Compressor

Abstract

This compressor according to the present invention comprises a housing (6) and a compression mechanism (14). A discharge part (63) is formed in the housing (6). A compression chamber (12) is formed and a second boss (37b) is provided in the compression mechanism (14). A discharge communication hole (37d) is formed in the second boss (37b). In this compressor, the discharge-side flow resistance changes as the phases of the discharge part (63) and the discharge communication hole (37d) change accompanying the rotation of the second boss (37b). The discharge part (63) and the discharge communication hole (37d) have phases in which the discharge-side flow resistance increases as the flow rate of a fluid discharged from the compression chamber (12) to a discharge chamber (8) approaches the maximum.

Description

Compressor

[0001] The present invention relates to a compressor.

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

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

[0004] The driven scroll faces the driving scroll. The driven scroll is rotated eccentrically relative 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 that is integral with the driven end plate and protrudes spirally toward the driving scroll. A discharge chamber is formed in the driven scroll. The discharge chamber is in communication with the compression chamber and the discharge section.

[0005] In this compressor, fluid is drawn into the suction chamber from outside the housing through the suction port. In this compression mechanism, the volume of the compression chamber changes with the rotation of the drive 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 then discharged from the compression chamber to the discharge chamber and then discharged to the outside of the housing through the discharge port.

[0006] Japanese Patent Application Laid-Open No. 2002-310073

[0007] This type of compressor is required to reduce noise caused by discharge pulsation and suction pulsation during operation. To address this issue, it is conceivable to reduce discharge pulsation by increasing the volume of the discharge chamber in the conventional compressor and enhancing the muffler effect of the discharge chamber. However, this approach requires a larger compression mechanism due to the increased volume of the discharge chamber. This results in an increased size of the housing and, ultimately, the compressor. The same applies when the volume of the suction chamber is increased to reduce suction pulsation; the increased size of the housing results in an increased size of the compressor.

[0008] The present invention has been made in view of the above-described conventional circumstances, and an object to be achieved is to provide a compressor that can be kept small while achieving high quietness.

[0009] A first compressor of the present invention comprises a housing formed with a discharge portion that discharges fluid to the outside, and a compression mechanism provided within the housing, wherein the compression mechanism is formed with a compression chamber that compresses the fluid while reducing its volume, and is provided with a rotating shaft portion that is rotatably supported by the housing about a rotation axis, wherein the housing or the compression mechanism is formed with a discharge chamber that communicates with the compression chamber and from which the fluid compressed in the compression chamber is discharged, and the rotating shaft portion is formed with a discharge communication portion that circulates the fluid discharged into the discharge chamber to the discharge portion, and wherein a phase between the discharge portion and the discharge communication portion changes with rotation of the rotating shaft portion, thereby changing a discharge-side flow resistance that is the flow resistance of the fluid flowing from the discharge communication portion to the discharge portion, and wherein the discharge portion and the discharge communication portion are in a phase such that 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 portion is formed on the rotating shaft portion of the compression mechanism, and this discharge communication portion allows fluid discharged to the discharge chamber to flow to the discharge portion. As a result, in this compressor, fluid compressed in the compression chamber and discharged to the discharge chamber reaches the discharge portion through the discharge communication portion. Also, in this compressor, the phase between the discharge portion and the discharge communication portion changes as the rotating shaft portion rotates. Furthermore, the change in phase between the discharge portion and the discharge communication portion changes the discharge-side flow resistance.

[0011] 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 enter a phase in which the discharge-side flow resistance increases as the flow rate of 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 fluid is discharged from the compression chamber to the discharge chamber. As a result, this compressor can reduce 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 achieve high quietness while suppressing an increase in size.

[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, which makes it possible to reduce the size of the housing, and therefore the entire compressor, in the direction of the rotation axis of the rotating shaft.

[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, which makes it possible to reduce the size of the housing, and therefore the entire compressor, 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, thereby allowing the phase of the discharge portion and the discharge communication portion to 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, thereby more effectively reducing the discharge pulsation. Note that the "minimum flow rate of fluid discharged from the compression chamber to the discharge chamber" 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 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 fluid to be discharged from the compression chamber to the discharge chamber but prevents 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, it is possible to effectively prevent pulsation caused by the fluid flowing from the discharge chamber to the compression chamber.Furthermore, the flow of fluid from the discharge communication portion to the discharge passage assists in opening the discharge valve.

[0022] A second compressor of the present invention comprises a housing having a suction connection port for drawing in fluid from the outside, a suction chamber communicating with the suction connection port, and a suction passage communicating with the suction chamber; and a compression mechanism provided within the housing, wherein the compression mechanism has a compression chamber formed therein that compresses the fluid while reducing its volume, and is provided with a supported part that is rotatably supported by the housing about a rotation axis, and the supported part has a suction connection part that allows fluid in the suction passage to flow into the compression chamber, and the phase of the suction passage and the suction connection part changes with the rotation of the supported part, thereby changing the suction side flow resistance, which is the flow resistance of the fluid flowing from the suction passage to the suction connection part, and the suction passage and the suction connection part are in a phase where the suction side flow resistance increases as the volume of the compression chamber decreases from a maximum.

[0023] In a second compressor of the present invention, a suction communication portion is formed in a supported portion of the compression mechanism, and this suction communication portion allows fluid in a suction passage to flow to the compression chamber. As a result, in this compressor, 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 portion. Furthermore, because the suction communication portion is formed in the supported portion, the phase of the suction communication portion relative to the suction passage changes as the supported portion rotates. Furthermore, the change in phase between the suction passage and the suction communication portion 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 connecting portion. The magnitude of this pulsation changes as the suction-side flow resistance changes. In this compressor, the suction passage and the suction connecting portion enter a phase in which 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 drawn into the compression chamber. As a result, this compressor can reduce suction pulsation.

[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 achieve high quietness while suppressing an increase in size.

[0027] In the second compressor of the present invention, the suction passage and the suction communication section are preferably connected in the radial direction of the housing, which allows the housing, and therefore the entire compressor, to be made smaller in size in the direction of the rotational axis of the rotating shaft.

[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 drawn 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 include a drive scroll rotatable about a rotation axis, and a driven scroll facing the drive scroll and rotating eccentrically with respect to the drive scroll about a driven axis by the drive scroll and driven mechanism to form a compression chamber between the drive scroll and the driven scroll. The drive scroll may include a drive end plate and a drive spiral body integral with the drive end plate and protruding in a spiral shape toward the driven scroll. The driven scroll preferably includes a driven end plate and a driven spiral body integral with the driven end plate and protruding 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 comprises a housing having a suction chamber and a suction portion that draws in fluid from the outside; a drive shaft provided within the suction chamber and rotatable about a rotational axis; and a compression mechanism provided within the housing and connected to the drive shaft, wherein the drive shaft is formed with a suction connection portion that communicates with the suction portion in the direction of the rotational axis and that flows fluid from the suction portion to the suction chamber, and the compression mechanism is formed with a compression chamber that compresses the fluid while reducing its volume, and a suction port that draws fluid from the suction chamber into the compression chamber, and the phase of the suction portion and the suction connection portion changes as the drive shaft rotates, thereby changing the suction side flow resistance that is the flow resistance of the fluid flowing from the suction portion to the suction connection portion, and the suction portion 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 a maximum.

[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 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 rotational axis, and the suction communication portion is preferably formed in the drive shaft eccentrically with respect to the rotational axis, in which case the phase of the suction portion and the suction communication portion can be suitably changed.

[0037] In the third compressor, when the volume of the compression chamber is at a maximum, the suction section and the suction communication section 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 drawn 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.

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

[0041] FIG. 1 is a cross-sectional view of a compressor according to a first embodiment. 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. FIG. 3 is an enlarged cross-sectional view of a main portion of the compressor according to the first embodiment, showing a discharge communication portion, a second insertion hole, a discharge passage, and the like. FIG. 4 is a graph showing a relationship between a change in the rotational phase of the first scroll and the second scroll and a change in the volume of the compression chamber according to the compressor according to the first embodiment. FIG. 5 is a graph showing a relationship between a change in the rotational phase of the first scroll and the second scroll and a change in pressure in the compression chamber according to the compressor according to the first embodiment. FIG. 6 is a cross-sectional view of the compressor according to the first embodiment, taken along the line A-A in FIG. 1 when the rotational phase of the first scroll and the second scroll is in phase X1. FIG. 7 is an enlarged cross-sectional view of the compressor according to the first embodiment, taken along the line B-B in FIG. 1 when the rotational phase of the first scroll and the second scroll is in phase X1. FIG. 8 is a cross-sectional view of the compressor of the first embodiment, taken along line A-A in FIG. 1 , when the rotational phase of the first scroll and the second scroll is phase X2. FIG. 9 is an enlarged cross-sectional view of the compressor of the first embodiment, taken along line B-B in FIG. 1 , when the rotational phase of the first scroll and the second scroll is phase X2. FIG. 10 is a cross-sectional view of the compressor of the first embodiment, taken along line A-A in FIG. 1 , when the rotational phase of the first scroll and the second scroll is phase X3. FIG. 11 is an enlarged cross-sectional view of the compressor of the first embodiment, taken along line B-B in FIG. 1 , when the rotational phase of the first scroll and the second scroll is phase X3. FIG. 12 is a graph showing the waveform of the suction pulsation and the waveform of the first cancellation pulsation during operation, when the compressor of the first embodiment is in operation. FIG. 13 is a cross-sectional view of the compressor of the first embodiment, taken along line A-A in FIG. 1 , when the rotational phase of the first scroll and the second scroll is phase X4. Fig. 14 is an enlarged cross-sectional view of a main portion of the compressor according to the first embodiment, showing the CC cross section of Fig. 1 when the rotational phase of the first scroll and the second scroll is phase X4. Fig. 15 is a cross-sectional view of the compressor according to the first embodiment, showing the A-A cross section of Fig. 1 when the rotational phase of the first scroll and the second scroll is phase X5. Fig. 16 is an enlarged cross-sectional view of a main portion of the compressor according to the first embodiment, showing the CC cross section of Fig. 1 when the rotational phase of the first scroll and the second scroll is phase X5.FIG. 17 is a graph showing the waveform of the discharge pulsation and the waveform of the second cancel pulsation during operation of the compressor of the first embodiment. FIG. 18 is a cross-sectional view of the compressor of the second embodiment. FIGS. 19A to 19D are schematic diagrams showing changes in the 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 . FIG. 19A shows the phase between the discharge section and the discharge communication section when the rotation angle of the driving scroll is zero degrees. FIG. 19B shows the phase between the discharge section and the discharge communication section when the driving scroll has rotated approximately 90° from the state shown in FIG. 19A. FIG. 19C shows the phase between the discharge section and the discharge communication section when the driving scroll has rotated approximately 90° from the state shown in FIG. 19B. Fig. 19(D) shows the phase of the discharge portion and the discharge communication portion when the driving scroll has rotated approximately 90° from the state shown in Fig. 19(C). Fig. 20 is an enlarged cross-sectional view of a main portion of a compressor according to a third embodiment. Fig. 21 is a cross-sectional view of a compressor according to a fourth embodiment. Fig. 22 is an enlarged cross-sectional view of a main portion of a compressor according to a fifth embodiment.

[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 bi-rotary 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 conditioning system for the vehicle.

[0043] 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-to-rear direction of the compressor is indicated by a solid arrow in Fig. 1. In Fig. 2 and subsequent figures, the front-to-rear direction of the compressor is indicated in accordance with Fig. 1. Note that the front-to-rear direction is an example for convenience of explanation, and the compressor can change its own position as appropriate depending on the vehicle in which it is installed.

[0045] 1, the housing 6 is made up 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 cylindrical member with a bottom and an outer peripheral wall 60a and a rear wall 60b. The outer peripheral wall 60a is cylindrical and has a rotation axis O1 of the rotary shaft portion 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 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 an intake 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 through the first support portion 64 in the direction of the rotational 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 generally cylindrical shape centered on the rotational axis O1.

[0051] A sealing member 150 is provided at the location where the passage body 15a opens into 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 spaced apart in the front-to-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 portion 64, and extends linearly rearward within the first support portion 64. The pin hole 4 does not pass through the first support portion 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] 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 facing rearward and located opposite the front surface 62a, 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] The housing cover 62 is also 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 approximately at 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 rotational axis O1 and extends through the housing cover 62 in the direction of the rotational 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 rotational 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 in 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 portion 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 inside 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, with the rear surface 62b of the housing cover 62 abutting against the front end of the outer peripheral wall 60a of the housing main body 60. Then, a plurality of bolts (not shown) are inserted into the housing cover 62 abutting against the front end of the outer peripheral wall 60a to secure the housing cover 62 to the housing main body 60. In this way, in the housing 6, the housing main body 60 and the housing cover 62 are integrated.

[0062] In addition, the front of the housing body 60 is closed by the housing cover 62, thereby forming a suction chamber 65 within 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 outside 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 through 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 main body 60 and, by extension, the housing 6, by fitting into the inner circumferential surface of the outer circumferential wall 60a.

[0065] The rotor 11 is cylindrical 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 secure the permanent magnets.

[0066] The compression mechanism 14 is provided inside 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 and includes 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 generally 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-to-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 drive end plate 31 is formed with a recess 38 and a discharge port 39. The recess 38 is recessed in a generally cylindrical shape from the front surface 311 toward the rear. The discharge port 39 is formed in the drive end plate 31 at a location within the recess 38 and penetrates the drive end plate 31 in the front-to-rear direction. In the recess 38, a discharge reed valve 57 and a retainer 58 are fixed to the drive end plate 31 with fixing bolts 59. The discharge reed valve 57 is an example of the "discharge valve" of the present invention.

[0070] The discharge reed valve 57 elastically deforms to open, thereby allowing refrigerant gas in the compression chamber 12 to be discharged through the discharge port 39 into the discharge chamber 8. On the other hand, the discharge reed valve 57 elastically closes to prevent refrigerant gas in the compression chamber 12 from being discharged through the discharge port 39 into the discharge chamber 8. The closed discharge reed valve 57 also prevents refrigerant gas in the discharge chamber 8 from circulating through the discharge port 39 into the compression chamber 12. The retainer 58 is capable of adjusting the opening of the discharge reed valve 57. The compression chamber 12 and the discharge chamber 8 will be described in detail later.

[0071] The driving circumferential 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 circumferential wall 32 extends parallel to the rotation axis O1 and the driven axis O2.

[0072] The drive scroll 33 is integral with the drive end plate 31 and disposed inside the drive peripheral wall 32. The drive scroll 33 protrudes from the rear surface 312 of the drive end plate 31 toward the driven scroll 40 in parallel with the drive peripheral wall 32. As shown in FIG. 6 , the drive scroll 33 extends in a spiral shape from the center of the drive end plate 31 toward the outer periphery, with the center of the drive scroll 33 being the center of the drive end plate 31. The outer end of the drive scroll 33 is connected to the drive peripheral wall 32. Note that the electric motor 10 is not shown in FIG. 6 for ease of explanation. The same applies to FIGS. 8, 10, 13, and 15, which will be described later.

[0073] 1, the first cover body 35 has a generally disk-like shape and extends 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 of 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 communication hole 35e. The intake communication hole 35e is an example of the "intake communication portion" in 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] As shown in FIG. 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 decreases 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 Figure 1, the suction communication hole 35e is formed within the first boss 35c. The suction communication hole 35e extends at an angle from the outer radial direction of the first boss 35c toward the inner radial direction 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] Furthermore, 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 Fig. 1 illustrates two of the four rings 22.

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

[0081] As shown in Figure 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 penetrates the second cover body 37, including the second boss 37b, in the direction of the rotational axis O1. As a result, the second boss 37b has a cylindrical shape centered on the rotational axis O1.

[0084] The discharge communication hole 37d extends radially through the second boss 37b while connecting to the connection passage 37c. The discharge communication hole 37d opens to the outer peripheral surface of the second boss 37b, more specifically, to the outer peripheral surface of the second diameter portion 372. In other words, the discharge communication hole 37d is formed in the second boss 37b.

[0085] In the driving scroll 30, the cover body 37a of the second cover body 37 abuts against the front surface 311 of the driving end plate 31, and the rear end of the driving peripheral wall 32 abuts against 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, thereby communicating the connecting passage 37c from the front with the recess 38. In this way, in the driving scroll 30, the discharge chamber 8 is formed by the recess 38 and the connecting passage 37c.

[0087] Furthermore, the driving scroll 30 has the driving peripheral wall 32 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 with the rotor 11.

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

[0089] The driven end plate 41 extends in a generally 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] The driven end plate 41 also has a housing 71 formed therein. The housing 71 is recessed in a cylindrical shape from the rear surface 412 of the driven end plate 41 toward the front. A bushing 53 is housed within the housing 71. A driven pin 55 is inserted through the bushing 53. More specifically, the driven pin 55 is inserted through the bushing 53 at a position eccentric to the center of the bushing 53. The driven pin 55 is cylindrical and protrudes rearward from the bushing 53, and hence from the driven end plate 41, toward the first support portion 64. The bushing 53 may be housed within the housing 71 via a bearing such as a plain bearing.

[0091] Four rotation prevention pins 21 are fixed to the rear surface 412. Each rotation prevention pin 21 is located on the rear surface 412 at a location that is more outer than the housing portion 71 and faces one of the rings 22. Each rotation prevention pin 21 protrudes rearward from the rear surface 412. Note that two of the four rotation prevention pins 21 are shown in FIG. 1 .

[0092] The driven scroll 43 is integral with the driven end plate 41 and extends parallel to the rotation axis O1 and the driven axis O2 from the front surface 411 of the driven end plate 41 toward the driving scroll 30. As shown in Figure 6, the driven scroll 43 has a center on the central side of the driven end plate 41 as its center and extends in a spiral shape from the center toward the outer periphery.

[0093] 1 is composed of four rotation-preventing pins 21 and four rings 22. The number of rotation-preventing pins 21 and rings 22 can be appropriately designed as long as there are three or more of each.

[0094] In the compression mechanism 14, with the driven scroll 40 housed within the driving scroll 30, the driving scroll 33 of the driving scroll 30 and the driven scroll 43 of the driven scroll 40 are meshed with each other. Furthermore, 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-to-rear direction. Strictly speaking, after the driving scroll 33 and the driven scroll 43 are meshed with each other and the rotation-preventing pins 21 are inserted into each ring 22, the second cover body 37, the drive end plate 31, the drive peripheral wall 32, and the first cover body 35 of the driving scroll 30 are connected by each bolt 50.

[0095] 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 of 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 in place by abutting against a step formed between the first hole portion 351 and the second hole portion 352 due to the difference in inner diameter between the first hole portion 351 and the second hole portion 352. As a result, the first boss 35c, and therefore the first cover body 35, is rotatably supported by the first support portion 64 via the first plain bearing 51. The inner diameter of the second hole portion 352 of the first insertion hole 35d is 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 apart from the first support portion 64 in the radial direction of 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] Since the first cover body 35 is supported by the first support portion 64, the second diameter hole 15c of the suction passage 15 faces the inside of the second hole portion 352. As a result, the second diameter 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] 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. The second plain bearing 52 is held by the second insertion hole 61 while abutting against a step between the third diameter portion 373 and the second diameter portion 372, which is formed by the difference in outer diameter between the third diameter portion 373 and the second diameter portion 372. As a result, the second boss 37b, and therefore the second cover body 37, is rotatably supported by the second support portion 66 via the second plain bearing 52. 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 within the second insertion hole 61.

[0098] 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 spaced apart from the inner circumferential surface of the second insertion hole 61 in the radial direction of the second boss 37b. This prevents contact between the inner circumferential surface of the second insertion hole 61 and the second diameter portion 372. Support of the second boss 37b by the second support portion 66 places the discharge communication hole 37d in a state facing 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. In this compressor, the discharge passage 67 and the discharge communication hole 37d, and consequently the discharge portion 63 and the discharge communication hole 37d, communicate with each other in the radial direction of the housing 6. That is, the discharge communication hole 37 d allows the refrigerant gas discharged into the discharge chamber 8 to flow to the discharge portion 63 .

[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 driving scroll 30 and the driven scroll 40 are assembled in the front-to-rear direction, thereby forming two compression chambers 12 between the driving scroll 30's driving spiral 33 and the driven scroll 40's driven spiral 43, as shown in FIG. 6 . As shown in FIG. 1 , the driving scroll 30 and the driven scroll 40 are assembled in the front-to-rear direction, thereby forming a suction space 30a within the driving 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 operation of the compressor. Each compression chamber 12 and the suction space 30a are separated from the suction chamber 65 by the driving scroll 30 and the driven scroll 40.

[0101] In the compressor configured as described above, as shown by the dashed arrow in Figure 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 driven to rotate about the rotation axis O1 within the suction chamber 65. In other words, the driving scroll 30 and the rotor 11 are driven to rotate together. At this time, in the driven mechanism 20, each rotation-preventing pin 21 slides against the inner circumferential surface of each ring 22, causing the rings 22 to rotate relatively about the center of the rotation-preventing pin 21. In this way, the driven mechanism 20 transmits the torque of the driving scroll 30 to the driven scroll 40.

[0102] As a result, the driven scroll 40 is rotated around the driven axis O2 by the driving scroll 30 and the driven mechanism 20 while being eccentric with respect to the driving scroll 30. 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 other drawings.

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

[0104] In this way, the phase between the driving scroll 30, which is driven to rotate about the rotation axis O1, and the driven scroll 40, which is driven to rotate about the driven axis O2 (hereinafter, the phase between the driving scroll 30 and the driven scroll 40 will be referred to as the rotational phase), changes, thereby changing the volume of each compression chamber 12. As a result, as shown by the dashed arrow in Figure 1, refrigerant gas in the suction chamber 65 is drawn into the passage body 15a, i.e., the suction passage 15, through the first radial hole 15b. Furthermore, refrigerant gas in the passage body 15a is drawn 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 drawn 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 within each compression chamber 12. The refrigerant gas compressed to the discharge pressure within each compression chamber 12 is then discharged from the discharge port 39 into the recess 38, i.e., the discharge chamber 8.

[0106] The refrigerant gas discharged into the discharge chamber 8 flows through the discharge communication hole 37d, the second insertion hole 61, and the discharge passage 67, and is discharged toward the condenser (outside the housing) through 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 due to the suction of refrigerant gas from the suction chamber 65 into each compression chamber 12, and discharge pulsation inevitably occurs due to the discharge of refrigerant gas from each compression chamber 12 to the discharge chamber 8.

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

[0109] As shown in Figure 4, the volume of the compression chamber 12 gradually increases from its minimum state as the rotational phase between the driving scroll 30 and the driven scroll 40 changes. After the volume of the compression chamber 12 reaches its maximum, the volume of the compression chamber 12 gradually decreases as the rotational phase between the driving scroll 30 and the driven scroll 40 changes. Refrigerant is drawn into the compression chamber 12 as the volume of the compression chamber 12 increases from its minimum to its maximum. That is, as described above, refrigerant gas in the suction chamber 65 is drawn 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 rotational 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. As the volume of the compression chamber 12 increases from minimum to maximum, the flow rate of refrigerant drawn into the compression chamber 12 changes, and when the rotational phase between the driving scroll 30 and the driven scroll 40 is phase X1, the flow rate of refrigerant drawn into the compression chamber 12 is maximum. When the rotational 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 maximum, and the volume of the compression chamber 12 has not yet reached maximum.

[0111] In this compressor, the suction communication hole 35e is formed in the first cover body 35. Therefore, as the driving scroll 30 rotates, the suction communication hole 35e faces the second radial bore 15c and rotates around the second radial bore 15c in a rotational direction R1 around the rotation axis O1, as shown in Figures 7, 9, and 11. In other words, as the driving scroll 30 rotates, the phase between the second radial bore 15c and the suction communication hole 35e changes. That is, as the first cover body 35 rotates, the phase between the suction passage 15 and the suction communication hole 35e changes.

[0112] This change in the phase between the second radial hole 15c and the suction communication hole 35e changes the suction-side flow resistance, which is the flow resistance of the refrigerant gas flowing from the second radial hole 15c and, ultimately, from the suction passage 15 to the suction communication hole 35e. Furthermore, this suction-side flow resistance generates a pulsation different from the suction pulsation and discharge pulsation (hereinafter, this pulsation is referred to as "first canceling pulsation"). The magnitude of the first canceling pulsation changes as the suction-side flow resistance changes.

[0113] When the rotational phase of the driving scroll 30 and the driven scroll 40 is phase X1, as shown in FIG. 7 , the suction communication hole 35e is located on a position substantially opposite the second radial hole 15c in the rotational direction R1 across the rotational axis O1. Therefore, as indicated by the dashed arrow in FIG. 7 , when refrigerant gas is drawn into the compression chamber 12, the refrigerant gas travels approximately half a circle from the second radial hole 15c through the second hole portion 352 of the first insertion hole 35d in the rotational direction R1 before flowing through the suction communication hole 35e. As a result, when the phase of the second radial hole 15c and the suction communication hole 35e is as shown in FIG. 7 , i.e., when the rotational phase of the driving scroll 30 and the driven scroll 40 is 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 rotational phase of the driving scroll 30 and the driven scroll 40 is phase X1. As a result, in this compressor, when the flow rate of refrigerant gas sucked into the compression chamber 12 is at a maximum, the second radial hole 15c and the suction communication hole 35e are in a phase that maximizes the suction side flow resistance.

[0114] 4, the rotational phase of 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 prevent the compression chamber 12 from communicating with the suction space 30a. Therefore, when the volume of the compression chamber 12 becomes maximum, refrigerant gas is no longer drawn 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, as shown in Fig. 9, the suction communication hole 35e is located substantially directly opposite the second radial hole 15c. Therefore, as shown by the dashed arrow in Fig. 9, when refrigerant gas is drawn into the compression chamber 12, the refrigerant gas flows from the second radial hole 15c almost directly 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 as 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, and the volume of the compression chamber 12 becomes smaller than the maximum (see FIG. 10). As a result, the refrigerant gas in the compression chamber 12 begins to be compressed as the volume of the compression chamber 12 becomes smaller than the maximum.

[0117] Furthermore, when the rotational 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 begin to shift in the rotational direction R1 from their substantially directly opposed positions. Therefore, as shown by the dashed arrow in FIG. 9 , when refrigerant gas is drawn into the compression chamber 12, it is more difficult for the refrigerant gas to reach the suction communication hole 35e from the second radial hole 15c than when the suction communication hole 35e and the second radial hole 15c are substantially directly opposed. In other words, 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 enter a phase in which 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 change in the phase between the second diameter hole 15c and the suction connection hole 35e changes the suction-side flow resistance, and this change in suction-side flow resistance changes the magnitude of the first canceling pulsation. As shown in Figure 12, in this compressor, the first canceling pulsation has a waveform that is in opposite phase to the waveform of the suction pulsation. As a result, in this compressor, although suction pulsation is unavoidably 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, thereby reducing the suction pulsation.

[0119] 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 closed.

[0120] 5, the rotational phase of the driving scroll 30 and the driven scroll 40 reaches phase X5, which further compresses the refrigerant gas in the compression chamber 12. As a result, the pressure in the compression chamber 12 exceeds the pressure in the discharge chamber 8, opening the discharge reed valve 57. Thus, the refrigerant gas starts to be discharged from the compression chamber 12 to the discharge chamber 8.

[0121] 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 driven to rotate, the discharge communication hole 37d rotates within the second insertion hole 61 in the direction of rotation R1 around the rotation axis O1, as shown in Figures 14 and 16. Therefore, as the driving scroll 30 is driven to rotate, the phase between the discharge passage 67 and the discharge communication hole 37d changes. In other words, the phase between the discharge passage 67 and the discharge communication hole 37d changes as the second boss 37b rotates.

[0122] This change in the phase between the discharge passage 67 and the discharge communication hole 37d changes 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. Furthermore, this discharge-side flow resistance generates a pulsation different from the discharge pulsation, suction pulsation, and first canceling pulsation (hereinafter, this pulsation will be referred to as the "second canceling pulsation"). The magnitude of the second canceling pulsation changes as the discharge-side flow resistance changes.

[0123] When the rotational 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 substantially directly opposite the discharge passage 67. Therefore, as indicated by the dashed arrow in FIG. 14 , refrigerant gas discharged into the discharge chamber 8 can flow almost directly from the discharge communication hole 37d to the discharge passage 67. In other words, when the phase between the discharge passage 67 and the discharge communication hole 37d is as shown in FIG. 14 , 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 discharge-side flow resistance is minimized when the rotational phase between the driving scroll 30 and the driven scroll 40 is phase X4. As described above, when the rotational phase between the driving scroll 30 and the driven scroll 40 is phase X4, the discharge reed valve 57 is closed. Therefore, the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 is minimized to zero. 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 minimum, the discharge passage 67 and the discharge communication hole 37d are in a phase that minimizes the flow resistance on the discharge side.

[0124] Then, as shown in Fig. 5, when the rotational phase of the driving scroll 30 and the driven scroll 40 reaches phase X5, which is greater than phase X4, 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 of the driving scroll 30 and the driven scroll 40 is phase X5, the two compression chambers 12 are integrated together, as shown in Fig. 15.

[0125] When the rotational phase of the driving scroll 30 and the driven scroll 40 is phase X5, as shown in Figure 16, the discharge communication hole 37d is located on the opposite side of the rotational axis O1 in the rotational direction R1 from the discharge passage 67. Therefore, as shown by the dashed arrow in Figure 16, the refrigerant gas in the discharge chamber 8 travels from the discharge communication hole 37d through the second insertion hole 61 approximately halfway around in the rotational direction R1 to flow through the discharge passage 67.

[0126] 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 discharge passage 67 and the discharge communication hole 37d are in a phase that maximizes the discharge-side flow resistance.

[0127] As described above, in this compressor, the discharge passage 67 and the discharge communication hole 37d are displaced in the rotational direction R1 from their substantially opposite positions (see FIG. 14 ), making it difficult for 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. Thus, in this compressor, the discharge passage 67 and the discharge communication hole 37d enter a phase in which the discharge-side flow resistance increases as the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 approaches its maximum. More specifically, in this compressor, as the rotational phase of the driving scroll 30 and the driven scroll 40 approaches the rotational phase in which the flow rate of refrigerant gas discharged to the discharge chamber 8 is maximized, the discharge passage 67 of the discharge section 63 and the discharge communication hole 37d enter a phase in which the discharge-side flow resistance increases.

[0128] As described above, in this compressor, the change in the phase between the discharge passage 67 and the discharge communication hole 37d, and therefore the change in the phase between the discharge portion 63 and the discharge communication hole 37d, changes the discharge-side flow resistance, and the magnitude of the second canceling pulsation changes due to this change in discharge-side flow resistance. As shown in Figure 17, in this compressor, the second canceling pulsation has a waveform that is in opposite phase to the waveform of the discharge pulsation. As a result, in this compressor, although discharge pulsation inevitably occurs due to the discharge of refrigerant gas from each compression chamber 12 to the discharge chamber 8, the second canceling pulsation acts to cancel out the discharge pulsation, thereby reducing the discharge pulsation.

[0129] Thus, in this compressor, suction pulsation can be reduced by changing the suction-side flow resistance, and 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 to reduce 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, to reduce 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, ultimately, the compression mechanism 14.

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

[0131] In particular, in this compressor, the compression mechanism 14 is composed of a driving scroll 30, a driven scroll 40, and a driven mechanism 20, and the compression mechanism 14 is a bi-directional rotation type scroll compression mechanism. An intake 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 intake communication hole 35e and the discharge communication hole 37d can be formed in the driving scroll 30, making it easy to form the intake communication hole 35e and the discharge communication hole 37d.

[0132] Furthermore, since the compression mechanism 14 is a bi-rotating 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, a discharge reed valve 57 is provided on the driving scroll 30. The discharge reed valve 57 allows refrigerant gas to be discharged from each compression chamber 12 to the discharge chamber 8, while prohibiting refrigerant gas from flowing from the discharge chamber 8 to each compression chamber 12. This effectively prevents pulsation caused by backflow of refrigerant gas from the discharge chamber 8 to each compression chamber 12. Furthermore, because 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 refrigerant gas. Therefore, in this compressor, pressure fluctuations occurring when refrigerant gas flows from the discharge communication hole 37d to the discharge passage 67 can assist in opening the discharge reed valve 57. As a result, this compressor allows the discharge reed valve 57 to be opened and closed effectively.

[0134] Furthermore, 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 hole 37d are in communication with each other in the radial direction of the housing 6. Furthermore, the suction passage 15 and the suction communication hole 35e are in communication 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 hole 37d are in communication 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 hole 37d are in communication with each other in the direction of the rotational axis O1, and the suction passage 15 and the suction communication hole 35e are in communication with each other in the direction of the rotational axis O1.

[0135] 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 main body 60. The housing cover 70 is generally disk-shaped and centered on the rotation axis O1. The housing cover 70 has a front surface 70a facing forward, a rear surface 70b facing rearward and located opposite 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 main body 60 in the same manner as the housing cover 62 in the compressor of the first embodiment.

[0137] The housing cover 70 is also formed with a second insertion hole 72 and a discharge communication port 73. 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 rotational axis O1, and extends in the direction of the rotational axis O1 inside the housing cover 70. The rear end of the second insertion hole 72 opens to the rear surface 70b. A second plain bearing 52 is provided within the second insertion hole 72, as in the compressor of the first embodiment.

[0139] The discharge communication port 73 penetrates the housing cover 70 in the direction of the rotational 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 Figures 19(A) to 19(D), the discharge communication port 73 is formed in a cylindrical shape that is eccentric with respect to the rotational axis O1. In other words, the discharge communication port 73 is formed in the housing cover 70 at a position eccentric with respect to the rotational axis O1. The discharge communication port 73 is connected to a condenser (not shown) through piping (not shown).

[0140] As shown in Figure 18, the third cover body 81 has a cover main body 81a and a second boss 81b. The second boss 81b is also an example of the "rotating shaft portion" of the present invention. The cover main body 81a has a configuration similar to that of the cover main body 37a in the compressor of the first embodiment. The second boss 81b is formed integrally with the cover main body 81a and protrudes forward from the center of the cover main body 81a in the directions 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] A connecting passage 81c is formed in the third cover body 81. The connecting passage 81c is an example of a "discharge communication portion" according to the present invention. The connecting passage 81c penetrates the third cover body 81, including the second boss 81b, in the direction of the rotational axis O1. That is, the connecting passage 81c is formed in the second boss 81b. As shown in FIGS. 18 and 19A to 19D, the connecting passage 81c is formed in a cylindrical shape that is eccentric with respect to the rotational axis O1. That is, the connecting passage 81c is formed in the third cover body 81 at a position eccentric with respect to the rotational axis O1. The connecting passage 81c is formed with a smaller diameter than the discharge communication port 73. Note that, for ease of explanation, the discharge communication port 73 and the connecting passage 81c are illustrated in a simplified form in FIG. 19, and the second boss 81b and other components are not illustrated.

[0142] 18 has the same configuration as the recess 38 in the compressor of embodiment 1. That is, the discharge chamber 83 is recessed in a generally cylindrical shape extending rearward from the front surface 311 of the drive end plate 31, and communicates with the discharge port 39. A discharge reed valve 57 and a retainer 58 are fixed in the discharge chamber 83 by fixing bolts 59.

[0143] 18, in this compressor, as in the compressor of the first embodiment, the third cover body 81, the drive end plate 31, the drive peripheral wall 32, and the first cover body 35 are connected by a plurality of bolts 50. As a result, the cover main body 81a of the third cover body 81 covers the discharge chamber 83 of the drive end plate 31 from the front. Thus, the connecting passage 81c communicates with the discharge chamber 83 from the front. The connecting passage 81c is also located downstream of the discharge reed valve 57 in the flow direction of 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 plain bearing 52 within the second insertion hole 72. 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 the same as that of the compressor of the first embodiment, and the same components are designated by the same reference numerals, and detailed description of the configuration will be omitted.

[0145] In this compressor, 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 flows through the connecting passage 81c to the discharge communication port 73 and is discharged toward the condenser.

[0146] 19A to 19D, the discharge communication port 73 and the connecting passage 81c are each eccentric with respect to the rotation axis O1. Therefore, in this compressor, the phase between the discharge communication port 73 and the connecting passage 81c changes while the driving scroll 30 makes one rotation in the rotation direction R1 shown in FIG. 19A to 19D. That is, the phase between the discharge communication port 73 and the connecting passage 81c changes as the second boss 81b rotates.

[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 are in the phase shown in Fig. 19(A). Then, when the driving scroll 30 rotates approximately 90° in the rotation direction R1 from the position shown in Fig. 19(A), the discharge communication port 73 and the connecting passage 81c are in the phase shown in Fig. 19(B). Then, when the driving scroll 30 rotates approximately 90° in the rotation direction R1 from the position shown in Fig. 19(B) (when the driving scroll 30 rotates approximately 180° in the rotation direction R1 from the position shown in Fig. 19(A)), the discharge communication port 73 and the connecting passage 81c are in the phase shown in Fig. 19(C). Then, when the driving scroll 30 rotates approximately 90° in the rotation direction R1 from the position shown in Figure 19(C) (when the driving scroll 30 rotates approximately 270° in the rotation direction R1 from the position shown in Figure 19(A)), the discharge communication port 73 and the connecting passage 81c will be in the phase shown in Figure 19(D).

[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 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, as the communication area between the discharge communication port 73 and the connecting passage 81c increases, the discharge-side flow resistance decreases, and as the communication area between the discharge communication port 73 and the connecting passage 81c decreases, the discharge-side flow resistance increases. Therefore, in this compressor, when the phase of the discharge communication port 73 and the connecting passage 81c is in the state shown in Figure 19A, the communication area between the discharge communication port 73 and the connecting passage 81c is maximized, and the discharge-side flow resistance is minimized. On the other hand, when the phase of the discharge communication port 73 and the connecting passage 81c is in the state shown in Figure 19C, the communication area between the discharge communication port 73 and the connecting passage 81c is minimized, and the discharge-side flow resistance is maximized.

[0150] 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 connecting 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 connecting 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, discharge pulsation inevitably occurs in this compressor 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] Furthermore, in this compressor, the discharge communication port 73 and the connecting passage 81c communicate in the direction of the rotational axis O1, so it is possible to make the entire compressor, including the housing 6, smaller in size in the radial direction than in a configuration in which the discharge communication port 73 and the connecting passage 81c communicate in the radial direction of the housing 6. Other functions of this compressor are similar to those of the compressor of the first embodiment.

[0153] 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 addition, 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. Like the housing cover 70 in the compressor of Example 2, the first main body member 75a has a generally disk-like shape centered on the rotational axis O1. The first main body member 75a has a front surface 751 facing forward, a rear surface 752 facing rearward and located opposite 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 embodiment 1. In this manner, the housing main body 60 and the housing cover 75 are fixed to each other in this compressor as well.

[0156] The first main body member 75a is also 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 rotational axis O1 and extends through the first main body member 75a in the direction of the rotational axis O1. The rear end of the second insertion hole 76 opens to the rear surface 752. The second insertion hole 76 has 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 rotational 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 not shown in detail, the first communication port 77a is formed in a cylindrical shape that is eccentric with respect to the rotational 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 rotational 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 portion of the first holding member 75b. The second communication port 77b penetrates the front portion 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 portion 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 an unrotatable state. Thus, in the housing cover 75, both the first main body member 75a and the first holding member 75b are unrotatable. Furthermore, because the first holding member 75b is accommodated in the second insertion hole 76, the second communication port 77b is located rearward of 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 a discharge communication port 77. In other words, 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 a "discharge portion" in the present invention.

[0160] 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 while housed in the second insertion hole 76. Furthermore, seal rings 79a and 79b are provided on the outer peripheral surface of the first holding member 75b. The seal rings 79a and 79b seal the gap between the outer peripheral surface of the first holding member 75b and the inner peripheral 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. The first holding member 75b may also be formed from synthetic rubber or from a metal or the like that has lower rigidity than the first main body member 75a.

[0161] The fourth cover body 88 has a cover main body 88a and a second boss 88b. The second boss 88b is also an example of the "rotating shaft portion" of the present invention. The cover main body 88a has a configuration similar to that of the cover main body 81a in the compressor of the second embodiment and, by extension, the cover main body 37a in the compressor of the first embodiment. The second boss 88b is integrally formed with the cover main body 88a and protrudes forward from the center of the cover main 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 a "discharge communication portion" according to the present invention. The connection passage 88c penetrates the fourth cover body 88, including the second boss 88b, in the direction of the rotational axis O1. In other words, the connection passage 88c is formed in the second boss 88b. Similar to the connection passage 81c in the compressor of the second embodiment, the connection passage 88c is formed in a cylindrical shape that is eccentric with respect to the rotational axis O1. In other words, the connection passage 88c is formed in the fourth cover body 88 at a position eccentric with respect to the rotational axis O1. The connection passage 88c is also formed with a smaller diameter than the discharge communication port 77.

[0163] Similar to the third cover body 81 in the compressor of the second embodiment, the fourth cover body 88 is connected to the drive end plate 31 by a plurality of bolts 50. This allows a connecting passage 88c to communicate with the discharge chamber 83 from the front. The connecting passage 88c is also 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 within the first holding member 75b and further within the second insertion hole 76 of the first main body member 75a. The discharge communication port 77 and the connection passage 88c communicate with each other in the direction of the rotational 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 connecting 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 connecting passage 88c changes while the driving scroll 30 makes one rotation in the rotation direction R1 (see FIGS. 19B to 19D). That is, the phase between the discharge communication port 77 and the connecting passage 88c changes with the rotation of the second boss 88b. Thus, in this compressor, discharge pulsation can be reduced similarly to the compressor of the second embodiment.

[0166] In this compressor, the driving scroll 30 and the driven scroll 40 inevitably vibrate when compressing refrigerant gas in each compression chamber 12. In this regard, in this compressor, the first retaining 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 retaining member 75b can suppress transmission of vibration of the driving scroll 30 to the first body member 75a via the second boss 88b and the radial ball bearing 78. Therefore, in this compressor, vibration of the housing cover 75 and, ultimately, the housing 6 during operation can be suppressed as much as possible. Other functions of this compressor are similar to those of the compressor of the first embodiment.

[0167] 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 rotational axis O3 of the drive shaft 305. The rotational axis O3 is parallel to the front-to-rear direction. The rear wall 313a and the first peripheral wall 313b give the motor housing 313 a cylindrical shape with a bottom. The rear wall 313a and the first peripheral wall 313b form a suction chamber 317 within the motor housing 313.

[0170] The rear wall 313a is formed with a support recess 313c and a suction portion 313d. The support recess 313c is recessed rearward and faces the suction chamber 317. 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 peripheral 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 perpendicular to each other. The rear end of the second passage 402 communicates with the first passage 401. The front end of the second passage 402 communicates with the interior 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 rotational axis O3. The front wall 315a and the second peripheral wall 315b form the compressor housing 315 in 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 in the front side of the compressor housing 315 and extends radially of the compressor housing 315. The first discharge recess 315d is located in the compressor housing 315 rearward of the oil separation chamber 315c and is recessed toward the oil separation chamber 315c. The discharge passage 315e extends in the direction of the rotation axis O3 and connects the oil separation chamber 315c and the first discharge recess 315d. The discharge communication port 315f connects to 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 tube 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 tube 321. A filter 323 is provided below the separation tube 321 inside the oil separation chamber 315c.

[0177] The fixed block 303 is provided between the motor housing 313 and the compressor housing 315. A plurality of bolts 325 are inserted into the compressor housing 315 to fasten the motor housing 313, the compressor housing 315, and the fixed block 303 together. In this way, the fixed block 303 is sandwiched between the motor housing 313 and the compressor housing 315 and fixed to them. The fixed block 303 is disposed between the electric motor 307 and the compression mechanism 314 within the housing 301. Note that FIG. 21 illustrates only one of the plurality of bolts 25. The method of fastening the motor housing 313, the compressor housing 315, and the fixed block 303 can be designed as appropriate.

[0178] A boss 303a is formed on the fixed block 303, protruding into the suction chamber 317 and toward the electric motor 307. An insertion hole 303b is formed at the tip of the boss 303a. A second radial ball bearing 327 and a seal member 329 are provided inside the boss 303a.

[0179] The fixed block 303 has a plurality of communication passages 355 formed therein and a plurality of rotation-preventing pins 331 fixed thereto. Each communication passage 355 is located outside the boss 303a and passes through the fixed block 303 in the direction of the rotation axis O3. This allows each communication passage 355 to communicate with the suction chamber 317 and the interior of the compressor housing 315. Each rotation-preventing pin 331 is fixed to the fixed block 303 in a state where it protrudes rearward. Note that FIG. 21 shows one communication passage 355 and one rotation-preventing 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 radial passage 502.

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

[0182] The passage 502 opens to the outer peripheral 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 passage 502 communicates with the shaft passage 501.

[0183] 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 with a smaller diameter than the drive shaft 305, and extends forward from the drive shaft 305.

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

[0185] Furthermore, since the drive shaft 305 is disposed within the suction chamber 317, the front portion of the drive shaft 305 and the eccentric pin 505 are inserted through the insertion hole 303b of the fixed block 303 and enter the boss 303a. Within 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 within the suction chamber 317. Furthermore, a seal material 329 seals the gap between the fixed block 303 and the drive shaft 305. Furthermore, the eccentric pin 505 is fitted into a bushing 350 within the boss 303a.

[0186] Furthermore, a balance weight 333 is formed integrally with the drive shaft 305. The balance weight 333 is disposed in 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 on the opposite side of the rotation axis O3 from the eccentric pin 505. The balance weight 333 is located within the suction chamber 317, between the fixed block 303 and the electric motor 307.

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

[0188] The rotor 307b is disposed within the stator 307a. The drive shaft 305 is fixed to the rotor 307b by shrink fitting, thereby integrating the rotor 307b and the drive shaft 305. The rotor 307b rotates within the stator 307a, causing the drive shaft 305 to rotate around the rotation axis O3.

[0189] The compression mechanism 314 includes a fixed scroll 309 and a movable scroll 310. The fixed scroll 309 is disposed within a compressor housing 315 and fixed to the compressor housing 315. The fixed scroll 309 includes 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 disk-shaped. A second discharge recess 309d and a discharge port 309e are formed in the fixed end plate 309a. The second discharge recess 309d is recessed rearward from the front end surface of the fixed end plate 309a. When the fixed scroll 309 is fixed to the compressor housing 315, the second discharge recess 309d faces the first discharge recess 315d. Thus, 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] 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, discharge reed valve 339, and retainer 341 are disposed within 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 rearward. An inlet port 309f is formed in the fixed peripheral wall 309b. The inlet port 309f penetrates the fixed peripheral wall 309b in the radial direction of the fixed scroll 309. As a result, the inlet port 309f opens into the compressor housing 315. The fixed scroll wall 309c is raised from the rear surface of the fixed end plate 309a and is integral with the fixed peripheral wall 309b on the inside thereof.

[0192] 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 at the front surface of the fixed end plate 309a, and the rear end of the oil supply passage 343 opens at the rear surface of the fixed peripheral wall 309b. The oil supply passage 343 communicates with the oil separation chamber 315c via the filter 323. The shape of the oil supply passage 343 can be designed as appropriate.

[0193] The movable scroll 310 is provided in the 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 bushing 350 is rotatably supported on 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 bushing 350 and the eccentric pin 505 at a position eccentric from the rotation axis O3.

[0194] The movable end plate 310a is provided with rings 347, the number of which is the same as the number of rotation-preventing pins 331. Note that Fig. 21 shows only one of the plurality of rings 347.

[0195] Movable spiral wall 310b is raised from the front surface of movable end plate 310a and extends toward fixed end plate 309a. An air supply hole 310d is formed near the center of movable spiral wall 310b. The air supply hole 310d opens at the front end of movable spiral wall 310b and extends through movable spiral wall 310b toward rotation axis O3 to 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 in communication with the suction port 309f and the discharge port 309e, respectively.

[0197] Furthermore, each ring 47 is connected to each rotation-preventing pin 331 by inserting each rotation-preventing pin 331 into each ring 347. These rotation-preventing pins 331 and rings 347 form the rotation-preventing mechanism 316. The number of rotation-preventing pins 331 and rings 347 that make up the rotation-preventing mechanism 316 can be designed as appropriate, 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 elastically deformed. Furthermore, a back pressure chamber 363 is formed within 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 Figure 21, low-temperature, low-pressure refrigerant gas that has passed through the evaporator is drawn from the suction port 313d through the suction connection port 500 into the suction chamber 317. Then, when the electric motor 307 is operated, the rotor 307b rotates together with the drive shaft 305 within 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, allowing it to only revolve around the fixed scroll 309.

[0200] As the movable scroll 310 rotates, refrigerant gas in the suction chamber 317 passes through the communication passage 355 and is drawn into the compression chamber 349 through the suction port 309f. The volume of the compression chamber 349 decreases as the movable scroll 310 rotates, compressing the refrigerant gas therein. The high-pressure refrigerant gas compressed in the compression chamber 349 is discharged through the discharge port 309e into the discharge chamber 335, and then flows from the discharge chamber 335 through the discharge passage 315e to the oil separation chamber 315c. The high-pressure refrigerant gas circulates between the outer circumferential surface of the separation cylinder 321 and the inner circumferential surface of the oil separation chamber 315c, separating the lubricating oil from the gas. The high-pressure refrigerant gas then flows through the separation cylinder 321 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. This lubricating oil then passes through the filter 323 and flows through the oil supply passage 343, and is supplied to the sliding portions between the fixed scroll 309 and the movable scroll 310, the suction chamber 317, and the like.

[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 way, 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 radial passage 502 of the suction communication section 500, and is drawn into the suction chamber 317 through the radial passage 502.

[0204] 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. 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. 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 this changes the suction-side flow resistance, which is the flow resistance of refrigerant gas flowing from the second passage 402 to the axial passage 501.

[0205] Specifically, if the communication area between the second passage 402 and the axial passage 501 is increased, the suction side flow resistance is reduced, and if the communication area between the suction section 313d and the suction connection section 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 drawn from suction port 309f into compression chamber 349 is at a maximum, second passage 402 and axial passage 501 are in a phase that maximizes suction-side flow resistance. 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 the suction chamber 317 in order to reduce suction pulsation, and therefore, it is difficult to increase the size of the 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] 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 Figure 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 radially 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 rotational axis O3. Similar to the motor housing 313 in the compressor of the fourth embodiment, a suction chamber 317 is formed within 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] 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 and faces the suction chamber 317. The support recess 911 is formed in a substantially cylindrical shape centered on the rotation axis O3. The support recess 911 has 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 peripheral 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 its rear end communicates with the first passage 901. Furthermore, the second passage 902 communicates with the interior of the support recess 911 at its front end.

[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 portion of the second holding member 92. The third passage 903 penetrates the rear portion 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 portion 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 an unrotatable state. Thus, in the motor housing 318, both the second main body member 91 and the second holding member 92 are unrotatable. Furthermore, with the second holding member 92b housed in the support recess 911, the third passage 903 is located in front of the second passage 902 and communicates with the second passage 902. In this way, the first passage 901, the second passage 902, and the third passage 903 form a suction section 912.

[0217] A first radial ball bearing 319 is provided inside the second holding member 92. In this way, the second holding member 92 holds the first radial ball bearing 319 while being housed in the support recess 911. Furthermore, seal rings 79c and 79d are provided on the outer peripheral surface of the second holding member 92. The seal rings 79c and 79d seal the gap between the outer peripheral surface of the second holding member 92 and the inner peripheral 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. Furthermore, 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 a metal or the like that has lower rigidity than the second body member 91.

[0218] The rear portion of the drive shaft 305 is inserted into the first radial ball bearing 319. Thus, the rear portion of the drive shaft 305 is rotatably supported by the second holding member 92 and further by the support recess 911 via the first radial ball bearing 319. Furthermore, in the suction communication section 500, the axial passage 501 communicates with the third passage 903 of the suction section 912 in the direction of the rotational axis O3. As a result, in this compressor, the suction section 912 and the suction chamber 317 communicate with each other through the suction communication section 500. The 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 passes through the evaporator and flows sequentially from the first passage 901 to the second passage 902 and the third passage 903 of the suction section 912. Then, it flows from the axial passage 501 to the radial passage 502 of the suction communication section 500, and is drawn into the suction chamber 317 through the radial passage 502 (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 hence the movable scroll 310. Thus, in this compressor, suction pulsation can be reduced, similar to the compressor of the fourth embodiment.

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

[0221] Although the present invention has been described above in accordance with Examples 1 to 5, it goes without saying that the present invention is not limited to the above Examples 1 to 5, and can be appropriately modified and applied within the scope of the spirit of the present invention.

[0222] For example, in the compressors of Examples 1 to 3, both the discharge pulsation and the suction pulsation are reduced, but this is not limiting, and only the discharge pulsation or only the suction pulsation may be reduced.

[0223] In the compressors of Examples 1 to 3, 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 the 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] Furthermore, 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 pass through the second boss 37b.

[0226] Furthermore, in the compressor of Example 1, the second boss 37b is defined as the "rotating shaft" 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 interior of the second boss 37b. The same applies to the compressors of Examples 2 and 3.

[0227] In the compressor of Example 4, the second passage 402 and the axial passage 501 communicate with each other in the direction of the rotational axis O3, so that the suction portion 313d and the suction communication portion 500 communicate with each other in the direction of the rotational axis O3. However, this is not limiting, 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 Example 5.

[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 shape of 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] The present specification also includes the following inventions: (Supplementary Note 1) A compressor comprising: a housing formed with a discharge portion that discharges fluid to the outside; and a compression mechanism provided within the housing, wherein the compression mechanism is formed with a compression chamber that compresses the fluid while reducing its volume, and is provided with a rotating shaft portion that is rotatably supported by the housing about a rotation axis, wherein the housing or the compression mechanism is formed with a discharge chamber that communicates with the compression chamber and from which the fluid compressed in the compression chamber is discharged, wherein the rotating shaft portion is formed with a discharge communication portion that causes the fluid discharged into the discharge chamber to flow to the discharge portion, wherein a phase between the discharge portion and the discharge communication portion changes with rotation of the rotating shaft portion, thereby changing a discharge-side flow resistance that is the flow resistance of the fluid flowing from the discharge communication portion to the discharge portion, and wherein the discharge portion and the discharge communication portion 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. (Supplementary Note 2) The compressor according to Supplementary Note 1, wherein the discharge portion and the discharge communication portion communicate with each other in a radial direction of the housing. (Supplementary Note 3) The compressor according to Supplementary Note 1, wherein the discharge portion and the discharge communication portion communicate with each other in a direction of the rotational axis. (Supplementary Note 4) The compressor according to Supplementary Note 3, wherein the discharge portion is eccentric with respect to the rotational axis, and the discharge communication portion is eccentric with respect to the rotational axis. (Supplementary Note 5) The compressor according to any one of Supplements 1 to 4, wherein, when a flow rate of fluid discharged from the compression chamber to the discharge chamber is minimum, the discharge portion and the discharge communication portion are in a phase that minimizes the discharge-side flow resistance. (Supplementary Note 6) The compressor according to any one of Supplements 1 to 5, wherein, when a flow rate of fluid discharged from the compression chamber to the discharge chamber is maximum, the discharge portion and the discharge communication portion are in a phase that maximizes the discharge-side flow resistance. (Supplementary Note 7) The compressor according to any one of Supplementary Notes 1 to 6, wherein the compression mechanism is provided with a discharge valve that allows fluid to be discharged from the compression chamber to the discharge chamber while prohibiting fluid from flowing from the discharge chamber to the compression chamber, and the discharge communication part is located downstream of the discharge valve in the direction of fluid flow.(Appendix 8) A compressor comprising: a housing having a suction communication port for drawing in fluid from the outside, a suction chamber communicating with the suction communication port, and a suction passage communicating with the suction chamber; and a compression mechanism provided within the housing, wherein the compression mechanism has a compression chamber that compresses the fluid while reducing its volume, and is provided with a supported part that is rotatably supported by the housing about a rotation axis, wherein the supported part has a suction communication part that passes fluid in the suction passage to the compression chamber, wherein a phase between the suction passage and the suction communication part changes with rotation of the supported part, thereby changing a suction-side flow resistance that is a flow resistance of the fluid passing from the suction passage to the suction communication part, and wherein the suction passage and the suction communication part are in a phase such that the suction-side flow resistance increases as the volume of the compression chamber decreases from a maximum. (Appendix 9) The compressor according to Appendices 8, wherein the suction passage and the suction communication part are in communication in a radial direction of the housing. (Supplementary Note 10) The compressor according to Supplementary Note 8 or 9, 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. (Supplementary Note 11) The compressor according to any one of Supplementary Notes 8 to 10, wherein when a flow rate of fluid sucked into the compression chamber is maximum, the suction passage and the suction communication portion are in a phase that maximizes the suction-side flow resistance. (Supplementary Note 12) The compressor according to any one of Supplementary Notes 1 to 11, wherein the compression mechanism includes a drive scroll rotatable about the rotation axis, and a driven scroll facing the drive scroll and rotating eccentrically with respect to the drive scroll about the driven axis by the drive scroll and driven mechanism to form the compression chamber between the drive scroll and the driven scroll, wherein the drive scroll has a drive end plate and a drive spiral body that is integral with the drive end plate and protrudes in a spiral shape toward the driven scroll, and the driven scroll has a driven end plate and a driven spiral body that is integral with the driven end plate and protrudes in a spiral shape toward the drive scroll.(Appendix 13) A compressor comprising: a housing in which a suction chamber and a suction portion that draws in fluid from the outside are formed; a drive shaft that is provided in the suction chamber and rotatable about a rotation axis; and a compression mechanism that is provided in the housing and connected to the drive shaft, wherein the drive shaft is formed with a suction communication portion that communicates with the suction portion in the direction of the rotation axis and that flows fluid from the suction portion to the suction chamber, and the compression mechanism is formed with a compression chamber that compresses fluid while reducing its volume, and a suction port that draws fluid from the suction chamber to the compression chamber, and the phase of the suction portion and the suction communication portion changes as the drive shaft rotates, thereby changing suction-side flow resistance that is the flow resistance of the fluid flowing from the suction portion to the suction communication portion, and 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. (Supplementary Note 14) The compressor according to Supplementary Note 13, wherein the suction section is eccentric with respect to the rotational axis, and the suction communication section is eccentric with respect to the rotational axis. (Supplementary Note 15) The compressor according to Supplementary Note 13 or 14, wherein when the volume of the compression chamber is maximum, the suction section and the suction communication section are in a phase that minimizes the suction-side flow resistance. (Supplementary Note 16) The compressor according to any one of Supplementary Notes 13 to 15, wherein when a flow rate of fluid sucked into the compression chamber is maximum, the suction section and the suction communication section are in a phase that maximizes the suction-side flow resistance.

[0230] The present invention can be used in vehicle air conditioning systems and the like.

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

Claims

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

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

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

4. A compressor according to claim 3, wherein said discharge portion is eccentric with respect to said rotational axis, and said discharge communication portion is eccentric with respect to said rotational axis.

5. A compressor as claimed in any one of claims 1 to 3, wherein when the flow rate of fluid discharged from the compression chamber to the discharge chamber is at a minimum, the discharge section and the discharge communication section are in a phase that minimizes the discharge side flow resistance.

6. A compressor as claimed in any one of claims 1 to 3, wherein when the flow rate of fluid discharged from the compression chamber to the discharge chamber is at a maximum, the discharge section and the discharge communication section are in a phase that maximizes the discharge side flow resistance.

7. A compressor as claimed in any one of claims 1 to 3, wherein the compression mechanism is provided with a discharge valve which allows fluid to be discharged from the compression chamber to the discharge chamber while prohibiting fluid from circulating from the discharge chamber to the compression chamber, and the discharge communication part is located downstream of the discharge valve in the direction of fluid circulation.

8. A compressor comprising: a housing having an intake port for drawing in fluid from the outside, an intake chamber communicating with the intake port, and an intake passage communicating with the intake chamber; and a compression mechanism provided within the housing, wherein the compression mechanism has a compression chamber formed therein that compresses fluid while reducing its volume, and a supported part is provided which is rotatably supported by the housing about a rotation axis, and the supported part is formed with an intake communication part which allows fluid in the intake passage to flow to the compression chamber, and the phase of the intake passage and the intake communication part changes with the rotation of the supported part, thereby changing an intake side flow resistance which is the flow resistance of fluid flowing from the intake passage to the intake communication part, and the intake passage and the intake communication part are in a phase such that the intake side flow resistance increases as the volume of the compression chamber decreases from a maximum value.

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

10. A compressor according to claim 8 or 9, wherein when the volume of said compression chamber is at a maximum, said suction passage and said suction communication portion are in a phase that minimizes said suction side flow resistance.

11. A compressor according to claim 8 or 9, wherein when the flow rate of the fluid sucked into said compression chamber is at a maximum, said suction passage and said suction communication portion are in a phase that maximizes said suction side flow resistance.

12. A compressor as described in claim 1 or 8, wherein the compression mechanism comprises: a driving scroll rotatable about the rotation axis; and a driven scroll which faces the driving scroll and rotates about the driven axis while being eccentric with respect to the driving scroll by the driving scroll and driven mechanism, thereby forming the compression chamber between the driving scroll and the driven scroll; the driving scroll has a driving end plate and a driving scroll body which is integral with the driving end plate and protrudes in a spiral shape toward the driven scroll; and the driven scroll has a driven end plate and a driven scroll body which is integral with the driven end plate and protrudes in a spiral shape toward the driving scroll.

13. A compressor comprising: a housing having a suction chamber and a suction section for drawing in fluid from the outside; a drive shaft provided within the suction chamber and rotatable about a rotational axis; and a compression mechanism provided within the housing and connected to the drive shaft, wherein the drive shaft is formed with a suction connection section that communicates with the suction section in the direction of the rotational axis and allows fluid to flow from the suction section to the suction chamber, the compression mechanism is formed with a compression chamber that compresses fluid while reducing its volume, and a suction port that draws fluid from the suction chamber to the compression chamber, wherein a phase between the suction section and the suction connection section changes with the rotation of the drive shaft, thereby changing a suction side flow resistance that is the flow resistance of the fluid flowing from the suction section to the suction connection section, and wherein the suction section and the suction connection section are in a phase such that the suction side flow resistance increases as the volume of the compression chamber decreases from a maximum.

14. A compressor according to claim 13, wherein said suction portion is eccentric with respect to said rotational axis, and said suction communication portion is eccentric with respect to said rotational axis.

15. A compressor according to claim 13 or 14, wherein when the volume of said compression chamber is at a maximum, said suction portion and said suction communication portion are in a phase that minimizes said suction side flow resistance.

16. A compressor according to claim 13 or 14, wherein when the flow rate of the fluid sucked into said compression chamber is at a maximum, said suction section and said suction communication section are in a phase that maximizes said suction side flow resistance.

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