mechanism 14 is disposed in the housing 6. The compression mechanism 14 includes a driving scroll 30, a driven scroll 40, a driven mechanism 20, and a first cover body 37. The first cover body 37 is an example of the “cover body” of the present disclosure.

The driving scroll 30 is made of aluminum alloy. The driving scroll 30 includes a driving scroll end plate 31, a driving scroll peripheral wall 32, a driving scroll spiral body 33, and a closing body 35.

The driving scroll end plate 31 extends in a substantially disk shape, perpendicularly to the rotation axis O1 and a driven axis O2. The driven axis O2 is eccentric with respect to the rotation axis O1 and extends in parallel to the rotation axis O1. That is, the driven axis O2 is parallel to the front-rear direction. The driving scroll end plate 31 has a front surface 311 facing the first cover body 37, and a rear surface 312 located opposite from the front surface 311.

In addition, the driving scroll end plate 31 has a first recess 30b and a discharge port 30c. The first recess 30b is recessed rearward in a substantially columnar shape from the front surface 311. An inner diameter of the first recess 30b is equal to, or substantially equal to, an inner diameter of a second recess 37e, which will be described later, provided in the first cover body 37. The discharge port 30c is formed in the driving scroll end plate 31 in a portion inside the first recess 30b, and extends through the driving scroll end plate 31 in the front-rear direction. In the first recess 30b, a discharge reed valve 57 and a retainer 58 are fixed to the driving scroll end plate 31 by a fixing bolt 59. The discharge reed valve 57 is an example of the “discharge valve” of the present disclosure.

Opening of the discharge reed valve 57 by elastic deformation allows refrigerant gas in the compression chamber 12 to be discharged into a discharge chamber 91 through the discharge port 30c. Closing of the discharge reed valve 57 by elastic deformation prevents the refrigerant gas in the compression chamber 12 from being discharged into the discharge chamber 91 through the discharge port 30c. Furthermore, closing of the discharge reed valve 57 prevents the refrigerant gas in the discharge chamber 91 from flowing into the compression chamber 12 through the discharge port 30c. The retainer 58 is capable of adjusting an opening degree of the discharge reed valve 57. The compression chamber 12 and the discharge chamber 91 will be described in detail later.

The driving scroll peripheral wall 32 is formed integrally with the driving scroll end plate 31, and extends rearward, i.e., toward the driven scroll 40, from an outer peripheral edge of the driving scroll end plate 31 in a cylindrical shape. Thus, the driving scroll peripheral wall 32 extends parallel to the rotation axis O1 and the driven axis O2.

The driving scroll spiral body 33 is formed integrally with the driving scroll end plate 31 and is disposed inside the driving scroll peripheral wall 32. The driving scroll spiral body 33 extends from the rear surface 312 of the driving scroll end plate 31 toward the driven scroll 40 in parallel with the driving scroll peripheral wall 32. As illustrated in FIG. 5, the driving scroll spiral body 33 has a spiral shape, extending from a center of the driving scroll end plate 31 as a center of spiral toward an outer peripheral portion. An outer peripheral end of the driving scroll spiral body 33 is connected to the driving scroll peripheral wall 32. In FIG. 5, the electric motor 10 is not illustrated for ease of explanation. The same applies to FIGS. 6 to 8 and 10 described later.

As illustrated in FIG. 1, the closing body 35 extends in a substantially disk shape, perpendicularly to the rotation axis O1 and the driven axis O2. The closing body 35 has a front surface 351 facing forward and a rear surface 352 located opposite from the front surface 351.

The closing body 35 further has a first boss 35a and the intake port 35b. The first boss 35a is formed integrally with the rear surface 352 at the center thereof, and protrudes rearward along the rotation axis O1 and the driven axis O2. The first boss 35a has a cylindrical shape extending around the rotation axis O1. The intake port 35b extends through the closing body 35 in the direction of the rotation axis O1.

As illustrated in FIG. 1, the closing body 35 has four rings 22 in the front surface 351. The rings 22 are arranged at equal intervals in a circumferential direction of the closing body 35. In FIG. 1, two of the four rings 22 are illustrated.

The first cover body 37 is a bottomed tubular member, and has an outer peripheral wall 37a, a front wall 37b, and a flange 37c. The outer peripheral wall 37a has a cylindrical shape extending around the rotation axis O1. Here, an outer diameter of the outer peripheral wall 37a is larger than that of the second sliding bearing 52. More specifically, the outer diameter of the outer peripheral wall 37a is smaller than the inner diameter of the rotor 11 and the outer diameter of the driving scroll end plate 31 by a length of the flange 37c protruding radially outward from the outer peripheral wall 37a.

In addition, a recirculation passage 370 is formed in the outer peripheral wall 37a. The recirculation passage 370 is located in a front portion of the outer peripheral wall 37a, and extends through the outer peripheral wall 37a in a radial direction of the first cover body 37.

The front wall 37b is located at a front end of the first cover body 37. The front wall 37b extends in a substantially circular flat plate shape, perpendicularly to the rotation axis O1. An outer peripheral edge of the front wall 37b is connected to the front end of the outer peripheral wall 37a. Thus, the first cover body 37 has a second recess 37e that is defined by an inner peripheral surface of the outer peripheral wall 37a and a rear surface of the front wall 37b, and extends in a substantially columnar shape in the direction of the rotation axis O1.

The first cover body 37 is provided with a second boss 37d. The second boss 37d is an example of the “rotating shaft portion” of the present disclosure. The second boss 37d is formed integrally with the front wall 37b at the center thereof, and protrudes forward from the front wall 37b in the direction of the rotation axis O1 and the driven axis O2.

As illustrated in FIG. 2, the second boss 37d has a first diameter portion 371, a second diameter portion 372, and a third diameter portion 373. The first diameter portion 371 forms a rear portion of the second boss 37d. The second diameter portion 372 is located between the first diameter portion 371 and the third diameter portion 373, and forms a central portion of the second boss 37d. The third diameter portion 373 forms a front portion of the second boss 37d.

The first diameter portion 371 has a largest outer diameter among the first diameter portion 371, the second diameter portion 372, and the third diameter portion 373. The second diameter portion 372 has an outer diameter larger than that of the third diameter portion 373. As a result, the outer diameter of the second boss 37d decreases in three stages, that is, in the order of the first diameter portion 371, the second diameter portion 372, and the third diameter portion 373. The outer diameter of the third diameter portion 373 is approximately equal to the inner diameter of the second sliding bearing 52.

Further, a discharge communication portion 38 is formed in the second boss 37d. The discharge communication portion 38 allows refrigerant gas discharged into the discharge chamber 91 to flow to the discharge portion 63. The discharge communication portion 38 is formed of a connection passage 38a and a discharge communication hole 38b.

The connection passage 38a extends through the second boss 37d and the front wall 37b in the direction of the rotation axis O1. The connection passage 38a has a columnar shape extending around the rotation axis O1. As a result, the second boss 37d has a cylindrical shape extending around on the rotation axis O1.

The discharge communication hole 38b is connected to the connection passage 38a and extends in the second boss 37d in the radial direction of the second boss 37d. The discharge communication hole 38b is opened at an outer peripheral surface of the second boss 37d, more specifically, at an outer peripheral surface of the second diameter portion 372.

The flange 37c is integrally formed with the outer peripheral wall 37a at the rear end thereof. The flange 37c protrudes outward in the radial direction of the first cover body 37 beyond the outer peripheral wall 37a. As a result, a diameter of the flange 37c is larger than that of the outer peripheral wall 37a and is substantially the same as that of the driving scroll end plate 31 of the driving scroll 30. It is noted that the flange 37c may be omitted.

In this compressor, the first cover body 37 is fixed to the driving scroll 30. Specifically, in the driving scroll 30, the closing body 35 is in contact with the rear end of the driving scroll peripheral wall 32 with the front surface 351 of the closing body 35 facing the rear surface 312 of the driving scroll end plate 31. In the first cover body 37, the flange 37c is in contact with the front surface 311 of the driving scroll end plate 31 with the outer peripheral wall 37a and the flange 37c facing the driving scroll end plate 31.

In this state, the flange 37c of the first cover body 37, the driving scroll end plate 31, the driving scroll peripheral wall 32, and the closing body 35 are connected by a plurality of bolts 50 from the flange 37c side. Thus, in the driving scroll 30, the driving scroll end plate 31, the driving scroll peripheral wall 32, and the closing body 35 are integrated together. The first cover body 37 is integrated with the driving scroll end plate 31 and hence the driving scroll 30. In FIG. 1, two of the plurality of bolts 50 are illustrated.

In this way, the first cover body 37 is fixed to the driving scroll 30, thereby forming the discharge chamber 91 defined by the first recess 30b and the second recess 37e between the outer peripheral wall 37a and the front wall 37b of the first cover body 37 and the driving scroll end plate 31.

The discharge chamber 91 is in communication with the discharge port 30c, the recirculation passage 370, and the connection passage 38a. Here, the discharge port 30c and the connection passage 38a are in communication with the discharge chamber 91 in the direction of the rotation axis O1. On the other hand, the recirculation passage 370 is in communication with the discharge chamber 91 in the radial direction of the first cover body 37, that is, in a direction perpendicular to the direction of the rotation axis O1. The discharge port 30c, the recirculation passage 370, and the connection passage 38a each have a smaller diameter than that of the discharge chamber 91. The recirculation passage 370 provides fluid communication between the discharge chamber 91 and the intake chamber 65.

In this way, the first cover body 37 is accommodated in the intake chamber 65 and is rotatable integrally with the driving scroll 30 around the rotation axis O1. Furthermore, the first cover body 37 has the second boss 37d fitted into the second sliding bearing 52. As a result, the first cover body 37 is supported by the second support portion 66, i.e., the housing 6, via the second sliding bearing 52 so as to be rotatable around the rotation axis O1.

In addition, the driving scroll 30 has the driving scroll peripheral wall 32 that is inserted into and fixed to the rotor 11. As a result, the driving scroll 30 is fixed to the rotor 11 and is integrated with the rotor 11.

The driven scroll 40 is also made of an aluminum alloy. The driven scroll 40 is accommodated in the driving scroll 30. The driven scroll 40 has a driven scroll end plate 41 and a driven scroll spiral body 43.

The driven scroll end plate 41 extends in a substantially disk shape, perpendicularly to the rotation axis O1 and the driven axis O2. The driven scroll end plate 41 has a front surface 411 and a rear surface 412. The front surface 411 faces the rear surface 312 of the driving scroll end plate 31 in the driving scroll 30. The rear surface 412 is located opposite from the front surface 411 and faces the front surface 351 of the closing body 35.

Further, the driven scroll end plate 41 has an accommodation portion 71. The accommodation portion 71 is recessed forward in a columnar shape from the rear surface 412 of the driven scroll end plate 41. A bushing 53 is accommodated in the accommodation portion 71. A 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 with respect to the center of the bushing 53. The driven pin 55 has a columnar shape and protrudes rearward from the bushing 53 and hence the driven scroll end plate 41 towards the first support portion 64. The bushing 53 may be accommodated in the accommodation portion 71 via a bearing such as a sliding bearing.

Additionally, four anti-rotation pin 21 are fixed to the rear surface 412. The anti-rotation pins 21 each are fixed at a position outward relative to the accommodation portion 71 and facing the ring 22 in the rear surface 412. The anti-rotation pins 21 each protrude rearward from the rear surface 412. In FIG. 1, two of the four anti-rotation pins 21 are illustrated.

The driven scroll spiral body 43 is integrated with the driven scroll end plate 41 and extends forward from the front surface 411 of the driven scroll end plate 41 in parallel with the rotation axis O1 and the driven axis O2. As illustrated in FIG. 5, the driven scroll spiral body 43 has a spiral shape, extending from a center of the driven scroll end plate 41 as a center of spiral toward an outer peripheral portion.

The driven mechanism 20 illustrated in FIG. 1 is formed of the four anti-rotation pins 21 and the four rings 22. The number of the anti-rotation pins 21 and the number of the rings 22 may be designed as appropriate as long as each of them is three or more.

In the compression mechanism 14, the driving scroll spiral body 33 of the driving scroll 30 and the driven scroll spiral body 43 of the driven scroll 40 are meshed with each other with the driven scroll 40 accommodated in the driving scroll 30. In addition, the anti-rotation pins 21 are inserted into their associated rings 22. Thus, the driving scroll 30 and the driven scroll 40 are assembled to each other in the front-rear direction. More precisely, after the driving scroll spiral body 33 and the driven scroll spiral body 43 are meshed with each other and the anti-rotation pins 21 are inserted into their associated rings 22, the first cover body 37, the driving scroll end plate 31, the driving scroll peripheral wall 32, and the closing body 35 are connected by the bolts 50 in the driving scroll 30 and the first cover body 37.

After the driving scroll 30 and the driven scroll 40 are assembled together, the first sliding bearing 51 is inserted into a first insertion hole 35 d of the closing body 35 of the driving scroll 30. Accordingly, the first boss 35a and hence the closing body 35 are rotatably supported by the first support portion 64 through the first sliding bearing 51.

Furthermore, in the first cover body 37, the second boss 37d of the first cover body 37 is inserted into the second insertion hole 61. As a result, the third diameter portion 373 of the second boss 37d is inserted into the second sliding bearing 52, as illustrated in FIG. 2. The second sliding bearing 52 is held by the second insertion hole 61 with the second sliding bearing 52 placed in contact with a step between the third diameter portion 373 and the second diameter portion 372, which is formed by the difference in outer diameter. As a result, the second boss 37d and hence the first cover body 37 are rotatably supported by the second support portion 66 via the second sliding bearing 52. Accordingly, as illustrated in FIG. 1, the driving scroll 30 and the first cover body 37 are supported by the housing 6 via both the first support portion 64 and the second support portion 66 so as to be rotatable around the rotation axis O1. As a result, the second boss 37d is rotatable around the rotation axis O1 inside the second insertion hole 61.

As illustrated in FIG. 2, the second diameter portion 372 of the second boss 37d has a smaller diameter than that of the second insertion hole 61. Therefore, when the second boss 37d is supported by the second support portion 66, the second diameter portion 372 is spaced from an inner peripheral surface of the second insertion hole 61 in a radial direction of the second boss 37d. Thus, the inner peripheral surface of the second insertion hole 61 and the second diameter portion 372 are not in contact with each other. The second boss 37d is supported by the second support portion 66, so that the discharge communication hole 38b faces an inside of the second insertion hole 61. As a result, the discharge communication hole 38b is in communication with the discharge passage 67 of the discharge portion 63 through the second insertion hole 61. Accordingly, in this compressor, the discharge passage 67 and the discharge communication hole 38b, and hence the discharge portion 63 and the discharge communication hole 38b, are in communication with each other in the radial direction of the housing 6.

As illustrated in FIG. 1, in the driven scroll 40, the driven pin 55 is inserted into the pin hole 4 of the first support portion 64. Thus, the driven scroll 40 is supported by the first support portion 64 via the driven pin 55 so as to be rotatable around the driven axis O2. That is, unlike the driving scroll 30, the driven scroll 40 is supported only by the first support portion 64 of the housing 6 so as to be rotatable around the driven axis O2.

In the compression mechanism 14, with the driving scroll 30 and the driven scroll 40 assembled in the front-rear direction, two compression chambers 12 are formed between the driving scroll spiral body 33 of the driving scroll 30 and the driven scroll spiral body 43 of the driven scroll 40, as illustrated in FIG. 5. In addition, as illustrated in FIG. 1, with the driving scroll 30 and the driven scroll 40 assembled in the front-rear direction, an intake space 30a is formed inside the driving scroll peripheral wall 32. The intake space 30a is in communication with the intake port 35b, and communicable with the compression chambers 12 when the compressor is operated. The compression chambers 12 and the intake space 30a are separated from the intake chamber 65 by the driving scroll 30 and the driven scroll 40.

In the compressor having the above-described configuration, refrigerant gas at low temperature and low pressure having passed through the evaporator is drawn into the intake chamber 65 through the intake communication port 68 as indicated by a dashed arrow in FIG. 1. When the electric motor 10 is operated to rotate the rotor 11, the driving scroll 30 and the first cover body 37 rotate around the rotation axis O1 in the intake chamber 65. That is, the driving scroll 30 and the first cover body 37 rotate integrally with the rotor 11. At this time, in the driven mechanism 20, the anti-rotation pins 21 slide on inner peripheral surfaces of their associated rings 22 to rotate the rings 22 relative to the anti-rotation pins 21 around the center thereof. Thus, the driven mechanism 20 transmits a torque of the driving scroll 30 to the driven scroll 40.

As a result, the driven scroll 40 is driven to rotate around the driven axis O2 by the driving scroll 30 and the driven mechanism 20. At this time, the driven mechanism 20 prevents the driven scroll 40 from rotating. Accordingly, the driven scroll 40 makes orbital motion relative to the driving scroll 30 around the driven axis O2. In this compressor, the driving scroll 30 and the driven scroll 40 rotate in a rotational direction R1 as indicated in FIG. 5 and other drawings.

Furthermore, when the driving scroll 30 is driven to rotate around the rotation axis O1, the discharge communication hole 38b rotates relative to the discharge passage 67 in the rotational direction R1, as illustrated in FIGS. 9 and 11.

A difference in phase between the driving scroll 30, which is driven to rotate around the rotation axis O1, and the driven scroll 40, which is driven to rotate around the driven axis O2, is hereinafter referred to as a rotational phase between the driving scroll 30 and the driven scroll 40. As the rotational phase changes, the volume of each of the compression chambers 12 varies accordingly. As a result, as indicated by the dashed arrows in FIG. 1, the refrigerant gas in the intake chamber 65 is drawn into the intake space 30a through the intake port 35b and, then into the compression chambers 12.

The refrigerant gas drawn into the compression chambers 12 is compressed in the compression chambers 12 while flowing from outer peripheral portions of the driving scroll spiral body 33 and the driven scroll spiral body 43 toward the centers of the driving scroll spiral body 33 and the driven scroll spiral body 43. The refrigerant gas compressed to the discharge pressure in the compression chambers 12 is then discharged into the discharge chamber 91 from the discharge port 30c.

The refrigerant gas discharged into the discharge chamber 91 flows through the connection passage 38a, the discharge communication hole 38b, the second insertion hole 61, and the discharge passage 67, and is discharged through the discharge communication port 69 toward the condenser. In this manner, air conditioning is performed by the vehicle air conditioner.

In this way, refrigerant gas at high pressure is discharged into the discharge chamber 91, so that the pressure in the discharge chamber 91 is higher than that in the intake chamber 65 and the intake space 30a. In other words, the intake chamber 65 and the intake space 30a correspond to an intake pressure region that is a portion in the housing where pressure is lower than the discharge chamber 91.

In the compressor of the present disclosure, discharge pulsation inevitably occurs due to the discharge of the refrigerant gas from the compression chambers 12 to the discharge chamber 91. In this regard, the compressor can effectively reduce discharge pulsation by a muffler effect and a pulsation canceling function in the discharge chamber 91. In the present specification, the term “pulsation cancellation function” refers to a function whereby pulsations generated due to the flow resistance of the fluid passing from the discharge communication portion to the discharge portion serve to cancel out the discharge pulsations. These will be explained in detail below.

In the compressor of the present disclosure, the discharge chamber 91 is formed between the driving scroll end plate 31 and the first cover body 37. An inner diameter of the discharge chamber 91 is defined as a second length L2, and is larger than the outer diameter of the second sliding bearing 52. A length of the discharge chamber 91 in the direction of the rotation axis O1 is defined as a third length L3. As a result, in this compressor, the volume of the discharge chamber 91 can be suitably secured, and the muffler effect in the discharge chamber 91 can be effectively exerted.

As has been described above, the refrigerant gas compressed in the compression chamber 12 flows through the discharge port 30c and is discharged to the discharge chamber 91. Here, since the discharge port 30c has a smaller diameter than that of the discharge chamber 91, the refrigerant gas compressed in the compression chamber 12 flows through the discharge port 30c and is then discharged into the discharge chamber 91, which is a space having a larger volume than that of the discharge port 30c.

Furthermore, the refrigerant gas in the discharge chamber 91 flows through the connection passage 38a and the like, and is discharged to an outside of the discharge chamber 91, that is, to the outside of the compressor. Here, the second boss 37d of the first cover body 37 is inserted into the second sliding bearing 52 and is supported by the second sliding bearing 52. Therefore, the second boss 37d, and hence the connection passage 38a formed in the second boss 37d, have a smaller diameter than that of the second sliding bearing 52. That is, in this compressor, the inner diameter of the discharge chamber 91 is larger than the outer diameter of the second sliding bearing 52, so that the difference between the inner diameter of the discharge chamber 91 and the inner diameter of the connection passage 38a is sufficiently large.

Therefore, the refrigerant gas compressed in the compression chamber 12 flows through the discharge port 30c, the discharge chamber 91, and the connection passage 38a in this order. Thus, the refrigerant gas flows through a narrow space, a wide space, and a narrow space again to be discharged to the outside the compressor. Accordingly, this compressor is configured to sufficiently exert the muffler effect in the discharge chamber 91.

Furthermore, since the length of the discharge chamber 91 in the direction of the rotation axis O1 is the third length L3, the length of the discharge chamber 91 in the direction of the rotation axis O1 can be suitably secured in this compressor. As a result, a low frequency wavelength of the refrigerant gas compressed in the compression chamber 12 is suitably cancelled out in the discharge chamber 91 in the compressor.

Accordingly, in this compressor, discharge pulsation that occurs when refrigerant gas is discharged from the compression chamber 12 to the discharge chamber 91 can be suitably reduced by the muffler effect in the discharge chamber 91.

Next, with reference to one of the two compression chambers 12, the effect of reducing discharge pulsation by the pulsation canceling function will be described in detail.

As shown in FIG. 3, the volume of the compression chamber 12 gradually increases from a minimum with a change in rotational phase between the driving scroll 30 and the driven scroll 40. After the volume of the compression chamber 12 reaches a maximum, the volume of the compression chamber 12 gradually decreases with the change in rotational phase between the driving scroll 30 and the driven scroll 40. During a process in which the volume of the compression chamber 12 increases from the minimum to the maximum, refrigerant gas is drawn into the compression chamber 12. That is, as described above, the refrigerant gas in the intake chamber 65 is drawn into the compression chamber 12 from the intake port 35b through the intake space 30a.

In this compressor, when the rotational phase between the driving scroll 30 and the driven scroll 40 is at phase X1, the driving scroll 30, the driven scroll 40, and the compression chamber 12 are in a state illustrated in FIG. 5. Furthermore, in the process in which the volume of the compression chamber 12 increases from the minimum to the maximum, a flow rate of the refrigerant gas to be drawn into the compression chamber 12 changes, and when the rotational phase between the driving scroll 30 and the driven scroll 40 is at the phase X1, the flow rate of the refrigerant gas to be drawn into the compression chamber 12 becomes the maximum. When the rotational phase between the driving scroll 30 and the driven scroll 40 is at the phase X1, it is during the process in which the volume of the compression chamber 12 increases from the minimum to the maximum, so that the volume of the compression chamber 12 has not yet reached its maximum.

As shown in FIG. 3, when the rotational phase between the driving scroll 30 and the driven scroll 40 is at phase X2, which is greater than the phase X1, the volume of the compression chamber 12 reaches the maximum (see FIG. 6). When the volume of the compression chamber 12 is at the maximum, the driving scroll spiral body 33 and the driven scroll spiral body 43 cause the compression chamber 12 and the intake space 30a to be out of communication with each other. Therefore, when the volume of the compression chamber 12 is at the maximum, the refrigerant gas is not drawn into the compression chamber 12, and the refrigerant gas in the compression chamber 12 is confined within the compression chamber 12.

As shown in FIG. 3, when the rotational phase between the driving scroll 30 and the driven scroll 40 is at phase X3, which is greater than the phase X2, the volume of the compression chamber 12 becomes smaller than the maximum (see FIG. 7). Thus, the refrigerant gas in the compression chamber 12 starts being compressed as the volume of the compression chamber 12 becomes smaller than the maximum.

As shown in FIG. 4, as the rotational phase between the driving scroll 30 and the driven scroll 40 becomes greater than the phase X3, the compression of the refrigerant gas in the compression chamber 12 progresses, and the pressure in the compression chamber 12 increases. Then, when the rotational phase between the driving scroll 30 and the driven scroll 40 is at phase X4, as illustrated in FIG. 8, fluid communication between the compression chamber 12 and the discharge port 30c starts. However, at this time, the discharge reed valve 57 is still in a closed state.

Then, as shown in FIG. 4, the rotational phase between the driving scroll 30 and the driven scroll 40 is at phase X5, the compression of the refrigerant gas in the compression chamber 12 progresses further. As a result, the pressure in the compression chamber 12 exceeds the pressure in the discharge chamber 91, and thus, the discharge reed valve 57 opens. Accordingly, the refrigerant gas starts being discharged from the compression chamber 12 to the discharge chamber 91.

In this compressor, the discharge communication hole 38b is formed in the second boss 37d of the first cover body 37. Therefore, rotation of the first cover body 37 along with the rotation of the driving scroll 30 causes the discharge communication hole 38b to rotate in the rotational direction R1 around the rotation axis O1 in the second insertion hole 61 as illustrated in FIGS. 9 and 11. Thus, the rotation of the first cover body 37 along with the rotation of the driving scroll 30 changes a phase between the discharge passage 67 and the discharge communication hole 38b.

As a result of the change in phase between the discharge passage 67 and the discharge communication hole 38b, flow resistance (discharge-side flow resistance) for the refrigerant gas flowing from the discharge communication hole 38b to the discharge passage 67 changes in this compressor. Additionally, in this compressor, pulsation different from the discharge pulsation occurs due to the flow resistance (hereinafter, this pulsation is referred to as “canceling pulsation”). As the flow resistance changes, the magnitude of the canceling pulsation changes.

When the rotational phase between the driving scroll 30 and the driven scroll 40 is at the phase X4, the discharge communication hole 38b is located at a position substantially directly facing the discharge passage 67, as illustrated in FIG. 9. Therefore, as indicated by the dashed arrow in FIG. 9, the refrigerant gas discharged from the discharge chamber 91 to the connection passage 38a can flow substantially directly to the discharge passage 67 through the discharge communication hole 38b. That is, when the phase between the discharge passage 67 and the discharge communication hole 38b is in a state illustrated in FIG. 9, the flow resistance is at a minimum. In other words, in this compressor, the discharge communication hole 38b is formed in the second boss 37d so that the flow resistance becomes the minimum when the rotational phase between the driving scroll 30 and the driven scroll 40 is at the phase X4. As described above, when the rotational phase between the driving scroll 30 and the driven scroll 40 is at the phase X4, the discharge reed valve 57 is in the closed state. Therefore, the flow rate of the refrigerant gas discharged from the compression chamber 12 to the discharge chamber 91 is at the minimum, i.e., zero. As a result, in this compressor, when the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 91 is at the minimum, the discharge passage 67 and the discharge communication hole 38b are in a phase that minimizes flow resistance. It is noted that the expression “the flow rate of the fluid discharged from the compression chamber to the discharge chamber is at the minimum” includes not only a case where a small amount of fluid is discharged from the compression chamber to the discharge chamber, but also a case where the flow rate is zero.

Then, as shown in FIG. 4, when the rotational phase between the driving scroll 30 and the driven scroll 40 is at the phase X5, which is greater than the phase X4, the pressure in the compression chamber 12 reaches the discharge pressure, thereby opening the discharge reed valve 57. As a result, refrigerant gas is discharged from the compression chamber 12 to the discharge chamber 91. At this time, the flow rate of the refrigerant gas to be discharged from the compression chamber 12 to the discharge chamber 91 becomes at a maximum. When the rotational phase between the driving scroll 30 and the driven scroll 40 is at the phase X5, the two compression chambers 12 are merged as illustrated in FIG. 10.

Here, when the rotational phase between the driving scroll 30 and the driven scroll 40 is at the phase X5, the discharge communication hole 38b is located at a location that is approximately opposite from the discharge passage 67 with respect to the rotational direction R1 across the rotation axis O1, as illustrated in FIG. 11. Therefore, as indicated by the dashed arrow in FIG. 11, the refrigerant gas discharged from the discharge chamber 91 to the connection passage 38a makes an approximately half turn in the rotational direction R1 within the second insertion hole 61 from the discharge communication hole 38b, and then flows through the discharge passage 67.

That is, when the phase between the discharge passage 67 and the discharge communication hole 38b is in a state illustrated in FIG. 11, the flow resistance is at a maximum. As a result, in this compressor, when the flow rate of refrigerant gas to be discharged from the compression chamber 12 to the discharge chamber 91 is at the maximum, the discharge passage 67 and the discharge communication hole 38b are at a phase that maximizes flow resistance.

In this compressor, when the discharge passage 67 and the discharge communication hole 38b are shifted in the rotational direction R1 from their positions in which the discharge passage 67 and the discharge communication hole 38b face generally directly each other (see FIG. 9), it becomes difficult for the refrigerant gas to flow from the discharge communication hole 38b into the discharge passage 67. Therefore, the flow resistance becomes greater than the minimum. Thus, in this compressor, the discharge passage 67 and the discharge communication hole 38b enter a phase in which the flow resistance increases as the flow rate of the refrigerant gas to be discharged from the compression chamber 12 to the discharge chamber 91 approaches a maximum. More specifically, as the rotational phase between the driving scroll 30 and the driven scroll 40 approach the rotational phase at which the flow rate of the refrigerant gas to be discharged into the discharge chamber 91 is at the maximum, the discharge passage 67 of the discharge portion 63 and the discharge communication hole 38b enter a phase in which the flow resistance increases.

As described above, in this compressor, the change in phase between the discharge passage 67 and the discharge communication hole 38b, and hence the change in phase between the discharge portion 63 and the discharge communication hole 38b, change the flow resistance, and this change in flow resistance changes the magnitude of the canceling pulsation. As illustrated in FIG. 12, in this compressor, the canceling pulsation has a waveform that is in opposite phase to the waveform of the discharge pulsation. As a result, although discharge pulsation inevitably occurs due to the discharge of the refrigerant gas from the compression chambers 12 to the discharge chamber 91, the canceling pulsation acts to counter the discharge pulsation, thereby reducing the discharge pulsation.

When the rotor 11 rotates at a low speed, that is, when the compression mechanism 14 operates at a low speed, a volumetric flow rate of the refrigerant gas flowing from the discharge communication hole 38b to the discharge passage 67 decreases. As a result, the change in flow velocity resulting from the change in flow resistance is reduced, and therefore, a pressure fluctuation caused by the change in flow velocity is reduced. Therefore, when the compression mechanism 14 operates at a low speed, the pulsation reduction effect by the pulsation canceling function is small.

In this regard, even when the compression mechanism 14 operates at a low speed in the compressor, the discharge pulsation can be appropriately reduced in the discharge chamber 91 where an appropriate volume is secured. That is, when the compression mechanism 14 operates at a low speed, the amount of lubricating oil 18 that accumulates in the discharge chamber 91 is small, as illustrated in FIG. 1, so that a large volume to reduce the pulsation by the muffler effect may be secured in the discharge chamber 91. Therefore, in this compressor, even when the compression mechanism 14 operates at a low speed, the muffler effect effectively exerted in the discharge chamber 91 can reduce the discharge pulsation appropriately.

On the other hand, when the compression mechanism 14 operates at a high speed, i.e., when the rotor 11 rotates at a high speed, as illustrated in FIG. 13, the amount of the lubricating oil 18 that accumulates in the discharge chamber 91 increases. This reduces the volume to reduce the pulsation by the muffler effect in the discharge chamber 91. Therefore, when the compression mechanism 14 operates at a high speed, the pulsation reduction effect by the muffler effect in the discharge chamber 91 becomes smaller.

In this regard, when the compression mechanism 14 operates at a high speed, the pulsation cancelling effect is more effectively exerted in this compressor. Therefore, even when the compression mechanism 14 operates at a high speed, the discharge pulsation can be appropriately reduced by the pulsation canceling function in this compressor.

Furthermore, in this compressor, the outer diameter of the second sliding bearing 52 is smaller than that of the discharge chamber 91. Even if the diameter of the discharge chamber 91 is increased, the diameter of the second sliding bearing 52 is not increased. In other words, the second sliding bearing 52 is configured such that its diameter does not exceed, nor is it equal to, the diameter of the discharge chamber 91. As a result, an increase in power loss in the second sliding bearing 52 can be suppressed in this compressor. This can suppress a decrease in compressor efficiency. Furthermore, even if the first cover body 37 rotates at a high speed in conjunction with the rotor 11 rotating at a high speed, the second sliding bearing 52 can suitably support the first cover body 37, and further the driving scroll 30, via the first cover body 37.

Therefore, the compressor of the first embodiment can achieve high quietness while suppressing a decrease in efficiency.

In particular, in this compressor, the first cover body 37 is fixed to the driving scroll 30, and the discharge chamber 91 is formed between the driving scroll end plate 31 and the first cover body 37. Therefore, when the driving scroll 30 and the first cover body 37 rotate during operation of the compression mechanism 14, the centrifugal force generated by the rotation of the first cover body 37 and the like acts on the fluid discharged into the discharge chamber 91. As a result, the refrigerant gas and the lubricating oil 18 can be separated suitably in the discharge chamber 91. The lubricating oil 18 separated from the refrigerant gas tends to be attached to the inner peripheral surface of the discharge chamber 91 due to the centrifugal force of the first cover body 37, and the like, and also tends to remain in the discharge chamber 91 in a portion outward in the radial direction of the first cover body 37. Therefore, the lubricating oil 18 is less likely to be contained in the refrigerant gas to be discharged to the outside of the compressor via the discharge communication portion 38 and the discharge portion 63.

In addition, the discharge chamber 91 is located in front of the compression chamber 12 across the driving scroll end plate 31, and the discharge chamber 91 is close to the compression chamber 12, which allows the refrigerant gas and the lubricating oil 18 to be sufficiently separated in the discharge chamber 91.

The recirculation passage 370 is formed in the outer peripheral wall 37a of the first cover body 37. Therefore, in this compressor, the centrifugal force acting on the first cover body 37 and the like, more specifically, the pressure difference between the discharge chamber 91 and the intake chamber 65 in addition to the centrifugal force acting on the first cover body 37, allows the lubricating oil 18 together with part of the refrigerant gas in the discharge chamber 91 to flow into the intake chamber 65 through the recirculation passage 370. In this way, the lubricating oil 18 having flowed out from the discharge chamber 91 into the intake chamber 65 is recirculated to the intake space 30a and hence the compression chamber 12, together with the refrigerant gas drawn into the intake port 35b. Accordingly, the insides of the compression chambers 12 can be lubricated with the lubricating oil 18 in the compressor, so that the driving scroll end plate 31, the driving scroll spiral body 33, the driven scroll end plate 41, and the driven scroll spiral body 43 are less likely to wear. Furthermore, the lubricating oil 18 having flowed out from the discharge chamber 91 to the intake chamber 65 also lubricates the rotor 11, the first sliding bearing 51, the second sliding bearing 52, and the like.

Furthermore, the discharge chamber 91 is formed of the first recess 30b provided in the driving scroll end plate 31 and the second recess 37e provided in the first cover body 37. This configuration allows the size, shape, and position of the discharge chamber 91 to be easily changed by changing the size, shape, and position of each of the first recess 30b and the second recess 37e according to its purpose. As a result, a degree of freedom in design of the discharge chamber 91 in the compression mechanism 14 is increased.

Since the second boss 37d having the discharge communication portion 38 is provided in the first cover body 37 fixed to the driving scroll 30, the discharge communication portion 38 is easily formed in the driving scroll 30.

In addition, the compressor includes the discharge reed valve 57 provided in the driving scroll 30, and the discharge reed valve 57 allows the refrigerant gas to be discharged from the compression chambers 12 to the discharge chamber 91 while preventing the refrigerant gas from flowing from the discharge chamber 91 to the compression chambers 12. Therefore, occurrence of pulsation due to refrigerant gas flowing back from the discharge chamber 91 to the compression chambers 12 is suitably prevented in the compressor. Furthermore, since the discharge communication hole 38b is formed in second boss 37d, the discharge communication hole 38b is located downstream of the discharge reed valve 57 in a flow direction in which refrigerant gas flows. Thus, in the compressor, the pressure fluctuation that occurs when the refrigerant gas flows from the discharge communication hole 38b to the discharge passage 67 facilitates opening of the discharge reed valve 57. As a result, the discharge reed valve 57 can be opened and closed suitably in this compressor.

In the compressor, the discharge portion 63 has the discharge passage 67 and the discharge communication port 69, and the discharge passage 67 and the discharge communication hole 38b are in communication with each other in the radial direction of the housing 6. According to this configuration, the entire compressor including the housing 6 may be downsized in the direction of the rotation axis O1 as compared with a configuration in which the discharge passage 67 and the discharge communication hole 38b are in communication with each other in the direction of the rotation axis O1. Thus, in this compressor, the length of the discharge chamber 91 in the direction of the rotation axis O1 is set to the third length L3, and the discharge chamber 91 is formed long in the direction of the rotation axis O1 while increasing its volume. This configuration suppresses an excessive increase in size of the housing 6 in an axial direction as a whole.

Second Embodiment

As illustrated in FIG. 14, a compressor of the second embodiment includes the housing 6 formed of a housing body 60 and a housing cover 70. In addition, in the compressor of the second embodiment, the compression mechanism 14 includes a second cover body 81 in place of the first cover body 37. The second cover body 81 is an example of the “cover body” of the present disclosure.

The housing cover 70 is also made of an aluminum alloy. The housing cover 70 is disposed in front of the housing body 60. The housing cover 70 has a substantially disk shape extending around the rotation axis O1. The housing cover 70 has a front surface 70a facing forward, a rear surface 70b facing rearward and located opposite from the front surface 70a, and an outer peripheral surface 70c connected to the front surface 70a and the rear surface 70b and located between the front surface 70a and the rear surface 70b. The housing cover 70 is fixed to the outer peripheral wall 60a of the housing body 60 in the same manner as the housing cover 62 of the compressor of the first embodiment.

The housing cover 70 has a second insertion hole 72 and a discharge communication port 73. The discharge communication port 73 is an example of the “discharge portion” of the present disclosure.

The second insertion hole 72 extends in a columnar shape with the rotation axis O1 at the center, and extends in the housing cover 70 in the direction of the rotation axis O1. A rear end of the second insertion hole 72 is opened at the rear surface 70b. The second sliding bearing 52 is provided in the second insertion hole 72, similarly to the compressor of the first embodiment.

The discharge communication port 73 extends through the housing cover 70 in the direction of the rotation axis O1. Thus, the discharge communication port 73 has a front end that is opened at the front surface 70a, and a rear end that is in communication with the second insertion hole 72. As illustrated in FIGS. 15A to 15D, the discharge communication port 73 is formed in a columnar shape and eccentric with respect to the rotation axis O1. That is, the discharge communication port 73 is formed in the housing cover 70 at a position eccentric with respect to the rotation axis O1. The discharge communication port 73 is connected to a condenser (not illustrated) via a pipe (not illustrated).

As illustrated in FIG. 14, the second cover body 81 has the same configuration as that of the first cover body 37 of the compressor of the first embodiment, except that the second cover body 81 has a second boss 81d instead of the second boss 37d of the compressor of the first embodiment. The second boss 81d is an example of the “rotating shaft portion” of the present disclosure.

That is, the second cover body 81 is a bottomed tubular member, and has an outer peripheral wall 81a, a front wall 81b, and a flange 81c, similarly to the first cover body 37 of the compressor of the first embodiment. In addition, a recirculation passage 810 similar to the recirculation passage 370 of the compressor of the first embodiment is formed in the outer peripheral wall 81a. Thus, the second cover body 81 has a second recess 81e that is defined by an inner peripheral surface of the outer peripheral wall 81a and a rear surface of the front wall 81b, and extends in a substantially columnar shape in the direction of the rotation axis O1.

The driving scroll end plate 31 of the second embodiment has the same configuration as that of the driving scroll end plate 31 of the compressor of the first embodiment. In other words, the driving scroll end plate 31 has a first recess 30b, which is recessed rearward in a substantially columnar shape from the front surface 311 of the driving scroll end plate 31, and the discharge reed valve 57 and the like are fixed in the first recess 30b.

A discharge chamber 92 defined by the first recess 30b and the second recess 81e is formed between the driving scroll end plate 31 and the second cover body 81. The second length L2 and the third length L3 of the discharge chamber 92 are set to be the same as those of the discharge chamber 91 of the compressor of the first embodiment, respectively.

The second boss 81d is formed integrally with the front wall 81b at the center thereof, and protrudes forward from the front wall 81b in the direction of the rotation axis O1 and the driven axis O2. As a result, the center of the second boss 81d is coaxial with the rotation axis O1.

In addition, the second cover body 81 has a connection passage 82. The connection passage 82 is an example of the “discharge communication portion” of the present disclosure. The connection passage 82 extends through the front wall 81b of the second cover body 81, including the inside of the second boss 81d, in the direction of the rotation axis O1. As illustrated in FIGS. 14 and 15A through 15D, the connection passage 82 is formed in a columnar shape and eccentric with respect to the rotation axis O1. That is, the connection passage 82 is formed in the second cover body 81 at a position eccentric with respect to the rotation axis O1. The connection passage 82 has a smaller diameter than that of the discharge communication port 73. In FIGS. 15A through 15D, for ease of explanation, the discharge communication port 73 and the connection passage 82 are illustrated in a simplified form, and the second boss 81d and the like are not illustrated.

As illustrated in FIG. 14, in this compressor, similarly to the compressor of the first embodiment, the second cover body 81, the driving scroll end plate 31, the driving scroll peripheral wall 32, and the closing body 35 are connected by a plurality of bolts 50. Accordingly, the second cover body 81 covers the driving scroll end plate 31 from the front. In this way, the connection passage 82 is in communication with the discharge chamber 92 from the front. Furthermore, the connection passage 82 is located downstream of the discharge reed valve 57 in the flow direction in which the refrigerant gas flows.

In this compressor, the second boss 81d is inserted into the second insertion hole 72. Thus, the second boss 81d is rotatably supported by the second sliding bearing 52 inside the second insertion hole 72. The discharge communication port 73 and the connection passage 82 are in communication with each other in the direction of the rotation axis O1. It is to be noted that other components of the compressor of the second embodiment are the same as those of the compressor of the first embodiment, and components of the second embodiment that correspond to those of the first embodiment are designated by the same reference signs and detailed description of the configurations will be omitted.

In this compressor, the refrigerant gas compressed in the compression chambers 12 is discharged into the discharge chamber 92 through the discharge port 30c. The refrigerant gas discharged into the discharge chamber 92 flows through the connection passage 82, and is discharged from the discharge communication port 73 toward the condenser.

In this compressor, the discharge communication port 73 and the connection passage 82 are both eccentric with respect to the rotation axis O1, as illustrated in FIGS. 15A through 15D. Therefore, in this compressor, a phase between the discharge communication port 73 and the connection passage 82 changes while the driving scroll 30 makes one rotation in the rotational direction R1 as illustrated in FIG. 15A through 15D.

That is, in this compressor, when the rotation angle of the driving scroll 30 is zero degrees, the discharge communication port 73 and the connection passage 82 are at a phase illustrated in FIG. 15A. When the driving scroll 30 rotates by approximately 90 degrees in the rotational direction R1 from the position illustrated in FIG. 15A, the discharge communication port 73 and the connection passage 82 reach a phase illustrated in FIG. 15B. When the driving scroll 30 rotates by approximately 90 degrees in the rotational direction R1 from the position illustrated in FIG. 15B (when the driving scroll 30 rotates by approximately 180° in the rotational direction R1 from the position illustrated in FIG. 15A), the discharge communication port 73 and the connection passage 82 reach a phase illustrated in FIG. 15C. When the driving scroll 30 rotates by approximately 90 degrees in the rotational direction R1 from the position illustrated in FIG. 15C (when the driving scroll 30 rotates by approximately 270° in the rotational direction R1 from the position illustrated in FIG. 15A), the discharge communication port 73 and the connection passage 82 reach a phase illustrated in FIG. 15D.

Accordingly, when a communication area between the discharge communication port 73 and the connection passage 82 changes during one rotation of the driving scroll 30, in the compressor, a flow resistance of the refrigerant gas flowing from the connection passage 82 to the discharge communication port 73 changes.

Specifically, if the communication area between the discharge communication port 73 and the connection passage 82 is increased, the flow resistance is reduced, and if the communication area between the discharge communication port 73 and the connection passage 82 is reduced, the flow resistance is increased. Therefore, in the compressor, when the phase between the discharge communication port 73 and the connection passage 82 is in the state illustrated in FIG. 15A, the communication area between the discharge communication port 73 and the connection passage 82 is maximized and the flow resistance is minimized. On the other hand, when the phase between the discharge communication port 73 and the connection passage 82 is in the state illustrated in FIG. 15C, the communication area between the discharge communication port 73 and the connection passage 82 is minimized, and the flow resistance is maximized.

Here, in this compressor, when the flow rate of the refrigerant gas discharged from the compression chamber 12 to the discharge chamber 92 is at a minimum, the discharge communication port 73 and the connection passage 82 are at a phase that minimizes the flow resistance (see FIG. 15A). Then, when the flow rate of the refrigerant gas discharged from the compression chamber 12 to the discharge chamber 92 is at a maximum, the discharge communication port 73 and the connection passage 82 are at a phase that maximizes the flow resistance (see FIG. 15C).

As a result, in the compressor of the second embodiment, although discharge pulsation inevitably occurs due to the discharge of the refrigerant gas from the compression chambers 12 to the discharge chamber 92, the discharge pulsation is reduced by the canceling pulsation effect, similarly to the compressor of the first embodiment.

In addition, since the discharge communication port 73 and the connection passage 82 are in communication with each other in the direction of the rotation axis O1, the entire compressor including the housing 6 may be downsized in the radial direction as compared with a configuration in which the discharge communication port 73 and the connection passage 82 are in communication with each other in the radial direction of the housing 6. Other operations of the compressor of the second embodiment are the same as those of the compressor of the first embodiment.

Third Embodiment

As illustrated in FIG. 16, a compressor of the third embodiment includes the housing 6 formed of a housing body 60 and a housing cover 75. In addition, in the compressor of the third embodiment, the compression mechanism 14 includes a third cover body 83 in place of the first cover body 37 of the first embodiment. The third cover body 83 is an example of the “cover body” of the present disclosure.

The housing cover 75 is formed of a body member 75a and a holding member 75b. The body member 75a is made of an aluminum alloy. The body member 75a has a substantially disk shape extending around the rotation axis O1, similarly to the housing cover 70 of the compressor of the second embodiment. The body member 75a has a front surface 751 facing forward, a rear surface 752 facing rearward and located opposite from the front surface 751, and an outer peripheral surface 753 connected to the front surface 751 and the rear surface 752 and located between the front surface 751 and the rear surface 752.

The body member 75a is fixed to the outer peripheral wall 60a of the housing body 60 in the same manner as the housing cover 62 of the compressor of the first embodiment. Accordingly, the housing body 60 and the housing cover 75 are fixed together in the compressor of the third embodiment.

The body member 75a has a second insertion hole 76 and a first communication port 77a. The second insertion hole 76 is formed in a columnar shape extending around the rotation axis O1, and extends in the body member 75a in the direction of the rotation axis O1 extends. A rear end of the second insertion hole 76 is opened at the rear surface 752. Here, the second insertion hole 76 has a larger diameter than that of the second insertion hole 72 of the compressor of the second embodiment.

The first communication port 77a extends through the body member 75a in the direction of the rotation axis O1. Thus, the first communication port 77a has a front end that is opened at the front surface 751, and a rear end that is in communication with the second insertion hole 76. Although the detailed illustration is omitted, the first communication port 77a is formed in a columnar shape and eccentric with respect to the rotation axis O1, similarly to the discharge communication port 73 of the compressor of the second embodiment. That is, the first communication port 77a is formed in the body member 75a at a position eccentric with respect to the rotation axis O1.

The holding member 75b is made of resin. The holding member 75b has a generally bottomed tubular shape. A second communication port 77b is formed in a front portion of the holding member 75b. The second communication port 77b extends through the front portion of the holding member 75b in the direction of the rotation axis O1. The second communication port 77b extends in a columnar shape that is coaxial with and has the same diameter as the first communication port 77a. That is, the second communication port 77b is formed in the front portion of the holding member 75b at a position eccentric with respect to the rotation axis O1.

The holding member 75b is accommodated in the second insertion hole 76. The holding member 75b is accommodated in the second insertion hole 76 in a non-rotatable state. Thus, in the housing cover 75, neither the body member 75a nor the holding member 75b can rotate. Furthermore, with the holding member 75b accommodated in the second insertion hole 76, the second communication port 77b is located behind the first communication port 77a and is in communication with the first communication port 77a. In this way, the first communication port 77a and the second communication port 77b form the discharge communication port 77. That is, the discharge communication port 77 is formed in the housing cover 75 at a position eccentric with respect to the rotation axis O1. The discharge communication port 77 is an example of the “discharge portion” of the present disclosure.

Furthermore, a radial ball bearing 78 is provided inside the holding member 75b. The radial ball bearing 78 is an example of the “bearing” of the present disclosure. The holding member 75b holds the radial ball bearing 78 while being accommodated in the second insertion hole 76. An outer diameter of the radial ball bearing 78 is a defined as a fourth length L4. The fourth length L4 of the radial ball bearing 78 is longer than the first length L1 of the second sliding bearing 52 of the compressor of the second embodiment. Furthermore, seal rings 79a, 79b are provided on the outer peripheral surface of the holding member 75b. The seal rings 79a, 79b seal a gap between the outer peripheral surface of the holding member 75b and an inner peripheral surface of the second insertion hole 76. Instead of the radial ball bearing 78, a sliding bearing may be provided inside the holding member 75b. Furthermore, the holding member 75b may be made of synthetic rubber or metal or the like having lower rigidity than the body member 75a.

The third cover body 83 has the same configuration as the second cover body 81 of the compressor of the second embodiment. That is, the third cover body 83 is a bottomed tubular member, has an outer peripheral wall 83a, a front wall 83b, and a flange (not illustrated), similarly to the second cover body 81 of the compressor of the second embodiment, and has a recirculation passage 830 formed in the outer peripheral wall 83a. In addition, the third cover body 83 has a second recess 83e that is defined by an inner peripheral surface of the outer peripheral wall 83a and a rear surface of the front wall 83b, and extends in a substantially columnar shape in the direction of the rotation axis O1.

A discharge chamber 93 defined by the first recess (not illustrated) and the second recess 83e is formed between the driving scroll end plate (not illustrated) and the third cover body 83. The second length L2 and the third length L3 of the discharge chamber 93 are set to be the same as those of the discharge chamber 92 of the compressor of the second embodiment, respectively. The second length L2, which is the length of the inner diameter of the discharge chamber 93, is longer than the fourth length L4, which is a length of the outer diameter of the radial ball bearing 78.

Further, the third cover body 83 has a second boss 83d, similarly to the second cover body 81 of the compressor of the second embodiment. The second boss 83d is an example of the “rotating shaft portion” of the present disclosure. The second boss 83d is formed integrally with the front wall 83b at the center thereof, and protrudes forward from the front wall 83b in the direction of the rotation axis O1 and the driven axis O2. As a result, the center of the second boss 83d is coaxial with the rotation axis O1. Here, a forward protruded amount of the second boss 83d is smaller than that of the second boss 81d of the compressor of the second embodiment.

The third cover body 83 has a connection passage 84, similarly to the second cover body 81 of the compressor of the second embodiment. The connection passage 84 is an example of the “discharge communication portion” of the present disclosure. The connection passage 84 extends through the front wall 83b of the third cover body 83, including the inside of the second boss 83d, in the direction of the rotation axis O1. The connection passage 84 is formed in a columnar shape and eccentric with respect to the rotation axis O1, similarly to the connection passage 82 of the compressor of the second embodiment. That is, the connection passage 84 is formed in the third cover body 83 at a position eccentric with respect to the rotation axis O1. Furthermore, the connection passage 84 has a smaller diameter than that of the discharge communication port 77.

The third cover body 83 is connected to the driving scroll end plate (not illustrated) by a plurality of bolts (not illustrated), similarly to the second cover body 81 of the compressor of the second embodiment. Thus, the connection passage 84 is in communication with the discharge chamber 93 from the front. Furthermore, the connection passage 84 is located downstream of the discharge reed valve (not illustrated) in the flow direction in which the refrigerant gas flows.

In this compressor, the second boss 83d is inserted through an inside of the radial ball bearing 78. As a result, the second boss 83d is rotatably supported inside the holding member 75b, and further inside the second insertion hole 76 of the body member 75a. The discharge communication port 77 and the connection passage 84 are in communication with each other in the direction of the rotation axis O1. Other configurations of this compressor are the same as those of the compressor of the second embodiment.

In this compressor, the discharge communication port 77 and the connection passage 84 are both eccentric with respect to the rotation axis O1. Therefore, similarly to the compressor of the second embodiment, a phase between the discharge communication port 77 and the connection passage 84 changes while the driving scroll 30 makes one rotation in the rotational direction R1 (see FIG. 15A through 15D). In this way, in this compressor, similarly to the compressor of the second embodiment, discharge pulsation can be reduced by the pulsation canceling function.

In this compressor, when the refrigerant gas is compressed in the compression chamber (not illustrated), vibration inevitably occurs in the driving scroll 30 and other components. In this regard, the holding member 75b, which is made of resin and provided in the second insertion hole 76, holds the radial ball bearing 78. As a result, the holding member 75b can suppress transmission of vibration of the driving scroll 30 to the body member 75a through the second boss 83d and the radial ball bearing 78. Therefore, vibration of the housing cover 75, and hence the housing 6, can be suppressed as much as possible during operation in the compressor. Other operations of the compressor of the third embodiment are the same as those of the compressor of the second embodiment.

Fourth Embodiment

As illustrated in FIG. 17, in a compressor of the fourth embodiment, the compression mechanism 14 has a fourth cover body 85 in place of the first cover body 37 of the compressor of the first embodiment. The fourth cover body 85 is an example of the “cover body” of the present disclosure. In the compressor of the fourth embodiment, the driving scroll 30 has a driving scroll end plate 310 in place of the driving scroll end plate 31 of the compressor of the first embodiment.

A length of the driving scroll end plate 310 in the direction of the rotation axis O1 is shorter than that of the driving scroll end plate 31 of the compressor of the first embodiment. Furthermore, a front surface 311 of the driving scroll end plate 310 does not have a recess corresponding to the first recess 30b of the driving scroll end plate 31. Other than these, the driving scroll end plate 310 has the same configuration as the driving scroll end plate 31 of the compressor of the first embodiment.

The fourth cover body 85 has the same configuration as that of the first cover body 37 of the compressor of the first embodiment, except that the fourth cover body 85 has an outer peripheral wall 85a instead of the outer peripheral wall 37a of the compressor of the first embodiment. The outer peripheral wall 85a of the fourth cover body 85 is longer than the outer peripheral wall 37a of the compressor of the first embodiment in the direction of the rotation axis O1.

That is, the fourth cover body 85 is a bottomed tubular member, and has the outer peripheral wall 85a, a front wall 85b, and a flange 85c, similarly to the first cover body 37 of the compressor of the first embodiment. In addition, a recirculation passage 850 similar to the recirculation passage 370 of the compressor of the first embodiment is formed in the outer peripheral wall 85a. Thus, the fourth cover body 85 has a second recess 85e that is defined by an inner peripheral surface of the outer peripheral wall 85a and a rear surface of the front wall 85b, and extends in a substantially columnar shape in the direction of the rotation axis O1.

A discharge chamber 94 defined by the front surface 311 of the driving scroll end plate 310 and the second recess 85e is formed between the driving scroll end plate 310 and the fourth cover body 85. The second length L2 and the third length L3 of the discharge chamber 94 are set to be the same as those of the discharge chamber 91 of the compressor of the first embodiment, respectively.

Further, the fourth cover body 85 has a second boss 85d, similarly to the first cover body 37 of the compressor of the first embodiment. The second boss 85d is an example of the “rotating shaft portion” of the present disclosure. The fourth cover body 85 has a discharge communication portion 86 formed of a connection passage 86a and a discharge communication hole 86b, similarly to the first cover body 37 of the compressor of the first embodiment.

In the compressor of the fourth embodiment, the front surface 311 of the driving scroll end plate 310 is formed as a flat surface, which allows the driving scroll 30 to be manufactured easily.

Other configurations and effects of this compressor are the same as those of the compressor of the first embodiment.

Fifth Embodiment

As illustrated in FIG. 18, in a compressor of the fifth embodiment, the compression mechanism 14 includes a fifth cover body 87 in place of the first cover body 37 of the compressor of the first embodiment. The fifth cover body 87 is an example of the “cover body” of the present disclosure. In the compressor of the fifth embodiment, the driving scroll 30 has a driving scroll end plate 320 in place of the driving scroll end plate 31 of the compressor of the first embodiment.

A length of the driving scroll end plate 320 in the direction of the rotation axis O1 is longer than that of the driving scroll end plate 31 of the compressor of the first embodiment. Furthermore, a length of a first recess 30d formed in the front surface 311 of the driving scroll end plate 320 in the direction of the rotation axis O1 is longer than that of the first recess 30b of the compressor of the first embodiment. Other than these, the driving scroll end plate 320 of the fifth embodiment has the same configuration as the driving scroll end plate 31 of the compressor of the first embodiment.

The fifth cover body 87 has a cover main body 87a and a second boss 87b. The second boss 87b is an example of the “rotating shaft portion” of the present disclosure. The cover main body 87a extends in a substantially disk shape, perpendicularly to the rotation axis O1 and the driven axis O2. A diameter of the cover main body 87a is substantially the same as that of the driving scroll end plate 320. The second boss 87b is formed integrally with the cover main body 87a, and protrudes forward from the cover main body 87a in the direction of the rotation axis O1 and the driven axis O2. Other configurations of the second boss 87b are the same as those of the second boss 37d of the compressor of the first embodiment.

The fifth cover body 87 has a discharge communication portion 88 formed of a connection passage 88a and a discharge communication hole 88b, similarly to the first cover body 37 of the compressor of the first embodiment.

In the driving scroll 30, the fifth cover body 87, the driving scroll end plate 320, the driving scroll peripheral wall 32, and the closing body 35 are connected by a plurality of bolts 50 with the cover main body 87a of the fifth cover body 87 placed in contact with the front surface 311 of the driving scroll end plate 320. Accordingly, the driving scroll end plate 320, the driving scroll peripheral wall 32, the closing body 35, and the fifth cover body 87 are integrated together in the driving scroll 30.

In this way, a discharge chamber 95 defined by the first recess 30d and the rear surface of the cover main body 87a is formed between the driving scroll end plate 320 and the fifth cover body 87. A fifth length L5, which is the length of the inner diameter of this discharge chamber 95, is longer than the second length L2, which is the length of the inner diameter of the discharge chamber 91 of the compressor of the first embodiment, and a sixth length L6, which is the length of the discharge chamber 95 in the direction of the rotation axis O1, is shorter than the third length L3 of the discharge chamber 91 of the compressor of the first embodiment. It is noted that the fifth length L5, which is the length of the inner diameter of the discharge chamber 95, may be the same as the second length L2 or may be shorter than the second length L2. Furthermore, the sixth length L6, which is the length of the discharge chamber 95 in the direction of the rotation axis O1, may be set to the third length L3 or may be longer than the third length L3.

In the fifth cover body 87, the cover main body 87a covers the first recess 30d of the driving scroll end plate 320 from the front. Thus, the discharge communication portion 88 is in communication with the discharge chamber 95 defined by the first recess 30d from the front.

In the compressor, the cover main body 87a does not have an outer peripheral wall or a flange, so that the fifth cover body 87 can be easily manufactured. Furthermore, since the sixth length L6 of the discharge chamber 95 is shorter, a length of the housing 6 along the axis can be made shorter than that of the compressor of the first embodiment.

Other configurations and effects of this compressor are the same as those of the compressor of the first embodiment.

Although the present disclosure has been described above based on the first to fifth embodiments, the present disclosure is not limited to the above-described first to fifth embodiments, and may be modified as appropriate within the gist of the present disclosure.

In the compressor of the first embodiment, the driving scroll 30 and the driven scroll 40 are assembled with the driven scroll 40 accommodated in the driving scroll 30. However, the present disclosure is not limited thereto, and the driving scroll 30 and the driven scroll 40 may be assembled with the driven scroll 40 disposed outside the driving scroll 30. In this case, the driven scroll end plate 41 and the “cover body” of the present disclosure may be fixed together. The same applies to the compressors according to the second to fifth embodiments.

In the compressor of the first embodiment, the second boss 37d is defined as the “rotating shaft portion” of the present disclosure. The second boss 37d is rotatably supported by the second support portion 66 with the second boss 37d inserted through the second insertion hole 61. However, the present disclosure is not limited to this. The second boss 37d is rotatably supported by the second support portion 66 with the second support portion 66 inserted into an inside of the second boss 37d. The same applies to the compressors according to the second to fifth embodiments.

In the compressor of the second embodiment, the discharge communication port 73 is formed in a columnar shape and eccentric with respect to the rotation axis O1. However, the shape of the discharge communication port 73 is not limited to this, and it may be another shape. The same applies to the discharge communication port 77 of the compressor of the third embodiment.

Furthermore, in the compressor of the first embodiment, the driving scroll 30 is integrated with the rotor 11 by fixing the driving scroll peripheral wall 32 to the rotor 11, but the configuration is not limited to this. The first cover body 37 and the rotor 11 may be integrated together by fixing the rotor 11 to the outer peripheral wall 37a. The same applies to the compressors of the second to fourth embodiments, and the rotor 11 may be fixed to the “cover body” of the present disclosure.

The compressor of the first embodiment may have a configuration in which the driving scroll 30 is spaced from the rotor 11 in the direction of the rotation axis O1 by connecting the driving scroll 30 to the rotor 11 via a shaft so that motive power is transmitted. The same applies to the compressors according to the second to fifth embodiment.

In the compressor of the first embodiment, the driven mechanism 20 is formed of the anti-rotation pins 21 and the rings 22. However, the configuration is not limited thereto, and the driven mechanism 20 may be formed of a pin-ring-pin mechanism in which two pins slide on an inner peripheral surface of one free ring, a pin-and-pin mechanism in which outer peripheral surfaces of two pins slide on each other, a mechanism using an Oldham coupling, or the like. The same applies to the compressors according to the second to fifth embodiments.

This specification includes the following disclosure.

Additional Note 1

A co-rotating scroll compressor comprising:

• • a housing having a discharge portion through which fluid is discharged to an outside; and
  • a compression mechanism disposed in the housing;
  • the compression mechanism having:
    • a compression chamber in which fluid is compressed while a volume of the compression chamber is reduced;
    • a discharge chamber that is in communication with the compression chamber and to which the fluid compressed in the compression chamber is discharged; and
    • a rotating shaft portion that is supported by the housing via a bearing so as to be rotatable around a rotation axis,
  • the compression mechanism including a driving scroll and a driven scroll, the driving scroll being configured to be rotated by a drive mechanism, the driving scroll having a driving scroll end plate and a driving scroll spiral body that is formed integrally with the driving scroll end plate and protrudes in a spiral shape toward the driven scroll; and
    • the driven scroll facing the driving scroll, and configured to be rotated by the driving scroll and a driven mechanism at a position eccentric with respect to the driving scroll to form the compression chamber between the driving scroll and the driven scroll, the driven scroll having a driven scroll end plate, and a driven scroll spiral body that is formed integrally with the driven scroll end plate and protrudes toward the driving scroll in a spiral shape, wherein characterized in that
  • the discharge chamber has a diameter larger than an outer diameter of the bearing,
  • the rotating shaft portion has a discharge communication portion through which the fluid discharged into the discharge chamber flows to the discharge portion,
  • a change in phase between the discharge portion and the discharge communication portion with rotation of the rotating shaft portion changes a flow resistance for the fluid flowing from the discharge communication portion to the discharge portion, and
  • the discharge portion and the discharge communication portion reach a phase in which the flow resistance increases as a flow rate of the fluid to be discharged from the compression chamber to the discharge chamber approaches a maximum.

Additional Note 2

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

• • the compression mechanism includes a cover body that is fixed to the driving scroll or the driven scroll, and is provided with the rotating shaft portion, and
  • the discharge chamber is formed between the cover body and the driving scroll end plate of the driving scroll to which the cover body is fixed, or between the cover body and the driven scroll end plate of the driven scroll to which the cover body is fixed.

Additional Note 3

The co-rotating scroll compressor according to Additional note 1 or 2, wherein

• • lubricating oil is discharged into the discharge chamber together with the fluid compressed in the compression chamber, and
  • the discharge chamber and a portion in the housing where pressure is lower than the discharge chamber are connected via a recirculation passage through which the lubricating oil in the discharge chamber is recirculated.

Additional Note 4

The co-rotating scroll compressor according to any one of Additional notes 1 to 3, wherein

• • the discharge portion and the discharge communication portion are in communication with each other in a radial direction of the housing.

Additional Note 5

The co-rotating scroll compressor according to any one of additional notes 1 to 3, wherein

• • the discharge portion and the discharge communication portion are in communication with each other in a direction of the rotation axis.

Additional Note 6

The co-rotating scroll compressor according to claim 5, wherein

• • the discharge portion is formed in the housing at a position eccentric with respect to the rotation axis, and
  • the discharge communication portion is formed in the rotating shaft portion at a position eccentric with respect to the rotation axis.

Additional Note 7

The co-rotating scroll compressor according to any one of Additional notes 1 to 6, wherein

• • when the flow rate of the fluid to be discharged from the compression chamber to the discharge chamber is at a minimum, the discharge portion and the discharge communication portion are in a phase in which the flow resistance is minimized.

Additional Note 8

The co-rotating scroll compressor according to any one of Additional notes 1 to 7, characterized in that

• • when the flow rate of the fluid to be discharged from the compression chamber to the discharge chamber is at a maximum, the discharge portion and the discharge communication portion are in a phase in which the flow resistance is maximized.

Additional Note 9

The co-rotating scroll compressor according to any one of Additional notes 1 to 8, wherein

• • the compression mechanism includes a discharge valve that allows the fluid to be discharged from the compression chamber to the discharge chamber, and prevents the fluid from flowing from the discharge chamber to the compression chamber, and
  • the discharge communication portion is positioned downstream of the discharge valve in a flow direction in which the fluid flows.

Industrial Applicability

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