Compressor

Abstract

To provide a compressor capable of suppressing an increase in the size while actualizing high quietness.SOLUTION: The compressor includes a housing 6 and a compression mechanism 14, the housing 6 being formed with a discharge part 63, the compression mechanism 14 being formed with a compression chamber 12, and provided with a rotary shaft part 37b, the rotary shaft part 37b being formed with a discharge communication portion 37d. In the compressor, the discharge part 63 and the discharge communication portion 37d have phase changes with the rotation of the rotary shaft part 37b to change discharge side distribution resistance. Then, the discharge part 63 and the discharge communication portion 37d each have a phase where the discharge side distribution resistance increases as the flow amount of fluid to be discharged from the compression chamber 12 to a discharge chamber 8 approaches an approximately maximum.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a compressor. [Background technology]

[0002] Patent Document 1 discloses a conventional compressor. This compressor includes a housing and a compression mechanism. The housing is formed with a discharge part that discharges fluid to the outside, a suction part that draws in fluid from the outside, and a suction chamber that communicates with the suction part.

[0003] The compression mechanism is provided in the housing. More specifically, the compression mechanism has a drive scroll and a driven scroll. The drive scroll is rotatable about a rotation axis. The drive scroll has a drive end plate and a drive scroll that is integral with the drive end plate and protrudes in a spiral shape toward the driven scroll.

[0004] The driven scroll faces the driving scroll. The driven scroll is rotated eccentrically with respect to the driving scroll around a driven axis by the driving scroll and a driven mechanism. A compression chamber is formed between the driven scroll and the driving scroll. The driven scroll has a driven end plate and a driven scroll body that is integral with the driven end plate and protrudes in a spiral shape toward the driving scroll. A discharge chamber is formed in the driven scroll. The discharge chamber communicates with the compression chamber and also communicates with the discharge section.

[0005] In this compressor, fluid is drawn into the suction chamber from outside the housing through the suction portion. In this compression mechanism, the volume of the compression chamber changes with the rotation of the driving scroll and the driven scroll. As a result, in this compressor, fluid is drawn into the compression chamber from the suction chamber, and the fluid is compressed in the compression chamber as the volume of the compression chamber decreases. The fluid compressed in the compression chamber is discharged from the compression chamber to the discharge chamber and then discharged to the outside of the housing from the discharge portion. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] JP 2002-310073 A Summary of the Invention [Problem to be solved by the invention]

[0007] In this type of compressor, it is required to reduce noise caused by discharge pulsation and suction pulsation during operation. Therefore, in the above-mentioned conventional compressor, it is conceivable to reduce discharge pulsation by increasing the volume of the discharge chamber and enhancing the muffler effect of the discharge chamber. In this case, however, the compression mechanism becomes larger as the volume of the discharge chamber increases. This results in an increase in the size of the housing and, ultimately, the compressor. The same is true when the volume of the suction chamber is increased to reduce suction pulsation, and the compressor becomes larger due to the increase in the size of the housing.

[0008] The present invention has been made in consideration of the above-mentioned conventional circumstances, and has an object to provide a compressor that can be prevented from becoming large while achieving high quietness. [Means for solving the problem]

[0009] The first compressor of the present invention includes a housing having a discharge portion formed therein for discharging a fluid to an outside, a compression mechanism provided within the housing, The compression mechanism is provided with a compression chamber that compresses a fluid while reducing a volume thereof, and is provided with a rotating shaft portion that is rotatably supported about a rotation axis by the housing, a discharge chamber that communicates with the compression chamber and through which the fluid compressed in the compression chamber is discharged is formed in the housing or the compression mechanism; a discharge communication portion that allows the fluid discharged into the discharge chamber to flow to the discharge portion is formed in the rotating shaft portion, a phase between the discharge portion and the discharge communication portion changes with the rotation of the rotating shaft portion, thereby changing a discharge-side flow resistance, which is a flow resistance of a fluid flowing from the discharge communication portion to the discharge portion; The discharge portion and the discharge communication portion are in a phase where the discharge side flow resistance increases as the flow rate of the fluid discharged from the compression chamber to the discharge chamber approaches a maximum.

[0010] In the first compressor of the present invention, a discharge communication part is formed on the rotating shaft part of the compression mechanism, and this discharge communication part allows the fluid discharged to the discharge chamber to flow to the discharge part. As a result, in this compressor, the fluid compressed in the compression chamber and discharged to the discharge chamber reaches the discharge part from the discharge communication part. Also, in this compressor, the phase between the discharge part and the discharge communication part changes with the rotation of the rotating shaft part. Furthermore, the change in phase between the discharge part and the discharge communication part changes the discharge side flow resistance.

[0011] Here, in this compressor, pulsation occurs due to discharge-side flow resistance, and the magnitude of this pulsation changes as the discharge-side flow resistance changes. In this compressor, the discharge section and the discharge communication section are in a phase where the discharge-side flow resistance increases as the flow rate of the fluid discharged from the compression chamber to the discharge chamber approaches a maximum. As a result, in this compressor, the pulsation caused by the discharge-side flow resistance acts to cancel out the discharge pulsation that occurs when the fluid is discharged from the compression chamber to the discharge chamber. As a result, the compressor can reduce the discharge pulsation.

[0012] Thus, in this compressor, there is no need to form an excessively large discharge chamber in order to reduce discharge pulsation, and the compression mechanism and housing are unlikely to become large.

[0013] Therefore, the first compressor of the present invention can suppress an increase in size while realizing high quietness.

[0014] In the first compressor of the present invention, it is preferable that the discharge portion and the discharge communication portion communicate with each other in the radial direction of the housing. In this case, the housing, and therefore the entire compressor, can be made smaller in size in the direction of the rotation axis.

[0015] In the first compressor of the present invention, it is also preferable that the discharge portion and the discharge communication portion communicate with each other in the direction of the rotation axis. In this case, the housing, and therefore the entire compressor, can be made compact in the radial direction of the housing.

[0016] In this case, the discharge portion may be formed on the housing eccentrically with respect to the rotation axis, and the discharge communication portion is preferably formed on the rotating shaft eccentrically with respect to the rotation axis, whereby the phase of the discharge portion and the discharge communication portion can be suitably changed.

[0017] In the first compressor of the present invention, when the flow rate of the fluid discharged from the compression chamber to the discharge chamber is at a minimum, the discharge portion and the discharge communication portion are preferably in a phase that minimizes the flow resistance on the discharge side.

[0018] In the first compressor of the present invention, when the flow rate of the fluid discharged from the compression chamber to the discharge chamber is at a maximum, the discharge portion and the discharge communication portion are preferably in a phase that maximizes the discharge side flow resistance.

[0019] In these cases, the pulsation caused by the discharge-side flow resistance acts to more effectively cancel out the discharge pulsation, and therefore the discharge pulsation can be more effectively reduced. Note that "the flow rate of the fluid discharged from the compression chamber to the discharge chamber is minimum" includes cases where a small amount of fluid is discharged from the compression chamber to the discharge chamber, as well as cases where the flow rate of the fluid discharged from the compression chamber to the discharge chamber is zero.

[0020] The compression mechanism may be provided with a discharge valve that allows the fluid to be discharged from the compression chamber to the discharge chamber, while prohibiting the fluid from flowing from the discharge chamber to the compression chamber. The discharge communication part is preferably located downstream of the discharge valve in the direction of fluid flow.

[0021] In this case, the generation of pulsation due to the flow of fluid from the discharge chamber to the compression chamber can be suitably prevented. Also, the flow of fluid from the discharge communication portion to the discharge passage can assist in opening the discharge valve.

[0022] A second compressor of the present invention includes a housing having a suction port for sucking in a fluid from the outside, a suction chamber communicating with the suction port, and a suction passage communicating with the suction chamber; a compression mechanism provided within the housing, The compression mechanism includes a compression chamber that compresses a fluid while reducing a volume thereof, and a supported portion that is supported rotatably about a rotation axis of the housing. a suction communication portion that allows fluid in the suction passage to flow to the compression chamber is formed in the supported portion, a phase between the suction passage and the suction communication portion changes with the rotation of the supported portion, thereby changing a suction side flow resistance, which is a flow resistance of a fluid flowing from the suction passage to the suction communication portion, The suction passage and the suction communication portion are in a phase where the suction side flow resistance increases as the volume of the compression chamber decreases from a maximum volume.

[0023] In the second compressor of the present invention, a suction communication part is formed in the supported part of the compression mechanism, and this suction communication part allows the fluid in the suction passage to flow to the compression chamber. As a result, in this compressor, the fluid drawn into the suction chamber from the suction communication port is drawn into the compression chamber from the suction passage via the suction communication part. In addition, since the suction communication part is formed in the supported part, the phase of the suction communication part with respect to the suction passage changes as the supported part rotates. Furthermore, the change in phase between the suction passage and the suction communication part changes the suction side flow resistance.

[0024] In this compressor, pulsation occurs due to suction-side flow resistance, which is the flow resistance of the fluid flowing from the suction passage to the suction connection portion, and the magnitude of this pulsation changes as the suction-side flow resistance changes. In this compressor, the suction passage and the suction connection portion are in a phase where the suction-side flow resistance increases as the volume of the compression chamber decreases from its maximum. As a result, in this compressor, the pulsation caused by the suction-side flow resistance acts to cancel out the suction pulsation that occurs when fluid is sucked into the compression chamber. As a result, in this compressor, the suction pulsation can be reduced.

[0025] Thus, in this compressor, there is no need to form an excessively large suction chamber in order to reduce suction pulsation, and the housing is unlikely to become large.

[0026] Therefore, the second compressor of the present invention can suppress an increase in size while realizing high quietness.

[0027] In the second compressor of the present invention, the suction passage and the suction communication part are preferably in communication with each other in the radial direction of the housing, which makes it possible to reduce the size of the housing, and therefore the entire compressor, in the axial direction of the rotation axis.

[0028] In the second compressor of the present invention, when the volume of the compression chamber is at a maximum, the suction passage and the suction communication portion are preferably in a phase that minimizes the flow resistance on the suction side.

[0029] In the second compressor of the present invention, when the flow rate of the fluid sucked into the compression chamber is at a maximum, the suction passage and the suction communication portion are preferably in a phase that maximizes the suction side flow resistance.

[0030] In these cases, the pulsation caused by the flow resistance on the suction side acts to more effectively cancel out the suction pulsation, so that the suction pulsation can be more effectively reduced.

[0031] In the first compressor of the present invention or the second compressor of the present invention, the compression mechanism may have a drive scroll rotatable about a rotation axis, and a driven scroll that faces the drive scroll and is rotated by the drive scroll and the driven mechanism about a driven axis while being eccentric with respect to the drive scroll, thereby forming a compression chamber between the drive scroll and the driven scroll. The drive scroll may have a drive end plate and a drive scroll body that is integral with the drive end plate and protrudes in a spiral shape toward the driven scroll. It is preferable that the driven scroll has a driven end plate and a driven scroll body that is integral with the driven end plate and protrudes in a spiral shape toward the drive scroll.

[0032] In this case, the configuration of the compression mechanism can be simplified.

[0033] A third compressor of the present invention includes a housing having a suction chamber and a suction portion for sucking in a fluid from the outside; a drive shaft provided in the suction chamber and rotatable about a rotation axis; a compression mechanism provided in the housing and connected to the drive shaft; a suction communication portion is formed in the drive shaft, the suction communication portion being connected to the suction portion in the direction of the rotation axis and allowing fluid to flow from the suction portion to the suction chamber; The compression mechanism is formed with a compression chamber that compresses a fluid while reducing a volume thereof, and a suction port that draws the fluid from the suction chamber into the compression chamber. A phase between the suction portion and the suction communication portion changes with the rotation of the drive shaft, thereby changing a suction side flow resistance, which is a flow resistance of a fluid flowing from the suction portion to the suction communication portion, The suction portion and the suction communication portion are characterized in that they are in a phase in which the suction side flow resistance increases as the volume of the compression chamber decreases from a maximum value.

[0034] The third compressor can also reduce suction pulsation in the same way as the second compressor. Therefore, in this compressor, there is no need to form an excessively large suction chamber in order to reduce suction pulsation, and the compression mechanism and housing are unlikely to become large.

[0035] Therefore, the third compressor of the present invention can suppress an increase in size while realizing high quietness.

[0036] In the third compressor, the suction portion may be formed in the housing eccentrically with respect to the rotation axis. It is preferable that the suction connection portion is formed in the drive shaft eccentrically with respect to the rotation axis. In this case, the phase of the suction portion and the suction connection portion can be suitably changed.

[0037] In the third compressor, when the volume of the compression chamber is maximum, the suction portion and the suction communication portion are preferably in a phase that minimizes the flow resistance on the suction side.

[0038] In the third compressor, when the flow rate of the fluid sucked into the compression chamber is at a maximum, the suction portion and the suction communication portion are preferably in a phase that maximizes the suction side flow resistance.

[0039] In these cases, the pulsation caused by the flow resistance on the suction side acts to more effectively cancel out the suction pulsation, so that the suction pulsation can be more effectively reduced. Effect of the Invention

[0040] The first compressor of the present invention can suppress an increase in size while realizing high quietness. The second compressor of the present invention can suppress an increase in size while realizing high quietness. The third compressor of the present invention can suppress an increase in size while realizing high quietness. [Brief description of the drawings]

[0041] [Figure 1] FIG. 1 is a cross-sectional view of the compressor according to the first embodiment. [Diagram 2] FIG. 2 is an enlarged cross-sectional view of a main portion of the compressor according to the first embodiment, showing a first support portion, a suction passage, a first insertion hole, a suction communication portion, and the like. [Diagram 3] FIG. 3 is an enlarged cross-sectional view of a main portion of the compressor according to the first embodiment, illustrating a discharge communication portion, a second insertion hole, a discharge passage, and the like. [Figure 4] FIG. 4 is a graph showing the relationship between the change in rotational phase of the first scroll and the second scroll and the change in volume of the compression chamber in the compressor of the first embodiment. [Diagram 5] FIG. 5 is a graph showing the relationship between the change in rotation phase of the first scroll and the second scroll and the change in pressure in the compression chamber in the compressor of the first embodiment. [Figure 6] FIG. 6 is a cross-sectional view of the compressor according to the first embodiment, taken along line AA in FIG. 1 when the rotation phase of the first scroll and the second scroll is in phase X1. [Figure 7] FIG. 7 is an enlarged cross-sectional view of a main part of the compressor according to the first embodiment, showing the cross section BB in FIG. 1 when the rotation phase of the first scroll and the second scroll is the phase X1. [Figure 8] FIG. 8 is a cross-sectional view of the compressor according to the first embodiment, taken along line AA in FIG. 1 when the rotation phase of the first scroll and the second scroll is in phase X2. [Figure 9] FIG. 9 is an enlarged cross-sectional view of a main part of the compressor according to the first embodiment, showing the cross section BB in FIG. 1 when the rotation phase of the first scroll and the second scroll is the phase X2. [Figure 10] FIG. 10 is a cross-sectional view of the compressor according to the first embodiment, taken along line AA in FIG. 1 when the rotation phase of the first scroll and the second scroll is in phase X3. [Figure 11] FIG. 11 is an enlarged cross-sectional view of a main part of the compressor according to the first embodiment, showing the cross section BB in FIG. 1 when the rotation phase of the first scroll and the second scroll is the phase X3. [Figure 12] FIG. 12 is a graph showing a waveform of the suction pulsation and a waveform of the first canceling pulsation during operation of the compressor of the first embodiment. [Figure 13] FIG. 13 is a cross-sectional view of the compressor according to the first embodiment, taken along line AA in FIG. 1 when the rotation phase of the first scroll and the second scroll is in phase X4. [Figure 14] FIG. 14 is an enlarged cross-sectional view of a main part of the compressor according to the first embodiment, showing the cross section CC in FIG. 1 when the rotation phase of the first scroll and the second scroll is the phase X4. [Figure 15] FIG. 15 is a cross-sectional view of the compressor according to the first embodiment, taken along line AA in FIG. 1 when the rotational phase of the first scroll and the second scroll is in phase X5. [Figure 16] FIG. 16 is an enlarged cross-sectional view of a main part of the compressor according to the first embodiment, showing the cross section CC in FIG. 1 when the rotational phase of the first scroll and the second scroll is the phase X5. [Figure 17] FIG. 17 is a graph showing a waveform of the discharge pulsation and a waveform of the second canceling pulsation during operation of the compressor of the first embodiment. [Figure 18] FIG. 18 is a cross-sectional view of the compressor according to the second embodiment. [Figure 19] FIG. 19 is a schematic diagram showing a change in phase between the discharge section and the discharge communication section associated with the rotational drive of the driving scroll when the discharge section and the discharge communication section are viewed from the D1 direction in FIG. 18 in the compressor of the second embodiment. FIG. 19(A) shows the phase between the discharge section and the discharge communication section when the rotation angle of the driving scroll is zero degrees. FIG. 19(B) shows the phase between the discharge section and the discharge communication section when the driving scroll has rotated about 90° from the state shown in FIG. 19(A). FIG. 19(C) shows the phase between the discharge section and the discharge communication section when the driving scroll has rotated about 90° from the state shown in FIG. 19(B). FIG. 19(D) shows the phase between the discharge section and the discharge communication section when the driving scroll has rotated about 90° from the state shown in FIG. 19(C). [Figure 20] FIG. 20 is an enlarged cross-sectional view of a main portion of the compressor of the third embodiment. [Figure 21] FIG. 21 is a cross-sectional view of the compressor according to the fourth embodiment. [Figure 22] FIG. 22 is an enlarged cross-sectional view of a main portion of the compressor of the fifth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0042] Hereinafter, first to fifth embodiments of the present invention will be described with reference to the drawings. The compressors of the first to third embodiments are specifically double-rotating scroll-type electric compressors. The compressors of the fourth and fifth embodiments are specifically scroll-type electric compressors. These compressors are mounted in a vehicle (not shown) and form an air conditioner for the vehicle.

[0043] Example 1 As shown in FIG. 1, the compressor of the first embodiment includes a housing 6, an electric motor 10, and a compression mechanism 14.

[0044] In this embodiment, the front-rear direction of the compressor is defined by the solid arrow shown in Fig. 1. In Fig. 2 and subsequent figures, the front-rear direction of the compressor is defined in accordance with Fig. 1. Note that the front-rear direction is an example for convenience of explanation, and the compressor can change its own attitude as appropriate depending on the vehicle in which it is installed.

[0045] 1, the housing 6 is composed of a housing body 60 and a housing cover 62. The housing body 60 and the housing cover 62 are made of an aluminum alloy.

[0046] The housing body 60 is a bottomed tubular member having an outer peripheral wall 60a and a rear wall 60b. The outer peripheral wall 60a is cylindrical and has a rotation axis O1 as its center. The rotation axis O1 is parallel to the front-rear direction.

[0047] Further, an intake communication port 68 is formed in the outer peripheral wall 60a. The intake communication port 68 extends in the radial direction of the housing body 60. The intake communication port 68 is connected to an evaporator (not shown) through a pipe (not shown).

[0048] The rear wall 60b is located at the rear end of the housing body 60. The rear wall 60b extends in a generally circular flat plate shape perpendicular to the rotation axis O1. The outer peripheral edge of the rear wall 60b is connected to the rear end of the outer peripheral wall 60a. The above-mentioned suction communication port 68 may be formed in the rear wall 60b.

[0049] A first support portion 64 is formed at the center of the 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 suction passage 15 and a pin hole 4 formed therein.

[0050] The suction passage 15 is composed of a passage body 15a, a first radial hole 15b, and a second radial hole 15c. The passage body 15a extends in the first support portion 64 in the direction of the rotation axis O1. The passage body 15a opens at the rear end of the first support portion 64, i.e., at the rear wall 60b. On the other hand, the front end of the passage body 15a does not open at the front end of the first support portion 64. By forming the passage body 15a in this manner, the first support portion 64 has a substantially cylindrical shape centered on the rotation axis O1.

[0051] Further, a sealing member 150 is provided at a location where the passage body 15a opens to the rear wall 60b. As a result, the passage body 15a is not in communication with the outside of the housing 6.

[0052] The first radial hole 15b is formed in the rear of the first support portion 64. The first radial hole 15b opens to the outer peripheral surface of the first support portion 64, extends in the radial direction of the first support portion 64, and communicates with the rear of the passage body 15a. The second radial hole 15c is formed in the front of the first support portion 64. As a result, the first radial hole 15b and the second radial hole 15c are separated in the front-rear direction. The second radial hole 15c opens to the outer peripheral surface of the first support portion 64, extends in the radial direction of the first support portion 64, and communicates with the front of the passage body 15a.

[0053] The pin hole 4 is cylindrical, opens to the front end face of the first support part 64, and extends linearly rearward within the first support part 64. The pin hole 4 does not penetrate the first support part 64 in the front-rear direction. Therefore, the pin hole 4 is not in communication with the suction passage 15 including the passage body 15a.

[0054] Further, a first plain bearing 51 is provided on the outer peripheral surface of the first support portion 64. The first plain bearing 51 is formed in a cylindrical shape with a larger diameter than the first support portion 64. The first plain bearing 51 is disposed on the outer peripheral surface of the first support portion 64 at a location between the first radial hole 15b and the second radial hole 15c. Note that a ball bearing may be provided instead of the first plain bearing 51.

[0055] The housing cover 62 is disposed in front of the housing main body 60. The housing cover 62 is generally disk-shaped and centered on the rotation axis O1. The housing cover 62 has a front surface 62a facing forward, a rear surface 62b located opposite the front surface 62a and facing rearward, and an outer circumferential surface 62c that is connected to the front surface 62a and the rear surface 62b and is located between the front surface 62a and the rear surface 62b.

[0056] Further, the housing cover 62 is formed with a second support portion 66, a second insertion hole 61, and a discharge portion 63.

[0057] The second support portion 66 is integrally formed at 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 cylindrical shape centered on the rotation axis O1 and extends through the housing cover 62 in the direction of the rotation axis O1. The rear end of the second insertion hole 61 opens at the rear end of the second support portion 66, i.e., the rear end of the housing cover 62. By forming the second insertion hole 61 in this manner, the second support portion 66 has a cylindrical shape centered on the rotation axis O1.

[0058] On the other hand, the front end of the second insertion hole 61 does not open to the front end of the housing cover 62. A second plain bearing 52 is provided in the second insertion hole 61. The second plain bearing 52 is formed in a cylindrical shape, and is disposed at the front part of the second insertion hole 61. Note that a ball bearing may be provided instead of the second plain bearing 52.

[0059] The discharge section 63 is composed 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 opens from the outer peripheral surface 62c toward the outside in the radial direction of the housing cover 62. The discharge communication port 69 is connected to a condenser (not shown) through piping (not shown).

[0060] The discharge passage 67 is formed in the housing cover 62. The discharge passage 67 extends inside the housing cover 62 in the radial direction of the housing cover 62. One end of the discharge passage 67 is connected to the discharge communication port 69, and the other end is connected to the second insertion hole 61. As a result, the discharge passage 67 communicates with the discharge communication port 69 and the second insertion hole 61, and also connects the second insertion hole 61 to the discharge communication port 69.

[0061] In the housing 6, the housing cover 62 is disposed in front of the housing main body 60, and the rear surface 62b of the housing cover 62 is abutted against the front end of the outer peripheral wall 61a of the housing main body 60. In this state, the housing cover 62 is fixed to the housing main body 60 by a plurality of bolts (not shown) from the housing cover 62 side. Thus, in the housing 6, the housing main body 60 and the housing cover 62 are integrated.

[0062] In addition, in the housing 6, the front of the housing body 60 is closed by the housing cover 62, so that a suction chamber 65 is formed in the housing body 60. The suction chamber 65 communicates with the suction communication port 68. As a result, refrigerant gas is drawn into the suction chamber 65 from the outside of the housing 6 through the suction communication port 68. The refrigerant gas is an example of the "fluid" in the present invention. The suction chamber 65 also communicates with the suction passage 15. As a result, the refrigerant gas in the suction chamber 65 is drawn into the passage body 15a from the first radial hole 15b.

[0063] The electric motor 10 is accommodated in the suction chamber 65. As a result, the suction chamber 65 also serves as a motor chamber that accommodates the electric motor 10.

[0064] The electric motor 10 is composed of a stator 17 and a rotor 11. The stator 17 is cylindrical and has a rotation axis O1 as its center, and has windings 17a. The stator 17 is fixed to the housing body 60 and, by extension, to the housing 6, by being fitted into the inner peripheral surface of the outer peripheral wall 60a.

[0065] The rotor 11 has a cylindrical shape around the rotation axis O1 and is disposed inside the stator 17. Although not shown in detail, the rotor 11 is composed of a plurality of permanent magnets corresponding to the stator 17 and laminated steel plates that fix the respective permanent magnets.

[0066] The compression mechanism 14 is provided in the housing 6. The compression mechanism 14 is composed of a driving scroll 30, a driven scroll 40, and a driven mechanism 20.

[0067] The driving scroll 30 is made of an aluminum alloy. The driving scroll 30 has a driving end plate 31, a driving peripheral wall 32, a driving scroll 33, a first cover body 35, and a second cover body 37. The first cover body 35 is an example of the "supported portion" in the present invention.

[0068] The driving end plate 31 extends in a substantially disk-like shape perpendicular to the rotation axis O1 and the driven axis O2. The driven axis O2 extends parallel to the rotation axis O1 while being eccentric with respect to the rotation axis O1. In other words, the driven axis O2 is also parallel to the front-rear direction. The driving end plate 31 has a front surface 311 facing the second cover body 37 and a rear surface 312 located on the opposite side of the front surface 311.

[0069] Furthermore, the driving end plate 31 has a recess 38 and a discharge port 39 formed therein. The recess 38 is recessed rearward from the front surface 311 in a generally cylindrical shape. The discharge port 39 is formed in the driving end plate 31 at a location within the recess 38, and penetrates the driving end plate 31 in the front-rear direction. In addition, a discharge reed valve 57 and a retainer 58 are fixed to the driving end plate 31 in the recess 38 by a fixing bolt 59. The discharge reed valve 57 is an example of the "discharge valve" in the present invention.

[0070] The discharge reed valve 57 opens by elastic deformation, thereby allowing the refrigerant gas in the compression chamber 12 to be discharged through the discharge port 39 to the discharge chamber 8. On the other hand, the discharge reed valve 57 closes by elastic deformation, thereby preventing the refrigerant gas in the compression chamber 12 from being discharged through the discharge port 39 to the discharge chamber 8. In addition, the closed discharge reed valve 57 prevents the refrigerant gas in the discharge chamber 8 from flowing into the compression chamber 12 through the discharge port 39. The retainer 58 is capable of adjusting the opening degree of the discharge reed valve 57. The compression chamber 12 and the discharge chamber 8 will be described in detail later.

[0071] The driving peripheral wall 32 is integral with the driving end plate 31 and extends cylindrically from the outer circumferential edge of the driving end plate 31 rearward, i.e., toward the driven scroll 40. In this case, the driving peripheral wall 32 extends parallel to the rotation axis O1 and the driven axis O2.

[0072] The driving scroll 33 is integral with the driving end plate 31 and is disposed inside the driving peripheral wall 32. The driving scroll 33 extends from the rear surface 312 of the driving end plate 31 in parallel with the driving peripheral wall 32 toward the driven scroll 40. As shown in FIG. 6, the driving scroll 33 extends in a spiral shape from the center of the driving end plate 31 toward the outer periphery, with the center of the driving scroll 33 being the center of the driving end plate 31. The outer periphery end of the driving scroll 33 is connected to the driving peripheral wall 32. Note that the electric motor 10 is omitted in FIG. 6 for ease of explanation. The same applies to FIGS. 8, 10, 13, and 15 described below.

[0073] 1, the first cover body 35 extends in a substantially circular plate shape perpendicular to the rotation axis O1 and the driven axis O2. The first cover body 35 has a front surface 35a facing forward and a rear surface 35b located on the opposite side to the front surface 35a.

[0074] The first cover body 35 is formed with a first boss 35c, a first insertion hole 35d, and an intake hole 35e. The intake hole 35e is an example of the "intake portion" of the present invention. The first boss 35c is integrally formed at the center of the rear surface 35b, and protrudes rearward in the direction of the rotation axis O1 and the driven axis O2.

[0075] The first insertion hole 35d penetrates the first cover body 35, including the first boss 35c, in the direction of the rotation axis O1. As a result, the first boss 35c has a cylindrical shape centered on the rotation axis O1.

[0076] 2, the first insertion hole 35d is composed of a first hole portion 351, a second hole portion 352, and a third hole portion 353. The first hole portion 351 constitutes the rear portion of the first insertion hole 35d. The second hole portion 352 is located between the first hole portion 351 and the third hole portion 353, and constitutes the center portion of the first insertion hole 35d. The third hole portion 353 constitutes the rear portion of the first insertion hole 35d.

[0077] The first hole portion 351 is formed to have the largest inner diameter among the first hole portion 351, the second hole portion 352, and the third hole portion 353. The second hole portion 352 is formed to have a larger inner diameter than the third hole portion 353. As a result, the inner diameter of the first insertion hole 35d becomes smaller in three stages, in the order of the first hole portion 351, the second hole portion 352, and the third hole portion 353.

[0078] As shown in Fig. 1, the suction communication hole 35e is formed in the first boss 35c. The suction communication hole 35e extends at an incline from the outer side to the inner side in the radial direction of the first boss 35c as it moves from the front to the rear. The front end of the suction communication hole 35e opens to the front surface 35a. The rear end of the suction communication hole 35e opens to the second hole portion 352 of the first insertion hole 35d.

[0079] Further, four rings 22 are provided on the front surface 35a of the first cover body 35. The rings 22 are arranged at equal intervals in the circumferential direction of the first cover body 35. Note that two of the four rings 22 are illustrated in FIG.

[0080] The second cover body 37 has a cover body 37a and a second boss 37b. The second boss 37b is an example of the "rotating shaft portion" in the present invention. The cover body 37a extends in a substantially disk-like shape perpendicular to the rotation axis O1 and the driven axis O2. The cover body 37a is formed to have substantially the same diameter as the driving end plate 31. The second boss 37b is formed integrally with the cover body 37a and protrudes forward from the cover body 37a in the direction of the rotation axis O1 and the driven axis O2.

[0081] As shown in Fig. 3, the second boss 37b is composed of a first diameter portion 371, a second diameter portion 372, and a third diameter portion 373. The first diameter portion 371 constitutes the rear portion of the second boss 37b. The second diameter portion 372 is located between the first diameter portion 371 and the third diameter portion 373, and constitutes the center portion of the second boss 37b. The third diameter portion 373 constitutes the front portion of the second boss 37b.

[0082] The first diameter portion 371 is formed to have the 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 is formed to have a larger outer diameter than the third diameter portion 373. As a result, the outer diameter of the second boss 37b decreases in three stages, in the order of the first diameter portion 371, the second diameter portion 372, and the third diameter portion 373.

[0083] 1, the second cover body 37 is formed with a connection passage 37c and a discharge communication hole 37d. The discharge communication hole 37d is an example of a "discharge communication portion" in the present invention. The connection passage 37c passes through the second cover body 37, including the second boss 37b, in the direction of the rotation axis O1. As a result, the second boss 37b has a cylindrical shape centered on the rotation axis O1.

[0084] The discharge communication hole 37d extends in the radial direction of the second boss 37b while connecting to the connection passage 37c. The discharge communication hole 37d opens to the outer circumferential surface of the second boss 37b, more specifically, to the outer circumferential surface of the second diameter portion 372.

[0085] In the driving scroll 30, the cover body 37a of the second cover body 37 is in contact with the front surface 311 of the driving end plate 31, and the rear end of the driving peripheral wall 32 is in contact with the front surface 35a of the first cover body 35. In this state, the second cover body 37, the driving end plate 31, the driving peripheral wall 32, and the first cover body 35 are connected by a plurality of bolts 50. As a result, in the driving scroll 30, the driving end plate 31, the driving peripheral wall 32, the first cover body 35, and the second cover body 37 are integrated. Note that two of the plurality of bolts 50 are shown in FIG. 1.

[0086] In the second cover body 37, the cover main body 37a covers the recess 38 of the driving end plate 31 from the front. This allows the connecting passage 37c to communicate with the recess 38 from the front. In this way, in the driving scroll 30, the discharge chamber 8 is formed by the recess 38 and the connecting passage 37c.

[0087] Further, in the driving scroll 30, the driving peripheral wall 32 is inserted into the rotor 11 and fixed to the rotor 11. As a result, the driving scroll 30 is fixed to the rotor 11 and integrated therewith.

[0088] The driven scroll 40 is also made of an aluminum alloy. The driven scroll 40 is housed within the driving scroll 30. The driven scroll 40 has a driven end plate 41 and a driven scroll body 43.

[0089] The driven end plate 41 extends in a substantially disk-like shape perpendicular to the rotation axis O1 and the driven axis O2. The driven 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 end plate 31 inside the driving scroll 30. The rear surface 412 is located on the opposite side of the front surface 411 and faces the front surface 35a of the first cover body 35.

[0090] Further, the driven end plate 41 is formed with a housing portion 71. The housing portion 71 is recessed in a cylindrical shape from the rear surface 412 of the driven end plate 41 toward the front. The bush 53 is housed in the housing portion 71. The driven pin 55 is inserted into the bush 53. More specifically, the driven pin 55 is inserted into the bush 53 at a position eccentric to the center of the bush 53. The driven pin 55 is cylindrical and protrudes rearward from the bush 53 and hence the driven end plate 41 toward the first support portion 64. The bush 53 may be housed in the housing portion 71 via a bearing such as a slide bearing.

[0091] Further, four rotation prevention pins 21 are fixed to the rear surface 412. Each rotation prevention pin 21 is disposed on the rear surface 412 at a location on the outer periphery of the housing portion 71 and at a position facing each ring 22. Each rotation prevention pin 21 protrudes rearward from the rear surface 412. Note that two of the four rotation prevention pins 21 are illustrated in FIG. 1.

[0092] The driven spiral body 43 is integral with the driven end plate 41 and extends forward in parallel with the rotation axis O1 and the driven axis O2 from the front surface 411 of the driven end plate 41. As shown in Fig. 6, the driven spiral body 43 extends in a spiral shape from the spiral center toward the outer periphery, with the center side of the driven end plate 41 being the spiral center.

[0093] 1 is composed of four rotation prevention pins 21 and four rings 22. Here, the number of rotation prevention pins 21 and rings 22 can be appropriately designed as long as there are three or more.

[0094] In the compression mechanism 14, the driving scroll 30 has the driven scroll 40 housed within it, and the driving scroll 33 of the driving scroll 30 and the driven scroll 43 of the driven scroll 40 are meshed with each other. Also, each rotation-preventing pin 21 is inserted into each ring 22. In this manner, the driving scroll 30 and the driven scroll 40 are assembled in the front-rear direction. Strictly speaking, after the driving scroll 33 and the driven scroll 43 are meshed with each other and each rotation-preventing pin 21 is inserted into each ring 22, the second cover body 37, the driving end plate 31, the driving peripheral wall 32, and the first cover body 35 of the driving scroll 30 are connected by each bolt 50.

[0095] Then, after the drive scroll 30 and the driven scroll 40 are assembled, the first plain bearing 51 is inserted into the first insertion hole 35d of the first cover body 35 in the drive scroll 30. More specifically, as shown in FIG. 2, the first plain bearing 51 is inserted into the first hole portion 351 of the first insertion hole 35d. The first plain bearing 51 is held by abutting against the step between the first hole portion 351 and the first hole portion 351 formed by the difference in inner diameter. As a result, the first boss 35c, and therefore the first cover body 35, are rotatably supported by the first support portion 64 via the first plain bearing 51. Here, the inner diameter of the second hole portion 352 of the first insertion hole 35d is formed to be larger than the outer diameter of the first support portion 64. Therefore, when the first cover body 35 is supported by the first support portion 64, in the second hole portion 352, the first cover body 35 is spaced radially from the first support portion 64, and the first cover body 35 and the first support portion 64 are not in contact with each other.

[0096] Then, with the first cover body 35 supported by the first support portion 64, the second radial hole 15c of the suction passage 15 faces the inside of the second hole portion 352. As a result, the second radial hole 15c communicates with the suction communication hole 35e through the second hole portion 352. In other words, the suction passage 15 and the suction communication hole 35e communicate with each other in the radial direction of the first support portion 64, i.e., in the radial direction of the housing 6, through the first insertion hole 35d.

[0097] Also, as shown in FIG. 1, in the driving scroll 30, the second boss 37b of the second cover body 37 is inserted into the second insertion hole 61. As a result, as shown in FIG. 3, the third diameter portion 373 of the second boss 37b is inserted into the second plain bearing 52. Then, the second plain bearing 52 is held by the second insertion hole 61 while being abutted against the step between the third diameter portion 373 and the second diameter portion 372 formed by the difference in outer diameter. As a result, the second boss 37b, and therefore the second cover body 37, are rotatably supported by the second support portion 66 via the second plain bearing 52. In this way, as shown in FIG. 1, the driving scroll 30 is rotatably supported by the housing 6 by both the first support portion 64 and the second support portion 66 around the rotation axis O1. As a result, the second boss 37b is rotatable around the rotation axis O1 in the second insertion hole 61.

[0098] Here, as shown in FIG. 3, the second diameter portion 372 of the second boss 37b is formed to have a smaller diameter than the second insertion hole 61. Therefore, when the second boss 37b is supported by the second support portion 66, the second diameter portion 372 is separated from the inner peripheral surface of the second insertion hole 61 in the radial direction of the second boss 37b. As a result, the inner peripheral surface of the second insertion hole 61 and the second diameter portion 372 are not in contact with each other. Then, the second boss 37b is supported by the second support portion 66, so that the discharge communication hole 37d faces the inside of the second insertion hole 61. As a result, the discharge communication hole 37d communicates with the discharge passage 67 of the discharge portion 63 through the second insertion hole 61. Thus, in this compressor, the discharge passage 67 and the discharge communication portion 37d, and further, the discharge portion 63 and the discharge communication portion 37d communicate with each other in the radial direction of the housing 6.

[0099] 1, in the driven scroll 40, the driven pin 55 is inserted into the pin hole 4 of the first support portion 64. As a result, the driven scroll 40 is supported by the first support portion 64 by the driven pin 55 so as to be rotatable about the driven axis O2. In other words, unlike the driving scroll 30, the driven scroll 40 is supported by the housing 6 only by the first support portion 64 so as to be rotatable about the driven axis O2.

[0100] In the compression mechanism 14, the drive scroll 30 and the driven scroll 40 are assembled in the front-rear direction to form two compression chambers 12 between the drive scroll 30 and the driven scroll 43 of the driven scroll 40, as shown in FIG. 6. In addition, as shown in FIG. 1, the drive scroll 30 and the driven scroll 40 are assembled in the front-rear direction to form a suction space 30a in the drive peripheral wall 32. The suction space 30a communicates with the front end of the suction communication hole 35e, and can communicate with each compression chamber 12 by the operation of the compressor. Each compression chamber 12 and the suction space 30a are partitioned from the suction chamber 65 by the drive scroll 30 and the driven scroll 40.

[0101] In the compressor configured as described above, as shown by the dashed arrow in FIG. 1, low-temperature, low-pressure refrigerant gas that has passed through the evaporator is drawn into the suction chamber 65 through the suction port 68. When the electric motor 10 is operated and the rotor 11 rotates, the driving scroll 30 is rotated about the rotation axis O1 in the suction chamber 65. That is, the driving scroll 30 and the rotor 11 are rotated integrally. At this time, in the driven mechanism 20, the rotation prevention pins 21 slide against the inner peripheral surfaces of the rings 22, causing the rings 22 to rotate relatively about the centers of the rotation prevention pins 21. In this way, the driven mechanism 20 transmits the torque of the driving scroll 30 to the driven scroll 40.

[0102] As a result, the driven scroll 40 is rotated around the driven axis O2 by the driving scroll 30 and the driven mechanism 20. At this time, the driven mechanism 20 restricts the rotation of the driven scroll 40. As a result, the driven scroll 40 revolves around the driven axis O2 relatively to the driving scroll 30. Here, in this compressor, the driving scroll 30 and the driven scroll 40 rotate in a rotation direction R1 shown in FIG. 6 and the like.

[0103] As a result of the driving scroll 30 being rotationally driven about the rotation axis O1, the suction communication hole 35e rotates relative to the second radial hole 15c of the suction passage 15 in the rotation direction R1, as shown in Figures 7, 9, and 11. As a result of the driving scroll 30 being rotationally driven about the rotation axis O1, the discharge communication hole 37d rotates relative to the discharge passage 67 in the rotation direction R1, as shown in Figures 14 and 16.

[0104] In this way, the phase between the driving scroll 30, which is rotationally driven about the rotation axis O1, and the driven scroll 40, which is rotationally driven about the driven axis O2 (hereinafter, the phase between the driving scroll 30 and the driven scroll 40 is referred to as the rotation phase), changes, thereby changing the volume of each compression chamber 12. As a result, as shown by the dashed arrow in Fig. 1, the refrigerant gas in the suction chamber 65 is sucked into the passage body 15a, i.e., the suction passage 15, through the first radial hole 15b. Furthermore, the refrigerant gas in the passage body 15a is sucked into each compression chamber 12 from the second radial hole 15c through the second hole portion 352 of the first insertion hole 35d, the suction communication hole 35e, and the suction space 30a.

[0105] The refrigerant gas sucked into each compression chamber 12 flows from the outer periphery of the drive scroll 33 and the driven scroll 43 toward the center of the scroll, and is compressed in each compression chamber 12. The refrigerant gas compressed to the discharge pressure in each compression chamber 12 is discharged from the discharge port 39 into the recess 38, i.e., into the discharge chamber 8.

[0106] The refrigerant gas discharged into the discharge chamber 8 flows through the discharge passage 67 via the discharge communication hole 37d and the second insertion hole 61, and is discharged toward the condenser from the discharge communication port 69. In this manner, air conditioning is performed by the vehicle air conditioner.

[0107] In this compressor, suction pulsation inevitably occurs when refrigerant gas is sucked from the suction chamber 65 into each compression chamber 12, and discharge pulsation inevitably occurs when refrigerant gas is discharged from each compression chamber 12 to the discharge chamber 8.

[0108] In this regard, the compressor is capable of effectively reducing the suction pulsation and the discharge pulsation. The effect of this will be specifically described below. The following description will be focused on one of the two compression chambers 12.

[0109] As shown in Fig. 4, the rotational phase between the driving scroll 30 and the driven scroll 40 changes, so that the volume of the compression chamber 12 gradually increases from a minimum state. After the volume of the compression chamber 12 reaches a maximum, the rotational phase between the driving scroll 30 and the driven scroll 40 changes, so that the volume of the compression chamber 12 gradually decreases. Then, refrigerant is sucked into the compression chamber 12 as the volume of the compression chamber 12 increases from the minimum to the maximum. That is, as described above, the refrigerant gas in the suction chamber 65 is sucked into the compression chamber 12 from the suction passage 15 through the second hole portion 352 of the first insertion hole 35d, the suction communication hole 35e, and the suction space 30a.

[0110] In this compressor, when the rotation phase between the driving scroll 30 and the driven scroll 40 is phase X1, the driving scroll 30, the driven scroll 40, and the compression chamber 12 are in the state shown in Fig. 6. In addition, in the process in which the volume of the compression chamber 12 increases from the minimum to the maximum, the flow rate of the refrigerant sucked into the compression chamber 12 changes, and when the rotation phase between the driving scroll 30 and the driven scroll 40 is phase X1, the flow rate of the refrigerant sucked into the compression chamber 12 is maximum. Note that, when the rotation phase between the driving scroll 30 and the driven scroll 40 is phase X1, the volume of the compression chamber 12 is in the process of increasing toward the maximum, and the volume of the compression chamber 12 has not yet reached maximum.

[0111] Here, in this compressor, the suction communication hole 35e is formed in the first cover body 35. Therefore, as the drive scroll 30 is rotationally driven, the suction communication hole 35e rotates around the second radial hole 15c in a rotation direction R1 around the rotation axis O1 while facing the second radial hole 15c, as shown in Figures 7, 9, and 11. In other words, as the drive scroll 30 is rotationally driven, the phase between the second radial hole 15c and the suction communication hole 35e changes.

[0112] Then, by changing the phase between the second radial hole 15c and the suction communication hole 35e in this way, in this compressor, the suction side flow resistance, which is the flow resistance of the refrigerant gas flowing from the second radial hole 15c and therefore the suction passage 15 to the suction communication hole 35e, changes. Also, in this compressor, the suction side flow resistance generates a pulsation different from the suction pulsation and the discharge pulsation (hereinafter, this pulsation is referred to as a "first canceling pulsation"). And, by changing the suction side flow resistance, the magnitude of the first canceling pulsation changes.

[0113] Here, when the rotation phase between the driving scroll 30 and the driven scroll 40 is in phase X1, as shown in FIG. 7, the suction communication hole 35e is located at a position that is almost opposite to the second radial hole 15c in the rotation direction R1 across the rotation axis O1. Therefore, as shown by the dashed arrow in FIG. 7, when the refrigerant gas is sucked into the compression chamber 12, the refrigerant gas flows through the suction communication hole 35e from the second radial hole 15c through the second hole portion 352 of the first insertion hole 35d in the rotation direction R1, making almost a half turn. As a result, when the phase between the second radial hole 15c and the suction communication hole 35e is in the state shown in FIG. 7, that is, when the rotation phase between the driving scroll 30 and the driven scroll 40 is in phase X1, the suction side flow resistance is maximized. In other words, in this compressor, the suction communication hole 35e is formed in the first cover body 35 so that the suction side flow resistance is maximized when the rotation phase between the driving scroll 30 and the driven scroll 40 is in phase X1. As a result, in this compressor, when the flow rate of refrigerant gas sucked into compression chamber 12 is at a maximum, second radial hole 15c and suction communication hole 35e are in a phase that maximizes the suction side flow resistance.

[0114] 4, the rotational phase between the driving scroll 30 and the driven scroll 40 becomes phase X2, which is greater than phase X1, and the volume of the compression chamber 12 becomes maximum (see FIG. 8). When the volume of the compression chamber 12 is maximum, the driving scroll 33 and the driven scroll 43 put the compression chamber 12 and the suction space 30a out of communication with each other. Therefore, when the volume of the compression chamber 12 becomes maximum, refrigerant gas is not sucked into the compression chamber 12 and the refrigerant gas in the compression chamber 12 is trapped within the compression chamber 12.

[0115] Furthermore, when the volume of the compression chamber 12 is at its maximum, the suction communication hole 35e is located at a position that is almost directly opposite the second radial hole 15c, as shown in Fig. 9. Therefore, as shown by the dashed arrow in Fig. 9, when refrigerant gas is drawn into the compression chamber 12, the refrigerant gas can flow almost directly from the second radial hole 15c to the suction communication hole 35e. As a result, when the phase of the second radial hole 15c and the suction communication hole 35e is in the state shown in Fig. 9, the suction side flow resistance is minimized. As a result, in this compressor, when the volume of the compression chamber 12 is at its maximum, the second radial hole 15c and the suction communication hole 35e are in a phase that minimizes the suction side flow resistance.

[0116] 4, the rotational phase between the driving scroll 30 and the driven scroll 40 becomes phase X3, which is greater than phase X2, so that the volume of the compression chamber 12 becomes smaller than the maximum (see FIG. 10). Therefore, the refrigerant gas in the compression chamber 12 starts to be compressed as the volume of the compression chamber 12 becomes smaller than the maximum.

[0117] Also, when the rotation phase of the driving scroll 30 and the driven scroll 40 is in phase X3, as shown in FIG. 11, the suction communication hole 35e and the second radial hole 15c start to shift from the position where they were almost directly facing each other in the rotation direction R1 again. Therefore, as shown by the dashed arrow in FIG. 9, when the refrigerant gas is sucked into the compression chamber 12, the refrigerant gas is less likely to reach the suction communication hole 35e from the second radial hole 15c compared to when the suction communication hole 35e and the second radial hole 15c were almost directly facing each other. That is, when the phase of the second radial hole 15c and the suction communication hole 35e is in the position shown in FIG. 11, the suction side flow resistance is greater than the minimum. As a result, in this compressor, as the volume of the compression chamber 12 decreases from the maximum, the suction side flow resistance increases from the minimum. Thus, in this compressor, the second radial hole 15c and the suction communication hole 35e are in a phase where the suction side flow resistance increases as the volume of the compression chamber 12 decreases from the maximum.

[0118] As described above, in this compressor, the suction side flow resistance changes due to the change in phase between the second diameter hole 15c and the suction communication hole 35e, and the magnitude of the first canceling pulsation changes due to the change in the suction side flow resistance. As shown in Fig. 12, in this compressor, the first canceling pulsation has a waveform in opposite phase to the waveform of the suction pulsation. As a result, in this compressor, although suction pulsation is inevitably generated by the suction of refrigerant gas from the suction chamber 65 to each compression chamber 12, the first canceling pulsation acts to cancel the suction pulsation, so that the suction pulsation can be reduced.

[0119] As shown in Fig. 5, as the rotational phase between the driving scroll 30 and the driven scroll 40 becomes greater than 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 becomes phase X4, the compression chamber 12 begins to communicate with the discharge port 39, as shown in Fig. 13. However, at this time, the discharge reed valve 57 is still in a closed state.

[0120] 5, the rotation phase between the driving scroll 30 and the driven scroll 40 becomes phase X5, so that the compression of the refrigerant gas in the compression chamber 12 further progresses. As a result, the pressure in the compression chamber 12 exceeds the pressure in the discharge chamber 8, and the discharge reed valve 57 opens. Thus, the discharge of the refrigerant gas from the compression chamber 12 to the discharge chamber 8 begins.

[0121] Here, in this compressor, the discharge communication hole 37d is formed in the second boss 37b of the second cover body 37. Therefore, as the driving scroll 30 is rotationally driven, the discharge communication hole 37d rotates within the second insertion hole 61 in the rotation direction R1 around the rotation axis O1, as shown in Figures 14 and 16. Therefore, as the driving scroll 30 is rotationally driven, the phase between the discharge passage 67 and the discharge communication hole 37d changes.

[0122] Then, by changing the phase between the discharge passage 67 and the discharge communication hole 37d in this way, in this compressor, the discharge side flow resistance, which is the flow resistance of the refrigerant gas flowing from the discharge communication hole 37d to the discharge passage 67, changes. Also, in this compressor, the discharge side flow resistance generates a pulsation different from the discharge pulsation, the suction pulsation, and the first cancel pulsation (hereinafter, this pulsation is referred to as the "second cancel pulsation"). Then, as the discharge side flow resistance changes, the magnitude of the second cancel pulsation changes.

[0123] Here, when the rotation phase between the driving scroll 30 and the driven scroll 40 is phase X4, as shown in FIG. 14, the discharge communication hole 37d is located at a position almost directly facing the discharge passage 67. Therefore, as shown by the dashed arrow in FIG. 14, the refrigerant gas discharged to the discharge chamber 8 can flow from the discharge communication hole 37d almost directly to the discharge passage 67. That is, when the phase between the discharge passage 67 and the discharge communication hole 37d is in the state shown in FIG. 14, the discharge side flow resistance is minimized. In other words, in this compressor, the discharge communication hole 37d is formed in the second boss 37b so that the discharge side flow resistance is minimized when the rotation phase between the driving scroll 30 and the driven scroll 40 is phase X4. Here, as described above, when the rotation phase between the driving scroll 30 and the driven scroll 40 is phase X4, the discharge reed valve 57 is in a closed state. Therefore, the flow rate of the refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 is minimum, zero. As a result, in this compressor, when the flow rate of refrigerant gas discharged from compression chamber 12 to discharge chamber 8 is at a minimum, discharge passage 67 and discharge communication hole 37d are in a phase that minimizes flow resistance on the discharge side.

[0124] Then, as shown in Fig. 5, the rotational phase between the driving scroll 30 and the driven scroll 40 becomes phase X5 which is greater than phase X4, so that the pressure in the compression chamber 12 reaches the discharge pressure and the discharge reed valve 57 opens. As a result, refrigerant gas is discharged from the compression chamber 12 to the discharge chamber 8. At this time, the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 becomes maximum. Furthermore, when the rotational phase between the driving scroll 30 and the driven scroll 40 is phase X5, the two compression chambers 12 are integrated with each other as shown in Fig. 15.

[0125] Here, when the rotation phase of the driving scroll 30 and the driven scroll 40 is phase X5, as shown in Fig. 16, the discharge communication hole 37d is located at a position that is substantially opposite the discharge passage 67 in the rotation direction R1 across the rotation axis O1. Therefore, as shown by the dashed arrow in Fig. 16, the refrigerant gas in the discharge chamber 8 travels from the discharge communication hole 37d through the second insertion hole 61 approximately half a circle in the rotation direction R1 to flow through the discharge passage 67.

[0126] For this reason, when the phase between the discharge passage 67 and the discharge communication hole 37d is in the state shown in Fig. 16, the discharge side flow resistance is maximized. As a result, in this compressor, when the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 is at a maximum, the phase between the discharge passage 67 and the discharge communication hole 37d is such that the discharge side flow resistance is maximized.

[0127] In this manner, in this compressor, the discharge passage 67 and the discharge communication hole 37d are shifted in the rotation direction R1 from a position where they were almost directly facing each other (see FIG. 14), so that it becomes difficult for the refrigerant gas to flow from the discharge communication hole 37d to the discharge passage 67. As a result, the discharge side flow resistance becomes greater than the minimum. In this manner, in this compressor, the discharge passage 67 and the discharge communication hole 37d are in a phase where the discharge side flow resistance increases as the flow rate of the refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 approaches the maximum. More specifically, in this compressor, the discharge passage 67 of the discharge section 63 and the discharge communication hole 37d are in a phase where the discharge side flow resistance increases as the rotation phase of the driving scroll 30 and the driven scroll 40 approaches the rotation phase where the flow rate of the refrigerant gas discharged to the discharge chamber 8 is maximum.

[0128] As described above, in this compressor, the discharge side circulation resistance changes due to the change in phase between the discharge passage 67 and the discharge communication hole 37d, and in turn the change in phase between the discharge portion 63 and the discharge communication hole 37d, and the magnitude of the second canceling pulsation changes due to the change in discharge side circulation resistance. As shown in Fig. 17, in this compressor, the second canceling pulsation has a waveform in opposite phase to the waveform of the discharge pulsation. As a result, in this compressor, although discharge pulsation is unavoidably generated by the discharge of refrigerant gas from each compression chamber 12 to the discharge chamber 8, the second canceling pulsation acts to cancel the discharge pulsation, so that the discharge pulsation can also be reduced.

[0129] Thus, in this compressor, the suction pulsation can be reduced by changing the suction side flow resistance, and the discharge pulsation can be reduced by changing the discharge side flow resistance. Therefore, in this compressor, it is not necessary to excessively increase the size of the suction chamber 65 in order to reduce the suction pulsation, and it is also not necessary to excessively increase the size of the recess 38 and the connecting passage 37c, i.e., the discharge chamber 8, in order to reduce the discharge pulsation. Therefore, in this compressor, it is difficult to increase the size of the housing 6, and it is also difficult to increase the size of the driving scroll 30 and the compression mechanism 14.

[0130] Therefore, the compressor of the first embodiment can suppress an increase in size while realizing high quietness.

[0131] In particular, in this compressor, the compression mechanism 14 is composed of the driving scroll 30, the driven scroll 40, and the driven mechanism 20, and the compression mechanism 14 is a bi-rotation type scroll compression mechanism. A suction communication hole 35e is formed in the first cover body 35, and a discharge communication hole 37d is formed in the second boss 37b of the second cover body 37. In this manner, in this compressor, both the suction communication hole 35e and the discharge communication hole 37d can be formed in the driving scroll 30, making it easy to form the suction communication hole 35e and the discharge communication hole 37d.

[0132] In addition, since the compression mechanism 14 is a bidirectional scroll compression mechanism, the generation of suction pulsation and discharge pulsation is less likely to become complicated in this compressor, and it is possible to suitably reduce suction pulsation and discharge pulsation by changing the suction side flow resistance and the discharge side flow resistance.

[0133] In addition, in this compressor, the driving scroll 30 is provided with a discharge reed valve 57, which allows the refrigerant gas to be discharged from each compression chamber 12 to the discharge chamber 8, while prohibiting the refrigerant gas from flowing from the discharge chamber 8 to each compression chamber 12. Therefore, in this compressor, the generation of pulsation due to the refrigerant gas flowing back from the discharge chamber 8 to each compression chamber 12 is preferably prevented. In addition, since the discharge communication hole 37d is formed in the second boss 37b, the discharge communication hole 37d is located downstream of the discharge reed valve 57 in the flow direction of the refrigerant gas. Therefore, in this compressor, the pressure fluctuation when the refrigerant gas flows from the discharge communication hole 37d to the discharge passage 67 can assist the opening of the discharge reed valve 57. As a result, in this compressor, the discharge reed valve 57 can be opened and closed preferably.

[0134] Moreover, in this compressor, the discharge section 63 has a discharge passage 67 and a discharge communication port 69, and the discharge passage 67 and the discharge communication section 37d communicate with each other in the radial direction of the housing 6. Furthermore, the suction passage 15 and the suction communication hole 35e communicate with each other in the radial direction of the housing 6. As a result, in this compressor, the discharge passage 67 and the discharge communication section 37d communicate with each other in the direction of the rotational axis O1, and the entire compressor, including the housing 6, can be made smaller in size in the direction of the rotational axis O1 than in a configuration in which the discharge passage 67 and the discharge communication section 37d communicate with each other in the direction of the rotational axis O1 and the suction passage 15 and the suction communication hole 35e communicate with each other in the direction of the rotational axis O1.

[0135] Example 2 18, in the compressor of the second embodiment, the housing 6 is composed of a housing main body 60 and a housing cover 70. In this compressor, the driving scroll 30 has a third cover body 81 instead of the second cover body 37. In this compressor, a discharge chamber 83 is formed in the driving end plate 31 instead of the recess 38.

[0136] 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 is substantially disk-shaped with the rotation axis O1 as its center. The housing cover 70 has a front surface 70a facing forward, a rear surface 70b facing rearward and located on the opposite side of 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 housing body 60 in the same manner as the housing cover 62 in the compressor of the first embodiment.

[0137] Further, a second insertion hole 72 and a discharge communication port 73 are formed in the housing cover 70. The discharge communication port 73 is an example of the "discharge portion" in the present invention.

[0138] The second insertion hole 72 is formed in a cylindrical shape centered on the rotation axis O1, and extends in the direction of the rotation axis O1 inside the housing cover 70. The rear end of the second insertion hole 72 opens to the rear surface 70b. The second insertion hole 72 is provided with the second plain bearing 52, similar to the compressor of the first embodiment.

[0139] The discharge communication port 73 penetrates the housing cover 70 in the direction of the rotation axis O1. As a result, the front end of the discharge communication port 73 opens to the front surface 70a, and the rear end communicates with the second insertion hole 72. As shown in Fig. 19, the discharge communication port 73 is formed in a cylindrical shape that is eccentric with respect to the rotation axis O1. In other words, the discharge communication port 73 is formed in the housing cover 70 at a position that is eccentric with respect to the rotation axis O1. The discharge communication port 73 is connected to a condenser (not shown) through a pipe (not shown).

[0140] As shown in FIG. 18, the third cover body 81 has a cover body 81a and a second boss 81b. The second boss 81b is also an example of the "rotating shaft portion" in the present invention. The cover body 81a has a configuration similar to that of the cover body 37a in the compressor of the first embodiment. The second boss 81b is integrally formed with the cover body 81a and protrudes forward from the center of the cover body 81a in the direction of the rotation axis O1 and the driven axis O2. As a result, the center of the second boss 81b is coaxial with the rotation axis O1.

[0141] Further, a connection passage 81c is formed in the third cover body 81. The connection passage 81c is an example of the "discharge communication part" in the present invention. The connection passage 81c penetrates the third cover body 81 including the inside of the second boss 81b in the direction of the rotation axis O1. As shown in Figs. 18 and 19, the connection passage 81c is formed in a cylindrical shape eccentric to the rotation axis O1. That is, the connection passage 81c is formed in the third cover body 81 at a position eccentric to the rotation axis O1. The connection passage 81c is formed to have a smaller diameter than the discharge communication port 73. In Fig. 19, for ease of explanation, the discharge communication port 73 and the connection passage 81c are illustrated in a simplified manner, and the second boss 81b and the like are not illustrated.

[0142] 18 has the same configuration as the recess 38 in the compressor of the first embodiment. That is, the discharge chamber 83 is recessed in a substantially cylindrical shape from the front surface 311 of the driving end plate 31 toward the rear, and communicates with the discharge port 39. A discharge reed valve 57 and a retainer 58 are fixed in the discharge chamber 83 by a fixing bolt 59.

[0143] 18, in this compressor, similarly to the compressor of the first embodiment, the third cover body 81, the driving end plate 31, the driving peripheral wall 32, and the first cover body 35 are connected by a plurality of bolts 50. As a result, in the third cover body 81, the cover body 81a covers the discharge chamber 83 of the driving end plate 31 from the front. Thus, the connecting passage 81c communicates with the discharge chamber 83 from the front. Also, the connecting passage 81c is located downstream of the discharge reed valve 57 in the flow direction of the refrigerant gas.

[0144] In this compressor, the second boss 81b is inserted into the second insertion hole 72. As a result, the second boss 81b is rotatably supported by the second sliding bearing 52 in the second insertion hole 72. Furthermore, the discharge communication port 73 and the connection passage 81c communicate with each other in the direction of the rotation axis O1. The other configuration of this compressor is similar to that of the compressor in the first embodiment, and the same configuration is denoted by the same reference numerals, and detailed description of the configuration will be omitted.

[0145] In this compressor, the refrigerant gas compressed in the compression chamber is discharged from the discharge port 39 into the discharge chamber 83. The refrigerant gas discharged into the discharge chamber 83 passes through the connection passage 81c and is discharged from the discharge communication port 73 toward the condenser.

[0146] In this compressor, the discharge communication port 73 and the connection passage 81c are each eccentric with respect to the rotation axis O1, as shown in Fig. 19. Therefore, in this compressor, the phase of the discharge communication port 73 and the connection passage 81c changes while the driving scroll 30 makes one rotation in the rotation direction R1 shown in Fig. 19.

[0147] That is, in this compressor, when the rotation angle of the driving scroll 30 is zero degrees, the discharge communication port 73 and the connecting passage 81c have a phase as shown in Fig. 19(A). Then, when the driving scroll 30 rotates about 90° in the rotation direction R1 from the position shown in Fig. 19(A), the discharge communication port 73 and the connecting passage 81c have a phase as shown in Fig. 19(B). Then, when the driving scroll 30 rotates about 90° in the rotation direction R1 from the position shown in Fig. 19(B) (when the driving scroll 30 rotates about 180° in the rotation direction R1 from the position shown in Fig. 19(A), the discharge communication port 73 and the connecting passage 81c have a phase as shown in Fig. 19(C). Then, when the driving scroll 30 rotates approximately 90° in the rotational direction R1 from the position shown in (C) of Figure 19 (when the driving scroll 30 rotates approximately 270° in the rotational direction R1 from the position shown in (A) of Figure 19), the discharge communication port 73 and the connecting passage 81c will be in the phase shown in (D) of Figure 19.

[0148] In this way, the communication area between the discharge communication port 73 and the connecting passage 81c changes during one rotation of the driving scroll 30, and as a result, in this compressor, the discharge side flow resistance, which is the flow resistance of the refrigerant gas flowing from the connecting passage 81c to the discharge communication port 73, changes.

[0149] Specifically, if the communication area between the discharge communication port 73 and the connection passage 81c is increased, the discharge side flow resistance is decreased, and if the communication area between the discharge communication port 73 and the connection passage 81c is decreased, the discharge side flow resistance is increased. Therefore, in this compressor, when the phase between the discharge communication port 73 and the connection passage 81c is in the state shown in Fig. 19(A), the communication area between the discharge communication port 73 and the connection passage 81c is maximum, and the discharge side flow resistance is minimum. On the other hand, when the phase between the discharge communication port 73 and the connection passage 81c is in the state shown in Fig. 19(C), the communication area between the discharge communication port 73 and the connection passage 81c is minimum, and the discharge side flow resistance is maximum.

[0150] Here, in this compressor, when the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 83 is minimum, the discharge communication port 73 and the connection passage 81c are in a phase that minimizes the discharge side flow resistance (see FIG. 19A). When the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 83 is maximum, the discharge communication port 73 and the connection passage 81c are in a phase that maximizes the discharge side flow resistance (see FIG. 19C).

[0151] As a result, like the compressor of the first embodiment, in this compressor, discharge pulsation inevitably occurs due to the discharge of refrigerant gas from each compression chamber 12 to the discharge chamber 83, but the discharge pulsation can be reduced.

[0152] In addition, in this compressor, because the discharge communication port 73 and the connection passage 81c communicate with each other in the direction of the rotation axis O1, it is possible to reduce the radial size of the entire compressor, including the housing 6, compared to a configuration in which the discharge communication port 73 and the connection passage 81c communicate with each other in the radial direction of the housing 6. Other operations of this compressor are similar to those of the compressor of the first embodiment.

[0153] Example 3 20, in the compressor of the third embodiment, the housing 6 is composed of a housing main body 60 and a housing cover 75. In this compressor, the driving scroll 30 has a fourth cover body 88 instead of the second cover body 37.

[0154] The housing cover 75 is composed of a first main body member 75a and a first holding member 75b. The first main body member 75a is made of an aluminum alloy. The first main body member 75a is generally disk-shaped and centered on the rotation axis O1, similar to the housing cover 70 in the compressor of the second embodiment. The first main body member 75a has a front surface 751 facing forward, a rear surface 752 facing rearward and located on the opposite side of the front surface 751, and an outer circumferential 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.

[0155] The first main body member 75a is fixed to the housing main body 60 in the same manner as the housing cover 62 in the compressor of the first embodiment. Thus, in this compressor, the housing main body 60 and the housing cover 75 are fixed together.

[0156] Further, the first main body member 75a is formed with a second insertion hole 76 and a first communication port 77a. The second insertion hole 76 is formed in a cylindrical shape centered on the rotation axis O1 and extends in the first main body member 75a in the direction of the rotation axis O1. The rear end of the second insertion hole 76 opens to the rear surface 752. Here, the second insertion hole 76 is formed with a larger diameter than the second insertion hole 72 in the compressor of the second embodiment.

[0157] The first communication port 77a penetrates the first main body member 75a in the direction of the rotation axis O1. As a result, the front end of the first communication port 77a opens to the front surface 751, and the rear end communicates with the second insertion hole 76. Although detailed illustration is omitted, the first communication port 77a is formed in a cylindrical shape eccentric with respect to the rotation axis O1, similar to the discharge communication port 73 in the compressor of the second embodiment. In other words, the first communication port 77a is formed in the first main body member 75a at a position eccentric with respect to the rotation axis O1.

[0158] The first holding member 75b is made of resin. The first holding member 75b is formed in a generally cylindrical shape with a bottom. A second communication port 77b is formed in the front part of the first holding member 75b. The second communication port 77b penetrates the front part of the first holding member 75b in the direction of the rotation axis O1. The second communication port 77b is formed in a cylindrical shape that is coaxial with and has the same diameter as the first communication port 77a. In other words, the second communication port 77b is formed in the front part of the first holding member 75b at a position eccentric to the rotation axis O1.

[0159] The first holding member 75b is accommodated in the second insertion hole 76. At this time, the first holding member 75b is accommodated in the second insertion hole 76 in a state in which it cannot rotate. Thus, in the housing cover 75, both the first main body member 75a and the first holding member 75b are unable to rotate. Also, by accommodating the first holding member 75b in the second insertion hole 76, the second communication port 77b is located behind the first communication port 77a and communicates with the first communication port 77a. Thus, 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 to the rotation axis O1. The discharge communication port 77 is an example of the "discharge portion" in the present invention.

[0160] Further, a radial ball bearing 78 is provided inside the first holding member 75b. That is, the first holding member 75b holds the radial ball bearing 78 in a state of being housed in the second insertion hole 76. Furthermore, seal rings 79a and 79b are provided on the outer circumferential surface of the first holding member 75b. The seal rings 79a and 79b seal the gap between the outer circumferential surface of the first holding member 75b and the inner circumferential surface of the second insertion hole 76. Note that instead of the radial ball bearing 78, a sliding bearing may be provided inside the first holding member 75b. Also, the first holding member 75b may be formed of synthetic rubber, or may be formed of a metal or the like having a lower rigidity than the first main body member 75a.

[0161] The fourth cover body 88 has a cover body 88a and a second boss 88b. The second boss 88b is also an example of the "rotating shaft portion" in the present invention. The cover body 88a has a configuration similar to that of the cover body 81a in the compressor of the second embodiment, and further, the cover body 37a in the compressor of the first embodiment. The second boss 88b is integrally formed with the cover body 88a and protrudes forward from the center of the cover body 88a in the direction of the rotation axis O1 and the driven axis O2. As a result, the center of the second boss 88b is coaxial with the rotation axis O1. Here, the second boss 88b protrudes forward shorter than the second boss 81b in the compressor of the second embodiment.

[0162] A connection passage 88c is formed in the fourth cover body 88. The connection passage 88c is also an example of the "discharge communication portion" in the present invention. The connection passage 88c penetrates the fourth cover body 88 including the inside of the second boss 88b in the direction of the rotation axis O1. The connection passage 88c is formed in a cylindrical shape eccentric to the rotation axis O1, similar to the connection passage 81c in the compressor of the second embodiment. That is, the connection passage 88c is formed in the fourth cover body 88 at a position eccentric to the rotation axis O1. The connection passage 88c is also formed to have a smaller diameter than the discharge communication port 77.

[0163] The fourth cover body 88 is connected to the drive end plate 31 by a plurality of bolts 50, similar to the third cover body 81 in the compressor of the second embodiment. This allows a connecting passage 88c to communicate with the discharge chamber 83 from the front. In addition, the connecting passage 88c is located downstream of the discharge reed valve 57 in the flow direction of the refrigerant gas.

[0164] In this compressor, the second boss 88b is inserted into the radial ball bearing 78. As a result, the second boss 88b is rotatably supported in the first holding member 75b and further in the second insertion hole 76 of the first body member 75a. In addition, the discharge communication port 77 and the connection passage 88c communicate with each other in the direction of the rotation axis O1. The other configurations of this compressor are similar to those of the compressor of the second embodiment.

[0165] In this compressor, the discharge communication port 77 and the connection passage 88c are each eccentric with respect to the rotation axis O1. Therefore, similar to the compressor of the second embodiment, in this compressor, the phase between the discharge communication port 77 and the connection passage 88c changes while the driving scroll 30 rotates once in the rotation direction R1 (see FIG. 19). Thus, in this compressor, discharge pulsation can be reduced similarly to the compressor of the second embodiment.

[0166] Here, in this compressor, when compressing the refrigerant gas in each compression chamber 12, the driving scroll 30 and the driven scroll 40 inevitably vibrate. In this regard, in this compressor, the first holding member 75b made of resin and provided in the second insertion hole 76 holds the radial ball bearing 78. As a result, in this compressor, the first holding member 75b can suppress the transmission of the vibration of the driving scroll 30 to the first body member 75a through the second boss 88b and the radial ball bearing 78. Therefore, in this compressor, it is possible to suppress the vibration of the housing cover 75 and therefore the housing 6 as much as possible during operation. Other functions of this compressor are similar to those of the compressor of the first embodiment.

[0167] Example 4 As shown in FIG. 21, the compressor of the fourth embodiment includes a housing 301, a fixed block 303, a drive shaft 305, an electric motor 307, and a compression mechanism 314.

[0168] The housing 301 is composed of a motor housing 313 and a compressor housing 315. The motor housing 313 has a rear wall 313a and a first peripheral wall 313b. The rear wall 313a is located at the rear end of the motor housing 313, i.e., the rear end of the housing 301, and extends in the radial direction of the motor housing 313.

[0169] The first peripheral wall 313b is connected to the rear wall 313a and extends forward from the rear wall 313a in the direction of the rotation axis O3. The rotation axis O3 is parallel to the front-rear direction. The rear wall 313a and the first peripheral wall 313b form the motor housing 313 in a cylindrical shape with a bottom. The rear wall 313a and the first peripheral wall 313b form a suction chamber 317 in the motor housing 313.

[0170] Further, a support recess 313c and a suction portion 313d are formed in the rear wall 313a. The support recess 313c faces the suction chamber 317 and is recessed rearward. The support recess 313c is formed in a substantially cylindrical shape centered on the rotation axis O3. A first radial ball bearing 319 is provided inside the support recess 313c.

[0171] The suction section 313d is composed of a first passage 401 and a second passage 402. The first passage 401 opens to the outer circumferential surface of the rear wall 313a and extends inside the rear wall 313a in the radial direction of the motor housing 313. Here, the first passage 401 does not penetrate the rear wall 313a in the radial direction of the motor housing 313. In addition, the first passage 401 is connected to an evaporator (not shown).

[0172] The second passage 402 extends through the rear wall 313a in the direction of the rotation axis O3. As a result, the first passage 401 and the second passage 402 are in a perpendicular relationship. The rear end of the second passage 402 communicates with the first passage 401. In addition, the front end of the second passage 402 communicates with the inside of the support recess 313c.

[0173] The second passage 402 is formed in a cylindrical shape that is eccentric with respect to the rotation axis O3. That is, the second passage 402 is formed in the rear wall 313a at a position that is eccentric with respect to the rotation axis O3.

[0174] The compressor housing 315 has a front wall 315a and a second peripheral wall 315b. The front wall 315a is located at the front end of the compressor housing 315, i.e., the front end of the housing 301, and extends in the radial direction of the compressor housing 315. The second peripheral wall 315b is connected to the front wall 315a and extends rearward from the front wall 315a in the direction of the rotation axis O3. The front wall 315a and the second peripheral wall 315b form the compressor housing 315 into a cylindrical shape with a bottom.

[0175] The compressor housing 315 is formed with an oil separation chamber 315c, a first discharge recess 315d, a discharge passage 315e, and a discharge communication port 315f. The oil separation chamber 315c is located on the front side in the compressor housing 315 and extends in the radial direction of the compressor housing 315. The first discharge recess 315d is located on the rear side of the oil separation chamber 315c in the compressor housing 315 and has a shape recessed toward the oil separation chamber 315c. The discharge passage 315e extends in the direction of the rotation axis O3 and communicates the oil separation chamber 315c with the first discharge recess 315d. The discharge communication port 315f communicates with the upper end of the oil separation chamber 315c and opens toward the outside of the compressor housing 315. A pipe (not shown) is connected to the discharge communication port 315f.

[0176] A separation cylinder 321 is fixed inside the oil separation chamber 315c. A separator is formed by the inner peripheral surface of the oil separation chamber 315c and the outer peripheral surface of the separation cylinder 321. A filter 323 is provided below the separation cylinder 321 inside the oil separation chamber 315c.

[0177] The fixed block 303 is provided between the motor housing 313 and the compressor housing 315. The motor housing 313, the compressor housing 315, and the fixed block 303 are fastened to each other by a plurality of bolts 325 from the compressor housing 315 side. In this way, the fixed block 303 is fixed to the motor housing 313 and the compressor housing 315 while being sandwiched between them. The fixed block 303 is disposed between the electric motor 307 and the compression mechanism 314 in the housing 301. Note that FIG. 21 illustrates one of the plurality of bolts 25. The method of fixing the motor housing 313, the compressor housing 315, and the fixed block 303 can be designed as appropriate.

[0178] Fixed block 303 is formed with boss 303a which protrudes toward suction chamber 317 and, ultimately, toward electric motor 307. An insertion hole 303b is formed at the tip of boss 303a. A second radial ball bearing 327 and a seal member 329 are provided within boss 303a.

[0179] In addition, the fixed block 303 has a plurality of communication passages 355 formed therein, and also has a plurality of rotation prevention pins 331 fixed thereto. Each communication passage 355 is disposed at a position outside the boss 303a, and passes through the fixed block 303 in the direction of the rotation axis O3. As a result, each communication passage 355 communicates with the suction chamber 317 and the inside of the compressor housing 315. Each rotation prevention pin 331 is fixed to the fixed block 303 in a state where it protrudes rearward. Note that FIG. 21 illustrates one each of the communication passages 355 and each rotation prevention pin 331.

[0180] The drive shaft 305 has a cylindrical shape extending in the direction of the rotation axis O3. The drive shaft 305 is formed with an intake communication part 500. The intake communication part 500 is composed of an axial passage 501 and a path 502.

[0181] The axial passage 501 opens to the rear end surface of the drive shaft 305 and extends inside the drive shaft 305 in the direction of the rotation axis O3. Here, the axial passage 501 does not penetrate the drive shaft 305 in the direction of the rotation axis O3. The axial passage 501 is formed in a cylindrical shape that is eccentric with respect to the rotation axis O3. In other words, the axial passage 501 is formed in the drive shaft 305 at a position eccentric with respect to the rotation axis O3. Also, the axial passage 501 is formed to have a smaller diameter than the second passage 402.

[0182] The path 502 opens to the outer circumferential surface of the drive shaft 305, and extends inside the drive shaft 305 in the radial direction of the drive shaft 305 and therefore the housing 301. As a result, the path 502 communicates with the shaft path 501.

[0183] In addition, an eccentric pin 505 is fixed to the drive shaft 305. The eccentric pin 505 is disposed at a position eccentric from the rotation axis O3 on the front end surface of the drive shaft 305. The eccentric pin 505 is formed in a cylindrical shape having a smaller diameter than the drive shaft 305, and extends forward from the drive shaft 305.

[0184] Drive shaft 305 is provided in suction chamber 317. A rear portion of drive shaft 305 is rotatably supported in support recess 313c of motor housing 313 via first radial ball bearing 319. As a result, in suction communication part 500, shaft passage 501 communicates with second passage 402 of suction part 313d in the direction of rotation axis O3. In addition, in suction communication part 500, path 502 opens into suction chamber 317. In this way, suction communication part 500 communicates between suction part 313d and suction chamber 317.

[0185] Further, by providing the drive shaft 305 in the suction chamber 317, the front portion of the drive shaft 305 and the eccentric pin 505 are inserted into the insertion hole 303b of the fixed block 303 and enter the boss 303a. In the boss 303a, the front portion of the drive shaft 305 is rotatably supported by the second radial ball bearing 327. Thus, the drive shaft 305 is rotatable around the rotation axis O3 in the suction chamber 317. In addition, the gap between the fixed block 303 and the drive shaft 305 is sealed by the seal material 329. Furthermore, the eccentric pin 505 is fitted into the bush 350 in the boss 303a.

[0186] Further, a balance weight 333 is formed integrally with the drive shaft 305. The balance weight 333 is disposed at a position eccentric from the rotation axis O3 in the front portion of the drive shaft 305. More specifically, the balance weight 333 is disposed at a position opposite the eccentric pin 505 across the rotation axis O3. The balance weight 333 is disposed within the suction chamber 317, between the fixed block 303 and the electric motor 307.

[0187] The electric motor 307 is composed of a stator 307a and a rotor 307b. The stator 307a is formed in a cylindrical shape, and is fixed in the suction chamber 317 to the inner circumferential surface of the first circumferential wall 313b.

[0188] The rotor 307b is disposed within the stator 307a. The drive shaft 305 is fixed to the rotor 307b by shrink fitting. This makes the rotor 307b and the drive shaft 305 integral with each other. The rotor 307b rotates within the stator 307a, thereby rotating the drive shaft 305 around the rotation axis O3.

[0189] The compression mechanism 314 has a fixed scroll 309 and a movable scroll 310. The fixed scroll 309 is disposed in a compressor housing 315 and fixed to the compressor housing 315. The fixed scroll 309 has a fixed end plate 309a, a fixed peripheral wall 309b, and a fixed spiral wall 309c. The fixed end plate 309a is located at the front end of the fixed scroll 309 and is formed in a disk shape. A second discharge recess 309d and a discharge port 309e are formed in the fixed end plate 309a. The second discharge recess 309d is shaped to be recessed rearward from the front end surface of the fixed end plate 309a. The second discharge recess 309d faces the first discharge recess 315d by fixing the fixed scroll 309 to the compressor housing 315. In this way, the first discharge recess 315d and the second discharge recess 309d form a discharge chamber 335. The discharge chamber 335 communicates with the oil separation chamber 315c through a discharge passage 315e. The discharge port 309e penetrates the fixed end plate 309a in the direction of the rotation axis O3 and communicates with the discharge chamber 335.

[0190] Further, a discharge reed valve 339 and a retainer 341 are attached to the fixed end plate 309a by a fixing bolt 337. The fixing bolt 337, the discharge reed valve 339, and the retainer 341 are disposed in the discharge chamber 335. The discharge reed valve 339 opens and closes the discharge port 309e by elastically deforming. The retainer 341 adjusts the opening degree of the discharge reed valve 339.

[0191] The fixed peripheral wall 309b is connected to the fixed end plate 309a at the outer periphery of the fixed end plate 309a and extends cylindrically toward the rear. The fixed peripheral wall 309b is formed with an intake port 309f. The intake port 309f penetrates the fixed peripheral wall 309b in the radial direction of the fixed scroll 309. As a result, the intake port 309f opens into the compressor housing 315. The fixed scroll wall 309c is raised on the rear surface of the fixed end plate 309a and is integral with the fixed peripheral wall 309b on the inside of the fixed peripheral wall 309b.

[0192] Further, an oil supply passage 343 is formed in the fixed scroll 309. The oil supply passage 343 penetrates through the fixed end plate 309a and the fixed peripheral wall 309b. As a result, the front end of the oil supply passage 343 opens to the front surface of the fixed end plate 309a, and the rear end of the oil supply passage 343 opens to the rear surface of the fixed peripheral wall 309b. The oil supply passage 343 communicates with the oil separation chamber 315c through the filter 323. The shape of the oil supply passage 343 can be designed as appropriate.

[0193] The movable scroll 310 is provided in a compressor housing 315 and is located between the fixed scroll 309 and the fixed block 303. The movable scroll 310 has a movable end plate 310a and a movable spiral wall 310b. The movable end plate 310a is located at the rear end of the movable scroll 310 and is formed in a disk shape. A bush 350 is rotatably supported by the movable end plate 310a via a third radial ball bearing 345. As a result, the movable scroll 310 is connected to the drive shaft 305 via the bush 350 and the eccentric pin 505 at a position eccentric to the rotation axis O3.

[0194] Furthermore, the movable end plate 310a is provided with rings 347, the number of which is the same as the number of rotation-prevention pins 331. Note that in Fig. 21, one of the plurality of rings 347 is shown.

[0195] The movable spiral wall 310b is raised on the front surface of the movable end plate 310a and extends toward the fixed end plate 309a. An air supply hole 310d is formed near the center of the movable spiral wall 310b. The air supply hole 310d opens at the front end of the movable spiral wall 310b and extends through the movable spiral wall 310b in the direction of the rotation axis O3 to the movable end plate 310a.

[0196] The fixed scroll 309 and the movable scroll 310 are meshed with each other. As a result, a compression chamber 349 is formed between the fixed scroll 309 and the movable scroll 310 by the fixed end plate 309a, the fixed spiral wall 309c, the movable end plate 310a, and the movable spiral wall 310b. The volume of the compression chamber 349 changes as the movable scroll 310 rotates. As a result, the compression chamber 349 is communicated with the suction port 309f and the discharge port 309e, respectively.

[0197] Furthermore, each ring 47 is connected to each rotation prevention pin 331 by inserting each rotation prevention pin 331 into each ring 347. These rotation prevention pins 331 and rings 347 form rotation prevention mechanism 316. Note that the number of each of rotation prevention pins 331 and rings 347 constituting rotation prevention mechanism 316 can be appropriately designed as long as there are three or more of each.

[0198] Furthermore, a metallic thrust plate 361 is provided between the movable scroll 310 and the fixed block 303. The thrust plate 361 is capable of biasing the movable scroll 310 forward, i.e., toward the fixed scroll 309, by a restoring force generated when the movable scroll 310 is elastically deformed. In addition, a back pressure chamber 363 is formed in the boss 303a of the fixed block 303 by the movable end plate 310a and the thrust plate 361. The back pressure chamber 363 is in communication with the air supply hole 310d.

[0199] In the compressor configured as described above, as shown by the dashed arrow in Fig. 21, low-temperature, low-pressure refrigerant gas that has passed through the evaporator is drawn from the suction section 313d through the suction connection section 500 into the suction chamber 317. Then, as the electric motor 307 operates, the rotor 307b rotates together with the drive shaft 305 in the stator 307a. Thus, in the compression mechanism 314, the movable scroll 310 rotates, the movable end plate 310a slides on the tip of the fixed spiral wall 309c, and the fixed spiral wall 309c and the movable spiral wall 310b slide against each other. At this time, the rotation prevention mechanism 316 restricts the rotation of the movable scroll 310, and the movable scroll 310 only revolves around the fixed scroll 309.

[0200] In addition, as the movable scroll 310 rotates, the refrigerant gas in the suction chamber 317 is sucked into the compression chamber 349 through the suction port 309f via the communication passage 355. The compression chamber 349 compresses the refrigerant gas therein while decreasing its volume due to the rotation of the movable scroll 310. The high-pressure refrigerant gas compressed in the compression chamber 349 is discharged from the discharge port 309e to the discharge chamber 335, and then reaches the oil separation chamber 315c through the discharge passage 315e. The high-pressure refrigerant gas flows through the inside of the separation tube 321 while separating the lubricating oil as it circulates between the outer circumferential surface of the separation tube 321 and the inner circumferential surface of the oil separation chamber 315c, and is discharged to the outside of the housing 301 through the discharge communication port 315f.

[0201] Meanwhile, the lubricating oil separated from the refrigerant gas is stored in the oil separation chamber 315c. Then, this lubricating oil passes through the filter 323 and flows through the oil supply passage 343, and is supplied to the sliding parts between the fixed scroll 309 and the movable scroll 310, the inside of the suction chamber 317, etc.

[0202] Furthermore, a portion of the high-pressure refrigerant gas compressed in the compression chamber 349 flows through the air supply hole 310d and is supplied into the back pressure chamber 363. As a result, the movable scroll 310 is urged toward the compression chamber 349 by the pressure in the back pressure chamber 363 via the thrust plate 361. The movable scroll 310 is also urged toward the compression chamber 349 by the elastic force of the thrust plate 361. In this manner, in this compressor, the movable scroll 310 is prevented from rotating in a state inclined with respect to the rotation axis O3.

[0203] Although suction pulsation inevitably occurs during operation of this compressor, it is possible to suitably reduce the suction pulsation. That is, in this compressor, the low-temperature, low-pressure refrigerant gas that has passed through the evaporator flows from the first passage 401 to the second passage 402 of the suction section 313d, and then flows from the axial passage 501 to the path 502 of the suction communication section 500, and is sucked from the path 502 into the suction chamber 317.

[0204] Here, in this compressor, the second passage 402 and the axial passage 501 are each eccentric with respect to the rotation axis O3. Therefore, in this compressor, the phase between the second passage 402 and the axial passage 501 changes during one rotation of the drive shaft 305, and therefore the movable scroll 310. Then, as the phase between the second passage 402 and the axial passage 501 changes, the communication area between the second passage 402 and the axial passage 501, and therefore the communication area between the suction section 313d and the suction communication section 500, changes. Thus, in this compressor, the communication area between the second passage 402 and the axial passage 501 changes during one rotation of the drive shaft 305, and thus the suction side flow resistance, which is the flow resistance of the refrigerant gas flowing from the second passage 402 to the axial passage 501, changes.

[0205] Specifically, if the communication area between second passage 402 and axial passage 501 is increased, the suction side flow resistance is reduced, and if the communication area between suction portion 313d and suction connecting portion 500 is reduced, the suction side flow resistance is increased.

[0206] Although detailed illustration is omitted, in this compressor, when the flow rate of refrigerant gas sucked from suction port 309f to compression chamber 349 is at a maximum, second passage 402 and axial passage 501 are in a phase that maximizes suction-side flow resistance. In addition, in this compressor, when the volume of compression chamber 349 is at a maximum, second passage 402 and axial passage 501 are in a phase that minimizes suction-side flow resistance.

[0207] As a result, this compressor can also reduce suction pulsation in the same way as the compressor of embodiment 1. As a result, in this compressor, it is not necessary to excessively increase the size of suction chamber 317 in order to reduce suction pulsation, and therefore, it is difficult to increase the size of housing 301 in this compressor.

[0208] Therefore, the compressor of the fourth embodiment can also achieve high quietness while suppressing an increase in size.

[0209] Example 5 As shown in FIG. 22, in the compressor of the fifth embodiment, the housing 301 is composed of a motor housing 318 and a compressor housing 315 (see FIG. 21).

[0210] The motor housing 318 shown in Fig. 22 is composed of a second main body member 91 and a second holding member 92. The second main body member 91 is made of an aluminum alloy. The second main body member 91 has a rear wall 91a and a first peripheral wall 91b. The rear wall 91a is located at the rear end of the second main body member 91, and therefore the motor housing 318, and extends in the radial direction of the motor housing 318.

[0211] The first peripheral wall 91b is connected to the rear wall 91a and extends forward from the rear wall 91a in the direction of the rotation axis O3. Similar to the motor housing 313 in the compressor of the fourth embodiment, a suction chamber 317 is formed in the motor housing 318. The motor housing 318 is also fastened to the compressor housing 315 and the fixed block 303 by a plurality of bolts 325.

[0212] Further, the rear wall 91a is formed with a support recess 911, a first passage 901, and a second passage 902. The support recess 911 is recessed rearward while facing the suction chamber 317. The support recess 911 is formed in a substantially cylindrical shape centered on the rotation axis O3. Here, the support recess 911 is formed with a larger diameter than the support recess 313c in the compressor of the fourth embodiment.

[0213] The first passage 901 and the second passage 902 have the same configuration as the first passage 401 and the second passage 402 in the compressor of the fourth embodiment. That is, the first passage 901 opens to the outer circumferential surface of the rear wall 91a and extends inside the rear wall 91a in the radial direction of the motor housing 318. The first passage 901 is also connected to an evaporator (not shown). The second passage 902 extends through the rear wall 91a in the direction of the rotation axis O3 and has a rear end communicating with the first passage 901. Also, the second passage 902 has a front end communicating with the inside of the support recess 911.

[0214] The second passage 902 is formed in a cylindrical shape that is eccentric with respect to the rotation axis O3. That is, the second passage 902 is formed in the rear wall 91a at a position that is eccentric with respect to the rotation axis O3.

[0215] The second holding member 92 is made of resin. The second holding member 92 is formed in a generally cylindrical shape with a bottom. A third passage 903 is formed in the rear of the second holding member 92. The third passage 903 penetrates the rear of the second holding member 92 in the direction of the rotation axis O3. The third passage 903 is formed in a cylindrical shape that is coaxial with and has the same diameter as the second passage 902. In other words, the third passage 903 is formed in the rear of the second holding member 92 at a position eccentric to the rotation axis O3.

[0216] The second holding member 92 is housed in the support recess 911. At this time, the second holding member 92 is housed in the support recess 911 in a non-rotatable state. Thus, in the motor housing 318, both the second main body member 91 and the second holding member 92 are non-rotatable. Furthermore, by housing the second holding member 92b in the support recess 911, the third passage 903 is located in front of the second passage port 902 and communicates with the second passage 902. Thus, the first passage 901, the second passage 902, and the third passage 903 form a suction section 912.

[0217] Further, the first radial ball bearing 319 is provided inside the second holding member 92. Thus, the second holding member 92 holds the first radial ball bearing 319 in a state of being accommodated in the support recess 911. Furthermore, the seal rings 79c and 79d are provided on the outer circumferential surface of the second holding member 92. The seal rings 79c and 79d seal the gap between the outer circumferential surface of the second holding member 92 and the inner circumferential surface of the support recess 911. Note that instead of the first radial ball bearing 319, a sliding bearing may be provided inside the second holding member 92. Also, like the first holding member 75b in the compressor of the third embodiment, the second holding member 92 may be formed of synthetic rubber or may be formed of a metal or the like having a lower rigidity than the second body member 91.

[0218] A rear portion of drive shaft 305 is inserted into first radial ball bearing 319. Thus, the rear portion of drive shaft 305 is rotatably supported by second retaining member 92 and further by support recess 911 via first radial ball bearing 319. In suction communication portion 500, shaft passage 501 communicates with third passage 903 of suction portion 912 in the direction of rotation axis O3. As a result, in this compressor, suction portion 912 and suction chamber 317 communicate with each other through suction communication portion 500. Other configurations of this compressor are similar to those of the compressor of the fourth embodiment.

[0219] In this compressor, low-temperature, low-pressure refrigerant gas that has passed through the evaporator flows in order from a first passage 901 to a second passage 902 and a third passage 903 of a suction section 912, and then flows from an axial passage 501 to a path 502 of a suction communication section 500, and is sucked from the path 502 into a suction chamber 317 (see the dashed arrow in FIG. 22). In this compressor, the phases of the third passage 903 and the second passage 902 and the axial passage 501 change during one rotation of the drive shaft 305, and thus the movable scroll 310. In this manner, in this compressor, as in the compressor of the fourth embodiment, suction pulsation can be reduced.

[0220] Furthermore, in this compressor, the second retaining member 92 can suppress the vibration of the movable scroll 310 during operation from being transmitted to the second body member 91 via the drive shaft 305 and the first radial ball bearing 319. Therefore, in this compressor, the vibration of the motor housing 318, and therefore the housing 301, during operation can be suppressed as much as possible. Other functions of this compressor are similar to those of the compressor of the fourth embodiment.

[0221] In the above, the present invention has been described based on Examples 1 to 5. However, the present invention is not limited to the above Examples 1 to 5, and it goes without saying that the present invention can be modified and applied as appropriate without departing from the spirit of the present invention.

[0222] For example, in the compressors of the first to third embodiments, both the discharge pulsation and the suction pulsation are reduced, but the present invention is not limited to this, and only the discharge pulsation or only the suction pulsation may be reduced.

[0223] In the compressors of the first to third embodiments, the compression mechanism 14 is a double-rotating scroll compression mechanism. However, the present invention is not limited to this, and the compression mechanism 14 may be a scroll compression mechanism in which one of two scrolls is fixed to the housing 6.

[0224] In the compressors of the first to third embodiments, the compression mechanism 14 may be a rotary type compression mechanism, a vane type compression mechanism, etc. The same applies to the compression mechanism 314 in the compressors of the fourth and fifth embodiments.

[0225] In the compressor of the first embodiment, the discharge chamber 8 is formed in the driving scroll 30, i.e., the compression mechanism 14, but this is not limiting, and the discharge chamber 8 may be formed in the housing 6. In this case, the discharge chamber 8 may be communicated with a portion of the second insertion hole 61 that is opposite the discharge passage 67 in the rotational direction R1 across the second boss 37b, and the discharge communication hole 37d may be configured to radially penetrate the second boss 37b.

[0226] In the compressor of the first embodiment, the second boss 37b is defined as the "rotating shaft portion" in the present invention. The second boss 37b is inserted into the second insertion hole 61, whereby the second boss 37b is rotatably supported by the second support portion 66. However, this is not limiting, and the second boss 37b may be rotatably supported by the second support portion 66 by inserting the second support portion 66 into the inside of the second boss 37b. The same applies to the compressors of the second and third embodiments.

[0227] In the compressor of the fourth embodiment, the second passage 402 and the axial passage 501 communicate with each other in the direction of the rotation axis O3, so that the suction portion 313d and the suction communication portion 500 communicate with each other in the direction of the rotation axis O3. However, the present invention is not limited to this, and the suction portion 313d and the suction communication portion 500 may communicate with each other in the radial direction of the housing 301. The same applies to the compressor of the fifth embodiment.

[0228] In the compressor of the second embodiment, the discharge communication port 73 is formed in a cylindrical shape that is eccentric with respect to the rotation axis O3. However, the shape of the discharge communication port 73 is not limited to this, and the discharge communication port 73 may be other shapes. The same applies to the discharge communication port 77 in the compressor of the third embodiment, the second passage 402 in the compressor of the fourth embodiment, and the second passage 902 and the third passage 903 in the compressor of the fifth embodiment.

[0229] This specification also includes the following inventions. (Appendix 1) a housing having a discharge portion formed therein for discharging the fluid to the outside; a compression mechanism provided within the housing, The compression mechanism is provided with a compression chamber that compresses a fluid while reducing a volume thereof, and is provided with a rotating shaft portion that is rotatably supported about a rotation axis by the housing, a discharge chamber that communicates with the compression chamber and through which the fluid compressed in the compression chamber is discharged is formed in the housing or the compression mechanism; a discharge communication portion that allows the fluid discharged into the discharge chamber to flow to the discharge portion is formed in the rotating shaft portion, a phase between the discharge portion and the discharge communication portion changes with the rotation of the rotating shaft portion, thereby changing a discharge-side flow resistance, which is a flow resistance of a fluid flowing from the discharge communication portion to the discharge portion; a discharge portion and a discharge communication portion that are in a phase such that the discharge side flow resistance increases as a flow rate of the fluid discharged from the compression chamber to the discharge chamber approaches a maximum; (Appendix 2) 2. The compressor according to claim 1, wherein the discharge portion and the discharge communication portion communicate with each other in a radial direction of the housing. (Appendix 3) The compressor according to claim 1, wherein the discharge portion and the discharge communication portion communicate with each other in a direction of the rotation axis. (Appendix 4) The discharge portion is formed in the housing so as to be eccentric with respect to the rotation axis, 4. The compressor according to claim 3, wherein the discharge communication portion is formed on the rotating shaft portion eccentrically with respect to the rotating shaft center. (Appendix 5) 5. The compressor according to claim 1, wherein, when a flow rate of fluid 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 that minimizes the discharge side flow resistance. (Appendix 6) 6. The compressor according to claim 1, wherein when a flow rate of fluid 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 that maximizes the discharge side flow resistance. (Appendix 7) the compression mechanism is provided with a discharge valve that allows fluid to be discharged from the compression chamber to the discharge chamber while preventing fluid from flowing from the discharge chamber to the compression chamber, 7. The compressor according to claim 1, wherein the discharge communication portion is located downstream of the discharge valve in a fluid flow direction. (Appendix 8) a housing having a suction port for suctioning fluid from the outside, a suction chamber communicating with the suction port, and a suction passage communicating with the suction chamber; a compression mechanism provided within the housing, The compression mechanism includes a compression chamber that compresses a fluid while reducing a volume thereof, and a supported portion that is supported rotatably about a rotation axis of the housing. a suction communication portion that allows fluid in the suction passage to flow to the compression chamber is formed in the supported portion, a phase between the suction passage and the suction communication portion changes with the rotation of the supported portion, thereby changing a suction side flow resistance, which is a flow resistance of a fluid flowing from the suction passage to the suction communication portion, 2. A compressor comprising: a compressor in which the suction passage and the suction communication portion are in a phase in which the suction side flow resistance increases as the volume of the compression chamber decreases from a maximum volume. (Appendix 9) The compressor according to claim 8, wherein the suction passage and the suction communication portion communicate with each other in a radial direction of the housing. (Appendix 10) 10. The compressor according to claim 8, wherein when the volume of the compression chamber is maximum, the suction passage and the suction communication portion are in a phase that minimizes the suction side flow resistance. (Appendix 11) 11. The compressor according to claim 8, wherein when a flow rate of the fluid sucked into the compression chamber is at a maximum, the suction passage and the suction communication portion are in a phase that maximizes the suction side flow resistance. (Appendix 12) The compression mechanism includes a drive scroll rotatable about the rotation axis; a driven scroll that faces the driving scroll and is rotated by the driving scroll and a driven mechanism around a driven axis while being eccentric with respect to the driving scroll, thereby forming the compression chamber between the driving scroll and the driven scroll, The drive scroll has a drive end plate and a drive scroll that is integral with the drive end plate and protrudes in a spiral shape toward the driven scroll, 12. The compressor according to claim 1, wherein the driven scroll has a driven end plate and a driven scroll body that is integral with the driven end plate and protrudes in a spiral shape toward the driving scroll. (Appendix 13) a housing in which a suction chamber and a suction portion for suctioning fluid from the outside are formed; a drive shaft provided in the suction chamber and rotatable about a rotation axis; a compression mechanism provided in the housing and connected to the drive shaft; a suction communication portion is formed in the drive shaft, the suction communication portion being connected to the suction portion in the direction of the rotation axis and allowing fluid to flow from the suction portion to the suction chamber; The compression mechanism is formed with a compression chamber that compresses a fluid while reducing a volume thereof, and a suction port that draws the fluid from the suction chamber into the compression chamber. A phase between the suction portion and the suction communication portion changes with the rotation of the drive shaft, thereby changing a suction side flow resistance, which is a flow resistance of a fluid flowing from the suction portion to the suction communication portion, 2. A compressor comprising: a compressor in which the suction portion and the suction communication portion are in a phase in which the suction side flow resistance increases as the volume of the compression chamber decreases from a maximum volume. (Appendix 14) The intake portion is formed in the housing eccentrically with respect to the rotation axis, 14. The compressor according to claim 13, wherein the suction communication portion is formed on the drive shaft eccentrically with respect to the rotation axis. (Appendix 15) 15. The compressor according to claim 13, wherein when the volume of the compression chamber is maximum, the suction portion and the suction communication portion are in a phase that minimizes the suction side flow resistance. (Appendix 16) 16. The compressor according to any one of claims 13 to 15, wherein when a flow rate of the fluid sucked into the compression chamber is at a maximum, the suction portion and the suction communication portion are in a phase that maximizes the suction side flow resistance. [Industrial Applicability]

[0230] The present invention can be used in vehicle air conditioners and the like. [Explanation of symbols]

[0231] 6, 301…Housing 8, 83, 335...Discharge chamber 12, 349…Compression chamber 14, 314…Compression mechanism 15...Suction passage 20…Following mechanism 30...Drive scroll 31...Drive end plate 33...Driven scroll 35...First cover body (supported part) 35e…Suction connection hole (suction connection part) 37b, 81b, 88b...Second boss (rotating shaft part) 37d…Discharge connection hole (discharge connection part) 40…Driven scroll 41…Driven end plate 43...Driven spiral body 57...Discharge reed valve (discharge valve) 63…Discharge part 65, 317...Suction chamber 68…Suction port 73, 77...Discharge connection port (discharge section) 81c, 88c...connecting passage (discharge connection part) 305…Drive shaft 309f…Intake port 313d, 912...Suction part 500…Suction connection part O1, O3...rotation axis O2…driven shaft center

Claims

1. a housing having a discharge portion formed therein for discharging the fluid to the outside; a compression mechanism provided within the housing, The compression mechanism is provided with a compression chamber that compresses a fluid while reducing a volume thereof, and is provided with a rotating shaft portion that is rotatably supported about a rotation axis by the housing, a discharge chamber that communicates with the compression chamber and through which the fluid compressed in the compression chamber is discharged is formed in the housing or the compression mechanism; a discharge communication portion that allows the fluid discharged into the discharge chamber to flow to the discharge portion is formed in the rotating shaft portion, a phase between the discharge portion and the discharge communication portion changes with the rotation of the rotating shaft portion, thereby changing a discharge-side flow resistance, which is a flow resistance of a fluid flowing from the discharge communication portion to the discharge portion; a discharge portion and a discharge communication portion that are in a phase such that the discharge side flow resistance increases as a flow rate of the fluid discharged from the compression chamber to the discharge chamber approaches a maximum;

2. The compressor according to claim 1 , wherein the discharge portion and the discharge communication portion communicate with each other in a radial direction of the housing.

3. The compressor according to claim 1 , wherein the discharge portion and the discharge communication portion communicate with each other in the direction of the rotation axis.

4. The discharge portion is formed in the housing so as to be eccentric with respect to the rotation axis, The compressor according to claim 3 , wherein the discharge communication portion is formed on the rotary shaft portion so as to be eccentric with respect to the rotary shaft center.

5. 4. The compressor according to claim 1, wherein when a flow rate of the fluid 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 that minimizes the discharge side flow resistance.

6. 4. The compressor according to claim 1, wherein when a flow rate of the fluid 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 that maximizes the discharge side flow resistance.

7. the compression mechanism is provided with a discharge valve that allows fluid to be discharged from the compression chamber to the discharge chamber while preventing fluid from flowing from the discharge chamber to the compression chamber, 4. The compressor according to claim 1, wherein the discharge communication portion is located downstream of the discharge valve in a flow direction of the fluid.

8. a housing having a suction port for suctioning fluid from the outside, a suction chamber communicating with the suction port, and a suction passage communicating with the suction chamber; a compression mechanism provided within the housing, The compression mechanism includes a compression chamber that compresses a fluid while reducing a volume thereof, and a supported portion that is supported rotatably about a rotation axis of the housing. a suction communication portion that allows fluid in the suction passage to flow to the compression chamber is formed in the supported portion, a phase between the suction passage and the suction communication portion changes with the rotation of the supported portion, thereby changing a suction side flow resistance, which is a flow resistance of a fluid flowing from the suction passage to the suction communication portion, 2. A compressor comprising: a compressor in which the suction passage and the suction communication portion are in a phase in which the suction side flow resistance increases as the volume of the compression chamber decreases from a maximum volume.

9. 9. The compressor according to claim 8, wherein the suction passage and the suction communication portion communicate with each other in a radial direction of the housing.

10. 10. The compressor according to claim 8, wherein when the volume of the compression chamber is at a maximum, the suction passage and the suction communication portion are in a phase that minimizes the flow resistance on the suction side.

11. 10. The compressor according to claim 8, wherein when a flow rate of the fluid sucked into the compression chamber is at a maximum, the suction passage and the suction communication portion are in a phase that maximizes the suction side flow resistance.

12. The compression mechanism includes a drive scroll rotatable about the rotation axis; a driven scroll that faces the driving scroll and is rotated by the driving scroll and a driven mechanism around a driven axis while being eccentric with respect to the driving scroll, thereby forming the compression chamber between the driving scroll and the driven scroll, The drive scroll has a drive end plate and a drive scroll that is integral with the drive end plate and protrudes in a spiral shape toward the driven scroll, 9. The compressor according to claim 1, wherein the driven scroll includes a driven end plate and a driven scroll that is integral with the driven end plate and protrudes in a spiral shape toward the driving scroll.

13. a housing in which a suction chamber and a suction portion for suctioning fluid from the outside are formed; a drive shaft provided in the suction chamber and rotatable about a rotation axis; a compression mechanism provided in the housing and connected to the drive shaft; a suction communication portion is formed in the drive shaft, the suction communication portion being connected to the suction portion in the direction of the rotation axis and allowing fluid to flow from the suction portion to the suction chamber; The compression mechanism is formed with a compression chamber that compresses a fluid while reducing a volume thereof, and a suction port that draws the fluid from the suction chamber into the compression chamber. A phase between the suction portion and the suction communication portion changes with the rotation of the drive shaft, thereby changing a suction side flow resistance, which is a flow resistance of a fluid flowing from the suction portion to the suction communication portion, 2. A compressor comprising: a compressor in which the suction portion and the suction communication portion are in a phase in which the suction side flow resistance increases as the volume of the compression chamber decreases from a maximum volume.

14. The intake portion is formed in the housing eccentrically with respect to the rotation axis, The compressor according to claim 13, wherein the suction communication portion is formed on the drive shaft eccentrically with respect to the rotation axis.

15. 15. The compressor according to claim 13, wherein when the volume of the compression chamber is maximum, the suction portion and the suction communication portion are in a phase that minimizes the suction side flow resistance.

16. 15. The compressor according to claim 13, wherein when a flow rate of the fluid sucked into the compression chamber is at a maximum, the suction portion and the suction communication portion are in a phase that maximizes the suction side flow resistance.

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